Heat exchanger and refrigeration cycle device provided with same

Abstract

This heat exchanger is provided with: a plurality of flat heat transfer tubes, which each have a cross-section formed in a flat shape, which have a plurality of flow paths formed of through-holes and are disposed upright in the vertical direction, and are arranged side by side at intervals in a direction orthogonal to the airflow direction; and a corrugated fin which is disposed between the plurality of flat heat transfer tubes. The corrugated fin has a configuration in which plate-like fin parts are continuous in wave shapes in the tube-axis direction of the plurality of flat heat transfer tubes. The fin parts are provided with: a plurality of louver groups comprising a plurality of louvers having louver slits that extend in a tube-arrangement direction which is a direction in which the plurality of flat heat transfer tubes are arranged side by side, and having plate parts inclined to flat plate portions of the fin parts; and drainage slits that are formed in between the plurality of louver groups and extending in the tube-arrangement direction, and that cause water on upper surfaces of the fin parts to drop and drain therethrough. When defining the width of each of the fin parts in the airflow direction as L, the pitch of each of the plate parts as Rp, and the inclination angle of the plate parts with respect to the flat plate portions in the inclination direction as α, 18°≤α≤30° and 0.042≤(Rp / L)≤0.10 are satisfied.

Description

Heat exchanger and refrigeration cycle device equipped with the same

[0001] The present disclosure relates to a heat exchanger having corrugated fins and a refrigeration cycle device including the same.

[0002] For example, corrugated fin tube heat exchangers, which are constructed by alternately stacking flat heat transfer tubes and corrugated fins, are widely used. When such heat exchangers are used as evaporators, the surface temperature of the corrugated fins can drop below freezing, causing condensation on the fin surfaces to freeze. The frozen condensation on the fin surfaces creates resistance to air passing through the heat exchanger, reducing the heat transfer performance of the corrugated fins. To address this issue, some heat exchangers have drainage slits between louver groups, which are formed to improve heat exchange efficiency and allow water to drain from the fin surfaces (see, for example, Patent Document 1). Condensed water refers to water that condenses from the air and adheres to the surface of the heat exchanger.

[0003] Japanese Utility Model Application Publication No. 56-78966

[0004] In the heat exchanger of Patent Document 1, condensation water on the fin surface flows into the drainage slits and is discharged from the drainage slits, but when the condensation water passes through the louvers on its way to the drainage slits, it can cause a meandering flow, which deteriorates drainage. Therefore, the heat exchanger of Patent Document 1 has room for improvement in terms of drainage performance.

[0005] In order to solve the above-mentioned problems, an object of the present disclosure is to provide a heat exchanger capable of improving drainage performance and a refrigeration cycle apparatus including the same.

[0006] The heat exchanger according to the present disclosure is a heat exchanger including a plurality of flat heat transfer tubes, each having a flat cross section, each having a plurality of flow paths formed by through holes, and arranged vertically and parallel to each other at intervals in a direction perpendicular to an air flow direction, and corrugated fins arranged between the plurality of flat heat transfer tubes, wherein the corrugated fins have a configuration in which plate-like fin portions are arranged in a wave-like manner in the tube axial direction of the plurality of flat heat transfer tubes, and the fin portions are arranged in a louvers extending in the tube juxtaposition direction, which is the direction in which the plurality of flat heat transfer tubes are arranged parallel to each other. The fin section has a plurality of louver groups each consisting of a plurality of louvers, each having a slit and a plate portion inclined relative to the flat plate portion of the fin section, and drainage slits formed between the plurality of louver groups and extending in the pipe arrangement direction, for allowing water on the upper surface of the fin section to fall and be drained. When the width of the fin section in the air flow direction is defined as L, the pitch of the plate portions is defined as Rp, and the angle of inclination of the plate portions relative to the flat plate portion is defined as α, the fin section satisfies 18°≦α≦30° and 0.042≦(Rp / L)≦0.10.

[0007] A refrigeration cycle device according to the present disclosure includes the above-described heat exchanger.

[0008] According to the heat exchanger and refrigeration cycle device equipped with the same disclosed herein, condensation water flows down between the louvers without meandering, improving water conductivity to the drainage slits and thereby improving drainage performance.

[0009] 1 is a diagram illustrating the configuration of a heat exchanger according to embodiment 1. FIG. 2 is a schematic perspective view of a portion of the heat exchanger according to embodiment 1. FIG. 3 is a schematic view of the A1-A1 cross section of the corrugated fin shown in FIG. 3, viewed in the direction of the arrows. FIG. 4 is a diagram illustrating the relationship between the amount of condensation water and water conductivity in the heat exchanger according to embodiment 1. FIG. 5 is a diagram illustrating the relationship between the louver angle and water conductivity in the heat exchanger according to embodiment 1. FIG. 6 is a diagram illustrating the relationship between the louver pitch and water conductivity in the heat exchanger according to embodiment 1. FIG. 7 is a diagram illustrating the relationship between the louver pitch and the overall fin width at each louver angle in the heat exchanger according to embodiment 1, and drainage performance. FIG. 8 is a diagram illustrating the configuration of a heat exchanger according to embodiment 2. FIG. 9 is a diagram illustrating the relationship between the height and drainage performance of the heat exchanger according to embodiment 2. FIG. 10 is a front view of the fin portion of the heat exchanger according to embodiment 3, illustrating the minimum and maximum distances between vertically adjacent louvers. FIG. 11 is a diagram illustrating the relationship between the minimum and maximum distances between vertically adjacent louvers in the heat exchanger according to embodiment 3, and drainage performance. FIG. 12 is a schematic plan view of a heat exchanger according to embodiment 4. 13 is a schematic view of the A2-A2 cross section of the corrugated fin shown in FIG. 13 , viewed in the direction of the arrows. FIG. 14 is a schematic plan view of a heat exchanger according to embodiment 5. FIG. 15 is a schematic view of the A3-A3 cross section of the corrugated fin shown in FIG. 15 , viewed in the direction of the arrows. FIG. 16 is a schematic plan view of a heat exchanger according to embodiment 6. FIG. 17 is a schematic view of the A4-A4 cross section of the corrugated fin shown in FIG. 17 , viewed in the direction of the arrows. FIG. 18 is a schematic plan view of a heat exchanger according to embodiment 7. FIG. 19 is a schematic view of the A5-A5 cross section of the corrugated fin shown in FIG. 19 , viewed in the direction of the arrows. FIG. 20 is a schematic plan view of a heat exchanger according to embodiment 8. FIG. 21 is a schematic view of the A6-A6 cross section of the corrugated fin shown in FIG. 21 , viewed in the direction of the arrows. FIG. 22 is a schematic plan view of a heat exchanger according to embodiment 9. FIG. 23 is a diagram showing the configuration of an air conditioning apparatus according to embodiment 10.

[0010] A heat exchanger and a refrigeration cycle apparatus including the same according to an embodiment will be described below with reference to the accompanying drawings. In the following drawings, components with the same reference numerals are identical or equivalent and will be common throughout the following embodiments. The configurations of components shown throughout the specification are merely illustrative and are not limited to those described in the specification. In particular, the combinations of components are not limited to those in each embodiment, and components described in other embodiments may be applied to other embodiments. In the following description, the upper side in the drawings will be referred to as the "upper side" and the lower side as the "lower side." Furthermore, for ease of understanding, directional terms (e.g., "right," "left," etc.) will be used as appropriate, but these terms are for illustrative purposes only and do not limit the present disclosure. Furthermore, the levels of humidity and temperature are not determined in relation to absolute values, but are determined relatively based on the state and operation of the device, etc. The relative sizes of components in the drawings may differ from those in reality.

[0011] Embodiment 1. Figure 1 is a diagram illustrating the configuration of a heat exchanger 10 according to embodiment 1. As shown in Figure 1, the heat exchanger 10 according to embodiment 1 is a parallel piping type corrugated fin tube heat exchanger. The heat exchanger 10 has a plurality of flat heat transfer tubes 1, a plurality of corrugated fins 2, and a pair of headers 3.

[0012] The pair of headers 3 are each connected to other devices that make up the refrigeration cycle apparatus, and are pipes through which a refrigerant, a fluid that serves as a heat exchange medium, flows in and out and through which the refrigerant branches or merges. The pair of headers 3 includes a header 3A and a header 3B. The headers 3A and 3B are arranged vertically with a gap between them. When the heat exchanger 10 is used as an evaporator, liquid refrigerant passes through the upper header 3B, and gaseous refrigerant passes through the lower header 3A. When the heat exchanger 10 is used as a condenser, gaseous refrigerant passes through the upper header 3B, and liquid refrigerant passes through the lower header 3A.

[0013] A plurality of flat heat transfer tubes 1 are arranged between the pair of headers 3, perpendicular to each header 3, and parallel to one another. The plurality of flat heat transfer tubes 1 are arranged side by side at equal intervals in a direction perpendicular to the air flow direction. Hereinafter, the direction in which the flat heat transfer tubes 1 are arranged side by side (the left-right direction in FIG. 1 ) will be referred to as the "pipe arrangement direction," and the axial direction of the flat heat transfer tubes 1 (the up-down direction in FIG. 1 ) will be referred to as the "pipe axial direction."

[0014] The flat heat transfer tube 1 has a flat cross section. The flat heat transfer tube 1 is a heat transfer tube in which the outer surface on the long side of the flat cross section (hereinafter referred to as the flat surface) is flat and the outer surface on the short side of the flat shape is curved. The flat heat transfer tube 1 is a multi-hole flat heat transfer tube having a plurality of refrigerant flow paths formed by through holes inside the tube. Each flat heat transfer tube 1 is arranged upright, and the through holes of the flat heat transfer tube 1 extend in the vertical direction and communicate with a pair of headers 3. The flat heat transfer tube 1 is arranged so that the long side of the flat cross section is aligned with the air flow direction. Each flat heat transfer tube 1 is joined to a pair of headers 3 by inserting both ends of the flat heat transfer tube 1 into insertion holes (not shown) formed in each of the pair of headers 3 and brazing them. A brazing filler metal containing aluminum, for example, is used for brazing.

[0015] When the heat exchanger 10 is used as an evaporator, a low-temperature, low-pressure refrigerant flows through the refrigerant flow paths in the flat heat transfer tubes 1. When the heat exchanger 10 is used as a condenser, a high-temperature, high-pressure refrigerant flows through the refrigerant flow paths in the flat heat transfer tubes 1. The solid arrows in Figure 1 indicate the refrigerant flow when the heat exchanger 10 is used as an evaporator.

[0016] The first embodiment describes the drainage of condensation water that forms on the fin surfaces when the heat exchanger 10 is used as an evaporator. Therefore, the flow of refrigerant through the heat exchanger 10 when used as an evaporator will be described below. As shown by the solid arrows in FIG. 1 , the refrigerant flows into the header 3A through a pipe (not shown) that supplies refrigerant from an external device (not shown) to the heat exchanger 10. The refrigerant that flows into the header 3A is distributed and passes through each of the flat heat transfer tubes 1. The flat heat transfer tubes 1 exchange heat between the refrigerant passing through the tubes and the outside air, i.e., the ambient air, passing outside the tubes. During this process, the refrigerant absorbs heat from the ambient air while passing through the flat heat transfer tubes 1. The refrigerant that has exchanged heat while passing through each of the flat heat transfer tubes 1 flows into the header 3B and merges within the header 3B. The refrigerant that merges within the header 3B is returned to the external device (not shown) through a pipe (not shown) connected to the header 3B.

[0017] Corrugated fins 2 are arranged between the flat heat transfer tubes 1. The corrugated fins 2 are arranged to increase the heat transfer area between the refrigerant and the outside air. The corrugated fins 2 are formed by corrugating a flat fin material and folding it in a zigzag pattern with repeated mountain and valley folds, forming a corrugated bellows. The folded portions resulting from the unevenness created by the corrugated shape become the peaks 20 of the corrugated shape (see FIG. 2, which will be described later). In the first embodiment, the peaks 20 of the corrugated fins 2 are aligned along the height direction.

[0018] Fig. 2 is a schematic perspective view of a portion of the heat exchanger 10 according to the first embodiment. Fig. 3 is a schematic plan view of the heat exchanger 10 according to the first embodiment. Fig. 4 is a schematic view of the A1-A1 cross section of the corrugated fin 2 shown in Fig. 3, viewed in the direction of the arrows. The outline arrows shown in Figs. 2 to 4 indicate the direction of air flow. The solid arrows shown in Fig. 2 indicate the flow of condensed water 4. The solid arrows shown in Fig. 4 indicate the direction of gravity g.

[0019] As shown in Figures 2 to 4, the corrugated fin 2 is joined to the flat surface 1a of the flat heat transfer tube 1, except for an upstream protruding portion 2a that protrudes upstream of the flat heat transfer tube 1 in the air flow direction. This joint is brazed and joined using a brazing material. The material of the fin material that constitutes the corrugated fin 2 is, for example, an aluminum alloy. The surface of the fin material that constitutes the corrugated fin 2 is clad with a brazing material layer. The main material of the clad brazing material layer is, for example, an aluminum-silicon brazing material containing aluminum. Here, the plate thickness of the fin material that constitutes the corrugated fin 2 is, for example, approximately 50 μm to 200 μm.

[0020] The corrugated fin 2 has a configuration in which plate-shaped fin portions 24 are connected in a wave-like pattern in the tube axial direction. When viewed in the air flow direction, the corrugated fin 2 has a shape in which the fin portions 24 are connected in the tube axial direction with alternating inclinations in opposite directions. The fin portions 24 have flat plate-shaped flat plate portions 21 and curved apex portions 20 at both ends of the flat plate portions 21 in the tube arrangement direction. The corrugated fin 2 is joined to the flat heat transfer tube 1 at the apex portions 20 in surface contact with the flat surfaces 1a of the flat heat transfer tube 1.

[0021] A plurality of louvers 22 are formed on the fin portion 24, aligned in the air flow direction. Each louver 22 has louver slits 22a that allow air to pass through and plate portions 22b that guide air into the louver slits 22a. The plate portions 22b are inclined with respect to the flat plate portion 21. The louver slits 22a and the plate portions 22b are configured in a rectangular shape extending in the pipe arrangement direction. The louvers 22 are formed by cutting and raising the plate portions 22b from the flat plate portion 21.

[0022] The plurality of louvers 22 are divided into a first louver group 22A formed upstream in the air flow direction of drainage slits 23 (described later) formed in the fin portion 24, and a second louver group 22B formed downstream in the air flow direction of the drainage slits 23. The drainage slits 23 are openings for allowing water that accumulates on the upper surface of the fin portion 24, particularly on the nearly horizontal flat plate portion 21, to fall to the lower surface.

[0023] 4, l1 is a virtual center auxiliary line in the thickness direction of the plate portion 22b of the first louver group 22A, and l2 is a virtual center auxiliary line in the thickness direction of the plate portion 22b of the second louver group 22B. As shown in FIG. 4, when the upper and lower surfaces of the flat plate portion 21 are defined based on the direction of gravity g, the plate portions 22b of the first louver group 22A and the plate portions 22b of the second louver group 22B are inclined in directions such that the center auxiliary line l1 and the center auxiliary line l2 intersect on the lower surface side. In other words, the plate portions 22b of the first louver group 22A and the plate portions 22b of the second louver group 22B are inclined in opposite directions relative to the flat plate portion 21. In FIG. 4 , the plate portions 22b of the first louver group 22A are inclined toward the upstream side of the airflow direction (left side in FIG. 4 ), and the plate portions 22b of the second louver group 22B are inclined toward the downstream side of the airflow direction (right side in FIG. 4 ). By forming the plate portions 22b of the louvers 22 in this orientation, condensation water 4 flowing along the plate portions 22b of the louvers 22 formed on a certain fin portion 24 is guided toward the drainage slits 23 of the fin portion 24 below. Therefore, the heat exchanger 10 having this configuration can significantly improve drainage performance. Here, "drainage performance" is defined as the mass of water retained between the fin portions 24 that is drained per unit time. For example, this can be evaluated by submerging the heat exchanger 10 in a water tank and measuring the mass of water drained per unit time when the heat exchanger 10 is removed. Furthermore, "high drainage performance" means that a large mass of water is drained per unit time.

[0024] The fin portion 24 is formed with drainage slits 23 for draining condensation water 4 formed on the fin portion 24. The drainage slits 23 are through-holes formed in the corrugated fin 2. The drainage slits 23 are formed in a rectangular shape extending longitudinally in the pipe arrangement direction, i.e., perpendicular to the air flow direction. The drainage slits 23 are formed in the central portion of the fin portion 24 in the air flow direction, excluding the upstream protrusion 2a. Note that in the first embodiment, an example is shown in which the drainage slits 23 are formed in a single row in the air flow direction, but the number of rows of the drainage slits 23 may be two or more. When multiple rows of the drainage slits 23 are formed, the area of ​​the fin portion 24 between the drainage slits 23 in each row serves as a heat transfer area (not shown). When multiple rows of the drainage slits 23 are formed, the multiple rows of the drainage slits 23 are formed adjacent to each other in the central portion of the fin portion 24 in the air flow direction, excluding the upstream protrusion 2a. "Adjacent" means that there are no louvers 22 between the drainage slits 23.

[0025] The heat transfer areas between the rows of drainage slits 23 are typically flat, similar to the flat plate portion 21. Furthermore, flat areas may also be formed between the drainage slit 23 located most upstream in the air flow direction and the first louver group 22A, and between the drainage slit 23 located most downstream in the air flow direction and the second louver group 22B, similar to the flat plate portion 21. The number of rows of drainage slits 23 is synonymous with the number of drainage slits 23, and hereinafter the number of drainage slits 23 will be referred to using either the expression "number of rows" or "number."

[0026] When the heat exchanger 10 is used as an evaporator, the surface temperatures of the flat heat transfer tubes 1 and the corrugated fins 2 become lower than the temperature of the air passing through the heat exchanger 10. As a result, moisture in the air condenses, forming condensed water 4 on the surfaces of the flat heat transfer tubes 1 and the corrugated fins 2. The condensed water 4 formed on the surfaces of the fin portions 24 of the corrugated fins 2 flows down through the drainage slits 23 to the lower fin portions 24. In this case, in areas of the fin portions 24 where the amount of condensed water 4 is large, the condensed water 4 easily flows over the surfaces of the fin portions 24 and easily flows down through the drainage slits 23. On the other hand, in areas of the fin portions 24 where the amount of condensed water 4 is small, the condensed water 4 does not easily flow over the surfaces of the fin portions 24 and is easily retained and stagnates on the surfaces of the fin portions 24. It has been found that such stagnation occurs even though the fin portions 24 are inclined in the air flow direction.

[0027] Therefore, the multiple louver groups are each provided to face the drainage slits 23, and the plate portions 22b of the first louver group 22A and the plate portions 22b of the second louver group 22B are inclined in opposite directions relative to the flat plate portion 21. In other words, each plate portion 22b is inclined from the upper end to the lower end toward the drainage slits 23. With this configuration, condensation water 4 can be efficiently guided from the multiple louver groups to the drainage slits 23, improving drainage performance.

[0028] As shown in Figure 4, the louver groups are connected continuously from the flat plate portion 21 and have half-plate portions 25 that are inclined downward relative to the flat plate portion 21. The half-plate portions 25 are provided on both sides in the air flow direction. If the pitch of the plate portion 22b, which is the length in the air flow direction, is defined as Rp and the pitch of the half-plate portion 25, which is the length in the air flow direction, is defined as hRp, then hRp > (Rp / 2). This configuration can suppress the meandering flow of condensation water 4 and improve drainage.

[0029] [Relationship between the amount of condensed water and water conductivity] Figure 5 is a diagram illustrating the relationship between the amount of condensed water and water conductivity in the heat exchanger 10 according to embodiment 1. Note that the solid arrows in Figure 5 indicate the flow of condensed water 4. As shown in Figure 5, when the amount of condensed water 4 flowing down between the louvers is small, the condensed water 4 flows in a meandering manner due to the influence of surface tension, resulting in poor water conductivity. On the other hand, when the amount of condensed water 4 flowing down between the louvers is large, the influence of gravity g becomes greater, and the condensed water 4 flows down without being affected by surface tension, resulting in improved water conductivity.

[0030] [Relationship between Louver Angle and Water Conductivity] Figure 6 is a diagram illustrating the relationship between the louver angle and water conductivity of the heat exchanger 10 according to embodiment 1. The solid arrows in Figure 6 indicate the flow of condensation water 4. As shown in Figure 6, when the inclination angle of the plate portion 22b relative to the flat plate portion 21 (hereinafter also referred to as the louver angle) is small, the condensation water 4 flows downward in a meandering manner due to the influence of surface tension, resulting in poor water conductivity. When the louver angle is medium, the influence of gravity g is large, and the condensation water 4 flows downward without meandering, without being affected by surface tension, resulting in good water conductivity. When the louver angle is large, the influence of gravity g is large, and the condensation water 4 flows downward without meandering, without being affected by surface tension, but the water conductivity deteriorates due to a decrease in the horizontal velocity distribution.

[0031] [Relationship between Louver Pitch and Water Conductivity] Figure 7 is a diagram illustrating the relationship between louver pitch and water conductivity of the heat exchanger 10 according to embodiment 1. Note that the solid arrows in Figure 7 indicate the flow of condensation water 4. As shown in Figure 7, when the length of the plate portion 22b in the air flow direction (hereinafter also referred to as the louver pitch) is small, the downward inclined surface is short and the horizontal velocity distribution is small, resulting in poor water conductivity. On the other hand, when the louver pitch is large, the downward inclined surface is long and the horizontal velocity distribution is large, resulting in good water conductivity.

[0032] Figure 8 shows the relationship between louver pitch and fin width and drainage performance for each louver angle of the heat exchanger 10 according to embodiment 1. Note that the drainage performance values ​​shown in Figure 8 are values ​​when the drainage performance of a typical HFT heat exchanger is defined as 100%, and this also applies below. The fin width, which is the width of the fin portion 24 in the air flow direction, is defined as L; the louver pitch, which is the length of the plate portion 22b in the air flow direction, is defined as Rp; and the louver angle, which is the inclination angle of the plate portion 22b relative to the flat plate portion 21, is defined as α. Regarding the inclination angle of the plate portion 22b relative to the flat plate portion 21, when the plate portion 22b is inclined upstream in the air flow direction, this is the angle between the plate portion 22b and the flat plate portion 21 on the upstream side in the air flow direction. When the plate portion 22b is inclined downstream in the air flow direction, this is the angle between the plate portion 22b and the flat plate portion 21 on the downstream side in the air flow direction. As shown in Figure 8, in the heat exchanger 10 according to the first embodiment, when α = 18°, 25°, and 30°, the drainage performance was 80% or more when Rp / L was in the range of 0.042 or more and 0.10 or less. Experimental results have shown that when the drainage performance is 80% or more, the condensation water 4 flows down between the louvers without meandering. In other words, when 18° ≤ α ≤ 30° and 0.042 ≤ (Rp / L) ≤ 0.10 are satisfied, the condensation water 4 flows down without meandering. Therefore, the heat exchanger 10 according to the first embodiment is configured to satisfy 18° ≤ α ≤ 30° and 0.042 ≤ (Rp / L) ≤ 0.10.

[0033] As described above, the heat exchanger 10 according to the first embodiment is a heat exchanger 10 including a plurality of flat heat transfer tubes 1, each having a flat cross section, a plurality of flow paths formed by through holes, and arranged vertically and parallel to each other at intervals in a direction perpendicular to an air flow direction, and corrugated fins 2 arranged between the plurality of flat heat transfer tubes 1, and the corrugated fins 2 have a configuration in which plate-like fin portions 24 are arranged in a wave-like shape in the tube axial direction of the plurality of flat heat transfer tubes 1, and the fin portions 24 are formed as louvers extending in the tube juxtaposition direction, which is the direction in which the plurality of flat heat transfer tubes 1 are arranged parallel to each other. The fin section 24 is provided with a plurality of louver groups each consisting of a plurality of louvers 22 each having a slit 22a and a plate section 22b inclined relative to the flat plate section 21 of the fin section 24, and drainage slits 23 formed between the plurality of louver groups and extending in the pipe arrangement direction, for dropping and draining water on the upper surface of the fin section 24, wherein, when the width of the fin section 24 in the air flow direction is defined as L, the pitch of the plate sections 22b is defined as Rp, and the inclination angle of the inclination direction of the plate sections 22b relative to the flat plate section 21 is defined as α, the fin section 24 satisfies 18°≦α≦30° and 0.042≦(Rp / L)≦0.10.

[0034] According to the heat exchanger 10 of embodiment 1, the condensation water 4 flows down between the louvers without meandering, improving the water conductivity to the drainage slits 23, thereby improving drainage performance.

[0035] In addition, in the heat exchanger 10 according to the first embodiment, the plurality of louver groups are continuously connected to the flat plate portion 21 and have the half plate portion 25 that is inclined relative to the flat plate portion 21 .

[0036] Furthermore, in the heat exchanger 10 according to the first embodiment, when the pitch of the half plate portions 25 is defined as hRp, the condition hRp>(Rp / 2) is satisfied.

[0037] According to the heat exchanger 10 of the first embodiment, it is possible to suppress the meandering flow of the condensed water 4 and improve the drainage performance.

[0038] In addition, in the heat exchanger 10 according to embodiment 1, the multiple louver groups include a first louver group 22A formed upstream of the drainage slits 23 in the air flow direction, and a second louver group 22B formed downstream of the drainage slits 23 in the air flow direction, and the plate portions 22b of the first louver group 22A and the plate portions 22b of the second louver group 22B are inclined in opposite directions relative to the flat plate portion 21, and are inclined from the upper end to the lower end of the plate portion 22b toward the drainage slits 23.

[0039] According to the heat exchanger 10 of the first embodiment, the condensed water 4 can be efficiently guided from the plurality of louver groups to the drainage slits 23, thereby improving drainage performance.

[0040] Second Embodiment A second embodiment will be described below, but explanations of parts that overlap with those of the first embodiment will be omitted, and parts that are the same as or equivalent to those of the first embodiment will be given the same reference numerals.

[0041] FIG. 9 is a diagram illustrating the configuration of a heat exchanger 10 according to a second embodiment. FIG. 10 is a diagram illustrating the relationship between the height and drainage of the heat exchanger 10 according to the second embodiment. As shown in FIG. 9 , the height H of the heat exchanger 10, which is the distance between the lower end of the upper header 3B and the upper end of the lower header 3A, is defined as H. In the heat exchanger 10 according to the second embodiment, as shown in FIG. 10 , drainage is 90% or more when H is 0.42 m or more. Furthermore, drainage of 90% or more can further improve water permeability compared to 80%. Therefore, when the height H of the heat exchanger 10 is 0.42 m or more, which is the heat exchanger height of the outdoor unit of a typical stationary air conditioner, water permeability can be further improved, and drainage can be improved by approximately 10% or more compared to a heat exchanger height of less than 0.42 m for a vehicle.

[0042] As described above, the heat exchanger 10 according to the second embodiment has a pair of headers 3 arranged vertically at a distance from each other, and when the heat exchanger height, which is the length between the lower end of the upper header 3B and the upper end of the lower header 3A, is defined as H, it satisfies H≧0.42 m.

[0043] According to the heat exchanger 10 of the second embodiment, the height H of the heat exchanger 10 is equal to or greater than 0.42 m, which is the height of a heat exchanger in an outdoor unit of a typical stationary air conditioner. This further improves the water conductivity, and improves the drainage performance by approximately 10% or more compared to a heat exchanger for a vehicle with a height of less than 0.42 m.

[0044] Third Embodiment Hereinafter, a third embodiment will be described, but explanations of parts that overlap with those of the first and second embodiments will be omitted, and parts that are the same as or equivalent to those of the first and second embodiments will be denoted by the same reference numerals.

[0045] FIG. 11 is a front view of the fin portion 24 of the heat exchanger 10 according to the third embodiment, illustrating the minimum and maximum distances between vertically adjacent louvers 22. FIG. 12 is a diagram illustrating the relationship between the minimum and maximum distances between vertically adjacent louvers 22 and drainage performance in the heat exchanger 10 according to the third embodiment. As shown in FIG. 11 , the minimum distance between vertically adjacent louvers 22 when the fin portion 24 of the heat exchanger 10 is viewed from the front is defined as ymin, and the maximum distance is defined as ymax. In the heat exchanger 10 according to the third embodiment, as shown in FIG. 12 , drainage performance was 90% or more when ymin / ymax was in the range of 20% to 60%. Thus, by setting ymin / ymax in the range of 20% to 60%, water permeability in the louver-proximate portion 27 shown in FIG. 11 is improved. Furthermore, since drainage performance is 90% or more, water permeability can be further improved compared to 80%. 11, the condensation water 4 formed on the surface of the fin portion 24 flows downward as indicated by the dashed arrows. However, if ymin is too small, the condensation water 4 will bridge in the louver adjacent portion 27, and if ymin is too large, a drainage path for the condensation water 4 to flow downward will not be formed, so ymin should not be too small or too large.

[0046] As described above, the heat exchanger 10 according to embodiment 3 satisfies 20%≦(ymin / ymax)≦60%, where ymin is the shortest distance between adjacent louvers 22 in the vertical direction and ymax is the longest distance between adjacent louvers 22 in the vertical direction.

[0047] According to the heat exchanger 10 of the third embodiment, the drainage efficiency is 90% or more, which is further improved compared to the 80% water permeability.

[0048] Fourth Embodiment A fourth embodiment will be described below, but explanations of parts that overlap with those of the first to third embodiments will be omitted, and parts that are the same as or equivalent to those of the first to third embodiments will be given the same reference numerals.

[0049] FIG. 13 is a schematic plan view of a heat exchanger 10 according to a fourth embodiment. FIG. 14 is a schematic view of the A2-A2 cross section of the corrugated fin 2 shown in FIG. 13 , viewed in the direction of the arrows. The outline arrows in FIGS. 13 and 14 indicate the air flow direction. The solid arrows in FIG. 14 indicate the direction of gravity g. The dashed arrows in FIG. 14 indicate the flow of condensation water 4. As shown in FIGS. 13 and 14 , the heat exchanger 10 according to the fourth embodiment is configured with a single row of flat heat transfer tubes 1, and the fin section 24 extends across and is joined to the single row of flat heat transfer tubes 1. The multiple louver groups include a first louver group 22A formed upstream in the air flow direction and a second louver group 22B formed downstream in the air flow direction. One or multiple drainage slits 23 (one in the fourth embodiment) are formed in the fin section 24 between the first louver group 22A and the second louver group 22B in the air flow direction. Furthermore, the air conditioner has a plurality of units 26 (two in the fourth embodiment) in the air flow direction, each unit consisting of the first louver group 22A, the second louver group 22B, and the drainage slits 23. This configuration allows water to be guided through a plurality of highly efficient water conduction paths, improving drainage. Here, the "highly efficient water conduction path" refers to a water conduction path formed by a plurality of louver groups that is inclined from the upper end to the lower end of the plate portion 22b toward the drainage slits 23 and is configured to satisfy the conditions 18°≦α≦30° and 0.042≦(Rp / L)≦0.10.

[0050] As described above, the heat exchanger 10 according to the fourth embodiment has a plurality of units 26, each of which is made up of the first louver group 22A, the second louver group 22B, and the drainage slits 23, arranged in the air flow direction.

[0051] According to the heat exchanger 10 of the fourth embodiment, water can be guided through a plurality of highly efficient water guide paths, thereby improving the drainage performance.

[0052] Fifth Embodiment Hereinafter, a fifth embodiment will be described, but explanations of parts that overlap with those of the first to fourth embodiments will be omitted, and parts that are the same as or equivalent to those of the first to fourth embodiments will be given the same reference numerals.

[0053] FIG. 15 is a schematic plan view of a heat exchanger 10 according to a fifth embodiment. FIG. 16 is a schematic view of the A3-A3 cross section of the corrugated fin 2 shown in FIG. 15 , viewed in the direction of the arrows. The outline arrows in FIGS. 15 and 16 indicate the air flow direction. The solid arrows in FIG. 16 indicate the direction of gravity g. The dashed arrows in FIG. 16 indicate the flow of condensation water 4. As shown in FIGS. 15 and 16 , the heat exchanger 10 according to the fifth embodiment is configured with multiple rows of flat heat transfer tubes 1 in the air flow direction (two rows in the fifth embodiment), and the fin section 24 extends across and is joined to the multiple rows of flat heat transfer tubes 1. Furthermore, one or multiple drainage slits 23 (one in the fifth embodiment) are formed in the fin section 24 between adjacent flat heat transfer tubes 1 in the air flow direction. The multiple louver groups include a first louver group 22A formed upstream of the drainage slits 23 in the air flow direction and a second louver group 22B formed downstream of the drainage slits 23 in the air flow direction. When the overall fin width (width of the fin portion 24 in the air flow direction) is defined as L, the louver pitch (length of the plate portion 22b in the air flow direction) is defined as Rp, and the louver angle (angle of inclination of the plate portion 22b relative to the flat plate portion 21) is defined as α, the louver angles are configured to satisfy the following: 18°≦α≦30° and 0.042≦(Rp / L)≦0.10. This configuration allows water to be efficiently guided to the drainage paths between the rows, improving drainage performance.

[0054] As described above, in the heat exchanger 10 according to the fifth embodiment, the drainage slits 23 are formed in the fin portions 24 between the flat heat transfer tubes 1 adjacent to each other in the air flow direction.

[0055] In addition, in the heat exchanger 10 according to the fifth embodiment, a plurality of drainage slits 23 are formed in the air flow direction.

[0056] According to the heat exchanger 10 of the fifth embodiment, water can be efficiently guided to the drainage paths between the rows, thereby improving the drainage performance.

[0057] Sixth Embodiment A sixth embodiment will be described below, but explanations of parts that overlap with those of the first to fifth embodiments will be omitted, and parts that are the same as or equivalent to those of the first to fifth embodiments will be given the same reference numerals.

[0058] FIG. 17 is a schematic plan view of a heat exchanger 10 according to a sixth embodiment. FIG. 18 is a schematic view of the A4-A4 cross section of the corrugated fin 2 shown in FIG. 17 , viewed in the direction of the arrows. The outline arrows in FIGS. 17 and 18 indicate the air flow direction. The solid arrows in FIG. 18 indicate the direction of gravity g. The dashed arrows in FIG. 18 indicate the flow of condensation water 4. As shown in FIGS. 17 and 18 , the heat exchanger 10 according to the sixth embodiment is configured with multiple rows (two rows in the sixth embodiment) of flat heat transfer tubes 1 in the air flow direction, and the fin portion 24 extends across and is joined to the multiple rows of flat heat transfer tubes 1. The multiple louver groups include a first louver group 22A formed upstream in the air flow direction and a second louver group 22B formed downstream in the air flow direction. Furthermore, a plurality of drainage slits 23 (two in the sixth embodiment) are formed in the air flow direction in the fin portion 24 between the first louver group 22A and the second louver group 22B. Furthermore, a plurality of units 26 (two in the sixth embodiment) each consisting of the first louver group 22A, the second louver group 22B, and the drainage slits 23 are provided in the air flow direction. With this configuration, water can be efficiently guided to the plurality of drainage slits 23, thereby improving drainage performance.

[0059] As described above, the heat exchanger 10 according to the sixth embodiment has a plurality of units 26, each of which is made up of the first louver group 22A, the second louver group 22B, and the drainage slits 23, arranged in the air flow direction.

[0060] In the heat exchanger 10 according to the sixth embodiment, the unit 26 has a plurality of drainage slits 23 in the air flow direction.

[0061] According to the heat exchanger 10 of the sixth embodiment, water can be efficiently guided to the plurality of drainage slits 23, thereby improving drainage performance.

[0062] Seventh Embodiment Hereinafter, a seventh embodiment will be described, but explanations of parts that overlap with those of the first to sixth embodiments will be omitted, and parts that are the same as or equivalent to those of the first to sixth embodiments will be given the same reference numerals.

[0063] FIG. 19 is a schematic plan view of a heat exchanger 10 according to the seventh embodiment. FIG. 20 is a schematic view of the A5-A5 cross section of the corrugated fin 2 shown in FIG. 19 , viewed in the direction of the arrows. The outline arrows in FIGS. 19 and 20 indicate the air flow direction. The solid arrows in FIG. 20 indicate the direction of gravity g. The dashed arrows in FIG. 20 indicate the flow of condensation water 4. As shown in FIGS. 19 and 20 , the heat exchanger 10 according to the seventh embodiment is configured with multiple rows of flat heat transfer tubes 1 in the air flow direction (two rows in the seventh embodiment), and the fin section 24 extends across and is joined to the multiple rows of flat heat transfer tubes 1. Furthermore, multiple drainage slits 23 (two in the seventh embodiment) are formed in the fin section 24 between adjacent flat heat transfer tubes 1 in the air flow direction. The plurality of louver groups includes a first louver group 22A formed upstream in the air flow direction of the drainage slits 23, and a second louver group 22B formed downstream in the air flow direction of the drainage slits 23. This configuration allows water to be efficiently guided to the plurality of drainage slits 23 between the rows, improving drainage performance.

[0064] As described above, in the heat exchanger 10 according to the seventh embodiment, the drainage slits 23 are formed in the fin portions 24 between the flat heat transfer tubes 1 adjacent to each other in the air flow direction.

[0065] Furthermore, the heat exchanger 10 according to the seventh embodiment has a plurality of drainage slits 23 formed in the air flow direction.

[0066] According to the heat exchanger 10 of the seventh embodiment, water can be efficiently guided to the drainage paths between the rows, thereby improving the drainage performance.

[0067] Eighth Embodiment An eighth embodiment will be described below, but explanations of parts that overlap with those of the first to seventh embodiments will be omitted, and parts that are the same as or equivalent to those of the first to seventh embodiments will be given the same reference numerals.

[0068] FIG. 21 is a schematic plan view of a heat exchanger 10 according to the eighth embodiment. FIG. 22 is a schematic view of the A6-A6 cross section of the corrugated fin 2 shown in FIG. 21 , viewed in the direction of the arrows. The outline arrows in FIGS. 21 and 22 indicate the air flow direction. The solid arrows in FIG. 22 indicate the direction of gravity g. The dashed arrows in FIG. 22 indicate the flow of condensation water 4. As shown in FIGS. 21 and 22 , the heat exchanger 10 according to the eighth embodiment is configured with multiple rows (two rows in the eighth embodiment) of flat heat transfer tubes 1 in the air flow direction, and the fin portion 24 extends across and is joined to the multiple rows of flat heat transfer tubes 1. The multiple louver groups include a first louver group 22A formed upstream in the air flow direction and a second louver group 22B formed downstream in the air flow direction. Furthermore, one or multiple (one in embodiment 8) drainage slits 23A are formed in the air flow direction in the fin portion 24 between the first louver group 22A and the second louver group 22B. Furthermore, multiple (two in embodiment 8) units 26 each consisting of the first louver group 22A, the second louver group 22B, and the drainage slit 23A are formed in the air flow direction. Furthermore, one or multiple (two in embodiment 8) drainage slits 23B are formed in the air flow direction between adjacent units 26 in the air flow direction. This configuration allows water to be guided through multiple highly efficient water conduction paths, improving drainage. Furthermore, the drainage slits 23B have a larger opening area than the drainage slits 23A. This configuration increases the opening area of ​​the drainage slits 23B near the center, where a large amount of water flows down, thereby improving drainage while suppressing a reduction in the heat transfer area.

[0069] As described above, the heat exchanger 10 according to the eighth embodiment has a plurality of units 26, each of which is made up of the first louver group 22A, the second louver group 22B, and the drainage slits 23A, arranged in the air flow direction.

[0070] In the heat exchanger 10 according to the eighth embodiment, the unit 26 has a plurality of drainage slits 23A in the air flow direction.

[0071] In addition, in the heat exchanger 10 according to the eighth embodiment, the drain slits 23B are formed between the adjacent units 26 .

[0072] Furthermore, in the heat exchanger 10 according to the eighth embodiment, a plurality of drainage slits 23B are formed between adjacent units 26 in the air flow direction.

[0073] According to the heat exchanger 10 of the eighth embodiment, water can be guided through a plurality of highly efficient water guide paths, and water drainage can be improved.

[0074] In the heat exchanger 10 according to the eighth embodiment, the drain slits 23B between adjacent units 26 have a larger opening area than the drain slits 23A of the units 26 .

[0075] According to the heat exchanger 10 of embodiment 8, the opening area of ​​the drainage slits 23B near the center where the amount of water flowing down is large is increased, thereby improving drainage performance while suppressing a reduction in the heat transfer area.

[0076] Ninth Embodiment A ninth embodiment will be described below, but explanations of parts that overlap with those of the first to eighth embodiments will be omitted, and parts that are the same as or equivalent to those of the first to eighth embodiments will be given the same reference numerals.

[0077] FIG. 23 is a schematic plan view of a heat exchanger 10 according to embodiment 9. The white arrows in FIG. 23 indicate the airflow direction. As shown in FIG. 23 , the drainage slits 23A and 23B are formed at different positions in adjacent fin sections 24 in the vertical direction. In FIG. 23 , the drainage slits 23A and 23B of the upper fin section 24 (left side of FIG. 23 ) are formed in the center in the pipe arrangement direction (horizontal direction in FIG. 23 ), while the drainage slits 23A and 23B of the lower fin section 24 (right side of FIG. 23 ) are formed on both sides in the pipe arrangement direction (horizontal direction in FIG. 23 ). Experiments and analysis conducted by the inventors have shown that the drainage performance of the drainage slits increases with increasing opening area and slit perimeter. Therefore, by forming the drainage slits 23A and 23B at different positions, the perimeter of one of the slits can be increased even if the opening area is the same, thereby improving drainage performance.

[0078] As described above, in the heat exchanger 10 according to the ninth embodiment, the positions at which the drainage slits 23A and 23B are formed are different between the fin portions 24 adjacent to each other in the vertical direction.

[0079] According to the heat exchanger 10 of embodiment 9, by forming drainage slits 23A, 23B at different positions in the fin sections 24 adjacent to each other in the vertical direction, the circumference of one of the slits can be increased even if they have the same opening area, thereby improving drainage performance.

[0080] Tenth Embodiment A tenth embodiment will be described below, but explanations of parts that overlap with those of the first to ninth embodiments will be omitted, and parts that are the same as or equivalent to those of the first to ninth embodiments will be given the same reference numerals.

[0081] 24 is a diagram showing the configuration of an air conditioner according to a tenth embodiment. The tenth embodiment relates to an air conditioner as an example of a refrigeration cycle apparatus equipped with the heat exchanger 10 according to any one of the first to ninth embodiments. The air conditioner uses the heat exchanger 10 according to any one of the first to ninth embodiments as the outdoor heat exchanger 230. However, this is not limiting, and the heat exchanger 10 according to any one of the first to ninth embodiments may be used as the indoor heat exchanger 110, or may be used for both the outdoor heat exchanger 230 and the indoor heat exchanger 110.

[0082] As shown in Figure 24, the air conditioner configures a refrigerant circuit by connecting an outdoor unit 200 and an indoor unit 100 with gas refrigerant piping 300 and liquid refrigerant piping 400. The outdoor unit 200 has a compressor 210, a flow path switching valve 220, an outdoor heat exchanger 230, and an outdoor fan 240. The air conditioner according to embodiment 10 is configured such that one outdoor unit 200 and one indoor unit 100 are connected with each other through piping, although the number of units is arbitrary.

[0083] The compressor 210 compresses the drawn refrigerant and discharges it. Although not particularly limited, the compressor 210 can change the capacity of the compressor 210 by arbitrarily changing the operating frequency using, for example, an inverter circuit. The flow path switching valve 220 is a valve that switches the flow of the refrigerant depending on whether the operation is cooling or heating.

[0084] The outdoor heat exchanger 230 exchanges heat between the refrigerant and outdoor air. During heating operation, the outdoor heat exchanger 230 functions as an evaporator, evaporating and vaporizing the refrigerant. During cooling operation, the outdoor heat exchanger 230 functions as a condenser, condensing and liquefying the refrigerant. The outdoor fan 240 sends outdoor air to the outdoor heat exchanger 230 to promote heat exchange in the outdoor heat exchanger 230.

[0085] On the other hand, the indoor unit 100 has an indoor heat exchanger 110, a pressure reducing device 120, and an indoor fan 130. The indoor heat exchanger 110 exchanges heat between the refrigerant and the indoor air to be air-conditioned. During heating operation, the indoor heat exchanger 110 functions as a condenser, condensing and liquefying the refrigerant. During cooling operation, the indoor heat exchanger 110 functions as an evaporator, evaporating and vaporizing the refrigerant.

[0086] The pressure reducing device 120 reduces the pressure of the refrigerant to expand it. The pressure reducing device 120 is configured, for example, by an electronic expansion valve. When the pressure reducing device 120 is configured by an electronic expansion valve, the pressure reducing device 120 adjusts its opening degree based on instructions from a control device (not shown) or the like. The indoor fan 130 passes indoor air through the indoor heat exchanger 110 and supplies the air that has passed through the indoor heat exchanger 110 into the room.

[0087] Next, the operation of each component of the air conditioner will be described based on the flow of refrigerant. First, heating operation will be described. During heating operation, the flow path switching valve 220 is switched to the dotted line side in FIG. 24 . High-temperature, high-pressure gas refrigerant compressed and discharged by the compressor 210 passes through the flow path switching valve 220 and flows into the indoor heat exchanger 110. The gas refrigerant that flows into the indoor heat exchanger 110 condenses and liquefies by exchanging heat with the air in the space to be air-conditioned. The liquefied refrigerant is depressurized by the pressure reducing device 120 to a two-phase gas-liquid state, and then flows into the outdoor heat exchanger 230. The refrigerant that flows into the outdoor heat exchanger 230 evaporates and gasifies by exchanging heat with outdoor air sent from the outdoor fan 240. The gasified refrigerant passes through the flow path switching valve 220 and is drawn back into the compressor 210. By circulating the refrigerant in this manner, the air conditioner performs air conditioning related to heating.

[0088] Next, cooling operation will be described. During cooling operation, the flow path switching valve 220 is switched to the solid line side in FIG. 24 . The high-temperature, high-pressure gas refrigerant compressed and discharged by the compressor 210 passes through the flow path switching valve 220 and flows into the outdoor heat exchanger 230. The gas refrigerant that flows into the outdoor heat exchanger 230 condenses and liquefies by exchanging heat with outdoor air supplied by the outdoor fan 240. The liquefied refrigerant is decompressed by the pressure reducing device 120 to a two-phase gas-liquid state, and then flows into the indoor heat exchanger 110. The refrigerant that flows into the indoor heat exchanger 110 evaporates and gasifies by exchanging heat with the air in the space to be air-conditioned. The gasified refrigerant passes through the flow path switching valve 220 and is drawn back into the compressor 210. By circulating the refrigerant in this manner, the air conditioner performs air conditioning related to cooling.

[0089] As described above, the air conditioner according to the tenth embodiment is equipped with the heat exchanger 10 according to any one of the first to ninth embodiments.

[0090] As described above, according to the air conditioning apparatus of the tenth embodiment, it is possible to improve the drainage performance while maintaining the heat transfer performance of the heat exchanger 10.

[0091] In the tenth embodiment, the refrigeration cycle device is described as an air conditioning device, but is not limited to this and may be a cooling device for cooling a refrigerated warehouse or a hot water supply device.

[0092] 1 Flat heat transfer tube, 1a Flat surface, 2 Corrugated fin, 2a Upstream protrusion, 3 Header, 3A Header, 3B Header, 4 Condensed water, 10 Heat exchanger, 20 Top, 21 Flat plate portion, 22 Louver, 22A First louver group, 22B Second louver group, 22a Louver slit, 22b Plate portion, 23 Drainage slit, 23A Drainage slit, 23B Drainage slit, 24 Fin portion, 25 Half plate portion, 26 Unit, 27 Louver adjacent portion, 100 Indoor unit, 110 Indoor heat exchanger, 120 Pressure reducing device, 130 Indoor fan, 200 Outdoor unit, 210 Compressor, 220 Flow path switching valve, 230 Outdoor heat exchanger, 240 Outdoor fan, 300 Gas refrigerant piping, 400 Liquid refrigerant piping.

Claims

1. A heat exchanger comprising: a plurality of flat heat transfer tubes having a flat cross-section, having a plurality of flow paths formed by through-holes, arranged vertically, and arranged in parallel at intervals in a direction orthogonal to the air flow direction; and corrugated fins disposed between the plurality of flat heat transfer tubes, wherein the corrugated fins have a configuration in which a plate-like fin portion is continuously connected in a wave shape in the tube axis direction of the plurality of flat heat transfer tubes, and the fin portion includes: a plurality of louver groups each including a plurality of louvers having a louver slit extending in the tube parallel direction, which is the parallel arrangement direction of the plurality of flat heat transfer tubes, and a plate portion inclined with respect to the flat plate portion of the fin portion; and a drainage slit formed between the plurality of louver groups and extending in the tube parallel direction for draining water on the upper surface of the fin portion. When the width of the fin portion in the air flow direction is defined as L, the pitch of the plate portion is defined as Rp, and the inclination angle of the plate portion with respect to the flat plate portion in the inclination direction of the plate portion is defined as α, the heat exchanger satisfies 18° ≤ α ≤ 30° and 0.042 ≤ (Rp / L) ≤ 0.

10.

2. The heat exchanger according to claim 1, wherein the plurality of louver groups are continuously connected from the flat plate portion and have a semi-plate portion inclined with respect to the flat plate portion.

3. The heat exchanger according to claim 2, when the pitch of the semi-plate portion is defined as hRp, satisfies hRp > (Rp / 2).

4. The heat exchanger according to any one of claims 1 to 3, comprising a pair of headers arranged at intervals in the vertical direction, and when the height of the heat exchanger, which is the length between the lower end of the upper header and the upper end of the lower header, is defined as H, satisfies H ≥ 0.42 m.

5. The heat exchanger according to any one of claims 1 to 4, when the shortest distance between adjacent louvers vertically among the plurality of louvers is defined as ymin and the longest distance is defined as ymax, satisfies 20% ≤ (ymin / ymax) ≤ 60%.

6. The plurality of louver groups include a first louver group formed upstream of the drainage slit in the air flow direction and a second louver group formed downstream of the drainage slit in the air flow direction. The plate portions of the first louver group and the plate portions of the second louver group are inclined in opposite directions with respect to the flat plate portion and are inclined from the upper end portion to the lower end portion of the plate portion toward the drainage slit. The heat exchanger according to any one of claims 1 to 5.

7. The plurality of flat heat transfer tubes are arranged in parallel at intervals in the air flow direction. The heat exchanger according to claim 6.

8. The drainage slit is formed in the fin portion between the plurality of flat heat transfer tubes adjacent to each other in the air flow direction. The heat exchanger according to claim 7.

9. A plurality of the drainage slits are formed in the air flow direction. The heat exchanger according to claim 8.

10. The heat exchanger according to claim 6 or 7 has a plurality of unit units each composed of the first louver group, the second louver group, and the drainage slit in the air flow direction.

11. The unit unit has a plurality of the drainage slits in the air flow direction. The heat exchanger according to claim 10.

12. The drainage slit is formed between adjacent unit units. The heat exchanger according to claim 10 or 11.

13. A plurality of the drainage slits are formed in the air flow direction between adjacent unit units. The heat exchanger according to claim 12.

14. The drainage slit between adjacent unit units has a larger opening area than the drainage slit of the unit unit. The heat exchanger according to claim 12 or 13.

15. The positions where the drainage slits are formed are different from each other in the fin portions adjacent to each other in the vertical direction. The heat exchanger according to any one of claims 1 to 14.

16. A refrigeration cycle device including the heat exchanger according to any one of claims 1 to 15.

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