Heat exchanger

Abstract

A heat exchanger according to the present disclosure comprises: a plurality of refrigerant tubes arranged to be spaced apart from each other in a first direction; and a plurality of fins connecting adjacent refrigerant tubes and conducting heat, wherein each of the fins comprises an inner portion positioned to overlap the refrigerant tubes in the first direction, and a drop portion positioned to at least partially overlap one of the refrigerant tubes in a second direction that intersects the first direction.

Description

heat exchanger

[0001] The present disclosure relates to a heat exchanger, and more particularly, to a heat exchanger that reduces differential pressure of air flowing between a plurality of fins and improves heat exchange efficiency.

[0002] The conventional heat exchanger of Patent Document 1 is composed of an upper header (2) positioned to correspond to the upper portion of a lower header (1), a plurality of tubes (3) positioned between the upper header (2) and the lower header (1), and fins (6) positioned between each of the tubes (3). The lower header (1) is formed in a cylindrical shape, has a hollow interior, and a plurality of header holes (4) are formed at equal intervals along the length direction of the lower header (1) on one side of the outer peripheral portion forming the outer shape, into which tubes (3) are inserted and fixed.

[0003] Here, the upper header (2) positioned above to correspond to the lower header (1) has the same shape as the lower header (1). Each tube (3) is arranged parallel to the longitudinal direction of the header (1, 2) with both longitudinal ends of the tube (3) fixed to each header hole (4).

[0004] Meanwhile, the flowing air flows with a constant slope toward the plane connecting the longitudinal axes of the two headers (1, 2) and passes between each tube (3) and the two headers (1, 2). The tube (3) has a length which is the distance between the two ends fixed to the two headers (1, 2), a thickness which is the distance perpendicular to the direction of the flowing air, and a width which is the distance parallel to the direction of the flowing air. The tube (3) is a rectangular plate having a width and a thin thickness that can be accommodated in the two headers (1, 2), and has a plurality of hollow channels (5) formed therein.

[0005] Each pin (6) is a thin plate-shaped plate that is folded in a zigzag pattern several times and installed between each tube (4). The pin (6) may have various shapes and be fixed, but it is generally preferable to form a space so that the flow resistance of the flowing air is minimized.

[0006] The space between each fin (6) is generally very small, and although air can flow through these spaces, there is a problem in that the heat exchange efficiency is reduced because the air introduced between each fin does not have sufficient heat exchange time with the fins and is discharged.

[0007] In addition, in the case of patent document 2, a heat exchanger heat dissipation fin is disclosed, which has a fin body of a bent structure and a plurality of ventilation guides, i.e., louvers, formed at a certain angle on the fin body to guide wind to the lower and upper parts of the heat dissipation fin through ventilation guide holes formed by the ventilation guides.

[0008] However, the heat dissipation fin for the heat exchanger of the above-mentioned patent document 2 has a problem in that not only is the productivity poor due to the difficulty in managing the individual dimensions of the louvers, but also the flow of the fluid passing through it is not smooth due to the irregular angle of the louvers, resulting in a reduced heat dissipation effect.

[0009] In addition, in the case of patent document 2, when the angle of the louver is the same, there is a problem that the air resistance becomes large and the heat dissipation efficiency is not excellent.

[0010]

[0011] [Prior Art Literature]

[0012] [Patent Document]

[0013] Patent Document 1 - Korean Publication No. 20040053551

[0014] Patent Document 2 - Korean Patent Registration No. 10-0740697

[0015] The problem to be solved by the present disclosure is to provide a heat exchanger that reduces the air pressure loss of air flowing between fins and improves heat exchange efficiency.

[0016] Another problem to be solved by the present disclosure is to provide a heat exchanger that is easy to manufacture with a plurality of louvers formed on fins.

[0017] Another problem that the present disclosure seeks to solve is to provide a heat exchanger with excellent space utilization by reducing the width of the fins.

[0018] Another problem that the present disclosure seeks to solve is to provide a heat exchanger that prevents external water from entering the space between the fins.

[0019] Another problem that the present disclosure seeks to solve is to provide a heat exchanger in which water in the space between the fins is easily discharged to the outside.

[0020] The tasks of the present disclosure are not limited to the tasks mentioned above, and other tasks not mentioned will be clearly understood by those skilled in the art from the description below.

[0021]

[0022] The heat dissipation fin and the heat exchanger including the same according to the present disclosure are characterized in that the inclination angle of the louver located at the uppermost position among the plurality of louvers is greater than the inclination angles of the other louvers.

[0023] Specifically, a heat dissipation fin according to the present disclosure includes a heat dissipation plate extending in a first direction parallel to a flow direction of a fluid, a heat dissipation hole formed through the heat dissipation plate, and a plurality of louvers arranged in the heat dissipation hole and having an incline with respect to the heat dissipation plate, wherein the plurality of louvers include a first louver having a first incline angle with respect to the heat dissipation plate, and a second louver having a second incline angle with respect to the heat dissipation plate and positioned further from an inlet side through which a fluid flows than the first louver, wherein the first incline angle is greater than the second incline angle.

[0024]

[0025] The first slope angle may be 41% to 48% greater than the second slope angle.

[0026] The first inclination angle may be in the range of 33° to 37°.

[0027] The second inclination angle may be in the range of 22° to 26°.

[0028] The number of the first louvers may be smaller than the number of the second louvers.

[0029] The number of the first louvers may be 10% to 20% of the number of the second louvers.

[0030] The area in which the first louver is formed may be smaller than the area in which the second louver is formed.

[0031] The length of the first louver and the length of the second louver may be the same.

[0032] The first louver and the second louver may extend in a second direction that intersects the first direction.

[0033] The width of the first louver may be smaller than the width of the second louver.

[0034] The above heat sink may further include an inlet portion connected to one end of the first louver and positioned adjacent to the inlet side through which the fluid flows rather than the first louver.

[0035] The width of the above inlet portion may be 90% to 120% of the width of the second louver.

[0036] In addition, a heat dissipation fin according to another embodiment of the present disclosure includes a heat dissipation plate extending in a first direction parallel to a flow direction of a fluid, a first heat dissipation hole formed through the heat dissipation plate, a second heat dissipation hole formed spaced apart from the first heat dissipation hole in the first direction, and a plurality of louvers arranged in the first heat dissipation hole and the second heat dissipation hole and having an incline with respect to the heat dissipation plate, wherein the plurality of louvers include a front louver group arranged in the first heat dissipation hole, and a rear louver group arranged in the second heat dissipation hole, and the front louver group includes a first louver having a first incline angle with respect to the heat dissipation plate, and second louvers having a second incline angle with respect to the heat dissipation plate and positioned further from an inlet side through which a fluid flows than the first louvers, wherein the first incline angle may be greater than the second incline angle.

[0037] The rear louver group includes a third louver having a third inclination angle with respect to the heat sink, and a fourth louver having a fourth inclination angle with respect to the heat sink and positioned further from the inlet side through which the fluid flows than the fourth louver, wherein the third inclination angle may be greater than the fourth inclination angle.

[0038] The number of the first louver and the third louver may be 1.

[0039] The number of the third louver and the fourth louver may be plural.

[0040] The first slope angle may be the same as the third slope angle, and the second slope angle may be the same as the fourth slope angle.

[0041] According to another embodiment of the present disclosure, a heat exchanger includes a plurality of refrigerant tubes spaced apart from each other and a plurality of heat dissipation fins connecting the adjacent refrigerant tubes and conducting heat, wherein the heat dissipation fins include a heat dissipation plate extending in a first direction parallel to a flow direction of a fluid, a heat dissipation hole formed through the heat dissipation plate, and a plurality of louvers arranged in the heat dissipation hole and having an incline with respect to the heat dissipation plate, wherein the plurality of louvers include a first louver having a first incline angle with respect to the heat dissipation plate, and a second louver having a second incline angle with respect to the heat dissipation plate and positioned further from an inlet side through which a fluid flows than the first louver, wherein the first incline angle may be greater than the second incline angle.

[0042] Each of the above heat dissipation fins may include an inner portion positioned to overlap the refrigerant tubes in a second direction intersecting the first direction and an outer portion positioned not to overlap the refrigerant tubes in the second direction.

[0043] The above heat dissipation hole and the plurality of louvers can be formed in the inner portion.

[0044] The inner portion may be positioned closer to the inlet side through which the fluid flows than the outer portion.

[0045] The heat dissipation fin includes a plurality of first bodies extending in the first direction, a plurality of second bodies extending in the first direction and positioned between the plurality of first bodies, an upper body connecting one end of the adjacent first bodies and one end of the adjacent second bodies and in contact with one refrigerant tube among the plurality of refrigerant tubes, and a lower body connecting the other end of the adjacent first bodies and the other end of the adjacent second bodies and in contact with another refrigerant tube among the plurality of refrigerant tubes, and the heat dissipation hole and the louver can be formed in the first bodies and the second bodies.

[0046]

[0047] The heat exchanger of the present disclosure has one or more of the following effects.

[0048] First, the present disclosure has the advantage of reducing air pressure loss of air flowing between fins and improving heat exchange efficiency by making the angle of the louver located at the uppermost point among a plurality of louvers formed on the fins larger than the angles of the other louvers.

[0049] Second, the present disclosure has the advantage of reducing the air pressure loss of the flowing air and improving the heat exchange efficiency when the direction of air flow is changed when entering the second through hole from the first through hole by forming a plurality of through holes in the fin and making the angle of the louver located at the uppermost position among the louvers arranged in each through hole larger than the angles of the other louvers.

[0050] Third, since the angle of the louver located at the uppermost position among the plurality of louvers formed on the fin is made larger than the angles of the other louvers, there is an advantage in that the fin is easy to manufacture since only the angle needs to be changed in the process of bending the fin and then bending the louver again.

[0051] Fourth, the present disclosure has an inner region in which fins overlap with a plurality of adjacent tubes in one direction, and an outer region in which they do not overlap, and a drop portion extends downward at the bottom of the outer region, so that heat from the tubes is transferred to the fins in the inner region, and even if external water flows in from the outer region, the lower part of the outer region is not blocked by the tube, so that the surface tension is weaker than gravity, and the water falls along the drop portion, and in addition, since gravity is greatly applied to the water in the drop portion by the sum of the heights of the outer region and the drop portion, there is an advantage in that water easily falls from the drop portion.

[0052]

[0053] FIG. 1 is a diagram illustrating a refrigeration cycle device according to one embodiment of the present disclosure.

[0054] Figure 2 is a perspective view showing the exterior of the outdoor unit illustrated in Figure 1.

[0055] FIG. 3 is a perspective view of a heat exchanger according to one embodiment of the present disclosure.

[0056] Figure 4 is a longitudinal cross-sectional view of the heat exchanger illustrated in Figure 3.

[0057] Figure 5 is a cross-sectional view taken along line 5-5' of Figure 3.

[0058] Figure 6 is an enlarged view of a portion of Figure 5.

[0059] Fig. 7 is a partial perspective view of Fig. 5.

[0060] Figure 8 is a rear view of Figure 6.

[0061] Figure 9 is a cross-sectional view taken along line 9-9' of Figure 6.

[0062] Figure 10 is a diagram showing the velocity of air around the louver and fin according to a comparative example.

[0063] FIG. 11 is a diagram showing the velocity of air around a louver and fin according to one embodiment of the present disclosure.

[0064] FIG. 12 is a perspective view of another heat dissipation fin according to another embodiment of the present disclosure.

[0065] The advantages and features of the present disclosure, and methods for achieving them, will become clearer with reference to the embodiments described in detail below together with the accompanying drawings. However, the present disclosure is not limited to the embodiments disclosed below and may be implemented in various different forms. These embodiments are provided solely to ensure that the disclosure of the present disclosure is complete and to fully inform those skilled in the art of the scope of the invention, and the present disclosure is defined only by the scope of the claims. Like reference numerals designate like elements throughout the specification.

[0066] Spatially relative terms such as "below," "beneath," "lower," "above," and "upper" can be used to easily describe the relationship between one component and another, as illustrated in the drawings. Spatially relative terms should be understood to include different orientations of the components during use or operation in addition to the orientations depicted in the drawings. For example, if a component depicted in the drawings were flipped over, a component described as "below" or "beneath" another component could be positioned "above" the other component. Thus, the exemplary term "below" can include both the above and below orientations. Components can also be oriented in other directions, and thus spatially relative terms can be interpreted based on their orientation.

[0067] The terminology used herein is for the purpose of describing embodiments only and is not intended to be limiting of the present disclosure. As used herein, the singular includes the plural unless specifically stated otherwise. As used herein, the terms "comprises" and / or "comprising" do not exclude the presence or addition of one or more other components, steps, and / or operations.

[0068] Unless otherwise defined, all terms (including technical and scientific terms) used herein may be used in their common sense to those of ordinary skill in the art to which this disclosure pertains. Furthermore, terms defined in commonly used dictionaries are not to be interpreted ideally or excessively unless explicitly and specifically defined otherwise.

[0069] The thickness and size of each component in the drawings are exaggerated, omitted, or schematically illustrated for convenience and clarity. Furthermore, the size and area of ​​each component do not entirely reflect its actual size or area.

[0070] Additionally, the angles and directions mentioned in the process of describing the structure of the embodiment are based on those described in the drawings. If the reference points and positional relationships for angles are not clearly mentioned in the description of the structure forming the embodiment in the specification, the relevant drawings should be referenced.

[0071] The present disclosure will be described in detail with reference to the attached drawings.

[0072] FIG. 1 is a drawing showing a refrigeration cycle device according to one embodiment of the present disclosure, and FIG. 2 is a perspective view showing the outside of the outdoor unit shown in FIG. 1.

[0073] Referring to FIGS. 1 and 2, a refrigeration cycle device according to the present embodiment may include a compressor (10) that compresses a refrigerant, an outdoor heat exchanger (11) in which the refrigerant exchanges heat with outdoor air, an expansion mechanism (12) in which the refrigerant expands, and an indoor heat exchanger (13) in which the refrigerant exchanges heat with indoor air.

[0074] The refrigerant compressed in the compressor (10) can be condensed by exchanging heat with the outdoor air while passing through the outdoor heat exchanger (11). The outdoor heat exchanger (11) can be used as a condenser.

[0075] The refrigerant condensed in the outdoor heat exchanger (11) can flow to the expansion device (12) and be expanded. The refrigerant expanded by the expansion device (12) can be evaporated by exchanging heat with indoor air while passing through the indoor heat exchanger (13).

[0076] The indoor heat exchanger (12) can be used as an evaporator that evaporates refrigerant. The refrigerant evaporated in the indoor heat exchanger (12) can be recovered by the compressor (10).

[0077] The heat exchanger may include an indoor heat exchanger (12) and an outdoor heat exchanger (11). The refrigerant circulates through the compressor (10), the outdoor heat exchanger (11), the expansion device (12), and the indoor heat exchanger (13) to operate in a refrigeration cycle.

[0078] A compressor (10) suction path that guides the refrigerant that has passed through the indoor heat exchanger (13) to the compressor (10) may be connected to the compressor (10). An accumulator (14) in which liquid refrigerant is accumulated may be installed in the compressor (10) suction path.

[0079] The indoor heat exchanger (13) can form a refrigerant passage through which the refrigerant passes.

[0080] The refrigeration cycle device may be a split-type air conditioner with an indoor unit (I) and an outdoor unit (O) separated, in which case the compressor (10) and the outdoor heat exchanger (11) may be installed inside the outdoor unit (I). In addition, the refrigeration cycle device may be a refrigerator, in which the indoor heat exchanger (13) may be arranged to exchange heat with air inside a food storage, and the outdoor heat exchanger (11) may exchange heat with air outside the food storage. In the case of a refrigerator, the indoor unit (I) and the outdoor unit (O) may be arranged together in the main body.

[0081] The expansion device (12) may be installed in either the indoor unit (I) or the outdoor unit (O). The indoor heat exchanger (13) may be installed inside the indoor unit (I).

[0082] An outdoor fan (15) that blows outdoor air to an outdoor heat exchanger (11) may be installed in the outdoor unit (O). In addition, a compressor (10) may be installed in the machine room of the outdoor unit (O).

[0083] An indoor fan (16) that blows indoor air to an indoor heat exchanger (13) can be installed in the indoor unit (I).

[0084] Hereinafter, a heat exchanger of the present disclosure that suppresses external water inflow and improves internal water discharge is described. The heat exchanger can be used as an indoor heat exchanger (13) or / and an outdoor heat exchanger (11).

[0085]

[0086] FIG. 3 is a perspective view of a heat exchanger according to one embodiment of the present disclosure, FIG. 4 is a longitudinal cross-sectional view of the heat exchanger illustrated in FIG. 3, and FIG. 5 is a cross-sectional view taken along line 5-5' of FIG. 4.

[0087] Referring to FIGS. 3 to 5, a heat exchanger (100) is a device that exchanges heat between the refrigerant of a refrigeration cycle and external air. It is preferable that the heat exchanger (100) evenly distribute the refrigerant within it and have a large heat transfer area.

[0088] The heat exchanger (100) may be arranged with multiple rows, and the direction of flow of the refrigerant may be alternated in one row.

[0089] For example, a heat exchanger (100) includes a plurality of refrigerant tubes (50) through which refrigerant flows, heat dissipation fins (60) arranged between adjacent refrigerant tubes (50) to conduct heat, and a sacrificial sheet (90) having one surface in contact with the refrigerant tubes (50) and the other surface in contact with the heat dissipation fins (60).

[0090] In addition, the heat exchanger (100) further includes a header (70) in which one end of a plurality of refrigerant tubes (50) is connected to supply refrigerant to the inside of the plurality of refrigerant tubes (50), an outer pipe (110) inside the header (70), and an inner pipe (120) inside the outer pipe (110).

[0091] The refrigerant tube (50) has a fine inner diameter to maximize the contact area with air as the refrigerant flows inside. A plurality of refrigerant tubes (50) are connected to a header (70). The refrigerant tubes (50) extend in a direction intersecting the header (70).

[0092] Specifically, the refrigerant tube (50) is arranged long in the horizontal (left-right) direction (LeRi), and a plurality of refrigerant tubes (50) can be stacked vertically (longitudinal) (UD). As air passes through the space between the plurality of refrigerant tubes (50) stacked vertically, heat is exchanged with the refrigerant in the refrigerant tubes (50). The plurality of refrigerant tubes (50) stacked horizontally define a heat exchange surface together with the heat dissipation fins (60) described later. Here, the vertical direction can be defined as the first direction, the front-back direction as the second direction, and the left-right direction as the third direction.

[0093] The refrigerant tube (50) may include a plurality of microchannels (50a) therein. The plurality of microchannels (50a) provide a space through which the refrigerant passes. The plurality of microchannels (50a) may extend in a direction parallel to the refrigerant tube (50).

[0094] Specifically, as shown in FIG. 5, the cross-sectional shape of the refrigerant tube (50) is a rectangular shape that is longer from left to right than from top to bottom, and the cross-sectional shape of the microchannel (50a) may be a rectangular shape.

[0095] Micro channels (50a) are usually stacked in a single row in a direction (front-back direction) (FR) that intersects the longitudinal direction of the refrigerant tube (50).

[0096] The heat dissipation fin (60) transfers heat from the refrigerant tube (50). The heat dissipation fin (60) increases the contact area with air, thereby improving heat dissipation performance.

[0097] A heat sink fin (60) is positioned between adjacent refrigerant tubes (50). The heat sink fin (60) may have various shapes, but may be formed by bending a plate having the same width as the refrigerant tube (50). The heat sink fin (60) may be coated with a clad (601).

[0098] A heat dissipation fin (60) can conduct heat by connecting two refrigerant tubes (50) that are stacked vertically. The heat dissipation fin (60) may be in direct contact with the refrigerant tube (50) or may be connected to the refrigerant tube (50) by a sacrificial sheet (90).

[0099] When viewed from the front-back direction, the contact area between the heat dissipation fin (60) and the sacrificial sheet (90) is in a U or V shape. The heat dissipation fin (60) and the refrigerant tube (50) are alternately stacked in the vertical direction, and the refrigerant tube (50) is positioned at the bottom and the top.

[0100] If the refrigerant tube (50) located at the top is defined as the first refrigerant tube (50, 51), and the refrigerant tube (50) located below the first refrigerant tube (50, 51) is defined as the second refrigerant tube (50, 52), the heat dissipation fin (60) between the first refrigerant tube (50, 51) and the second refrigerant tube (50, 52) can be defined as the first heat dissipation fin (60, 61). In this way, the n-th refrigerant tube and the n-th heat dissipation fin can be defined.

[0101] A header (70) can be connected to one end of a plurality of refrigerant tubes (50) to supply refrigerant into the interior of the plurality of refrigerant tubes (50). In addition, the header (70) can be connected to one end of the refrigerant tubes (50) to collect refrigerant discharged from the refrigerant tubes (50) and supply it to another device.

[0102] The header (70) has a larger diameter, inner diameter, or size than the refrigerant tube (50) and extends in the vertical direction. The header (70) may include a left header (71) connected to one end of the refrigerant tube (50) and a lower header (70) (81) connected to the other end of the refrigerant tube (50).

[0103] The right header (81) is connected to the right side of the plurality of refrigerant tubes (50). The right header (81) is arranged to extend vertically and is connected to the inlet pipe (22). The interior of the right header (81) is formed as a single space, so that the refrigerant introduced through the inlet pipe (22) is distributed and supplied to the plurality of refrigerant tubes (50). The inlet pipe (22) is an example of a refrigerant supply unit.

[0104] An inlet pipe (22) is connected to an area adjacent to the bottom of the right header (81).

[0105] The left header (71) is connected to the left side of the plurality of refrigerant tubes (50). The left header (71) is arranged to extend vertically and is connected to the outlet pipe (24). The interior of the left header (71) is formed as a single space, so that the refrigerant discharged to the upper side of the plurality of refrigerant tubes (50) is guided to the outlet pipe (24).

[0106] Of course, the refrigerant flowing out from the left header (71) may be supplied to the header (70) of another heat exchanger (100).

[0107] The heat exchanger (100) may have an outer pipe (110) and an inner pipe (120) positioned to prevent refrigerant from being concentrated inside the header (70). The refrigerant is uniformly distributed through the holes of the outer pipe (110) and the inner pipe (120).

[0108] The sacrificial sheet (90) has one surface in contact with the refrigerant tube (50) and the other surface in contact with the heat dissipation fin (60), so that it corrodes instead of the heat dissipation fin (60) and the refrigerant tube (50), thereby suppressing corrosion of the heat dissipation fin (60) and the refrigerant tube (50) and preventing peeling of the heat dissipation fin (60) and the refrigerant tube (50).

[0109] For example, the corrosion potential of the sacrificial sheet (90) may be lower than the corrosion potential of the refrigerant tube (50). When corrosion occurs while the two metals are in contact, the metal with the lower corrosion potential is corroded first, so that the sacrificial sheet (90) is corroded instead of the refrigerant tube (50), thereby preventing the refrigerant from leaking due to the corrosion of the refrigerant tube (50).

[0110] In addition, the corrosion potential of the sacrificial sheet (90) may be lower than the corrosion potential of the radiating fin (60). Even if only the refrigerant tube (50) is not corroded, there is no problem because the refrigerant is prevented from leaking, but if the radiating fin (60) is corroded, the flow of air is obstructed and the refrigerant efficiency is reduced, so it is preferable that the corrosion potential of the sacrificial sheet (90) be lower than the corrosion potential of the radiating fin (60).

[0111] If the corrosion potential of the sacrificial sheet (90) is lower than the corrosion potential of the heat dissipation fin (60), the sacrificial sheet (90) is corroded first instead of the heat dissipation fin (60), thereby preventing corrosion of the heat dissipation fin (60).

[0112] Preferably, the corrosion potential of the radiator fin (60) may be lower than the corrosion potential of the refrigerant tube (50). Among the radiator fin (60) and the refrigerant tube (50), the part that is at risk of corrosion is the refrigerant tube (50). If the radiator fin (60) corrodes, the problem of a slight decrease in efficiency occurs, but if the refrigerant tube (50) corrodes, the major problem of refrigerant leakage and the air conditioner not operating occurs.

[0113] Accordingly, the present disclosure prevents corrosion of the refrigerant tube (50) by making the corrosion potential of the radiator fin (60) lower than that of the refrigerant tube (50), thereby causing the radiator fin (60) to corrode before the refrigerant tube (50).

[0114] In conclusion, the corrosion potential of the sacrificial sheet (90) is lower than the corrosion potential of the refrigerant tube (50), the corrosion potential of the sacrificial sheet (90) is lower than the corrosion potential of the radiating fin (60), and the corrosion potential of the radiating fin (60) may be lower than the corrosion potential of the refrigerant tube (50).

[0115]

[0116] Below, the structure of the heat dissipation fin (60) that improves heat exchange efficiency and drainage performance is described in detail.

[0117] Fig. 6 is an enlarged view of a portion of Fig. 5, Fig. 7 is a perspective view of a portion of Fig. 5, and Fig. 8 is a rear view of Fig. 6.

[0118] Referring to FIGS. 6 to 8, the heat dissipation fins (60) can partially protrude outside the tube to prevent water from flowing in from the outside and to allow water collected in the space between the heat dissipation fins (60) to be easily discharged to the outside.

[0119] In addition, the heat dissipation fins (60) have a portion protruding outward from the tube, and the lower end protruding outward extends downward, so that water flowing in from the outside can be suppressed, and water formed in the space between the heat dissipation fins (60) can be easily discharged to the outside.

[0120]

[0121] Each radiating fin (60) includes an inner portion (610) positioned to overlap with the refrigerant tubes (50) in the vertical direction, and a drop portion (630) positioned to overlap at least a portion of one of the refrigerant tubes in the front-back direction. In addition, each radiating fin (60) may include an outer portion (620) positioned not to overlap with the refrigerant tubes (50) in the vertical direction.

[0122] The inner portion (610) connects adjacent refrigerant tubes (50). The upper end of the inner portion (610) is connected to the lower end of the refrigerant tube (50) located above the inner portion (610), and the lower end of the inner portion (610) is connected to the upper end of the refrigerant tube (50) located below the inner portion (610).

[0123] The inner part (610) is positioned to overlap the refrigerant tube (50) in the vertical direction.

[0124] Specifically, the outer portion (620) is connected to the rear end of the inner portion (610) and is positioned rearward relative to the inner portion (610). No refrigerant tube (50) is positioned below or above the outer portion (620). The inner portion (610) may be positioned closer to the inlet side where the fluid flows in than the outer portion (620).

[0125] The length in the front-back direction of the inner part (610) may be longer than the length in the front-back direction of the outer part (620). This is because if the length of the inner part (610) becomes shorter than that of the outer part (620), the area for heat exchange with the refrigerant tube (50) decreases. Even if the heat of the refrigerant tube (50) is transferred to the heat dissipation fin (60) in the inner part (610) and external water flows in from the outer part (620), since the lower part of the outer part (620) is not blocked by the tube, the surface tension becomes weaker than gravity and the water falls.

[0126] The water located in the space between the heat dissipation fins (60) in the inner part (610) spreads out horizontally due to surface tension, and some of the water that has spread out falls downward in the outer part (620), and the water in the inner part (610) moves to the outer part (620) due to surface tension and viscosity, and the water that has moved to the outer part (620) falls again due to gravity, so there is an advantage in that it is easy to discharge the water collected in the space between the heat dissipation fins (60) to the outside.

[0127] The front-to-back width of the outer portion (620) may be smaller than the spacing between adjacent refrigerant tubes (50). This is because, if the front-to-back width of the outer portion (620) becomes larger than the spacing between adjacent tubes, the heat exchange area decreases, resulting in lower heat exchange efficiency and no improvement in the ability to suppress water inflow.

[0128] The outer portion (620) is positioned so as not to overlap the refrigerant tube in the front-rear direction.

[0129] The inner portion is positioned so as to overlap at least a portion of one of the refrigerant tubes in the forward-reverse direction. Specifically, the inner portion may overlap at least a portion of the refrigerant tube positioned below the heat sink fin (60) on which the inner portion is positioned in the forward-reverse direction.

[0130] The drop portion (630) is connected to the outer portion (620). Specifically, the drop portion (630) is connected to the outer portion (620) at the bottom. The drop portion (630) extends downward from the bottom of the outer portion (620).

[0131] The front-back width of the drop portion (630) and the front-back width of the outer portion (620) may be the same or different. Preferably, the front-back width of the drop portion (630) and the front-back width of the outer portion (620) may be the same.

[0132] The drop portion (630) is positioned so as not to overlap the refrigerant tubes in the upper direction. The inner portion is positioned so as to overlap the outer portion (620) in the upper and lower direction.

[0133] The drop portion (630) can be formed by cutting and bending a portion of the heat dissipation fin (60). Accordingly, the structure of the heat dissipation fin (60) formed by bending a single plate has the effect of opening the lower portion.

[0134] Water located in the space between the heat dissipation fins (60) in the inner part (610) spreads out horizontally due to surface tension, and some of the spread out water falls downward in the outer part (620). A drop part (630) is located at the bottom of the outer part (620), so that gravity is applied to the water by the sum of the vertical lengths of the outer part (620) and the drop part (630).

[0135] The water in the inner part (610) moves to the outer part (620) due to surface tension and viscosity, and the water moved to the outer part (620) falls due to gravity and surface tension applied to the drop part (630) and the outer part (620), so there is an advantage in that it is easy to discharge water collected in the space between the heat dissipation fins (60) to the outside. In particular, since the drop part (630) is formed by cutting and bending a banded part of the heat dissipation fin (60), the lower part is open, so that water falls more easily from the drop part (630).

[0136] The front-to-back width of the drop portion (630) may be smaller than the spacing between adjacent refrigerant tubes (50). This is because, if the front-to-back width of the drop portion (630) becomes larger than the spacing between adjacent tubes, the heat exchange area decreases, resulting in lower heat exchange efficiency and no improvement in the ability to suppress water inflow.

[0137] The vertical length of the drop portion (630) is not limited and may have various embodiments. For example, the lower end of the drop portion (630) may be positioned to overlap with the middle or lower end of a refrigerant tube that overlaps the drop portion (630) in the front-back direction.

[0138] Specifically, the lower end of the drop portion (630) of the first heat dissipation fin (60) (51) can be positioned to overlap with the middle or lower end of the second refrigerant tube (52) in the front-back direction.

[0139] As another example, the lower end of the drop portion (630) may be positioned to completely overlap with the overlapping refrigerant tubes in the front-back direction and may be in contact with the outer portion (620) of another heat dissipation fin (60) positioned at the bottom.

[0140] Specifically, the lower end of the drop portion (630) of the first heat dissipation fin (60) (51) can be in contact with the upper end of the outer portion (620) of the second heat dissipation fin (60) (52).

[0141] As another example, the lower end of the drop portion (630) may be positioned to completely overlap with the overlapping refrigerant tube in the front-back direction, and may be positioned to overlap with the outer portion (620) of another heat dissipation fin (60) positioned at the bottom in the left-right direction.

[0142] Specifically, the lower end of the drop portion (630) of the first heat dissipation fin (60) (51) can be positioned to overlap with a part of the outer portion (620) of the second heat dissipation fin (60) (52) in the left-right direction.

[0143]

[0144] Referring to FIGS. 6 to 8, the heat dissipation fin (60) may be formed by bending a plurality of bodies in a zigzag pattern. For example, the heat dissipation fin (60) may include a plurality of first bodies (611, 621) extending in the vertical direction, a plurality of second bodies (613, 623) extending in the vertical direction and positioned between the plurality of first bodies (611, 621), an upper body (615, 625) connecting the upper ends of the adjacent first bodies (611, 621) and the upper ends of the second bodies (613, 623), and a lower body (617) connecting the lower ends of the adjacent first bodies (611, 621) and the lower ends of the second bodies (613, 623).

[0145] Of course, depending on the embodiment, the first body (611, 621) and the second body (613, 623) may have an inclination in the up-down direction.

[0146] The first body (611, 621) and the second body (613, 623) are arranged facing each other and can be arranged parallel to each other. The first body (611, 621) and the second body (613, 623) can be collectively referred to as a heat sink (640).

[0147] The first body (611, 621) and the second body (613, 623) can define a surface extending in a first direction (front-back direction) parallel to the flow direction of the fluid and intersecting with the left-right direction.

[0148] The upper body (615, 625) is connected to the lower end of the refrigerant tube (50) located at the upper end among the adjacent refrigerant tubes (50), and the lower body (617) is connected to the upper end of the refrigerant tube (50) located at the upper end among the adjacent refrigerant tubes (50).

[0149] A part (615) of the upper body of the first radiating fin (60) is connected to the lower end of the first refrigerant tube (51), and a part (617) of the lower body of the first radiating fin (60) is connected to the upper end of the second refrigerant tube (52).

[0150] The upper body (615, 625) is positioned so as not to overlap with the lower body (617) in the vertical direction. The upper body (615, 625) and the lower body (617) are positioned alternately in the left-right direction.

[0151] The first body (611, 621), the second body (613, 623), the upper body (615, 625), and the lower body (617) extend in a direction intersecting the longitudinal direction of the refrigerant tube (50). Specifically, the first body (611, 621), the second body (613, 623), the upper body (615, 625), and the lower body (617) extend in the front-back direction.

[0152] The first body (611, 621) and the second body (613, 623) can define a surface intersecting the left and right directions.

[0153] The first body (611, 621) may include a first inner body (611) positioned in the inner part (610) and a first outer body (621) positioned in the outer part (620), the second body (613, 623) may include a second inner body (613) positioned in the inner part (610) and a second outer body (623) positioned in the outer part (620), the upper body (615, 625) may include an upper inner body (615) positioned in the inner part (610) and an upper outer body (625) positioned in the outer part (620), and the lower body (617) may include a lower inner body (617) positioned in the inner part (610).

[0154] That is, the inner part (610) may include a first inner body (611), a second inner body (613), an upper inner body (615), and a lower inner body (617), and the outer part (620) may include a first outer body (621), a second outer body (623), and an upper outer body (625).

[0155] The first inner body (611) extends in the vertical direction, and the second inner body (613) extends in the vertical direction and is positioned between a plurality of first inner bodies (611).

[0156] The upper inner body (615) connects the upper end of the adjacent first inner body (611) and the upper end of the second inner body (613), and is in contact with one of the plurality of refrigerant tubes.

[0157] The lower inner body (617) connects the lower end of the adjacent first inner body (611) and the lower end of the second inner body (613), and is in contact with another refrigerant tube among the plurality of refrigerant tubes.

[0158] The upper inner body (615) is positioned so as not to overlap with the lower inner body (617) in the vertical direction. The upper inner body (615) and the lower inner body (617) are arranged alternately along the left-right direction.

[0159] Of course, in other embodiments where the first inner body (611) and the second inner body (613) are inclined with respect to the vertical direction, the center of the upper inner body (615) is positioned so as not to overlap with the center of the lower inner body (617) in the vertical direction.

[0160]

[0161] The first outer body (621) extends in the vertical direction and is connected to the first inner body (611). The first outer body (621) is connected to the rear end of the first inner body (611).

[0162] The second outer body (623) extends in the vertical direction, is positioned between a plurality of first outer bodies (621), and is connected to the second inner body (613). The second outer body (623) is connected to the rear end of the second inner body (613).

[0163] The upper outer body (625) connects the upper end of the adjacent first outer body (621) and the upper end of the second outer body (623). The upper outer body (625) does not contact the refrigerant tube. The upper outer body (625) is connected to the upper inner body (615).

[0164]

[0165] The drop portion (630) can be connected to one of the other end of the first outer body (621) and the other end of the second outer body (623). Specifically, the drop portion (630) can be connected to one of the lower end of the first outer body (621) and the lower end of the second outer body (623). The drop portion (630) can be formed by cutting and bending a portion connected to the lower inner body (617).

[0166] The drop portion (630) may protrude downwardly from the lower end of the plurality of second outer bodies (623). In addition, the drop portion (630) may protrude downwardly from the lower end of the plurality of first outer bodies (621). Of course, the drop portion (630) according to the embodiment may be alternately arranged on the first outer body (621) and the second outer body (623).

[0167] The drop portion (630) can be positioned to overlap one of the first outer body (621) and the second outer body (623) in the vertical direction. The drop portion (630) can extend in a direction parallel to the first outer body (621) and the second outer body (623).

[0168] In FIG. 8, the drop portion (630) is illustrated as being connected to the bottom of all external bodies, but is not limited thereto.

[0169] The drop portion (630) of each heat dissipation fin (60) can be positioned so as to overlap or not overlap in the vertical direction with the first outer body (621) and the second outer body (623) of the adjacent other heat dissipation fin (60).

[0170] The drop portion (630) can define a surface that intersects the left and right directions.

[0171] Specifically, the drop portion (630) of the first heat dissipation fin (60) (61) can overlap with the second outer body (623) of the second heat dissipation fin (60) (62) in the vertical direction.

[0172] Water located in the space between the heat dissipation fins (60) (the space between the first body and the second body) spreads out horizontally due to surface tension and is driven downwards of the heat dissipation fins (60) due to gravity. The falling force of the water driven downwards from the inner part (610) is increased by the outer part (620) and the drop part (630), thereby allowing the water to be easily discharged, and by causing the water flowing into the inner part (610) from the outer part (620) to drop, external water is prevented from easily flowing in.

[0173]

[0174] Below, the structure of the louver (650) for reducing fluid pressure loss and improving heat exchange efficiency is described in detail.

[0175] Figure 9 is a cross-sectional view taken along line 9-9' of Figure 6.

[0176] Referring to Fig. 9, the fluid that exchanges heat with the heat dissipation fin (60) flows from the front to the rear.

[0177] The heat dissipation fin (60) includes a heat dissipation hole (660) formed by penetrating the heat dissipation plate (640) and a plurality of louvers (650) arranged in the heat dissipation hole (660) and having an incline with the heat dissipation plate (640).

[0178] A plurality of heat dissipation holes (660) may be arranged. For example, it is preferable that two heat dissipation holes (660) are formed in each heat dissipation fin (60). The two heat dissipation holes (660) may be arranged spaced apart from each other in the front-back direction. The heat dissipation holes (660) are formed by penetrating a portion of the inner portion (610).

[0179] The heat dissipation hole (660) includes a first heat dissipation hole (661) and a second heat dissipation hole (662) formed spaced apart from the first heat dissipation hole (661) in the first direction. The second heat dissipation hole (662) is located at the rear of the first heat dissipation hole (661).

[0180] A plurality of louvers (650) may be arranged in the heat dissipation hole (660) and may have an incline with the heat dissipation plate (640). Specifically, the louvers (650) may be formed by bending a portion of the first body (611, 621) and the second body (613, 623).

[0181] Each louver (650) has an incline in the forward-backward direction, which is the direction of air flow, and can define a surface that intersects the left-right direction. Through this incline of the louver (650), the fluid flowing between the heat sinks (640) reduces air pressure loss and improves heat exchange efficiency.

[0182] The plurality of louvers (650) include a first louver (651) having a heat sink (640) and a first inclination angle (A1), and a second louver (652) having a heat sink (640) and a second inclination angle (A2) and positioned further from the inlet side where the fluid flows than the first louver (651). The first louver (651) is positioned forward of the second louver (652).

[0183] The first inclination angle (A1) may be greater than the second inclination angle (A2). Specifically, the first inclination angle (A1) may be 41% to 48% greater than the second inclination angle (A2).

[0184] Preferably, the first inclination angle (A1) may be in the range of 33° to 37°, and the second inclination angle (A2) may be in the range of 22° to 26°. If the first inclination angle (A1) is greater than 37°, the flow of the fluid may be hindered due to the large inclination angle, and if the first inclination angle (A1) is less than 33°, the effect of reducing pressure loss may be reduced.

[0185] The number of first louvers (651) may be smaller than the number of second louvers (652). Specifically, the number of first louvers (651) may be 10% to 20% of the number of second louvers (652).

[0186] Preferably, the number of first louvers (651) may be 1, and the number of second louvers (652) may be 6 to 7. This is because if the number of first louvers (651) is too large, the flow of fluid may be hindered due to the large inclination angle.

[0187] The area where the first louver (651) is formed may be smaller than the area where the second louver (652) is formed. Here, the area where the louver (650) is formed means the area where the louver (650) is formed in the heat sink (640) when viewed from the right side.

[0188] The length of the first louver (651) and the length of the second louver (652) may be the same. The upward length of the first louver (651) and the upward and downward length of the second louver (652) are the same.

[0189] The first louver (651) and the second louver (652) can extend in a second direction that intersects the first direction. That is, the first louver (651) and the second louver (652) extend in the upward direction, so that the upward direction is the length direction and the front-back direction is the width direction.

[0190] The width (W21) of the first louver (651) may be smaller than the width (W31) of the second louver (652). For example, the width (W21) of the first louver (651) may be 40% to 60% of the width (W31) of the second louver (652).

[0191] The front end of the first louver (651) is connected to the heat sink (640), and the rear end of the first louver (651) may be a free end. The left and right ends of the first louver (651) are connected to the heat sink (640).

[0192] The front and rear ends of the second louver (652) are connected to the heat sink (640), and the left and right ends of the second louver (652) are connected to the heat sink (640).

[0193] The heat sink (640) may further include an inlet portion (641) connected to one end of the first louver (651) and positioned closer to the inlet side where the fluid flows in than the first louver (651). The inlet portion (641) may be the front end of the first body (611) and the second body (613). The inlet portion (641) may be connected to the front end of the first louver (651). The inlet portion (641) may extend parallel to the front-rear direction.

[0194] The width (W11) of the inlet (641) may be 90% to 120% of the width (W31) of the second louver (652).

[0195]

[0196] A plurality of louvers (650) can be arranged in the first heat dissipation hole (661) and the second heat dissipation hole (662).

[0197] The plurality of louvers (650) include a front louver group (651, 652) arranged in the first heat dissipation hole (661) and a rear louver group (653, 654) arranged in the second heat dissipation hole (662).

[0198] The front louver group (651, 652) may include a first louver (651) having a heat sink (640) and a first inclination angle (A1), and a second louver (652) having a heat sink (640) and a second inclination angle (A2) and positioned further from the inlet side where the fluid flows in than the first louver (651). In this case, the first inclination angle (A1) may be greater than the second inclination angle (A2).

[0199] The rear louver group (653, 654) includes a third louver (653) having a heat sink (640) and a third inclination angle (A3), and a fourth louver (654) having a heat sink (640) and a fourth inclination angle (A4) and positioned further from the inlet side where the fluid flows than the fourth louver (654), and the third inclination angle (A3) may be greater than the fourth inclination angle (A4).

[0200] The number of the first louver (651) and the third louver (653) is 1, and the number of the third louver (653) and the fourth louver (654) may be plural.

[0201] Each louver (650) of the front louver group (651, 652) may have an inclination opposite to that of each louver (650) of the rear louver group (653, 654). Specifically, each louver (650) of the front louver group (651, 652) may have an inclination angle between the rear and the right side, and each louver (650) of the rear louver group (653, 654) may have an inclination angle between the rear and the left side.

[0202] The first slope angle (A1) may be equal to the third slope angle (A3), and the second slope angle (A2) may be equal to the fourth slope angle (A4).

[0203] The width (W21) of the first louver (651) and the width (W22) of the third louver (653) may be the same, and the width (W31) of the second louver (652) and the width (W32) of the fourth louver (654) may be the same.

[0204] The heat sink (640) may include a first inlet portion (641) positioned in front of the first heat dissipation hole (661) and a second inlet portion (642) positioned between the first heat dissipation hole (661) and the second heat dissipation hole (662). The width (W11) of the second inlet portion (642) may be greater than the width (W12) of the first inlet portion (641).

[0205] The rear end of the second inlet (642) can be connected to the front end of the third louver (653). The rear end of the third louver (653), which is located at the rearmost end among the third louvers (653), is connected to the outer portion (620).

[0206]

[0207] Fig. 10 is a drawing showing the velocity around the air louver (650) and fin according to a comparative example.

[0208] Referring to Fig. 10, in the comparative example, in the inner part of the dotted box (the part with 2-3 louvers (650) at the rear end of the inlet), the flow velocity distribution becomes uneven, which causes an increase in air pressure loss and a decrease in heat exchange efficiency.

[0209] FIG. 11 is a diagram showing the velocity of air around a louver (650) and fin according to one embodiment of the present disclosure.

[0210] Referring to FIG. 11, in the case of the embodiment, the velocity distribution becomes even around the first louver (650) due to the angle of the first louver (650) of each heat dissipation hole (660), which causes a reduction in air pressure loss and an increase in heat exchange efficiency.

[0211]

[0212] Fig. 12 is a perspective view of a heat dissipation fin (60A) according to another embodiment of the present disclosure.

[0213] Referring to FIG. 12, a heat dissipation fin (60A) according to another embodiment is different from the embodiment of FIG. 7 in that the outer portion and the drop portion of the heat dissipation fin (60) are omitted, and there are differences in the shapes of the upper body (615) and the lower body (617).

[0214] According to another embodiment, the heat dissipation fin (60) is positioned to completely overlap the refrigerant tube in the vertical direction.

[0215] According to another embodiment, the heat dissipation fin (60) may be formed such that the upper body (615) and the lower body (617) are round.

[0216]

[0217] Although the embodiments of the present disclosure have been described with reference to the attached drawings, the present disclosure is not limited to the embodiments described above, and can be manufactured in various different forms. Those skilled in the art to which the present disclosure pertains will understand that the present disclosure can be implemented in other specific forms without changing the technical spirit or essential characteristics of the present disclosure. Therefore, it should be understood that the embodiments described above are exemplary in all respects and not restrictive.

[0218]

[0219] [Explanation of symbols]

[0220] 10: Compressor 12: Expansion mechanism

[0221] 13: Indoor heat exchanger 14: Accumulator

[0222] 15: Outdoor fan 16: Indoor fan

[0223] 20: Outdoor heat exchanger 22: Inlet pipe

[0224] 50: refrigerant tube 60: heat sink fin

Claims

1. A heat sink extending in a first direction parallel to the flow direction of the fluid; A heat dissipation hole formed by penetrating the above heat dissipation plate; and A plurality of louvers are disposed in the above heat dissipation hole and have an incline with the heat dissipation plate, The above plurality of louvers are, A first louver having a first inclination angle with the above heat sink, It includes a second louver having the above heat sink and a second inclination angle and positioned further from the inlet side where the fluid flows in than the first louver, A heat exchanger fin having a first inclination angle greater than the second inclination angle.

2. In claim 1, A heat exchanger fin having the first inclination angle 41% to 48% greater than the second inclination angle.

3. In claim 1, The first inclination angle is in the range of 33° to 37°, A heat exchanger fin having a second inclination angle in the range of 22° to 26°.

4. In claim 1, A heat exchanger heat dissipation fin wherein the number of the first louvers is smaller than the number of the second louvers.

5. In claim 1, A heat exchanger heat dissipation fin in which the number of the first louvers is 10% to 20% of the number of the second louvers.

6. In claim 1, A heat exchanger heat dissipation fin in which the area where the first louver is formed is smaller than the area where the second louver is formed.

7. In claim 1, A heat exchanger heat dissipation fin having the same length as the first louver and the second louver.

8. In claim 1, A heat exchanger heat dissipation fin in which the first louver and the second louver extend in a second direction intersecting the first direction.

9. In claim 1, A heat exchanger heat dissipation fin having a width of the first louver smaller than the width of the second louver.

10. In claim 1 or 9, The above heat sink, A heat exchanger radiating fin further comprising an inlet portion connected to one end of the first louver and positioned adjacent to the inlet side through which fluid flows rather than the first louver.

11. In claim 10, A heat exchanger heat dissipation fin having a width of the above inlet portion of 90% to 120% of the width of the second louver.

12. A heat sink extending in a first direction parallel to the flow direction of the fluid; A first heat dissipation hole formed by penetrating the heat dissipation plate and a second heat dissipation hole formed spaced apart from the first heat dissipation hole in the first direction; and It includes a plurality of louvers arranged in the first heat dissipation hole and the second heat dissipation hole and having an incline with the heat dissipation plate, The above plurality of louvers are, A front louver group arranged in the first heat dissipation hole, Including a rear louver group arranged in the second heat dissipation hole, The above front louver group is, A first louver having a first inclination angle with the above heat sink, It includes second louvers having the above heat sink and the second inclination angle and positioned further from the inlet side where the fluid flows in than the first louver, A heat exchanger fin having a first inclination angle greater than the second inclination angle.

13. In claim 12, The above rear louver group is, A third louver having a third inclination angle with the above heat sink, It includes a fourth louver having a fourth inclination angle and positioned further from the inlet side where the fluid flows in than the fourth louver, and A heat exchanger fin having a third inclination angle greater than the fourth inclination angle.

14. In claim 12, The number of the first louver and the third louver is 1, A heat exchanger heat dissipation fin having a plurality of the third louvers and the fourth louvers.

15. In claim 12, The above first slope angle is the same as the above third slope angle, A heat exchanger fin having the second inclination angle and the fourth inclination angle.

16. A plurality of refrigerant tubes arranged spaced apart from each other; and Connecting the adjacent refrigerant tubes and including a plurality of heat dissipation fins for conducting heat, The above heat dissipation fins are, A heat sink extending in a first direction parallel to the flow direction of the fluid; A heat dissipation hole formed by penetrating the above heat dissipation plate; and A plurality of louvers are disposed in the above heat dissipation hole and have an incline with the heat dissipation plate, The above plurality of louvers are, A first louver having a first inclination angle with the above heat sink, It includes a second louver having the above heat sink and a second inclination angle and positioned further from the inlet side where the fluid flows in than the first louver, A heat exchanger wherein the first inclination angle is greater than the second inclination angle.

17. In claim 16, Each of the above heat dissipation fins, An inner portion positioned to overlap the refrigerant tubes in a second direction intersecting the first direction; and A heat exchanger comprising an outer portion that is not positioned to overlap the refrigerant tubes in the second direction.

18. In claim 17, A heat exchanger in which the above heat dissipation hole and the above plurality of louvers are formed in the inner part.

19. In claim 17, A heat exchanger in which the inner portion is positioned closer to the inlet side where the fluid flows in than the outer portion.

20. In claim 16, The above heat dissipation fins are, A plurality of first bodies extending in the first direction; A plurality of second bodies extending in the first direction and positioned between the plurality of first bodies; An upper body connecting one end of the first body and one end of the second body adjacent to each other and in contact with one of the plurality of refrigerant tubes; and A lower body is included that connects the other end of the first body and the other end of the second body, which are adjacent to each other, and is in contact with another refrigerant tube among the plurality of refrigerant tubes, A heat exchanger in which the above heat dissipation hole and the above louver are formed in the first bodies and the second bodies.

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