JP7592183B2 - Heat exchanger and refrigeration cycle device - Google Patents

Description

The present disclosure relates to a heat exchanger and a refrigeration cycle device equipped with the same.

In fin-tube heat exchangers, a technology is known that provides protrusions on the fin surface to control the direction of air flow in order to improve heat transfer performance.

For example, in the heat exchanger described in Patent Document 1, protrusions are provided around the heat transfer tubes to prevent separation of the airflow, reducing the dead water area behind the heat transfer tube and improving heat transfer performance. Here, the dead water area refers to an area into which air does not flow and into which the heat transfer coefficient decreases. In Patent Document 1, the airflow collides with the protrusions around the heat transfer tube, causing air to flow into the rear of the heat transfer tube, reducing the dead water area behind the heat transfer tube.

Japanese Unexamined Patent Publication No. 58-158496

In Patent Document 1, the protrusions are provided at angles of ±70° to ±80° from the stagnation point toward the center of the heat transfer tube, resulting in a state in which the protrusions are sparsely provided around the heat transfer tube. For this reason, in Patent Document 1, it is difficult to secure an area around the heat transfer tube in which to provide new protrusions to improve the strength of the fins. If it is not possible to provide new protrusions to improve the strength of the fins, there is an issue that the fins will bend in the longitudinal direction during processing. In addition, with the protrusions in Patent Document 1, the rate of expansion of the surface area of the fins is small, so there is an issue that the protrusions themselves do not sufficiently improve the heat transfer coefficient.

This disclosure has been made to solve such problems, and aims to provide a heat exchanger that improves the longitudinal strength of the fins and also improves the heat transfer coefficient, and a refrigeration cycle device equipped with the same.

The heat exchanger of the present disclosure comprises a plurality of fins arranged at intervals from one another in a first direction, and a plurality of heat transfer tubes penetrating the plurality of fins and arranged at intervals from one another in a second direction intersecting the first direction, each of the plurality of fins having a flat fin base surface and a plurality of fin protrusions, the plurality of fin protrusions being arranged to surround the respective periphery of the plurality of heat transfer tubes and having inner fin protrusions protruding from the fin base surface in the first direction, and outer fin protrusions being arranged to surround the respective periphery of the inner fin protrusions and protruding from the fin base surface in the same direction as the inner fin protrusions , the inner fin protrusions and the outer fin protrusions being adjacent to each other with no gaps .

The refrigeration cycle device of the present disclosure is equipped with the above-mentioned heat exchanger as a condenser or evaporator.

According to the heat exchanger of the present disclosure, an inner fin protrusion and an outer fin protrusion are provided around the heat transfer tube. The inner fin protrusion and the outer fin protrusion extend in the longitudinal direction of the fin to surround the heat transfer tube, improving the longitudinal strength of the fin. This reduces the longitudinal deflection of the fin that occurs during fin processing. In addition, the inner fin protrusion and the outer fin protrusion provided around the heat transfer tube increase the surface area of the fin base surface, improving the heat transfer coefficient on the surface of the fin 12. This improves the heat transfer performance of the heat exchanger.

1 is a perspective view showing a configuration of a heat exchanger 100 according to a first embodiment. FIG. 2 is a partial cross-sectional side view showing only the basic configuration of the heat exchanger 100 of FIG. 1. 1 is a refrigerant circuit diagram showing an example of the configuration of a refrigeration cycle device 1 according to a first embodiment. 2 is a partial cross-sectional side view showing the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. This is a cross-sectional view taken along line AA in FIG. This is a cross-sectional view taken along line B-B of FIG. 4 is a cross-sectional view showing a first modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. 10 is a partial cross-sectional side view showing a second modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. 11 is a partial cross-sectional side view showing a third modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. 11 is a partial cross-sectional side view showing a fourth modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. 11 is a partial cross-sectional side view showing a fifth modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. 13 is a partial cross-sectional side view showing a sixth modified example of the fins 12 of the heat exchanger 100 according to the first embodiment. FIG. 13 is a partial cross-sectional side view showing a seventh modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. This is a cross-sectional view taken along line AA in FIG. 13. 10 is a partial cross-sectional side view showing the fins 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view taken along line AA in FIG. 15. This is a cross-sectional view taken along the line CC of Figure 15. 11 is a cross-sectional view showing a first modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. 11 is a partial cross-sectional side view showing a second modified example of the fins 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view taken along line AA of Figure 19. 13 is a partial cross-sectional side view showing a third modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view of A-A in Figure 21. 13 is a partial cross-sectional side view showing a fourth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view of A-A in Figure 23. 13 is a partial cross-sectional side view showing a fifth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view taken along the line CC of Figure 25. 13 is a partial cross-sectional side view showing a sixth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view taken along the line CC of Figure 27. 13 is a partial cross-sectional side view showing a seventh modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view taken along the line CC of Figure 29. 13 is a partial cross-sectional side view showing an eighth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. This is a cross-sectional view taken along the line CC of Figure 31.

Below, an embodiment of a heat exchanger and a refrigeration cycle device including the same according to the present disclosure will be described with reference to the drawings. The present disclosure is not limited to the following embodiment, and various modifications are possible without departing from the spirit of the present disclosure. The present disclosure also includes all combinations of possible configurations among the configurations shown in the following embodiment and its modified examples. In each figure, the same reference numerals are used to denote the same or equivalent items, 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 ones.

Embodiment 1.
Hereinafter, a heat exchanger 100 according to a first embodiment and a refrigeration cycle apparatus 1 including the heat exchanger 100 will be described with reference to the drawings.

[Basic configuration of heat exchanger 100]
Fig. 1 is a perspective view showing a configuration of a heat exchanger 100 according to a first embodiment. The heat exchanger 100 is a fin-and-tube type heat exchanger. As shown in Fig. 1, the heat exchanger 100 includes a plurality of heat transfer tubes 11 and a plurality of fins 12. In the following description, when the terms "heat transfer tube 11" and "fin 12" are referred to, they are intended to include both the singular and plural.

As shown in FIG. 1, each of the fins 12 is a rectangular flat plate-shaped member. The fins 12 are arranged in parallel at regular intervals in the Y direction to form a space through which air flows. Hereinafter, the interval is referred to as the fin pitch. The fin pitch does not need to be constant and may be different. The fin pitch is the distance between the centers of adjacent fins 12 in the thickness direction. Air flows along the main surface of the fin 12 as shown by the arrow R1 in FIG. 1. The fin 12 is made of, for example, aluminum, but is not particularly limited to this. Hereinafter, the direction in which air flows as shown by the arrow R1 is referred to as the X direction (third direction). The longitudinal direction of the fin 12 is referred to as the Z direction (second direction). Furthermore, the stacking direction of the fins 12 is referred to as the Y direction (first direction). The X direction and the Z direction are mutually orthogonal. The X direction and the Y direction are mutually orthogonal. Furthermore, the Y direction and the Z direction are mutually orthogonal. The short-side direction of the fin 12 may be referred to as the X-direction (third direction). The Z-direction is, for example, the vertical direction. Here, if the X-direction is referred to as the row direction of the heat transfer tube 11 and the Z-direction is referred to as the row direction of the heat transfer tube 11, in the example of FIG. 1, the heat transfer tube 11 is in one row and 12 rows. The number of rows and the number of rows of the heat transfer tube 11 are not limited to this. For example, the heat transfer tube 11 may be arranged in two or more rows with respect to the fin 12. Note that FIG. 1 shows a case where the longitudinal direction of the heat transfer tube 11 extends in the Y-direction. The Y-direction is, for example, the horizontal direction. However, it is not limited to this case. That is, the longitudinal direction of the heat transfer tube 11 may extend in the vertical direction. In that case, the longitudinal direction of the fin 12 is horizontal.

As shown in FIG. 1, the heat transfer tubes 11 are arranged to penetrate the fins 12. Therefore, the longitudinal direction of the heat transfer tubes 11 is the Y direction. The heat transfer tubes 11 are arranged in parallel at regular intervals in the Z direction. Hereinafter, the intervals are referred to as the tube pitch. The tube pitch does not need to be constant and may be different. The tube pitch is the distance between the centers of adjacent heat transfer tubes 11 in the Z direction. As shown by the arrow R2 in FIG. 1, a refrigerant flows inside the heat transfer tubes 11. The ends of the heat transfer tubes 11 adjacent to each other in the Z direction are connected by a U-shaped tube 11a as shown in FIG. 1. As a result, the multiple heat transfer tubes 11 are connected to one another so that the refrigerant flows in sequence. The heat transfer tubes 11 do not have to be connected to one another. The heat transfer tubes 11 are made of a metal with high thermal conductivity, such as copper or a copper alloy, but are not particularly limited thereto.

Figure 2 is a partial side cross-sectional view showing only the basic configuration of the heat exchanger 100 in Figure 1. Figure 2 shows a cross section taken at one point in the Y direction. Specifically, Figure 2 shows the main surfaces of the fins 12 and a cross section of the heat transfer tubes 11. Each of the heat transfer tubes 11 is, for example, a circular tube or a flat tube. Figures 1 and 2 show the case where the heat transfer tubes 11 are circular tubes.

The heat exchanger 100 exchanges heat between the air flowing along the main surfaces of the fins 12 and the refrigerant flowing inside the heat transfer tube 11. The heat exchanger 100 is positioned so that the air flows in the X direction.

[Basic configuration of refrigeration cycle device 1]
The heat exchanger 100 shown in Fig. 1 is used, for example, in a refrigeration cycle apparatus 1. Fig. 3 is a refrigerant circuit diagram showing an example of the configuration of the refrigeration cycle apparatus 1 according to embodiment 1. As shown in Fig. 3, the refrigeration cycle apparatus 1 includes a heat source side unit 2 and a load side unit 3.

As shown in FIG. 3, the heat source side unit 2 and the load side unit 3 are connected to each other by refrigerant piping 8. The heat exchanger 100 can be used in both the heat source side unit 2 and the load side unit 3. In the following, the heat exchanger 100 arranged in the heat source side unit 2 is referred to as heat exchanger 100A, and the heat exchanger 100 arranged in the load side unit 3 is referred to as heat exchanger 100B.

As shown in Figure 3, the load side unit 3 includes a heat exchanger 100B, a blower 7B, a controller 9B, and a portion of the refrigerant piping 8. The blower 7B blows air to the heat exchanger 100B. The heat exchanger 100B exchanges heat between the refrigerant flowing through the heat transfer tube 11 and the air. The heat exchanger 100B functions as a condenser when the refrigeration cycle device 1 heats the load side unit 3 side, and functions as an evaporator when the refrigeration cycle device 1 cools the load side unit 3 side.

The blower 7B is, for example, a propeller fan. The blower 7B is composed of a fan motor 7a and a fan 7b. The fan 7b rotates using the fan motor 7a as a power source. The rotation speed of the blower 7B is controlled by the controller 9B.

3, the heat source unit 2 includes a heat exchanger 100A, a controller 9A, a compressor 4, a flow path switching device 5, an expansion valve 6, a blower 7A, and a portion of the refrigerant piping 8. The heat source unit 2 may further include other components such as an accumulator.

The heat exchanger 100A exchanges heat between the refrigerant flowing through the heat transfer tube 11 and the air. The heat exchanger 100A functions as an evaporator when the refrigeration cycle device 1 heats the load unit 3 side, and functions as a condenser when the refrigeration cycle device 1 cools the load unit 3 side.

The blower 7A blows air to the heat exchanger 100A. The blower 7A is, for example, a propeller fan. Like the blower 7B, the blower 7A is composed of a fan motor 7a and a fan 7b. The rotation speed of the blower 7A is controlled by the controller 9A.

The compressor 4 draws in low-pressure gas refrigerant, compresses it, and discharges it as high-pressure gas refrigerant. The compressor 4 is, for example, an inverter compressor. The inverter compressor can change the amount of refrigerant sent out per unit time by controlling an inverter circuit or the like. The inverter circuit is mounted, for example, on the controller 9A.

The flow path switching device 5 is a valve for switching the flow direction of the refrigerant in the refrigerant pipe 8. The flow path switching device 5 is, for example, a four-way valve. The flow path switching device 5 is switched between the cooling operation and the heating operation of the refrigeration cycle device 1 under the control of the controller 9A. When the refrigeration cycle device 1 cools the load side unit 3 side, the flow path switching device 5 is in the state shown by the solid line in FIG. 3. As a result, the refrigerant discharged from the compressor 4 flows into the heat exchanger 100A arranged in the heat source side unit 2. On the other hand, when the refrigeration cycle device 1 heats the load side unit 3 side, the flow path switching device 5 is in the state shown by the dashed line in FIG. 3. As a result, the refrigerant discharged from the compressor 4 flows into the heat exchanger 100B arranged in the load side unit 3.

The expansion valve 6 reduces the pressure of the liquid refrigerant that has been introduced by throttling it, allowing it to flow out so that the refrigerant liquefied in the condenser can easily evaporate in the evaporator. The expansion valve 6 also adjusts the amount of refrigerant to maintain an appropriate amount of refrigerant according to the load on the evaporator. The expansion valve 6 is, for example, an electronic expansion valve. The opening of the expansion valve 6 is controlled by a controller 9A. As shown in FIG. 3, the expansion valve 6 is connected between the heat exchanger 100A and the heat exchanger 100B by a refrigerant pipe 8.

As shown in Fig. 3, the refrigerant piping 8 connects the compressor 4, the flow switching device 5, the heat exchanger 100A, the expansion valve 6, and the heat exchanger 100B to form a refrigerant circuit. The refrigerant piping 8 is connected to the heat transfer tube 11 of the heat exchanger 100A and the heat transfer tube 11 of the heat exchanger 100B.

[Configuration of fin 12]
FIG. 4 is a partial cross-sectional side view showing the fin 12 of the heat exchanger 100 according to the first embodiment. FIG. 4 shows the main surface of the fin 12. FIG. 4 also shows a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. The heat transfer tube 11 shown in FIG. 4 is a circular tube, and the cross section has a circular shape. As shown in FIG. 4, the heat transfer tube 11 is arranged in a row along the Z direction. The fin 12 has a leading edge 12a and a trailing edge 12b. Since air flows in the direction of the arrow R1 in FIG. 4, the leading edge 12a is arranged on the windward side with respect to the trailing edge 12b. The heat transfer tube 11 is inserted into a through hole 12c formed in the fin 12. The outer diameter of the heat transfer tube 11 is equal to the inner diameter of the through hole 12c. Therefore, the heat transfer tube 11 is in close contact with the inner wall of the through hole 12c.

The main surface of the fin 12 constitutes a flat fin base surface 121. The fin base surface 121 is provided with a fin protrusion 122. The fin protrusion 122 protrudes in the Y direction from the fin base surface 121, which is the main surface of the fin 12. The fin protrusion 122 has an inner fin protrusion 122A provided to surround each of the heat transfer tubes 11. The fin protrusion 122 also has an outer fin protrusion 122B provided to surround each of the inner fin protrusions 122A. In the following description, when there is no need to particularly distinguish between the inner fin protrusion 122A and the outer fin protrusion 122B, they will simply be referred to as "fin protrusion 122". In addition, when the terms "fin protrusion 122", "inner fin protrusion 122A", and "outer fin protrusion 122B" are referred to, it is assumed that both the singular and plural are included.

In Fig. 4, the fin protrusions 122 are shown hatched to distinguish them from the fin base surface 121, but the fin protrusions 122 shown in Fig. 4 are not cross-sectional views. In Fig. 4, the outline and ridge lines of the fin protrusions 122 when the fin base surface 121 is viewed in the Y direction are shown in solid lines, and the portion sandwiched between the outline and ridge lines is shown hatched. This is common to Figs. 8 to 13, 15, 19, 21, 23, 25, 27, 29, and 31.

As shown in Figure 4, the fin protrusion 122 has a circular shape when the main surface of the fin 12 is viewed in the Y direction. The heat transfer tube 11, the inner fin protrusion 122A, and the outer fin protrusion 122B are arranged on a concentric circle. The diameter of the heat transfer tube 11, the diameter of the inner fin protrusion 122A, and the diameter of the outer fin protrusion 122B have the following relationship: diameter of heat transfer tube 11 < diameter of inner fin protrusion 122A < diameter of outer fin protrusion 122B.

The fin protrusion 122 will be described with reference to Figures 5 and 6. Figure 5 is a cross-sectional view taken along line A-A in Figure 4. Figure 6 is a cross-sectional view taken along line B-B in Figure 4. Note that the heat transfer tube is omitted from Figures 5 and 6. As shown in Figures 5 and 6, the edge of the through hole 12c may have a fin collar 12d. The fin collar 12d protrudes in the Y direction from the fin base surface 121, which is the main surface of the fin 12, and runs along the side of the heat transfer tube 11 (see Figure 4). In Figures 5 and 6, the protruding tip of the fin collar 12d has a bent portion, but it is not necessary for the tip to have a bent portion. The protruding portion of the fin collar 12d may be linear. Note that in Figures 5 and 6, the through hole 12c has a fin collar 12d, but the through hole 12c does not have to have a fin collar 12d.

5 and 6, a gap exists between the through hole 12c and the inner fin protrusion 122A. If the heat transfer tube 11 inserted into the through hole 12c and protruding from the fin base surface 121 is in contact with the inner fin protrusion 122A, stress will be concentrated at the boundary between the heat transfer tube 11 and the inner fin protrusion 122A when the fin 12 is formed. In this embodiment, by providing a gap between the heat transfer tube 11 and the inner fin protrusion 122A, stress concentration during the formation of the fin 12 is avoided.

In addition, the inner fin protrusion 122A and the outer fin protrusion 122B protrude in the same direction from the fin base surface 121 in the Y direction. A gap exists between the inner fin protrusion 122A and the outer fin protrusion 122B. This gap between the inner fin protrusion 122A and the outer fin protrusion 122B is called the first flat portion 121A. If the first flat portion 121A is not provided between the inner fin protrusion 122A and the outer fin protrusion 122B, stress will concentrate at the boundary between the inner fin protrusion 122A and the outer fin protrusion 122B during molding of the fin. By providing the first flat portion 121A, stress concentration during fin molding is avoided.

5 and 6, the cross sections of the inner fin protrusion 122A and the outer fin protrusion 122B have a triangular shape. However, the cross-sectional shapes of the inner fin protrusion 122A and the outer fin protrusion 122B do not have to be triangular. The cross-sectional shapes of the inner fin protrusion 122A and the outer fin protrusion 122B may be, for example, rectangular, polygonal, or circular.

Next, the height of the inner fin protrusion 122A and the height of the outer fin protrusion 122B will be described. The height at which the inner fin protrusion 122A protrudes from the fin base surface 121 is defined as h1, and the height at which the outer fin protrusion 122B protrudes from the fin base surface 121 is defined as h2. In this case, the height h1 of the inner fin protrusion 122A and the height h2 of the outer fin protrusion 122B may be equal as shown in Figures 5 and 6.

The heat exchanger 100 according to this embodiment includes a plurality of fins 12 arranged at intervals in a first direction Y, and a plurality of heat transfer tubes 11 that penetrate the plurality of fins 12 and are arranged at intervals in a second direction Z that intersects the first direction Y. Each of the plurality of fins 12 has a flat fin base surface 121 and a plurality of fin protrusions 122, and the plurality of fin protrusions 122 are provided to surround the periphery of each of the plurality of heat transfer tubes 11 and have inner fin protrusions 122A protruding from the fin base surface 121 in the first direction Y, and outer fin protrusions 122B protruding from the fin base surface 121 in the first direction Y, and are provided to surround the periphery of each of the inner fin protrusions 122A.

According to this configuration, the inner fin protrusion 122A and the outer fin protrusion 122B are arranged to surround the heat transfer tube 11. Therefore, the fin protrusion 122 has a portion extending in the second direction Z of the fin 12. In other words, the fin protrusion 122 having a portion along the longitudinal direction of the fin 12 is provided, thereby improving the longitudinal strength of the fin 12. Therefore, bending of the fin 12 in the longitudinal direction is suppressed during fin processing such as fin press and fin stack. Therefore, the productivity of the heat exchanger is improved.

In addition, since the inner fin protrusions 122A and the outer fin protrusions 122B are provided around the heat transfer tube 11, the same heat exchange promotion effect can be obtained as when protrusions are provided in both the longitudinal and lateral directions of the fin 12. In other words, whether air flows in from the longitudinal or lateral direction of the fin 12, the fin protrusions 122 are provided in the air flow direction. Therefore, the inner fin protrusions 122A and the outer fin protrusions 122B can be effectively used as heat transfer parts. As a result, the heat transfer coefficient on the surface of the fin 12 is improved, and the heat transfer performance as a heat exchanger is improved.

Furthermore, in the fin 12 according to this embodiment, an inner fin protrusion 122A and an outer fin protrusion 122B are provided around the through hole 12c into which the heat transfer tube 11 is inserted. When the fin protrusion 122 is formed, the material is pulled in a balanced manner from the entire area of the fin 12, so that shape distortion due to stress concentration on the fin base surface 121 can be suppressed. This improves the workability of the fin 12 and the manufacturability of the heat exchanger.

In addition, in the heat exchanger 100 according to this embodiment, each of the heat transfer tubes 11 has a circular cross section, and the inner fin protrusions 122A and the outer fin protrusions 122B are provided on the concentric circles of each of the heat transfer tubes 11. In this configuration, the inner fin protrusions 122A and the outer fin protrusions 122B are provided along the circumferential direction of the circular cross section of the heat transfer tube 11. When the inner fin protrusions 122A and the outer fin protrusions 122B are formed, the fins are uniformly deformed in the circumferential direction of the cross section of the heat transfer tube 11, so stress is less likely to concentrate. This improves the formability of the fins 12, and as a result, improves the manufacturability of the heat exchanger.

In addition, in the heat exchanger 100 according to this embodiment, the fin base surface 121 between the inner fin protrusion 122A and the outer fin protrusion 122B has a first flat portion 121A. In this configuration, the first flat portion 121A allows the inner fin protrusion 122A and the outer fin protrusion 122B to be provided on the fin 12 without contacting each other. For this reason, stress is less likely to concentrate between the inner fin protrusion 122A and the outer fin protrusion 122B during fin molding. This improves the moldability of the fin 12, and as a result, improves the manufacturability of the heat exchanger.

[First Modification of First Embodiment]
Fig. 7 is a cross-sectional view showing a first modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. Fig. 7 shows a portion of the first modified example corresponding to the cross section B-B in Fig. 4. In the first modified example shown in Fig. 7, similar to the first embodiment, the fin protrusion 122 has an inner fin protrusion 122A and an outer fin protrusion 122B.

In the heat exchanger 100 according to the first modification, the relationship between the height h1 at which the inner fin protrusions 122A protrude from the fin base surface 121 and the height h2 at which the outer fin protrusions 122B protrude from the fin base surface 121 differs from that of the first embodiment. In the first embodiment shown in Figures 5 and 6, the height h1 of the inner fin protrusions 122A and the height h2 of the outer fin protrusions 122B are equal. On the other hand, in the first modification, as shown in Figure 7, the height h1 of the inner fin protrusions 122A is higher than the height h2 of the outer fin protrusions 122B. The other configurations and functions are the same as those of the first embodiment, and therefore will not be described here.

In the heat exchanger 100 according to the first embodiment and the first modified example of the first embodiment, the height h1 of the inner fin protrusion 122A and the height h2 of the outer fin protrusion 122B are in a relationship of h2≦h1. A part of the air that collides with the outer fin protrusion 122B flows toward the top of the outer fin protrusion 122B along the slope of the outer fin protrusion 122B and passes through the highest part of the outer fin protrusion 122B. If the height h2 of the outer fin protrusion 122B is higher than the height h1 of the inner fin protrusion 122A, the air that passes through the highest part of the outer fin protrusion 122B flows into a space beyond the highest part of the inner fin protrusion 122A, that is, a space where the inner fin protrusion 122A does not exist. Therefore, a part of the air that collides with the outer fin protrusion 122B does not collide with the inner fin protrusion 122A. On the other hand, when the height h2 of the outer fin protrusions 122B and the height h1 of the inner fin protrusions 122A are equal, the air that collides with the outer fin protrusions 122B is likely to collide with the inner fin protrusions 122A. Therefore, more air flows between the outer fin protrusions 122B and the inner fin protrusions 122A. Furthermore, when the height h2 of the outer fin protrusions 122B is lower than the height h1 of the inner fin protrusions 122A, the air that exceeds the highest part of the outer fin protrusions 122B collides with the inner fin protrusions 122A. Therefore, more air flows between the outer fin protrusions 122B and the inner fin protrusions 122A. Moreover, the air that collides with the inner fin protrusions 122A is likely to flow into the gap between the inner fin protrusions 122A and the heat transfer tube 11. Therefore, in the configurations of the first embodiment and the first modification, in which the height h1 of the inner fin protrusions 122A and the height h2 of the outer fin protrusions 122B satisfy the relationship h2≦h1, more air flows into the gaps between the outer fin protrusions 122B and the inner fin protrusions 122A and the gaps between the inner fin protrusions 122A and the heat transfer tubes 11. This increases the area over which the air comes into contact with the outer fin protrusions 122B and the inner fin protrusions 122A, improving the heat transfer coefficient on the surfaces of the fins 12 and improving the heat transfer performance of the heat exchanger.

[Modification 2 of the First Embodiment]
Fig. 8 is a partial side cross-sectional view showing a second modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. Fig. 8 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the second modified example shown in Fig. 8, the fin protrusion 122 has an inner fin protrusion 122A and an outer fin protrusion 122B, similar to the first embodiment.

As shown in Figure 8, the inner fin protrusions 122A and the outer fin protrusions 122B in the second modification of the first embodiment are provided in a rectangular shape so as to surround the heat transfer tube 11. The difference from the first embodiment is the shape of the inner fin protrusions 122A and the outer fin protrusions 122B. The other configurations and functions are the same as those of the first embodiment, so the description thereof will be omitted here.

In the second modification, the inner fin protrusion 122A and the outer fin protrusion 122B are rectangular, so that the fin protrusion 122 has a portion that extends linearly in the Z direction of the fin 12. In other words, the fin protrusion 122 has a linear portion that runs along the longitudinal direction of the fin 12, so that the longitudinal strength of the fin 12 is further improved. Therefore, as in the first embodiment, the fin 12 is prevented from bending in the longitudinal direction during fin processing such as fin press and fin stack. This improves the productivity of the heat exchanger.

[Third Modification of First Embodiment]
Fig. 9 is a partial side cross-sectional view showing a third modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. Fig. 9 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the third modified example shown in Fig. 9, the fin protrusion 122 has an inner fin protrusion 122A and an outer fin protrusion 122B, similar to the first embodiment.

As shown in Fig. 9, the inner fin protrusions 122A and the outer fin protrusions 122B in the third modification of the first embodiment are provided in an elliptical shape so as to surround the heat transfer tube 11. The difference from the first embodiment is the shape of the inner fin protrusions 122A and the outer fin protrusions 122B. The other configurations and functions are the same as those of the first embodiment, so the description thereof will be omitted here.

9, the diameter of the inner fin protrusion 122A and the outer fin protrusion 122B in the X direction is longer than the diameter in the Z direction. In other words, the fin protrusion 122 has a portion that extends long in the short direction of the fin 12, which is the direction in which air flows in. This makes it easier for air to come into contact with the fin protrusion 122. As a result, similar to embodiment 1, the heat transfer coefficient on the surface of the fin 12 is improved.

[Fourth Modification of First Embodiment]
Fig. 10 is a cross-sectional view showing a fourth modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. Fig. 10 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the fourth modified example shown in Fig. 10, as in the first embodiment, the fin protrusion 122 has an inner fin protrusion 122A and an outer fin protrusion 122B.

As shown in FIG. 10, in the fourth modification of the first embodiment, the shape of the inner fin protrusion 122A is different from the shape of the outer fin protrusion 122B. The inner fin protrusion 122A in the fourth modification is provided on a concentric circle of the heat transfer tube 11, similar to the inner fin protrusion 122A in the first embodiment. On the other hand, the outer fin protrusion 122B in the fourth modification is provided in an elliptical shape so as to surround the heat transfer tube 11. The difference from the first embodiment is the shape of the outer fin protrusion 122B. The other configurations and functions are the same as those of the first embodiment, so a description thereof will be omitted here.

In the fourth modification, the inner fin protrusion 122A is circular and concentric with the heat transfer tube 11. On the other hand, the outer fin protrusion 122B is elliptical. As shown in FIG. 10, the diameter of the outer fin protrusion 122B in the X direction is longer than the diameter in the Z direction. In other words, the outer fin protrusion 122B has a portion that extends long in the short direction of the fin 12, which is the direction in which the air flows in. This makes it easier for the air to come into contact with the fin protrusion 122. As a result, the heat transfer coefficient on the surface of the fin 12 is improved, similar to the first embodiment.

[Fifth Modification of First Embodiment]
Fig. 11 is a cross-sectional view showing a fifth modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. Fig. 11 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the fifth modified example shown in Fig. 11, as in the first embodiment, the fin protrusion 122 has an inner fin protrusion 122A and an outer fin protrusion 122B.

As shown in Figure 11, in the fifth variation of the first embodiment, an additional fin protrusion 122D is provided to surround the outer fin protrusion 122B. The difference between the first embodiment and the fifth variation is the additional fin protrusion 122D. The other configurations and functions are the same as those of the first embodiment, so the description thereof will be omitted here.

In the fifth modification, one or more additional fin protrusions 122D are provided concentrically with the heat transfer tube 11 so as to surround the outer fin protrusion 122B. Therefore, the fin protrusion 122 has a portion that extends long in the second direction Z of the fin 12. In other words, the fin protrusion 122 having a portion along the longitudinal direction of the fin 12 is provided, thereby improving the longitudinal strength of the fin 12. Therefore, the fin is prevented from bending in the longitudinal direction during fin processing such as fin press or fin stack. Therefore, the productivity of the heat exchanger is improved.

In addition, because the additional fin protrusions 122D are provided to surround the outer fin protrusions 122B, the same effect can be obtained as when protrusions are added to both the longitudinal and lateral directions of the fin 12. In other words, whether air flows in from the longitudinal or lateral direction of the fin 12, protrusions are added in the direction of air flow, and the additional fin protrusions 122D can be effectively used as a heat transfer section. In addition, the additional fin protrusions 122D make it easier for the incoming air to come into contact with the additional fin protrusions 122D, improving the heat transfer coefficient and improving the heat transfer performance as a heat exchanger.

[Sixth Modification of the First Embodiment]
Fig. 12 is a partial side cross-sectional view showing a sixth modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. Fig. 12 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the sixth modified example shown in Fig. 12, as in the first embodiment, the fin protrusion 122 has an inner fin protrusion 122A and an outer fin protrusion 122B.

As shown in Figure 12, in the sixth variation of the first embodiment, the heat transfer tube 11 is made of a flat tube. The inner fin protrusions 122A and the outer fin protrusions 122B are provided in a rectangular shape so as to surround the heat transfer tube 11. The differences between the first embodiment and the sixth variation are the shape of the heat transfer tube 11, the shape of the inner fin protrusions 122A, and the shape of the outer fin protrusions 122B. The other configurations and functions are the same as those of the first embodiment, and therefore will not be described here.

In the sixth modification, since the inner fin protrusion 122A and the outer fin protrusion 122B are rectangular, the fin protrusion 122 has a portion that extends linearly in the Z direction of the fin 12. In other words, the fin protrusion 122 has a linear portion that runs along the longitudinal direction of the fin 12, which further improves the longitudinal strength of the fin 12. Therefore, as in the first embodiment, the fin is prevented from bending in the longitudinal direction during fin processing such as fin press and fin stack. This improves the productivity of the heat exchanger.

[Seventh Modification of the First Embodiment]
Fig. 13 is a partial side cross-sectional view showing a seventh modified example of the fin 12 of the heat exchanger 100 according to the first embodiment. Fig. 13 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the seventh modified example shown in Fig. 13, the fin protrusion 122 has an inner fin protrusion 122A and an outer fin protrusion 122B, similar to the first embodiment. Fig. 14 is a cross-sectional view taken along line A-A in Fig. 13.

13 and 14, in the seventh modification of the first embodiment, the first flat portion 121A is not provided between the inner fin protrusion 122A and the outer fin protrusion 122B. This is different from the first embodiment. The other configurations and functions are the same as those of the first embodiment, so the description thereof will be omitted here.

In the seventh modification, the fin base surface 121 does not have the first flat portion 121A. Therefore, the effect of avoiding stress concentration between the inner fin protrusion 122A and the outer fin protrusion 122B during fin molding cannot be obtained. However, the seventh modification can obtain the same effect as the first embodiment in terms of improving the longitudinal strength of the fin 12 and improving the heat transfer coefficient of the surface of the fin 12.

In the above embodiment 1 and its modified examples 1 to 7, the shapes of the inner fin protrusions 122A and the outer fin protrusions 122B have been described with reference to Figures 4, 8 to 14. In Figures 4, 8 to 14, the shapes of the inner fin protrusions 122A surrounding the multiple heat transfer tubes 11 are uniform. However, inner fin protrusions 122A having different shapes may be provided for each heat transfer tube 11. Also, in Figures 4, 8 to 14, the shapes of the outer fin protrusions 122B surrounding the multiple inner fin protrusions 122A are uniform. However, outer fin protrusions 122B having different shapes may be provided for each heat transfer tube 11.

Embodiment 2.
The heat exchanger 100 and the refrigeration cycle apparatus 1 according to the second embodiment will be described below.

[Basic configuration of heat exchanger 100]
The basic configuration of the heat exchanger 100 according to the second embodiment is the same as that of the heat exchanger 100 according to the first embodiment, and therefore a description thereof will be omitted here.

[Basic configuration of refrigeration cycle device 1]
The basic configuration of the refrigeration cycle apparatus 1 according to the second embodiment is the same as that of the refrigeration cycle apparatus 1 according to the first embodiment, and therefore a description thereof will be omitted here.

[Configuration of fin 12]
FIG. 15 is a partial cross-sectional side view showing the fin 12 of the heat exchanger 100 according to the second embodiment. FIG. 15 shows the main surface of the fin 12 and a cross section of the heat transfer tube 11. The cross section of the heat transfer tube 11 shown in FIG. 15 is a cross section parallel to the main surface of the fin 12. As shown in FIG. 15, the heat transfer tubes 11 are arranged in a row along a row direction parallel to the longitudinal direction of the fin 12. The fin 12 has a leading edge 12a and a trailing edge 12b. Hereinafter, the heat transfer tube 11 on the upper side of the paper surface of FIG. 15 is referred to as the first heat transfer tube 11A, and the heat transfer tube 11 on the lower side of the paper surface of FIG. 15 is referred to as the second heat transfer tube 11B.

The main surface of the fin 12 constitutes a flat fin base surface 121, as in the first embodiment. Also, as in the first embodiment, the inner fin protrusion 122A and the outer fin protrusion 122B are provided protruding from the fin base surface 121 in the Y direction. In the second embodiment, the inner fin protrusion 122A provided to surround the periphery of the first heat transfer tube 11A is called the first inner fin protrusion 122A-1. Also, the outer fin protrusion 122B provided to surround the periphery of the first inner fin protrusion 122A-1 is called the first outer fin protrusion 122B-1. Furthermore, in the second embodiment, the inner fin protrusion 122A provided to surround the periphery of the second heat transfer tube 11B is called the second inner fin protrusion 122A-2. The outer fin protrusion 122B provided so as to surround the periphery of the second inner fin protrusion 122A-2 is referred to as a second outer fin protrusion 122B-2.

The fins 12 in embodiment 2 will be described using Figures 15 to 17. Figure 16 is a cross-sectional view taken along line A-A in Figure 15. Figure 17 is a cross-sectional view taken along line C-C in Figure 15. In the following description, when there is no need to distinguish between the first inner fin protrusion 122A-1 and the second inner fin protrusion 122A-2, they will be referred to simply as "inner fin protrusion 122A" as appropriate. Also, when there is no need to distinguish between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2, they will be referred to simply as "outer fin protrusion 122B" as appropriate.

A gap exists between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. Of the gap between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2, the portion surrounded by the thick dashed line in FIG. 15 is called the second flat portion 121B. That is, in the plane of FIG. 15, the second flat portion 121B is the fin base surface 121 sandwiched between the lower semicircular portion of the first outer fin protrusion 122B-1 and the upper semicircular portion of the second outer fin protrusion 122B-2. Also, in FIG. 16, the straight line portion between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 corresponds to the second flat portion 121B. If the second flat portion 121B was not provided between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2, stress would be concentrated at the boundary between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 during fin molding. By providing the second flat portion 121B, stress concentration during fin molding is avoided.

15, the fin base surface 121 is provided with an intermediate fin protrusion 122C. As shown in FIG. 17, the intermediate fin protrusion 122C protrudes in the Y direction from the fin base surface 121 between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. That is, in the second embodiment, the fin protrusion 122 has an inner fin protrusion 122A, an outer fin protrusion 122B, and an intermediate fin protrusion 122C. As shown in FIGS. 16 and 17, the inner fin protrusion 122A, the outer fin protrusion 122B, and the intermediate fin protrusion 122C protrude in the same direction from the fin base surface 121 in the Y direction. The basic configuration of the fin 12 according to the second embodiment is the same as that of the first embodiment except for the intermediate fin protrusion 122C, and therefore will not be described. 15, two intermediate fin protrusions 122C are provided, but the number of intermediate fin protrusions 122C is not limited to two. The number of intermediate fin protrusions 122C may be one, or three or more intermediate fin protrusions 122C may be provided.

The intermediate fin protrusion 122C is provided between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 in the longitudinal direction of the fin 12. However, it is not necessary for the entire intermediate fin protrusion 122C to be located between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. As shown in FIG. 15, it is sufficient that a part of the intermediate fin protrusion 122C is located between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. In this disclosure, the space between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 refers to the fin base surface 121 corresponding to the second flat portion 121B.

In addition, in this disclosure, a straight line passing through the center of the first heat transfer tube 11A and the center of the second heat transfer tube 11B in the Z direction is called the center line CL. In Figure 15, the dashed dotted line showing the A-A cross section corresponds to the center line CL. The intermediate fin protrusion 122C is provided at a position that does not intersect with the center line CL.

Next, the shape of the intermediate fin protrusion 122C will be described with reference to Figure 15. The intermediate fin protrusion 122C has a first rising portion 122c-1 and a second rising portion 122c-2 that rise from the fin base surface 121. The first rising portion 122c-1 and the second rising portion 122c-2 extend parallel to each other along the Z direction of the fin 12. The length of the first rising portion 122c-1 is longer than the length of the second rising portion 122c-2. Furthermore, in the X direction, the distance between the first rising portion 122c-1 and the center line CL is longer than the distance between the second rising portion 122c-2 and the center line CL.

The first rising portion 122c-1 has two ends in the Z direction. Of the two ends of the first rising portion 122c-1, the end closer to the first outer fin protrusion 122B-1 is called the first end 122c-1a. Also, of the two ends of the first rising portion 122c-1, the end closer to the second outer fin protrusion 122B-2 is called the second end 122c-1b. That is, the first rising portion 122c-1 has a first end 122c-1a and a second end 122c-1b. Also, the second rising portion 122c-2 has two ends in the Z direction. Of the two ends of the second rising portion 122c-2, the end closer to the first outer fin protrusion 122B-1 is called the first end 122c-2a. Of the two ends of the second rising portion 122c-2, the end closer to the second outer fin protrusion 122B-2 is referred to as the second end 122c-2b. That is, the second rising portion 122c-2 has a first end 122c-2a and a second end 122c-2b.

Next, the positional relationship between the intermediate fin protrusion 122C and the outer fin protrusion 122B will be described using the first virtual line VL1 and the second virtual line VL2 shown by dashed lines in Figure 15. In this disclosure, the virtual straight line passing through the first end 122c-1a of the first rising portion 122c-1 and the first end 122c-2a of the second rising portion 122c-2 is called the first virtual line VL1. Also, the virtual straight line passing through the second end 122c-1b of the first rising portion 122c-1 and the second end 122c-2b of the second rising portion 122c-2 is called the second virtual line VL2. As shown in Figure 15, the first virtual line VL1 does not intersect with the first outer fin protrusion 122B-1. Therefore, a certain gap is formed between the portion connecting the first end 122c-1a of the first rising portion 122c-1 of the intermediate fin protrusion 122C and the first end 122c-2a of the second rising portion 122c-2, and the first outer fin protrusion 122B-1. In addition, the second virtual line VL2 does not intersect with the second outer fin protrusion 122B-2. Therefore, a certain gap is formed between the portion connecting the second end 122c-1b of the first rising portion 122c-1 of the intermediate fin protrusion 122C and the second end 122-2b of the second rising portion 122c-2, and the second outer fin protrusion 122B-2. Here, the certain gap is a part of the fin base surface 121, and is a flat region having an area for avoiding stress concentration around the intermediate fin protrusion 122C during fin molding. If the area of the gap between the intermediate fin protrusion 122C and the outer fin protrusion 122B is small, it is impossible to avoid stress concentration around the intermediate fin protrusion 122C during fin molding. The intermediate fin protrusion 122C is provided so that the first virtual line VL1 does not intersect with the first outer fin protrusion 122B-1. Therefore, a flat area of the fin base surface 121 can be secured between the intermediate fin protrusion 122C and the first outer fin protrusion 122B-1, which can avoid stress concentration during fin molding. In addition, the intermediate fin protrusion 122C is provided so that the second virtual line VL2 does not intersect with the second outer fin protrusion 122B-2. Therefore, a flat area of the fin base surface 121 can be secured between the intermediate fin protrusion 122C and the second outer fin protrusion 122B-2, which can avoid stress concentration during fin molding.

In the heat exchanger 100 according to this embodiment, the heat transfer tubes 11 include a first heat transfer tube 11A and a second heat transfer tube 11B adjacent to each other in the second direction Z. The inner fin protrusion 122A includes a first inner fin protrusion 122A-1 provided to surround the periphery of the first heat transfer tube 11A, and a second inner fin protrusion 122A-2 provided to surround the periphery of the second heat transfer tube 11B. The outer fin protrusion 122B includes a first outer fin protrusion 122B-1 provided to surround the periphery of the first inner fin protrusion 122A-1, and a second outer fin protrusion 122B-2 provided to surround the periphery of the second inner fin protrusion 122A-2. The fin base surface 121 between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 has a second flat portion 121B.

According to this configuration, the second flat portion 121B allows the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 to be provided on the fin 12 without contacting each other. Therefore, stress does not concentrate between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 when the fins are molded. This improves the moldability of the fin 12, and as a result, improves the manufacturability of the heat exchanger.

Furthermore, in the heat exchanger 100 according to this embodiment, the multiple fin protrusions 122 have intermediate fin protrusions 122C protruding from the fin base surface 121 in the first direction Y, and the intermediate fin protrusions 122C are arranged such that at least a portion of the intermediate fin protrusions 122C is positioned between the first outer fin protrusions 122B-1 and the second outer fin protrusions 122B-2 in the second direction Z.

According to this configuration, the intermediate fin protrusion 122C makes it easier for air to come into contact with the surface of the fin 12. As a result, the heat transfer rate on the surface of the fin 12 is further improved. In addition, the fact that a part of the intermediate fin protrusion 122C is located between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 means that the area in the longitudinal direction of the fin 12 where the fin protrusions 122 are not present is reduced. This further improves the longitudinal strength of the fin 12.

In the heat exchanger 100 according to this embodiment, the intermediate fin protrusion 122C is provided at a position that does not intersect with the center line CL that passes through the center of the first heat transfer tube 11A and the center of the second heat transfer tube 11B along the second direction Z. Here, in the second direction Z of the fin 12, the length between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 is shortest at the portion where the center line CL passes. In this embodiment, the intermediate fin protrusion 122C is provided at a location where the gap between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 is relatively large, avoiding the position where the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 are closest to each other. In this way, the intermediate fin protrusion 122C extending along the longitudinal direction of the fin 12 is provided to reduce the flat surface of the fin base surface 121, thereby improving the longitudinal strength of the fin 12. In addition, since the intermediate fin protrusion 122C has a long portion, air can easily come into contact with the surface of the fin 12, and the heat transfer coefficient is further improved.

In addition, in the heat exchanger 100 according to the present embodiment, when the short side direction of the multiple fins 12 is a third direction X intersecting the first direction Y and the second direction Z, the intermediate fin protrusion 122C has a first rising portion 122c-1 that extends in the second direction Z and that rises from the fin base surface 121, and a second rising portion 122c-2 that rises from the fin base surface 121 in parallel to the first rising portion 122c-1. In the second direction Z, the length of the first rising portion 122c-1 is longer than the length of the second rising portion 122c-2, and in the third direction X, the distance between the first rising portion 122c-1 and the center line CL is longer than the distance between the second rising portion 122c-2 and the center line CL. In the second direction Z, the first rising portion 122c-1 has a first end 122c-1a adjacent to the first outer fin protrusion 122B-1 and a second end 122c-1b adjacent to the second outer fin protrusion 122B-2. In the second direction Z, the second rising portion 122c-2 has a first end 122c-2a adjacent to the first outer fin protrusion 122B-1 and a second end 122c-2b adjacent to the second outer fin protrusion 122B-2. A first virtual line VL1 passing through the first end 122c-1a of the first rising portion 122c-1 and the first end 122c-2a of the second rising portion 122c-2 does not intersect with the first outer fin protrusion 122B-1. Further, a second imaginary line VL2 passing through the second end 122c-1b of the first rising portion 122c-1 and the second end 122c-2b of the second rising portion 122c-2 does not intersect with the second outer fin protrusion 122B-2.

According to this configuration, a flat fin base surface 121 area can be secured between the intermediate fin protrusion 122C and the outer fin protrusion 122B to prevent stress concentration between the intermediate fin protrusion 122C and the outer fin protrusion 122B during fin molding. This can further improve the moldability of the fin 12.

[First Modification of the Second Embodiment]
Fig. 18 is a cross-sectional view showing a first modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 18 shows a portion of the first modified example corresponding to the CC cross section of Fig. 15. In the first modified example shown in Fig. 18, the fin 12 has an intermediate fin protrusion 122C, as in the second embodiment.

In the heat exchanger 100 according to the first modified example of the second embodiment, in the Y direction, the direction in which the inner fin protrusions 122A protrude from the fin base surface 121 is the same as the direction in which the outer fin protrusions 122B protrude from the fin base surface 121. On the other hand, the intermediate fin protrusions 122C protrude in the Y direction in the opposite direction to the direction in which the inner fin protrusions 122A and the outer fin protrusions 122B protrude. The other configurations and functions are the same as those of the second embodiment, and therefore will not be described here.

In the heat exchanger 100 of the first modified example of the second embodiment, in the first direction Y, the direction in which the inner fin protrusion 122A protrudes from the fin base surface 121 is opposite to the direction in which the intermediate fin protrusion 122C protrudes from the fin base surface 121. Therefore, the inner fin protrusion 122A is not located in the downstream part of the intermediate fin protrusion 122C. In other words, the inner fin protrusion 122A is not affected by the dead water area of the intermediate fin protrusion 122C. As a result, the inner fin protrusion 122A can be used to the maximum for heat exchange, and the heat transfer coefficient on the surface of the fin 12 is improved.

In addition, in the first direction Y, the direction in which the outer fin protrusions 122B protrude from the fin base surface 121 is the same as the direction in which the inner fin protrusions 122A protrude. In other words, the outer fin protrusions 122B are not located downstream of the intermediate fin protrusions 122C, and are therefore not affected by the dead water area of the intermediate fin protrusions 122C. This allows the outer fin protrusions 122B to be used to the maximum extent for heat exchange, further improving the heat transfer coefficient on the surface of the fin 12.

In addition, in the first modification, the inner fin protrusion 122A and the intermediate fin protrusion 122C protrude in opposite directions, so that the center of gravity of the fin 12 is closer to the fin base surface 121 in the Y direction. This improves the strength of the fin 12.

[Modification 2 of the Second Embodiment]
Fig. 19 is a partial side cross-sectional view showing Modification 2 of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 19 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In Modification 2 shown in Fig. 19, the fin protrusion 122 has an intermediate fin protrusion 122C, as in the second embodiment. Fig. 20 is a cross-sectional view taken along line A-A in Fig. 19.

As shown in Figures 19 and 20, in variant 2 of embodiment 2, the intermediate fin protrusion 122C is provided overlapping the center line CL between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. As shown in Figure 19, in variant 2, the intermediate fin protrusion 122C has a rectangular shape with its long side in the Z direction when viewed from the Y direction. The difference between variant 2 and embodiment 2 is the position at which the intermediate fin protrusion 122C is provided and the shape of the intermediate fin protrusion 122C. The other configurations and functions are the same as those of embodiment 1, so their description will be omitted here.

In variant 2, the intermediate fin protrusion 122C overlaps with the center line CL between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. The distance between the first rising portion 122c-1 and the center line CL is equal to the distance between the second rising portion 122c-2 and the center line CL. Furthermore, the length of the first rising portion 122c-1 is equal to the length of the second rising portion 122c-2. In Figure 19, the long side on the left as you face the page is called the first rising portion 122c-1, and the long side on the right as you face the page is called the second rising portion 122c-2.

In the second modification, the intermediate fin protrusion 122C is located at the portion where the distance between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 is the shortest in the Z direction. When the distance between adjacent heat transfer tubes 11 is relatively large, providing the intermediate fin protrusion 122C as in the second modification improves the longitudinal strength of the fin 12 and improves the heat transfer coefficient of the surface of the fin 12.

[Third Modification of the Second Embodiment]
Fig. 21 is a partial side cross-sectional view showing a third modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 21 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the third modified example shown in Fig. 21, the fin protrusion 122 has an intermediate fin protrusion 122C, as in the second embodiment. Fig. 22 is a cross-sectional view taken along line A-A in Fig. 21.

21 and 22, in the third modification of the second embodiment, the intermediate fin protrusion 122C is provided between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2, crossing the center line CL. The intermediate fin protrusion 122C has a portion that extends long in the X direction. In FIG. 21, the length of the intermediate fin protrusion 122C in the X direction is longer than the diameter of each of the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. However, the length of the intermediate fin protrusion 122C in the X direction may be equal to or less than the diameter of each of the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. The difference between the third modification and the second embodiment is that in the third modification, the intermediate fin protrusion 122C is provided crossing the center line CL and the shape of the intermediate fin protrusion 122C. The other configurations and operations are the same as those of the second embodiment, and therefore will not be described here.

In the third modification, the intermediate fin protrusion 122C extending along the X direction, which is the short-side direction of the fin 12, is provided between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2, intersecting the center line CL. In addition, the length of each of the first rising portion 122c-1 and the second rising portion 122c-2 extending along the Z direction, which is the longitudinal direction of the fin 12, is shorter than the length of the portion extending along the X direction. That is, in the third modification, the intermediate fin protrusion 122C does not have a portion extending long along the longitudinal direction of the fin 12, as in the intermediate fin protrusion 122C in the second embodiment. However, even in the third modification, the intermediate fin protrusion 122C is provided, thereby improving the longitudinal strength of the fin 12. In addition, in the third modification, the intermediate fin protrusion 122C has a portion extending long in the X direction in which air flows, so that the air is more likely to come into contact with the surface of the fin 12. Therefore, the heat transfer coefficient on the surface of the fins 12 is improved.

[Fourth Modification of the Second Embodiment]
Fig. 23 is a partial side cross-sectional view showing a fourth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 23 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the fourth modified example shown in Fig. 23, the fin protrusion 122 has an intermediate fin protrusion 122C, as in the second embodiment. Fig. 24 is a cross-sectional view taken along line A-A in Fig. 23.

23 and 24, in the fourth modification of the second embodiment, the intermediate fin protrusion 122C is provided overlapping the center line CL between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. As shown in FIG. 23, in the fourth modification, the intermediate fin protrusion 122C has a circular shape when viewed from the Y direction. As shown in FIG. 24, the intermediate fin protrusion 122C protrudes in a hemispherical shape from the fin base surface 121. The difference between the fourth modification and the second embodiment is the position where the intermediate fin protrusion 122C is provided and the shape of the intermediate fin protrusion 122C. The other configurations and functions are the same as those of the second embodiment, and therefore will not be described here.

In variant 4, the intermediate fin protrusion 122C overlaps with the center line CL between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. In variant 4, the intermediate fin protrusion 122C does not have a portion that extends as far along the longitudinal direction of the fin 12 as the intermediate fin protrusion 122C in embodiment 2. However, even in variant 4, the provision of the intermediate fin protrusion 122C improves the longitudinal strength of the fin 12 and improves the heat transfer coefficient of the surface of the fin 12.

[Fifth Modification of the Second Embodiment]
Fig. 25 is a partial side cross-sectional view showing a fifth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 25 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the fifth modified example shown in Fig. 25, the fin protrusion 122 has an intermediate fin protrusion 122C, as in the second embodiment. Fig. 26 is a cross-sectional view taken along CC in Fig. 25.

As shown in FIG. 25, in variant 5 of embodiment 2, the intermediate fin protrusion 122C has first rising portion 122c-1 and second rising portion 122c-2 that are equal in length. In the above-mentioned embodiment 2, as shown in FIG. 15, a case has been described in which the length of the first rising portion 122c-1 is longer than the length of the second rising portion 122c-2. The difference between variant 5 and embodiment 2 is the relationship between the length of the first rising portion 122c-1 and the length of the second rising portion 122c-2. As the other configurations and functions are the same as those of embodiment 2, their description will be omitted here.

In variant 5, the first virtual line VL1 intersects with the first outer fin protrusion 122B-1. The second virtual line VL2 intersects with the second outer fin protrusion 122B-2. If the distance between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2 in the Z direction is secured, an intermediate fin protrusion 122C having a shape as in variant 5 may be provided. By providing the intermediate fin protrusion 122C of variant 5, the longitudinal strength of the fin 12 is improved, and the heat transfer coefficient of the surface of the fin 12 is improved.

[Sixth Modification of the Second Embodiment]
Fig. 27 is a partial side cross-sectional view showing a sixth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 27 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the sixth modified example shown in Fig. 27, the fin protrusion 122 has an intermediate fin protrusion 122C, as in the second embodiment. Fig. 28 is a cross-sectional view taken along CC in Fig. 27.

As shown in Figure 27, in variant 6 of embodiment 2, the intermediate fin protrusion 122C has a T-shape that is turned 90 degrees when viewed from the Y direction. Therefore, as shown in Figure 28, the intermediate fin protrusion 122C has a portion that extends long in the X direction. The difference between variant 6 and embodiment 2 is the shape of the intermediate fin protrusion 122C. The other configurations and functions are the same as those of embodiment 2, so their description will be omitted here.

In the sixth modification, the first virtual line VL1 intersects with the first outer fin protrusion 122B-1. The second virtual line VL2 intersects with the second outer fin protrusion 122B-2. Furthermore, the portion of the intermediate fin protrusion 122C that extends long in the X direction is located between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B-2. The intermediate fin protrusion 12C of the sixth modification has both a portion that extends linearly along the longitudinal direction (Z direction) of the fin 12 and a portion that extends linearly along the lateral direction (X direction). The provision of the intermediate fin protrusion 122C of the sixth modification improves the longitudinal strength of the fin 12. Furthermore, since the intermediate fin protrusion 122C has a portion that extends in the X direction in which air flows in, the air is more likely to come into contact with the surface of the fin 12 than in the second embodiment. Therefore, in the sixth modification, the heat transfer coefficient on the surface of the fin 12 can be improved more than in the second embodiment.

[Seventh Modification of the Second Embodiment]
Fig. 29 is a partial side cross-sectional view showing a seventh modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 29 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the seventh modified example shown in Fig. 29, the fin protrusion 122 has an intermediate fin protrusion 122C, as in the second embodiment. Fig. 30 is a cross-sectional view taken along CC in Fig. 29.

As shown in FIG. 29, in the seventh modification of the second embodiment, the intermediate fin protrusion 122C has a first intermediate fin protrusion 122C-1 and a second intermediate fin protrusion 122C-2. When viewed in the Y direction, the first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2 have a rectangular shape with the long side in the Z direction. The difference between the seventh modification and the second embodiment is that in the seventh modification, the intermediate fin protrusion 122C has a first intermediate fin protrusion 122C-1 and a second intermediate fin protrusion 122C-2. In addition, the shape of the intermediate fin protrusion 122C in the second embodiment is different from the shapes of the first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2 in the seventh modification. The other configurations and functions are the same as those in the second embodiment, so their description will be omitted here.

In the following description, when there is no need to distinguish between the first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2, they will be referred to simply as the "intermediate fin protrusion 122C" as appropriate. Furthermore, when referring to an "intermediate fin protrusion 122C", this includes both the singular and the plural. Furthermore, when there is no need to distinguish between the first rising portion 122c1-1 of the first intermediate fin protrusion 122C-1 and the first rising portion 122c2-1 of the second intermediate fin protrusion 122C-2, the first rising portion 122c-1 will be referred to simply as the "first rising portion 122c-1" as appropriate. Furthermore, when there is no need to particularly distinguish between the second rising portion 122c1-2 of the first intermediate fin protrusion 122C-1 and the first rising portion 122c2-2 of the second intermediate fin protrusion 122C-2, the second rising portion 122c-2 will be simply referred to as the "second rising portion 122c-2" as appropriate. Furthermore, when the terms "first rising portion 122c-1" and "second rising portion 122c-2" are used, it is intended to include both the singular and plural.

The first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2 will be described with reference to Figure 29. In the first intermediate fin protrusion 122C-1, the length of the first rising portion 122c1-1 is equal to the length of the second rising portion 122c1-2. In addition, in the second intermediate fin protrusion 122C-2, the length of the first rising portion 122c2-1 is equal to the length of the second rising portion 122c2-2. Note that the difference between the intermediate fin protrusion 122C in embodiment 2 and the intermediate fin protrusion 122C in variant 7 is the relationship between the length of the first rising portion 122c-1 and the length of the second rising portion 122c-2.

In addition, in FIG. 29, two first intermediate fin protrusions 122C-1 are provided, but the number of first intermediate fin protrusions 122C-1 is not limited to two. There may be one first intermediate fin protrusion 122C-1, or three or more first intermediate fin protrusions 122C-1 may be provided. In addition, in FIG. 29, two second intermediate fin protrusions 122C-2 are provided, but the number of second intermediate fin protrusions 122C-2 is not limited to two. There may be one second intermediate fin protrusion 122C-2, or three or more second intermediate fin protrusions 122C-2 may be provided.

Furthermore, the distance between the first intermediate fin protrusion 122C-1 and the center line CL is longer than the distance between the second intermediate fin protrusion 122C-2 and the center line CL. Furthermore, the length of the first rising portion 122c1-1 of the first intermediate fin protrusion 122C-1 is longer than the length of the first rising portion 122c2-1 of the second intermediate fin protrusion 122C-2. In other words, the first intermediate fin protrusion 122C-1 is larger than the second intermediate fin protrusion 122C-2.

As described above, in variant 7, the first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2, which extend linearly along the longitudinal direction of the fin 12, are arranged along the shorter side of the fin. In variant 7, the provision of the first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2 improves the longitudinal strength of the fin 12 and improves the heat transfer coefficient of the surface of the fin 12.

[Eighth Modification of the Second Embodiment]
Fig. 31 is a partial side cross-sectional view showing an eighth modified example of the fin 12 of the heat exchanger 100 according to the second embodiment. Fig. 31 shows the surface of the fin 12 and a cross section of the heat transfer tube 11 parallel to the main surface of the fin 12. In the eighth modified example shown in Fig. 31, the fin protrusion 122 has an intermediate fin protrusion 122C, as in the second embodiment. Fig. 32 is a cross-sectional view taken along CC in Fig. 31.

As shown in FIG. 31, in the eighth modification of the second embodiment, the intermediate fin protrusion 122C has a first intermediate fin protrusion 122C-1 and a second intermediate fin protrusion 122C-2. When viewed from the Y direction, the first intermediate fin protrusion 122C-1 has a rectangular shape with the Z direction as the long side. Also, when viewed from the Y direction, the second intermediate fin protrusion 122C-2 has a circular shape. The difference between the eighth modification and the second embodiment is that in the eighth modification, the intermediate fin protrusion 122C has a first intermediate fin protrusion 122C-1 and a second intermediate fin protrusion 122C-2. Also, the shape of the intermediate fin protrusion 122C in the second embodiment is different from the shapes of the first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2 in the eighth modification. The other configurations and functions are the same as those in the second embodiment, so their description will be omitted here.

The first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2 will be described with reference to FIG. 31. In the first intermediate fin protrusion 122C-1, the length of the first rising portion 122c1-1 is equal to the length of the second rising portion 122c1-2. The distance between the first intermediate fin protrusion 122C-1 and the center line CL is longer than the distance between the second intermediate fin protrusion 122C-2 and the center line CL. Note that the difference between the intermediate fin protrusion 122C in embodiment 2 and the first intermediate fin protrusion 122C-1 in variant 8 is the relationship between the length of the first rising portion 122c-1 and the length of the second rising portion 122c-2.

In FIG. 31, two first intermediate fin protrusions 122C-1 are provided, but the number of first intermediate fin protrusions 122C-1 is not limited to two. There may be one first intermediate fin protrusion 122C-1, or three or more first intermediate fin protrusions 122C-1 may be provided. In FIG. 31, two second intermediate fin protrusions 122C-2 are provided, but the number of second intermediate fin protrusions 122C-2 is not limited to two. There may be one second intermediate fin protrusion 122C-2, or three or more second intermediate fin protrusions 122C-2 may be provided.

As described above, in variant 8, a first intermediate fin protrusion 122C-1 is provided that extends linearly along the longitudinal direction of the fin 12. In addition, a circular second intermediate fin protrusion 122C-2 with a relatively short length along the longitudinal direction of the fin 12 is provided at a position where the distance between the first outer fin protrusion 122B-1 and the second outer fin protrusion 122B2 is relatively short, thereby reducing the area of the flat portion of the fin 12. In variant 8, the provision of the first intermediate fin protrusion 122C-1 and the second intermediate fin protrusion 122C-2 improves the longitudinal strength of the fin 12 and improves the heat transfer coefficient of the surface of the fin 12.

The heat exchanger 100 described in the above-mentioned embodiment 1, embodiment 2, and the modified examples thereof can be provided in the refrigeration cycle device 1 shown in FIG. 3, as described above. In that case, in the refrigeration cycle device 1, the fin protrusions 122 provided on the fins 12 of the heat exchanger 100 increase the strength of the fins 12 in the longitudinal direction, improving the formability of the fins. Therefore, the manufacturability of the heat exchanger 100 is improved, and as a result, the manufacturability of the entire refrigeration cycle device 1 is improved. In addition, the fin protrusions 122 provided on the fins 12 of the heat exchanger 100 make it easier for air to come into contact with the surface of the fins 12. Therefore, the heat transfer coefficient of the heat exchanger 100 is improved, and as a result, the energy efficiency of the entire refrigeration cycle device 1 can be improved.

Although the above describes the first embodiment, the second embodiment, and their modified examples, the heat exchanger 100 and the refrigeration cycle device 1 are not limited to the first embodiment, the second embodiment, and their modified examples, and various modifications and applications are possible without departing from the gist of the invention. The first embodiment, the second embodiment, and their modified examples can be combined with each other without impairing the function or structure of each embodiment and each modified example.

1 Refrigeration cycle device, 2 Heat source side unit, 3 Load side unit, 4 Compressor, 5 Flow path switching device, 6 Expansion valve, 7A Blower, 7B Blower, 7a Fan motor, 7b Fan, 8 Refrigerant piping, 9A Controller, 9B Controller, 11 Heat transfer tube, 11A Heat transfer tube, 11B Heat transfer tube, 11a U-shaped tube, 12 Fin, 12a Leading edge, 12b Trailing edge, 12c Through hole, 12d Fin collar, 100 Heat exchanger, 100A Heat exchanger, 100B Heat exchanger, 121 Fin base surface, 121A First flat portion, 121B Second flat portion, 122 Fin protrusion, 122A Inner fin protrusion, 122A-1 First inner fin protrusion, 122A-2 Second inner fin protrusion, 122B Outer fin protrusion, 122B-1 First outer fin protrusion, 122B-2 Second outer fin protrusion, 122B-3 Third outer fin protrusion, 122C Intermediate fin protrusion, 122C-1 First intermediate fin protrusion, 122C-2 Second intermediate fin protrusion, 122c-1 First rising portion, 122c-1a First end, 122c-1b Second end, 122c-2 Second rising portion, 122c-2a First end, 122c-2b Second end, 122c1-1 First rising portion, 122c1-1a First end, 122c1-1b Second end, 122c1-2 Second rising portion, 122c1-2a First end, 122c1-2b Second end, 122c2-1 First rising portion, 122c2-1a First end, 122c2-1b Second end, 122c2-2 Second rising portion, 122c2-2a First end, 122c2-2b Second end, 122D Additional fin protrusion, Y first direction, Z second direction, X third direction, CL center line, VL1 first virtual line, VL2 second virtual line.

Claims (9)

A plurality of fins spaced apart from one another in a first direction;
a plurality of heat transfer tubes that penetrate the plurality of fins and are arranged at intervals from each other in a second direction that intersects with the first direction,
Each of the plurality of fins is
A flat fin base surface;
A plurality of fin protrusions;
The plurality of fin protrusions include
an inner fin protrusion provided to surround each of the heat transfer tubes and protruding from the fin base surface in the first direction;
and outer fin protrusions provided so as to surround the periphery of each of the inner fin protrusions and protruding in the same direction as the inner fin protrusions from the fin base surface ,
The inner fin protrusion and the outer fin protrusion are adjacent to each other without any gap.
Heat exchanger. Each of the plurality of heat transfer tubes has a circular cross section,
The heat exchanger according to claim 1 , wherein the inner fin protrusions and the outer fin protrusions are provided on concentric circles of each of the plurality of heat transfer tubes. 3. The heat exchanger according to claim 1, wherein a height h1 that the inner fin protrusions protrude from the fin base surface is defined as h1, and a height h2 that the outer fin protrusions protrude from the fin base surface is defined as h2, and the heights h1 and h2 satisfy a relationship of h2≦h1. The plurality of heat transfer tubes include a first heat transfer tube and a second heat transfer tube adjacent to each other in the second direction,
The inner fin protrusion is
a first inner fin protrusion provided to surround the first heat transfer tube;
a second inner fin protrusion provided so as to surround the periphery of the second heat transfer tube,
The outer fin protrusion is
a first outer fin portion provided so as to surround the periphery of the first inner fin portion;
a second outer fin portion provided so as to surround the second inner fin portion,
The heat exchanger according to any one of claims 1 to 3 , wherein the fin base surface between the first outer fin projection and the second outer fin projection has a second flat portion. The plurality of fin protrusions include
an intermediate fin protrusion protruding from the fin base surface in the first direction;
The intermediate fin protrusion is
The heat exchanger according to claim 4 , wherein at least a portion of the intermediate fin projection is located between the first outer fin projection and the second outer fin projection. In the first direction,
The heat exchanger according to claim 5 , wherein a direction in which the inner fin projections protrude from the fin base surface is opposite to a direction in which the intermediate fin projections protrude from the fin base surface. The heat exchanger according to claim 5 or 6 , wherein the intermediate fin protrusion is provided at a position that does not intersect with a center line that passes through a center of the first heat transfer tube and a center of the second heat transfer tube along the second direction. When a short-side direction of the plurality of fins is a third direction intersecting the first direction and the second direction,
The intermediate fin protrusion is
a first raised portion extending in the second direction and raised from the fin base surface;
a second rising portion rising from the fin base surface in parallel to the first rising portion,
In the second direction, a length of the first rising portion is longer than a length of the second rising portion,
In the third direction, a distance between the first rising portion and the center line is longer than a distance between the second rising portion and the center line;
In the second direction, the first rising portion is
A first end portion adjacent to the first outer fin protrusion portion;
a second end portion provided adjacent to the second outer fin protrusion portion,
In the second direction, the second rising portion is
A first end portion adjacent to the first outer fin protrusion portion;
a second end portion provided adjacent to the second outer fin protrusion portion,
a first imaginary line passing through the first end of the first rising portion and the first end of the second rising portion does not intersect with the first outer fin protrusion;
The heat exchanger according to claim 7 , wherein a second imaginary line passing through the second end of the first raised portion and the second end of the second raised portion does not intersect with the second outer fin projection. A refrigeration cycle device comprising the heat exchanger according to any one of claims 1 to 8 as a condenser or an evaporator.

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