Heat exchanger and air conditioning device

Abstract

The heat exchanger includes a plurality of flat heat transfer tubes extending in the vertical direction and arranged in parallel to each other, and a corrugated fin arranged between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes, the corrugated fin having a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, and a louver is formed in the flat portion, the louver has louver slits and a plate portion inclined with respect to the flat portion, and a drainage slit is formed in the flat portion for draining condensation water, and at least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, and in a direction perpendicular to the flat portion, a protruding height of the inclined portion from the flat portion is lower than a protruding height of the plate portion from the flat portion.

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger and an air conditioner including the same. [Background technology]

[0002] Patent Document 1 discloses a corrugated fin for an evaporator. The flat surface of the corrugated fin is provided with a plurality of louvers and drainage holes for draining condensed water. The drainage holes are formed by bending downward notched pieces of the corrugated fin. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Utility Model Application Publication No. 56-78966 Summary of the Invention [Problem to be solved by the invention]

[0004] However, the corrugated fins described above have a problem in that the cutout pieces protrude into the air flow path, which can increase ventilation resistance.

[0005] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a heat exchanger and an air conditioning apparatus that can improve drainage performance while suppressing an increase in ventilation resistance. [Means for solving the problem]

[0006] A heat exchanger according to the present disclosure includes a plurality of flat heat transfer tubes extending in a vertical direction and arranged in parallel to one another, and a corrugated fin arranged between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes, the corrugated fin having a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, a louver is formed in the flat portion, the louver has louver slits and a plate portion inclined with respect to the flat portion, a drainage slit is formed in the flat portion for draining condensation water, at least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, and a protruding height of the inclined portion from the flat portion in a direction perpendicular to the flat portion is lower than a protruding height of the plate portion from the flat portion. The inclined portions are provided at least on two edge portions facing each other around the drainage slit, and the inclined portions provided on the two edge portions protrude in the same direction in the up-down direction. .

[0007] An air conditioning apparatus according to the present disclosure includes a heat exchanger according to the present disclosure. Effect of the Invention

[0008] According to the present disclosure, it is possible to improve the drainage performance of a heat exchanger while suppressing an increase in ventilation resistance. [Brief description of the drawings]

[0009] [Figure 1] FIG. 1 is a diagram showing a schematic configuration of a heat exchanger according to a first embodiment. [Diagram 2] 1 is a perspective view showing a schematic configuration of a heat exchanger according to a first embodiment. [Diagram 3] 2 is a diagram showing a schematic cross section of a corrugated fin in the heat exchanger according to the first embodiment. FIG. [Figure 4] 4 is a cross-sectional view showing a configuration of a drain slit in the heat exchanger according to the first embodiment. FIG. [Diagram 5] 4 is a cross-sectional view showing a configuration of a drain slit in the heat exchanger according to the first embodiment. FIG. [Figure 6] 1 is a diagram showing the configuration of an air conditioning apparatus according to a first embodiment. [Figure 7] 5 is a graph showing the relationship between the protruding height of a plate portion from a flat portion in a direction perpendicular to the flat portion of the heat exchanger according to the first embodiment and ventilation resistance. [Figure 8] 5A and 5B are diagrams illustrating examples of protruding directions of inclined portions in the heat exchanger according to the first embodiment. [Figure 9] 6A and 6B are diagrams illustrating other examples of the protruding direction of the inclined portions in the heat exchanger according to the first embodiment. [Figure 10] FIG. 11 is a top view showing the configuration of a flat portion in a heat exchanger according to a second embodiment. [Figure 11] FIG. 11 is a top view showing the configuration of a flat portion in a heat exchanger according to a second embodiment. [Figure 12] FIG. 11 is a top view showing the configuration of a flat portion in a heat exchanger according to a second embodiment. [Figure 13] FIG. 13 is a schematic diagram showing a cross section taken along line XIII-XIII in FIG. 12. [Figure 14] 11 is a diagram showing a schematic cross section of a corrugated fin in a heat exchanger according to a third embodiment. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] Hereinafter, the embodiments of the present disclosure will be described with reference to the drawings. The present disclosure is not limited to the following embodiments, and can be modified in various ways without departing from the spirit of the present disclosure. The present disclosure includes all combinations of the configurations shown in the following embodiments that can be combined. In particular, the combination of components is not limited to the combinations in each embodiment, and the components described in one embodiment can be applied to another embodiment. In the following description, terms indicating directions (e.g., "upper", "lower", "right", "left", "front", "rear", etc.) are used as appropriate to facilitate understanding, but these are for explanation and do not limit the present disclosure. In each drawing, the same reference numerals are assigned to the same or equivalent parts, and this is common throughout the entire specification. In each drawing, the relative dimensional relationship or shape of each component may differ from the actual one.

[0011] Embodiment 1 A heat exchanger and an air conditioner according to a first embodiment will be described. Fig. 1 is a diagram showing a schematic configuration of a heat exchanger according to the present embodiment. As shown in Fig. 1, a heat exchanger 10 according to the present embodiment is a corrugated fin tube type heat exchanger of a parallel piping type. The heat exchanger 10 has a plurality of flat heat transfer tubes 1, a plurality of corrugated fins 2, and a pair of headers 3A, 3B.

[0012] Here, in order to clarify the correspondence between the drawings including FIG. 1, the following coordinate system is defined. The Z axis is taken along the extension direction of the flat heat transfer tubes 1, and the upward direction is the +Z direction. In this embodiment, the Z axis is parallel to the vertical up-down direction. The X axis is taken along the air flow direction, and the downstream side in the air flow is the +X direction. The Y axis is taken along the parallel direction of the flat heat transfer tubes 1, and one of the directions along the Y axis is the +Y direction. In this embodiment, the XY plane including the X axis and the Y axis is a horizontal plane perpendicular to the Z axis.

[0013] Since the heat exchanger 10 of this embodiment is of a vertical flow type, the headers 3A and 3B are arranged vertically apart from each other. Each of the headers 3A and 3B is connected to other devices constituting the refrigerant circuit of the air conditioner via piping, and is configured to split or merge the refrigerant. Liquid refrigerant mainly flows through the header 3A arranged at the bottom. Gas refrigerant mainly flows through the header 3B arranged at the top.

[0014] The flat heat transfer tubes 1 extend in the vertical direction. One end of each of the flat heat transfer tubes 1 is connected to one header 3A. The other end of each of the flat heat transfer tubes 1 is connected to the other header 3B. The flat heat transfer tubes 1 are arranged in parallel to each other with intervals between them. Each of the flat heat transfer tubes 1 extends perpendicular to the extension direction of the headers 3A and 3B.

[0015] The flat heat transfer tube 1 has a flat cross-sectional shape. The longitudinal direction of the cross section of the flat heat transfer tube 1 is aligned with the air flow direction. The outer surface on the longitudinal side of the cross section of the flat heat transfer tube 1 is flat, and the outer surface on the lateral side is curved. The flat heat transfer tube 1 is a multi-hole flat heat transfer tube having a plurality of holes that serve as a flow path for the refrigerant. The flat heat transfer tubes 1 are arranged at equal intervals in the horizontal direction with the outer surfaces on the longitudinal sides facing each other. When manufacturing the heat exchanger 10 of the first embodiment, the flat heat transfer tubes 1 are inserted into insertion holes (not shown) of the headers 3A and 3B and joined by brazing.

[0016] When the heat exchanger 10 is used as a condenser, a high-temperature, high-pressure refrigerant flows through the refrigerant passage in the flat heat transfer tube 1. When the heat exchanger 10 is used as an evaporator, a low-temperature, low-pressure refrigerant flows through the refrigerant passage in the flat heat transfer tube 1. The refrigerant flows into one of the headers 3A and 3B through a pipe (not shown) that supplies the refrigerant from an external device (not shown) to the heat exchanger 10. The refrigerant that flows into one of the headers is distributed and passes through each of the flat heat transfer tubes 1. The flat heat transfer tube 1 exchanges heat between the refrigerant passing through the inside of the tube and the air passing outside the tube. When the temperature of the refrigerant is higher than the temperature of the air, the refrigerant releases its own heat to the air. When the temperature of the refrigerant is lower than the temperature of the air, the refrigerant absorbs heat from the air. The refrigerant that has passed through the flat heat transfer tube 1 and exchanged heat flows into the other of the headers 3A and 3B and merges. Then, the refrigerant flows back to the external device (not shown) through a pipe (not shown) connected to the other header.

[0017] The corrugated fin 2 is disposed between two adjacent flat heat transfer tubes 1. The corrugated fin 2 is provided to increase the heat transfer area between the refrigerant and the air. The corrugated fin 2 is formed by corrugating a plate material and folding it in a zigzag pattern with repeated mountain and valley folds, forming an accordion-like waveform. The folded portions of the corrugated fin 2 become the apexes of the corrugated fin 2.

[0018] FIG. 2 is a perspective view showing a schematic configuration of a heat exchanger according to the present embodiment. As shown in FIG. 2, the corrugated fin 2 has a first apex 2a on one side, a second apex 2b on the other side, a flat portion 2c, and a flat portion 2d. The first apex 2a is in surface contact with one of the flat heat transfer tubes 1. The second apex 2b is in surface contact with the other flat heat transfer tube 1. The contact portion between the corrugated fin 2 and the flat heat transfer tube 1 is joined by brazing. The corrugated fin 2 is formed, for example, using a clad material in which a brazing material layer is formed on both sides of a plate material made of an aluminum alloy. The brazing material layer is formed, for example, from an aluminum-silicon-based brazing material containing aluminum. The plate thickness of the corrugated fin 2 is about 50 μm to 200 μm.

[0019] The flat portion 2c and the flat portion 2d are formed between the first apex 2a and the second apex 2b. The flat portion 2c and the flat portion 2d are both formed in a flat plate shape. The flat portion 2c and the flat portion 2d are alternately arranged along the extension direction of the flat heat transfer tube 1. The flat portion 2c is inclined with respect to the horizontal plane so that the height of the first apex 2a side is higher than the height of the second apex 2b side. The flat portion 2d is inclined with respect to the horizontal plane so that the height of the second apex 2b side is higher than the height of the first apex 2a side. The flat portion 2c and the flat portion 2d have the same configuration except for the inclination direction. Below, the flat portion 2c will be mainly described as an example.

[0020] FIG. 3 is a schematic diagram showing a cross section of a corrugated fin in a heat exchanger according to the present embodiment. FIG. 3 shows a cross section of a flat portion 2c of a corrugated fin 2 cut along a plane parallel to the X-axis and perpendicular to the flat portion 2c. The up-down direction in FIG. 3 does not represent the Z-axis, but represents a direction perpendicular to the flat portion 2c. The left side of FIG. 3 represents the upstream side in the air flow. Note that FIG. 3 is a diagram mainly showing the positional relationship between the louver 22 and the drainage slit 23, and the inclination direction of the plate portion 22b of the louver 22. For this reason, the configuration of the flat portion 2c shown in FIG. 3 does not necessarily match the configuration of the flat portion 2c shown in FIG. 2.

[0021] As shown in Fig. 3, a plurality of louver groups 21 are formed on the flat portion 2c. The plurality of louver groups 21 are arranged in parallel along the air flow direction. Each of the louver groups 21 is made up of a plurality of louvers 22. The plurality of louvers 22 are arranged in parallel along the air flow direction.

[0022] Each louver 22 has a louver slit 22a that allows air to pass through and a plate portion 22b that guides the air to the louver slit 22a. The plate portion 22b is inclined obliquely with respect to the flat portion 2c. In a plurality of louvers 22 included in the same louver group 21, the plate portion 22b is inclined in the same direction. In the example shown in FIG. 3, the plate portion 22b is inclined in the same direction even in a plurality of louvers 22 included in different louver groups 21. The plate portion 22b of each louver 22 shown in FIG. 3 is inclined so that the height decreases from the windward side to the leeward side. Each louver 22 is formed by cutting and raising the plate portion 22b from the flat portion 2c. In this embodiment, each plate portion 22b is composed of an upper plate portion cut and raised upward from the flat portion 2c and a lower plate portion cut and raised downward from the flat portion 2c.

[0023] In the flat portion 2c, between two adjacent louver groups 21, a drainage slit 23 is formed to allow condensed water to pass and drain downward. The drainage slit 23 is formed in a rectangular shape in a plan view. The short side of the drainage slit 23 is aligned with the air flow direction. The long side of the drainage slit 23 is aligned with the parallel arrangement direction of the flat heat transfer tubes 1.

[0024] Figures 4 and 5 are cross-sectional views showing the configuration of the drainage slits in the heat exchanger according to this embodiment. Figure 4 shows a cross section of the flat portion 2c of the corrugated fin 2 cut perpendicular to the X-axis, i.e., a cross section of the flat portion 2c cut along the long side of the drainage slit 23. Figure 5 shows a cross section of the flat portion 2c of the corrugated fin 2 cut along a plane parallel to the X-axis and perpendicular to the flat portion 2c, i.e., a cross section of the flat portion 2c cut along the short side of the drainage slit 23. The up-down direction in Figures 4 and 5 does not represent the Z-axis, but represents the direction perpendicular to the flat portion 2c.

[0025] As shown in Figures 4 and 5, the flat portion 2c has edges 2c1, 2c2, 2c3, and 2c4 located around the drainage slit 23. The edges 2c1 and 2c2 are along the short sides of the drainage slit 23. The edges 2c1 and 2c2 face each other across the drainage slit 23. The edges 2c3 and 2c4 are along the long sides of the drainage slit 23. The edges 2c3 and 2c4 face each other across the drainage slit 23.

[0026] At least one edge around the drainage slit 23 is provided with an inclined portion. In this embodiment, the inclined portions 24a, 24b, 24c, and 24d are formed on all edges 2c1, 2c2, 2c3, and 2c4 of the drainage slit 23, respectively. The inclined portions may be provided only on the edges 2c1 and 2c2 along the short sides of the drainage slit 23. When the inclined portions are provided only on the edges 2c1 and 2c2 along the short sides of the drainage slit 23, each inclined portion is aligned with the air flow direction, so that an increase in ventilation resistance can be suppressed.

[0027] The inclined portions 24a, 24b, 24c, and 24d are all formed in a plate shape. The inclined portions 24a, 24b, 24c, and 24d may be connected in an elliptical shape so as to surround the entire circumference of the drainage slit 23. The inclined portions 24a, 24b, 24c, and 24d are all inclined with respect to the flat portion 2c. In this embodiment, the inclination angle of the inclined portions 24a, 24b, 24c, and 24d with respect to the flat portion 2c is larger than the inclination angle of the flat portion 2c with respect to the horizontal plane, so that the inclined portions 24a, 24b, 24c, and 24d are also inclined with respect to the horizontal plane. The inclination angles of the inclined portions 24a, 24b, 24c, and 24d with respect to the flat portion 2c may be different from each other. The inclination angle may be 90°.

[0028] The inclined portion 24a protrudes downward from the edge portion 2c1 toward the drainage slit 23. A bent portion 25a is formed between the inclined portion 24a and the edge portion 2c1. The bent portion 25a is curved so as to be convex toward the drainage slit 23. The inclination angle of the inclined portion 24a with respect to the flat portion 2c is θ1.

[0029] The inclined portion 24b protrudes downward from the edge portion 2c2 toward the drainage slit 23. A bent portion 25b is formed between the inclined portion 24b and the edge portion 2c2. The bent portion 25b is curved so as to be convex toward the drainage slit 23.

[0030] The inclined portion 24c protrudes downward from the edge portion 2c3 toward the drainage slit 23. A bent portion 25c is formed between the inclined portion 24c and the edge portion 2c3. The bent portion 25c is curved so as to be convex toward the drainage slit 23. The inclination angle of the inclined portion 24c with respect to the flat portion 2c is θ2. The inclination angle θ2 is smaller than the inclination angle θ1 (θ2<θ1).

[0031] The inclined portion 24d protrudes downward from the edge portion 2c4 toward the drainage slit 23. A bent portion 25d is formed between the inclined portion 24d and the edge portion 2c4. The bent portion 25d is curved so as to be convex toward the drainage slit 23.

[0032] In a direction perpendicular to the flat portion 2c, i.e., in the vertical direction in FIG. 3, the protruding height of each of the inclined portions 24a, 24b, 24c, and 24d from the flat portion 2c is defined as h. The protruding height h is the distance between the tip of each inclined portion and the center of the flat portion 2c in the thickness direction. Since each inclined portion protrudes from the flat portion 2c, the protruding height h is greater than 0. In a direction perpendicular to the flat portion 2c, i.e., in the vertical direction in FIG. 3, the protruding height of the plate portion 22b from the flat portion 2c is defined as H. The protruding height H is, for example, the distance between the tip of the plate portion 22b in the same direction as the protruding direction of the inclined portion and the center of the flat portion 2c in the thickness direction. The multiple plate portions 22b may be formed with a constant protruding height, or may be formed with a protruding height that varies irregularly. When the protruding heights of the multiple plate portions 22b formed on one flat portion 2c are not constant, the average value of the protruding heights of the plate portions 22b is defined as H. In this case, the protruding height h is lower than the protruding height H (h <H)。

[0033] 6 is a diagram showing the configuration of an air-conditioning apparatus according to this embodiment. In this embodiment, the above-mentioned heat exchanger 10 is used as the indoor heat exchanger 110. However, the above-mentioned heat exchanger 10 may be used as the outdoor heat exchanger 230, or may be used as both the indoor heat exchanger 110 and the outdoor heat exchanger 230.

[0034] As shown in Fig. 6, the air conditioner has an outdoor unit 200 and an indoor unit 100. The outdoor unit 200 and the indoor unit 100 are connected by a gas refrigerant piping 300 and a liquid refrigerant piping 400. The outdoor unit 200 has a compressor 210, a four-way valve 220, an outdoor heat exchanger 230, and an outdoor fan 240. The indoor unit 100 has an indoor heat exchanger 110, a pressure reducer 120, and an indoor fan 130.

[0035] The compressor 210 compresses the sucked 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 four-way valve 220 is a valve that switches the flow of the refrigerant depending on, for example, whether the operation is cooling or heating.

[0036] The outdoor heat exchanger 230 exchanges heat between the refrigerant and the 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 supplies outdoor air to the outdoor heat exchanger 230, promoting heat exchange in the outdoor heat exchanger 230.

[0037] The indoor heat exchanger 110 exchanges heat between the refrigerant and the indoor air, which is the space to be air-conditioned. The indoor heat exchanger 110 functions as a condenser during heating operation, condensing and liquefying the refrigerant. The indoor heat exchanger 110 functions as an evaporator during cooling operation, evaporating and vaporizing the refrigerant. The indoor fan 130 supplies indoor air to the indoor heat exchanger 110, and supplies the air that has passed through the indoor heat exchanger 110 to the room.

[0038] The pressure reducer 120 reduces the pressure of the refrigerant to expand it. An electronic expansion valve, a temperature-sensitive expansion valve, a throttling device, or the like is used as the pressure reducer 120. When an electronic expansion valve is used as the pressure reducer 120, the pressure reducer 120 adjusts the opening degree based on an instruction from a control device (not shown) or the like.

[0039] Next, the operation of each device of the air conditioner will be described based on the flow of the refrigerant. First, the operation of each device of the refrigerant circuit in heating operation will be described based on the flow of the refrigerant. The high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 210 passes through the four-way valve 220 and flows into the indoor heat exchanger 110. The gas refrigerant passing through the indoor heat exchanger 110 condenses and liquefies by exchanging heat with the indoor air. The liquefied refrigerant passes through the pressure reducer 120 and is reduced in pressure, becoming a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state passes through the outdoor heat exchanger 230. The refrigerant passing through the outdoor heat exchanger 230 evaporates and gasifies by exchanging heat with the outdoor air supplied by the outdoor fan 240. The gasified refrigerant passes through the four-way valve 220 and is sucked into the compressor 210 again. The refrigerant circulates as described above, thereby performing the heating operation of the air conditioner.

[0040] Next, the cooling operation will be described. The high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 210 passes through the four-way valve 220 and flows into the outdoor heat exchanger 230. The gas refrigerant passing through the outdoor heat exchanger 230 is condensed and liquefied by heat exchange with outdoor air supplied by the outdoor fan 240. The liquefied refrigerant is reduced in pressure by passing through the pressure reducer 120 and becomes a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state passes through the indoor heat exchanger 110. The refrigerant passing through the indoor heat exchanger 110 is evaporated and gasified by heat exchange with indoor air supplied by the indoor fan 130. The gasified refrigerant passes through the four-way valve 220 and is sucked into the compressor 210 again. The refrigerant circulates as described above, thereby performing the cooling operation of the air conditioner.

[0041] When the heat exchanger 10 functions as an evaporator, the temperature of the surfaces of the flat heat transfer tubes 1 and the corrugated fins 2 becomes lower than the temperature of the air passing through the heat exchanger 10. Therefore, moisture in the air condenses on the surfaces of the flat heat transfer tubes 1 and the corrugated fins 2. As a result, condensed water is generated on the surfaces of the flat heat transfer tubes 1 and the corrugated fins 2.

[0042] Condensation water generated on the surface of the corrugated fin 2 may accumulate on the flat portion 2c around the drainage slit 23. However, in this embodiment, the peripheral edge of the drainage slit 23 is provided with downwardly protruding inclined portions 24a, 24b, 24c, and 24d. Therefore, the condensation water adhering to the flat portion 2c around the drainage slit 23 flows down along the inclined portions 24a, 24b, 24c, and 24d, and is easily drained from the drainage slit 23.

[0043] Therefore, according to this embodiment, it is possible to improve the drainage of condensation water when the heat exchanger 10 functions as an evaporator. Also, in this embodiment, the protruding height h of the inclined parts 24a, 24b, 24c, and 24d from the flat part 2c is lower than the protruding height H of the plate part 22b from the flat part 2c. This makes it possible to make the protruding height of the inclined parts 24a, 24b, 24c, and 24d from the flat part 2c smaller than the protruding height of the plate part 22b, so that it is possible to suppress an increase in ventilation resistance caused by providing the inclined parts 24a, 24b, 24c, and 24d.

[0044] 7 is a graph showing the relationship between the protruding height of the plate parts from the flat parts in a direction perpendicular to the flat parts of the heat exchanger according to this embodiment and the ventilation resistance. The vertical axis of the graph represents the ventilation resistance ΔP of the air passing through the corrugated fin 2 in the +X direction. The horizontal axis of the graph represents the protruding height h of the inclined parts 24a, 24b, 24c, and 24d from the flat part 2c in a direction perpendicular to the flat part 2c in relation to the above-mentioned protruding height H.

[0045] As shown in Fig. 7, when the protrusion height h is equal to or greater than H / 2 and less than H, the ventilation resistance ΔP is generally constant regardless of the protrusion height h. On the other hand, when the protrusion height h is less than H / 2, the ventilation resistance ΔP decreases as the protrusion height h decreases. Therefore, in order to more effectively suppress the increase in ventilation resistance caused by providing the inclined portions 24a, 24b, 24c, and 24d, it is desirable that the protrusion height h be lower than half of the protrusion height H (h < H / 2).

[0046] Fig. 8 is a view showing an example of the protruding direction of the inclined portion in the heat exchanger according to the present embodiment. As shown in Fig. 8, the flat portions 2c and 2d are adjacent to each other with a space therebetween in the direction along the extending direction of the flat heat transfer tube 1. The flat portions 2c and 2d are inclined in opposite directions with respect to the horizontal plane.

[0047] The inclined portions 24a and 24b formed on the flat portion 2c protrude upward from the flat portion 2c. Although not shown, the inclined portions 24c and 24d formed on the flat portion 2c also protrude upward from the flat portion 2c. On the other hand, the inclined portions 24a and 24b formed on the flat portion 2d protrude downward from the flat portion 2d. Although not shown, the inclined portions 24c and 24d formed on the flat portion 2d also protrude downward from the flat portion 2d. Thus, in the example shown in Fig. 8, in the adjacent flat portions 2c and 2d, the protruding directions of the inclined portions 24a, 24b, 24c, and 24d in the vertical direction are different.

[0048] When the inclined portions 24a, 24b, 24c, and 24d protrude downward as in the flat portion 2d, the condensed water adhering to the flat portion 2d flows down along the inclined portions 24a, 24b, 24c, and 24d, so that it is easily drained from the drain slit 23.

[0049] Even when the inclined portions 24a, 24b, 24c, and 24d protrude upward like the flat portion 2c, the condensed water adhering to the flat portion 2c tends to move in the vertical direction along the inclined portions 24a, 24b, 24c, and 24d due to surface tension. This prevents the condensed water from staying on the flat portion 2c, and promotes drainage from the drainage slits 23 or along the flat heat transfer tube 1. Therefore, each of the inclined portions 24a, 24b, 24c, and 24d has the function of promoting drainage of the condensed water, regardless of the protruding direction in the vertical direction.

[0050] Fig. 9 is a diagram showing another example of the protruding direction of the inclined portion in the heat exchanger according to the present embodiment. As shown in Fig. 9, the inclined portion 24a formed on the flat portion 2c protrudes downward from the flat portion 2c. The inclined portion 24b formed on the flat portion 2c protrudes upward from the flat portion 2c. Although not shown, the inclined portion 24c and the inclined portion 24d formed on the flat portion 2c protrude upward or downward from the flat portion 2c.

[0051] The inclined portion 24a formed on the flat portion 2d protrudes upward from the flat portion 2d. The inclined portion 24b formed on the flat portion 2d protrudes downward from the flat portion 2d. Although not shown, the inclined portion 24c and the inclined portion 24d formed on the flat portion 2d protrude upward or downward from the flat portion 2d. The configuration shown in FIG. 9 also provides the same effect as the configuration shown in FIG.

[0052] As described above, the heat exchanger 10 according to the present embodiment includes a plurality of flat heat transfer tubes 1 and a corrugated fin 2. Each of the flat heat transfer tubes 1 extends in the vertical direction. The flat heat transfer tubes 1 are arranged in parallel to one another. The corrugated fin 2 is arranged between two adjacent flat heat transfer tubes 1 among the flat heat transfer tubes 1. The corrugated fin 2 has a first apex 2a joined to one of the two flat heat transfer tubes 1, a second apex 2b joined to the other of the two flat heat transfer tubes 1, and a flat portion 2c formed between the first apex 2a and the second apex 2b.

[0053] A louver 22 is formed on the flat portion 2c. The louver 22 has a louver slit 22a and a plate portion 22b inclined with respect to the flat portion 2c. A drainage slit 23 for draining condensation water is formed on the flat portion 2c. At least one edge portion 2c1, 2c2, 2c3, 2c4 around the drainage slit 23 is provided with inclined portions 24a, 24b, 24c, 24d inclined with respect to the flat portion 2c. In a direction perpendicular to the flat portion 2c, the protruding height h of the inclined portions 24a, 24b, 24c, 24d from the flat portion 2c is lower than the protruding height H of the plate portion 22b from the flat portion 2c.

[0054] According to this configuration, as described above, the provision of the inclined portions 24a, 24b, 24c, and 24d can improve the drainage performance of the heat exchanger 10. In addition, the protrusion of the inclined portions 24a, 24b, 24c, and 24d from the flat portion 2c can be made smaller than the protrusion of the plate portion 22b, so that an increase in ventilation resistance due to the provision of the inclined portions 24a, 24b, 24c, and 24d can be suppressed.

[0055] In the heat exchanger 10 of this embodiment, in a direction perpendicular to the flat portion 2c, the protruding height h of the inclined portions 24a, 24b, 24c, and 24d from the flat portion 2c is less than half the protruding height H of the plate portion 22b from the flat portion 2c.

[0056] According to this configuration, it is possible to more effectively suppress an increase in ventilation resistance caused by providing the inclined portions 24a, 24b, 24c, and 24d.

[0057] In the heat exchanger 10 according to the present embodiment, the inclined portions 24a, 24b, 24c, and 24d are provided at least on two edges facing each other around the drainage slit 23. The inclined portions provided on the two edges protrude in the same vertical direction.

[0058] According to this configuration, the inclined portions can be easily formed on the corrugated fins 2.

[0059] In the heat exchanger 10 according to the present embodiment, the flat portion includes two flat portions 2c, 2d adjacent to each other in the up-down direction. The inclined portions provided on the two flat portions 2c, 2d protrude in opposite directions in the up-down direction.

[0060] According to this configuration, the inclined portions provided on the two flat portions 2c, 2d both protrude from one surface side of the plate material that constitutes the corrugated fin 2. Therefore, the inclined portions can be easily formed on the corrugated fin 2.

[0061] In the heat exchanger 10 according to the present embodiment, the inclined portions 24a, 24b, 24c, and 24d are provided around the entire circumference of the drain slit 23.

[0062] According to this configuration, accumulation of condensed water can be suppressed all around the drainage slit 23, so that the drainage performance of the heat exchanger 10 can be further improved.

[0063] In the heat exchanger 10 according to the present embodiment, the drain slit 23 has a long side along the parallel arrangement direction of the flat heat transfer tubes 1 and a short side along the air flow direction. The inclination angle θ1 of the inclined portion 24a provided along the short side with respect to the flat portion 2c is larger than the inclination angle θ2 of the inclined portion 24c provided along the long side with respect to the flat portion 2c.

[0064] According to this configuration, the inclination angle θ1 of the inclined portion 24a can be made large on the short side where the effect of surface tension is greater than on the long side, so that the drainage performance of the heat exchanger 10 can be further improved.

[0065] The air conditioner according to the present embodiment has the heat exchanger 10 according to the present embodiment. According to this configuration, the same effects as those described above can be obtained in the air conditioner.

[0066] Embodiment 2 A heat exchanger according to a second embodiment will be described. Figs. 10 to 12 are top views showing the configuration of a flat portion in a heat exchanger according to the present embodiment. Fig. 10 shows the configuration of a certain flat portion 2c. Fig. 11 shows, for example, the configuration of a flat portion 2d arranged adjacent to the flat portion 2c shown in Fig. 10. Fig. 12 shows, for example, the configuration of a flat portion 2c arranged adjacent to the flat portion 2d shown in Fig. 11. Fig. 13 is a schematic view of a cross section taken along line XIII-XIII in Fig. 12.

[0067] As shown in Figs. 10 to 13, the drainage slits 23 of two flat parts adjacent to each other in the vertical direction are formed at different positions in the parallel direction of the flat heat transfer tubes 1. That is, the drainage slit 23 of the flat part located at the lower of the two flat parts is not located directly below the drainage slit 23 of the flat part located at the upper side. Therefore, the condensation water flowing down from the upper drainage slit 23 can be merged with the condensation water remaining in the flat part around the lower drainage slit 23. Therefore, the retention of the condensation water can be suppressed, and the drainage performance of the heat exchanger 10 can be improved.

[0068] In this embodiment, the positions of the drainage slits 23 in the parallel direction of the flat heat transfer tubes 1 are periodically shifted along the extension direction of the flat heat transfer tubes 1. The drainage slits 23 shown in FIG. 10 are formed only in the flat portion 2c. The drainage slits 23 shown in FIG. 11 are formed across the flat portion 2d and the first apex 2a. The drainage slits 23 shown in FIGS. 12 and 13 are formed across the flat portion 2c, the second apex 2b, and the flat portion 2d. The drainage slits 23 shown in FIGS. 10, 11, and 12 appear periodically along the extension direction of the flat heat transfer tube 1.

[0069] Generally, in the inner parts of the first and second apexes 2a and 2b, the distance between the flat parts 2c and 2d is narrow, and condensation water is likely to accumulate due to surface tension. However, in this embodiment, the drainage slits 23 formed across the first and second apexes 2a and 2b appear periodically, and this makes it easier for condensation water accumulated in the inner parts of the first and second apexes 2a and 2b to be drained.

[0070] The other configurations are the same as those of embodiment 1. According to this embodiment, the drainage performance can be further improved compared to embodiment 1.

[0071] As described above, in the heat exchanger 10 according to the present embodiment, the flat portion includes two flat portions 2c, 2d adjacent to each other in the vertical direction. The drainage slits 23 of the two flat portions 2c, 2d are formed at different positions in the parallel arrangement direction of the flat heat transfer tubes 1. The flat portion also includes a plurality of flat portions 2c, 2d arranged in parallel in the vertical direction. The positions of the drainage slits 23 of the flat portions 2c, 2d are periodically shifted in the parallel arrangement direction of the flat heat transfer tubes 1.

[0072] According to this configuration, the condensation water flowing down from the upper drainage slits 23 can be merged with the condensation water accumulated on the flat portion around the lower drainage slits 23. In addition, since the drainage slits 23 formed across the first apex 2a or the second apex 2b appear periodically, the condensation water accumulated on the inner portions of the first apex 2a and the second apex 2b can be easily drained. Therefore, the accumulation of condensation water can be suppressed, and the drainage performance of the heat exchanger 10 can be improved.

[0073] Embodiment 3 A heat exchanger according to embodiment 3 will be described. Fig. 14 is a schematic diagram showing a cross section of a corrugated fin in a heat exchanger according to this embodiment. Fig. 14 shows a cross section corresponding to Fig. 3.

[0074] 14, drainage slit 23 is disposed between louver group 21-1 and louver group 21-2. Louver group 21-1 is disposed on the windward side of drainage slit 23. Louver group 21-2 is disposed on the leeward side of drainage slit 23. Hereinafter, each louver 22 included in louver group 21-1 may be referred to as a first louver, and each louver 22 included in louver group 21-2 may be referred to as a second louver.

[0075] Plate portion 22b of the first louver is inclined with respect to flat portion 2c so that its height decreases as it approaches drainage slit 23. Plate portion 22b of the second louver is similarly inclined with respect to flat portion 2c so that its height decreases as it approaches drainage slit 23. That is, plate portion 22b of the first louver and plate portion 22b of the second louver are inclined in opposite directions to each other.

[0076] The other configurations are the same as those of the embodiment 1. The present embodiment also has the same effects as those of the embodiment 1.

[0077] As described above, in the heat exchanger 10 according to the present embodiment, the louvers include a first louver and a second louver. The first louver is disposed on the windward side of the drainage slit 23. The second louver is disposed on the leeward side of the drainage slit 23. Both the plate portion 22b of the first louver and the plate portion 22b of the second louver are inclined with respect to the flat portion 2c so that the height decreases as they approach the drainage slit 23. [Explanation of symbols]

[0078] 1 flat heat transfer tube, 2 corrugated fin, 2a first apex, 2b second apex, 2c flat portion, 2c1, 2c2, 2c3, 2c4 edge portion, 2d flat portion, 3A, 3B header, 10 heat exchanger, 21, 21-1, 21-2 louver group, 22 louver, 22a louver slit, 22b plate portion, 23 drainage slit, 24a, 24b, 24c, 24d inclined portion, 25a, 25b, 25c, 25d bent portion, 100 indoor unit, 110 indoor heat exchanger, 120 pressure reducer, 130 indoor fan, 200 outdoor unit, 210 compressor, 220 four-way valve, 230 outdoor heat exchanger, 240 outdoor fan, 300 gas refrigerant piping, 400 liquid refrigerant piping.

Claims

1. a plurality of flat heat transfer tubes extending in the vertical direction and arranged in parallel with one another; a corrugated fin disposed between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes; Equipped with the corrugated fin has a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, A louver is formed on the flat portion, The louver has a louver slit and a plate portion inclined with respect to the flat portion, The flat portion is formed with a drainage slit for draining condensation water, At least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, a protruding height of the inclined portion from the flat portion in a direction perpendicular to the flat portion is smaller than a protruding height of the plate portion from the flat portion, The inclined portions are provided on at least two edge portions facing each other around the drainage slit, A heat exchanger in which the inclined portions provided on the two edge portions protrude in the same direction in the up-down direction.

2. a plurality of flat heat transfer tubes extending in the vertical direction and arranged in parallel with one another; a corrugated fin disposed between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes; Equipped with the corrugated fin has a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, A louver is formed on the flat portion, The louver has a louver slit and a plate portion inclined with respect to the flat portion, The flat portion is formed with a drainage slit for draining condensation water, At least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, a protruding height of the inclined portion from the flat portion in a direction perpendicular to the flat portion is smaller than a protruding height of the plate portion from the flat portion, the flat portion includes two flat portions adjacent to each other in the up-down direction, A heat exchanger in which the inclined portions provided on the two flat portions protrude in opposite directions in the up-down direction.

3. a plurality of flat heat transfer tubes extending in the vertical direction and arranged in parallel with one another; a corrugated fin disposed between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes; Equipped with the corrugated fin has a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, A louver is formed on the flat portion, The louver has a louver slit and a plate portion inclined with respect to the flat portion, The flat portion is formed with a drainage slit for draining condensation water, At least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, a protruding height of the inclined portion from the flat portion in a direction perpendicular to the flat portion is smaller than a protruding height of the plate portion from the flat portion, A heat exchanger, wherein the inclined portion is provided around the entire circumference of the drainage slit.

4. a plurality of flat heat transfer tubes extending in the vertical direction and arranged in parallel with one another; a corrugated fin disposed between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes; Equipped with the corrugated fin has a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, A louver is formed on the flat portion, The louver has a louver slit and a plate portion inclined with respect to the flat portion, The flat portion is formed with a drainage slit for draining condensation water, At least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, a protruding height of the inclined portion from the flat portion in a direction perpendicular to the flat portion is smaller than a protruding height of the plate portion from the flat portion, The drainage slit has a long side along a parallel arrangement direction of the flat heat transfer tubes and a short side along an air flow direction, A heat exchanger in which the inclination angle of the inclined portion provided along the short side relative to the flat portion is larger than the inclination angle of the inclined portion provided along the long side relative to the flat portion.

5. a plurality of flat heat transfer tubes extending in the vertical direction and arranged in parallel with one another; a corrugated fin disposed between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes; Equipped with the corrugated fin has a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, A louver is formed on the flat portion, The louver has a louver slit and a plate portion inclined with respect to the flat portion, The flat portion is formed with a drainage slit for draining condensation water, At least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, a protruding height of the inclined portion from the flat portion in a direction perpendicular to the flat portion is smaller than a protruding height of the plate portion from the flat portion, the flat portion includes two flat portions adjacent to each other in the up-down direction, The drainage slits in each of the two flat portions are formed at different positions in the parallel arrangement direction of the flat heat transfer tubes.

6. a plurality of flat heat transfer tubes extending in the vertical direction and arranged in parallel with one another; a corrugated fin disposed between two adjacent flat heat transfer tubes among the plurality of flat heat transfer tubes; Equipped with the corrugated fin has a first apex joined to one of the two flat heat transfer tubes, a second apex joined to the other of the two flat heat transfer tubes, and a flat portion formed between the first apex and the second apex, A louver is formed on the flat portion, The louver has a louver slit and a plate portion inclined with respect to the flat portion, The flat portion is formed with a drainage slit for draining condensation water, At least one edge portion around the drainage slit is provided with an inclined portion inclined with respect to the flat portion, a protruding height of the inclined portion from the flat portion in a direction perpendicular to the flat portion is smaller than a protruding height of the plate portion from the flat portion, The flat portion includes a plurality of flat portions arranged in parallel in the vertical direction, A heat exchanger in which the positions of the drainage slits in each of the flat portions are periodically shifted in the parallel direction of the flat heat transfer tubes.

7. A heat exchanger as described in any one of claims 1 to 6, wherein in a direction perpendicular to the flat portion, the protruding height of the inclined portion from the flat portion is less than half the protruding height of the plate portion from the flat portion.

8. The louvers include a first louver arranged on the windward side of the drainage slit and a second louver arranged on the leeward side of the drainage slit, A heat exchanger as described in any one of claims 1 to 6, wherein the plate portions of the first louver and the plate portions of the second louver are both inclined relative to the flat portion so that their height decreases as they approach the drainage slit.

9. An air conditioner comprising the heat exchanger according to any one of claims 1 to 6.

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