JP7150157B2 - Heat exchanger and refrigeration cycle equipment - Google Patents

Description

TECHNICAL FIELD The present invention relates to a heat exchanger that maintains heat transfer coefficient and reduces draft resistance, and a refrigeration cycle apparatus having the same.

A conventional heat exchanger includes a plurality of heat transfer tubes arranged in parallel with each other at intervals, and a plurality of fins connected to the plurality of heat transfer tubes and having surfaces parallel to the direction of air flow. Air supplied to the heat exchanger passes between the plurality of heat transfer tubes and between the plurality of fins and contacts the heat transfer tubes and the fins. As a result, heat exchange is performed between the heat exchange fluid that flows through the heat transfer tubes and the air that is the heat exchange fluid that exchanges heat with the heat exchange fluid.

As a conventional heat exchanger, there is also known a heat exchanger in which a plurality of cut-and-raised portions called slits or louvers are formed on the surface of the fins and are open in the air circulation direction. Such heat exchangers are called slit fin heat exchangers. In the slit fin heat exchanger, the thermal boundary layer is reconstructed at each cut-and-raised part, and the air velocity near the fin surface increases. This increases the amount of heat transported, thereby improving the heat exchange performance of the heat exchanger under dry conditions. On the other hand, however, in the slit fin heat exchanger, the cut-and-raised portion may hinder the discharge of condensed water and block a part of the air passage in the heat exchanger. Further, in the slit fin heat exchanger, frost may be formed intensively on the cut-and-raised portion, and a part of the air passage in the heat exchanger may be blocked. For this reason, the slit fin heat exchanger deteriorates in heat exchange performance under wet conditions due to partial blockage of the air passage in the heat exchanger. Note that the condensed water is water adhered to the surface of the heat exchanger as a result of condensation of moisture in the air.

As a conventional heat exchanger, there is also known a heat exchanger in which corrugated unevenness projecting perpendicularly to the direction of air flow is formed on the surface of the fins (see, for example, Patent Document 1). Such heat exchangers are called slitless fin heat exchangers. In the slitless fin heat exchanger, vortex flow of air is generated due to the collision of the air against the projections on the fin surface. The heat exchange performance of the heat exchanger is improved by directing the vortex flow along the fin surface. Furthermore, since the slitless fin heat exchanger does not have cut-and-raised portions on the fins, it has good drainage of condensed water, and the formation of frost on a part of the fins is suppressed. . Therefore, the slitless fin heat exchanger can ensure heat exchange performance under wet conditions.

Japanese Patent No. 4815612

By the way, in the conventional slitless fin heat exchanger, the draft resistance increases due to the generation of the vortex flow and the vortex flow over the convex portion. Therefore, when a conventional slitless fin heat exchanger is applied to a refrigerating cycle device, the blowing efficiency of the blower may decrease, and the efficiency of the entire refrigerating cycle device may decrease. In order to reduce the airflow resistance, it is conceivable to reduce the amplitude of the corrugated unevenness formed on the fin, the number of unevenness, or the angle of attack with respect to the main stream of the air flow. However, if these parameters are reduced, the effect of improving the heat exchange performance due to the vortex flow is reduced, and the performance of the heat exchanger may be degraded. That is, the conventional heat exchanger has a problem that it is impossible to achieve both maintenance of heat exchange performance and reduction of airflow resistance.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems in the prior art, and provides a heat exchanger and a refrigeration cycle apparatus having the same that can reduce ventilation resistance while maintaining heat exchange performance. for the purpose.

A heat exchanger of the present invention is a heat exchanger to which air is supplied by an air blower, comprising heat transfer tubes extending in a direction intersecting with a direction of circulation of the air supplied from the air blower, and heat transfer tubes connected to the heat transfer tubes. fins, wherein the fins protrude in the thickness direction of the fins and are provided with at least one convex-facing surface facing the supplied air; and a switching portion for switching between the convex portion and the concave portion, and a boundary line between the convex portion and the switching portion, When the one formed by the attacking surface of the convex portion is the windward boundary line of the convex portion, and the boundary line between the concave portion and the switching portion formed by the attacking surface of the concave portion is the windward boundary line of the concave portion. and all the first angles formed on the leeward side by the air circulation direction and the windward boundary line of the convex portion are equal to all the second angles formed on the leeward side by the air circulation direction and the windward boundary line of the recessed portion. is smaller than the angle.

Further, a refrigeration cycle apparatus of the present invention includes the heat exchanger of the present invention, and the blower that supplies the air to the heat exchanger in a direction in which the air flows.

As described above, according to the present invention, the vortex flow that has crossed over the top of the convex portion flows into the top portion of the concave portion, thereby increasing the flow velocity and reducing the interference between the air currents generated in each of the convex portion and the concave portion. Therefore, the ventilation resistance can be reduced while maintaining the heat exchange performance.

1 is a schematic diagram showing an example of a configuration of a refrigeration cycle apparatus according to Embodiment 1; FIG. 1 is a perspective view showing an example of a configuration of a heat exchanger according to Embodiment 1; FIG. FIG. 2 is a cross-sectional view showing a main part of an example of a windward heat exchanger of the heat exchanger according to Embodiment 1; 4 is a cross-sectional view along the ridge line R of the convex portion in the region A of FIG. 3; FIG. FIG. 4 is a schematic diagram showing an example of the shape of a convex portion in FIG. 3; 4 is a schematic diagram showing an example of the shape of a recess in FIG. 3; FIG. It is a schematic diagram for explaining the flow of air on a convex part. It is a schematic diagram for explaining the flow of air over the recess. FIG. 4 is a schematic diagram showing another example of the shape of the convex portion of FIG. 3; FIG. 4 is a schematic diagram showing another example of the shape of the recess in FIG. 3; FIG. 7 is a cross-sectional view showing a main part of a first modification of the windward heat exchanger of the heat exchanger according to Embodiment 1; FIG. 12 is a cross-sectional view along the ridge line R of the convex portion in the region A of FIG. 11; FIG. 12 is a schematic diagram showing an example of the shape of a convex portion in FIG. 11; FIG. 12 is a schematic diagram showing an example of the shape of the recess in FIG. 11; 12A and 12B are schematic diagrams showing other examples of the shape of the convex portion of FIG. 11; FIG. 12 is a schematic diagram showing another example of the shape of the recess in FIG. 11; FIG. 7 is a cross-sectional view showing a main part of a second modification of the windward heat exchanger of the heat exchanger according to Embodiment 1; FIG. 18 is a cross-sectional view along the ridge line R of the convex portion in the region A of FIG. 17; FIG. 18 is a schematic diagram showing an example of the shape of a convex portion in FIG. 17; FIG. 18 is a schematic diagram showing an example of the shape of the recess in FIG. 17; 18 is a schematic diagram showing another example of the shape of the convex portion of FIG. 17; FIG. FIG. 18 is a schematic diagram showing another example of the shape of the recess in FIG. 17; FIG. 7 is a cross-sectional view showing a main part of an example of a windward heat exchanger of a heat exchanger according to Embodiment 2; FIG. 24 is a cross-sectional view along the ridge line R of the convex portion in the region A of FIG. 23; It is a schematic diagram for explaining the flow of air on a convex part. It is a schematic diagram for explaining the flow of air over the recess. FIG. 11 is a perspective view showing an example of a configuration of a heat exchanger according to a first example of Embodiment 3; FIG. 11 is a perspective view showing an example of a configuration of a heat exchanger according to a second example of Embodiment 3;

Embodiments will be described below with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated. Note that the white arrows in the drawing indicate the direction of flow of air supplied from the blower to the heat exchanger. In addition, in the following drawings including FIG. 1, the size relationship of each component may differ from that of the actual machine. Furthermore, the forms of components appearing throughout the specification are merely examples, and are not limited to the components described in the specification.

Embodiment 1.
A refrigeration cycle apparatus according to Embodiment 1 will be described below. FIG. 1 is a schematic diagram showing an example of the configuration of a refrigeration cycle apparatus 1 according to Embodiment 1. As shown in FIG. The refrigeration cycle device 1 is mounted, for example, in an air conditioner. In the following description, the heat exchange fluid flowing through the heat transfer tubes of the heat exchanger of the refrigeration cycle device 1 is refrigerant, and the heat exchange fluid that exchanges heat with the heat exchange fluid is air.

[Configuration of the refrigeration cycle device 1]
A refrigeration cycle device 1 includes a compressor 2 , an indoor heat exchanger 3 , an indoor fan 4 , an expansion device 5 , an outdoor heat exchanger 6 , an outdoor fan 7 and a four-way valve 8 . A refrigerant circuit is formed by connecting the compressor 2, the indoor heat exchanger 3, the expansion device 5, the outdoor heat exchanger 6, and the four-way valve 8 by refrigerant piping.

The compressor 2 compresses refrigerant. Refrigerant compressed by the compressor 2 is discharged from the compressor 2 and sent to the four-way valve 8 . The compressor 2 can be configured by, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.

The indoor heat exchanger 3 functions as a condenser during heating operation, and functions as an evaporator during cooling operation. The indoor heat exchanger 3 is, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double tube heat exchanger, or a plate heat exchanger. etc. An indoor fan 4 is provided near the indoor heat exchanger 3 . The indoor blower 4 supplies the indoor heat exchanger 3 with air, which is the fluid to be heat-exchanged.

The expansion device 5 expands the refrigerant flowing out from the indoor heat exchanger 3 or the outdoor heat exchanger 6 to reduce the pressure. The throttle device 5 is composed of, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant. It should be noted that the expansion device 5 is not limited to this, and a mechanical expansion valve employing a diaphragm as a pressure receiving portion, a capillary tube, or the like may be applied.

The outdoor heat exchanger 6 functions as an evaporator during heating operation, and functions as a condenser during cooling operation. An outdoor fan 7 is provided near the outdoor heat exchanger 6 . The outdoor blower 7 supplies the outdoor heat exchanger 6 with air, which is a fluid to be heat exchanged.

The four-way valve 8 switches the flow of refrigerant between heating operation and cooling operation. That is, when the refrigeration cycle device 1 performs heating operation, the four-way valve 8 connects the discharge port of the compressor 2 and the indoor heat exchanger 3, and connects the suction port of the compressor 2 and the outdoor heat exchanger 6. Connecting. Further, when the refrigeration cycle device 1 performs cooling operation, the four-way valve 8 connects the discharge port of the compressor 2 and the outdoor heat exchanger 6, and connects the suction port of the compressor 2 and the indoor heat exchanger 3. Connecting.

[Operation of the refrigeration cycle device 1]
Next, the operation of the refrigeration cycle device 1 configured in this way will be described together with the flow of the refrigerant with reference to FIG. In addition, in FIG. 1 , the flow of the refrigerant when the refrigeration cycle device 1 performs the cooling operation is indicated by the dashed arrow. Further, in FIG. 1 , the flow of the refrigerant when the refrigeration cycle device 1 performs the heating operation is indicated by solid arrows.

(during cooling operation)
First, the case where the refrigeration cycle device 1 performs the cooling operation will be described. When the compressor 2 is driven, a high-temperature, high-pressure gaseous refrigerant is discharged from the compressor 2 . The high-temperature, high-pressure gas refrigerant discharged from the compressor 2 flows through the four-way valve 8 into the outdoor heat exchanger 6 functioning as a condenser. In the outdoor heat exchanger 6 , heat is exchanged between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the outdoor blower 7 . As a result, the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant.

The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 6 is expanded by the expansion device 5 and becomes a two-phase refrigerant in which the low-pressure gas refrigerant and the low-pressure liquid refrigerant are mixed. The two-phase refrigerant flows into the indoor heat exchanger 3 functioning as an evaporator. In the indoor heat exchanger 3 , heat is exchanged between the flowing two-phase refrigerant and the air supplied by the indoor fan 4 . As a result, the liquid refrigerant of the refrigerant in the two-phase state evaporates to become a low-pressure gas refrigerant. The low-pressure gas refrigerant flowing out of the indoor heat exchanger 3 flows into the compressor 2 via the four-way valve 8, is compressed into high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 2 again. This cycle is then repeated.

(During heating operation)
Next, a case where the refrigeration cycle device 1 performs heating operation will be described. When the compressor 2 is driven, a high-temperature, high-pressure gaseous refrigerant is discharged from the compressor 2 . The high-temperature, high-pressure gas refrigerant discharged from the compressor 2 flows through the four-way valve 8 into the indoor heat exchanger 3 functioning as a condenser. In the indoor heat exchanger 3 , heat is exchanged between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the indoor blower 4 . As a result, the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant.

The high-pressure liquid refrigerant flowing out of the indoor heat exchanger 3 is expanded by the expansion device 5 and becomes a two-phase refrigerant in which the low-pressure gas refrigerant and the low-pressure liquid refrigerant are mixed. The two-phase refrigerant flows into the outdoor heat exchanger 6 which functions as an evaporator. In the outdoor heat exchanger 6 , heat is exchanged between the flowing two-phase refrigerant and the air supplied by the outdoor blower 7 . As a result, the liquid refrigerant of the refrigerant in the two-phase state evaporates to become a low-pressure gas refrigerant. The low-pressure gas refrigerant that has flowed out of the outdoor heat exchanger 6 flows into the compressor 2 via the four-way valve 8, is compressed into high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 2 again. This cycle is then repeated.

When the refrigerant flows into the compressor 2 in a liquid state during the cooling operation and the heating operation described above, liquid compression occurs, which causes the compressor 2 to malfunction. Therefore, it is desirable that the refrigerant flowing out of the evaporator is a single-phase gas refrigerant.

In the evaporator, heat is exchanged between the air supplied from the blower and the refrigerant flowing through the heat transfer tubes forming the evaporator. At this time, moisture in the air condenses to form water droplets on the surface of the evaporator. Hereinafter, water generated on the surface of the evaporator due to condensation of moisture in the air is referred to as condensed water. Condensed water on the surface of the evaporator falls down along the surfaces of the fins and the heat transfer tubes and is discharged below the evaporator as drain water.

Also, during heating operation in a low outdoor temperature state, the condensed water adhering to the outdoor heat exchanger 6 functioning as an evaporator may freeze and become frost or ice. For this reason, some refrigeration cycle devices capable of heating operation perform a defrosting operation to remove frost adhering to the outdoor heat exchanger 6 when the temperature of the outside air drops below a certain level. The constant temperature is 0° C., for example.

The defrosting operation is to supply high-temperature and high-pressure gas refrigerant from the compressor 2 to the outdoor heat exchanger 6 in order to prevent frost from adhering to the outdoor heat exchanger 6 that functions as an evaporator. Frost and ice adhering to the outdoor heat exchanger 6 are melted by the high-temperature, high-pressure gas refrigerant supplied to the outdoor heat exchanger 6 . Note that the defrosting operation may be executed when the duration of the heating operation reaches the set time. The set time is, for example, 30 minutes. Further, when the temperature of the outdoor heat exchanger 6 is below a certain temperature, the defrosting operation may be performed before the heating operation. The constant temperature is minus 6° C., for example.

Furthermore, a bypass refrigerant pipe is provided between the discharge port of the compressor 2 and the outdoor heat exchanger 6 so that the high-temperature and high-pressure gas refrigerant can be directly supplied from the compressor 2 to the outdoor heat exchanger 6 during defrosting operation. It may be configured to be connected.

[Heat exchanger 10]
Next, the heat exchanger according to Embodiment 1 will be described. FIG. 2 is a perspective view showing an example of the configuration of the heat exchanger 10 according to the first embodiment. This heat exchanger 10 is applicable to the indoor heat exchanger 3 or the outdoor heat exchanger 6 provided in the refrigeration cycle apparatus 1 shown in FIG.

(Configuration of heat exchanger 10)
The heat exchanger 10 is a fin-and-tube heat exchanger. The heat exchanger 10 has, for example, a two-row structure, and includes a windward heat exchanger 10a and a leeward heat exchanger 10b. The windward heat exchanger 10a and the leeward heat exchanger 10b are arranged side by side along the X direction. The X direction corresponds to the flow direction of air supplied to the heat exchanger 10 by the indoor fan 4 or the outdoor fan 7 . The windward heat exchanger 10a is arranged on the windward side of the leeward heat exchanger 10b, that is, on the upstream side in the X direction. The leeward heat exchanger 10b is arranged on the leeward side, that is, the downstream side of the windward heat exchanger 10a in the X direction. Note that the number of rows of the heat exchanger 10 is not limited to this example. For example, the heat exchanger 10 may have a single-row structure, or may have a multi-row structure of three or more rows.

The heat exchanger 10 includes a windward header manifold 11 , a leeward header manifold 12 and an inter-row connecting member 13 . Refrigerant as a working fluid flows inside the windward header manifold 11 , the leeward header manifold 12 , and the inter-row connection member 13 . The windward header manifold 11 and the leeward header manifold 12 are arranged side by side along the X direction. The windward header collecting pipe 11 has a refrigerant inlet/outlet port 11a. The leeward header collecting pipe 12 has a refrigerant inlet/outlet port 12a. Heat transfer tubes 14 , which will be described later, provided in the windward heat exchanger 10 a have one end connected to the windward header collecting pipe 11 and the other end connected to the inter-row connection member 13 . The heat transfer tubes provided in the leeward heat exchanger 10 b have one end connected to the leeward header collecting pipe 12 and the other end connected to the inter-row connection member 13 .

The windward heat exchanger 10a and the leeward heat exchanger 10b have the same configuration. Therefore, hereinafter, the windward heat exchanger 10a will be described as a representative of both. If either the windward heat exchanger 10a or the leeward heat exchanger 10b can cover the heat exchange load, the heat exchanger 10 may be configured with only one of the windward heat exchanger 10a and the leeward heat exchanger 10b. .

The windward heat exchanger 10 a includes a plurality of heat transfer tubes 14 and a plurality of fins 15 . A plurality of heat transfer tubes 14 are arranged to extend along the Y direction orthogonal to the X direction. The Y direction is the horizontal direction. Refrigerant flows inside the heat transfer tubes 14 . In addition, the plurality of heat transfer tubes 14 are arranged in parallel and spaced apart from each other in the Z direction orthogonal to the X and Y directions. The Z direction is the vertical direction. The multiple heat transfer tubes 14 are made of, for example, an aluminum alloy.

The plurality of fins 15 are elongate plate-like members having surfaces 15a parallel to the X direction. The plurality of fins 15 are plate fins, for example. That is, the windward heat exchanger 10a in this case is a plate-fin-and-tube heat exchanger. A plurality of fins 15 are arranged to extend along the Z direction in which the heat transfer tubes 14 are arranged. In addition, the plurality of fins 15 are spaced apart from each other in the Y direction in which the heat transfer tubes 14 extend. The plurality of fins 15 are made of, for example, an aluminum alloy.

A plurality of heat transfer tubes 14 penetrate through the surfaces 15 a of the plurality of fins 15 . The air supplied to the windward heat exchanger 10a by the indoor blower 4 or the outdoor blower 7 contacts the heat transfer tubes 14 and the fins 15 between the heat transfer tubes 14 and between the fins 15. pass while

(Refrigerant flow in heat exchanger 10)
Next, the flow of refrigerant in the outdoor heat exchanger 6 will be described. The refrigerant flowing into the windward header collecting pipe 11 from the refrigerant inlet/outlet port 11a is distributed to the plurality of heat transfer tubes 14 of the windward heat exchanger 10a. The refrigerant that has flowed through the plurality of heat transfer tubes 14 flows into the inter-row connection member 13 . The refrigerant that has flowed into the inter-row connecting member 13 is distributed to the plurality of heat transfer tubes of the leeward heat exchanger 10b. The refrigerant that has flowed through the plurality of heat transfer tubes of the leeward heat exchanger 10b merges at the leeward header collecting pipe 12 and flows out from the refrigerant inlet/outlet port 12a. Note that the flow direction of the coolant is not limited to this, and may be reversed.

Note that the windward heat exchanger 10a shown in FIG. 2 is a side flow type heat exchanger in which the Y direction is horizontal and the Z direction is vertical. However, the windward heat exchanger 10a is not limited to a side flow type heat exchanger. For example, the windward heat exchanger 10a may be a downflow type heat exchanger in which the Y direction is the vertical direction and the Z direction is the horizontal direction. Also, the X direction, Y direction and Z direction need not be parallel to each other, and are not limited to the directions described above. That is, the X-direction, Y-direction, and Z-direction need only intersect with each other, and need not be arranged at right angles to each other.

(Heat exchange by heat exchanger 10)
Next, heat exchange when the outdoor heat exchanger 6 is the heat exchanger 10 will be described. In this case, the air supplied to the outdoor heat exchanger 6 by the outdoor fan 7 sequentially passes through the windward heat exchanger 10a and the leeward heat exchanger 10b. The air supplied to the windward heat exchanger 10 a passes between the plurality of heat transfer tubes 14 and between the plurality of fins 15 while being in contact with the plurality of heat transfer tubes 14 and the plurality of fins 15 . Since the heat transfer tubes 14 and the fins 15 are connected, the heat of the refrigerant flowing inside the heat transfer tubes 14 is transferred to the heat transfer tubes 14 and the fins 15 . That is, the surfaces of the plurality of heat transfer tubes 14 and the plurality of fins 15 serve as heat transfer surfaces. Heat is exchanged between these heat transfer surfaces and the air passing through the windward heat exchanger 10a. The heat exchange in the leeward heat exchanger 10b is also the same as in the windward heat exchanger 10a.

[Structure of Heat Transfer Tube 14 and Fin 15]
Next, the structures of the heat transfer tubes 14 and the fins 15 in the windward heat exchanger 10a of the heat exchanger 10 will be described in detail with reference to FIGS. 3 to 6. FIG. Note that, as described above, the leeward heat exchanger 10b also has the same configuration as the windward heat exchanger 10a, so the description thereof is omitted here.

FIG. 3 is a cross-sectional view showing a main part of an example of the windward heat exchanger 10a of the heat exchanger 10 according to the first embodiment. FIG. 3 is a cross-sectional view of the main part of the windward heat exchanger 10a observed in a direction parallel to the Y direction and opposite to the Y direction. Note that FIG. 3 shows two heat transfer tubes 14 as representatives. Further, solid lines drawn on the surface of the fin 15 in FIG. Also, the dashed lines drawn on the surface of the fin 15 in FIG. Here, in the following description, a direction parallel to the Y direction and opposite to the Y direction will be referred to as a negative Y direction.

As shown in FIG. 3, the cross section of the heat transfer tube 14 is, for example, circular. Inside the heat transfer tube 14, a flow path 14a through which the refrigerant flows is formed in a circular shape along the Y direction. The heat transfer tube 14 and the fins 15 are brought into close contact by mechanically expanding the heat transfer tube 14 . Note that the heat transfer tubes 14 and the fins 15 may be adhered to each other by brazing. Moreover, the cross-sectional shape of the heat transfer tube 14 is not limited to a circular shape, and may be an elliptical shape or a flat shape. Furthermore, the shape of the flow path 14a is not limited to a circular shape, and may be an elliptical shape or a square shape. Further, the number of flow paths 14a formed in one heat transfer tube 14 is not limited to one, and may be plural.

A plurality of convex portions 16 and a plurality of concave portions 17 are formed on the surface 15 a of the fin 15 . In this example, the plurality of protrusions 16 and the plurality of recesses 17 are, for example, continuously formed adjacent to each other.

Each of the plurality of protrusions 16 has a triangular pyramidal shape protruding in the Y direction, that is, in the thickness direction. Each of the plurality of convex portions 16 has an apex portion 16a indicated by a black dot in FIG. Although all the convex portions 16 formed on the surface 15a are formed with the apex portions 16a, only the convex portions 16 in the area A are shown with the apex portions 16a in FIG. is marked with a black dot.

Each of the plurality of recesses 17 is recessed in the negative Y direction, that is, in the thickness direction, and has a triangular pyramid shape protruding from a surface opposite to the surface 15a. Each of the recesses 17 has a top portion 17a indicated by white dots in FIG. The top portion 17a indicates the highest portion when the fin 15 is observed from the negative Y direction, and indicates the lowest bottom portion when the fin 15 is observed from the Y direction. In addition, all the concave portions 17 formed in the surface 15a are formed with the apex portions 17a. However, in FIG. is attached.

Also, in the example shown in FIG. 3, the plurality of convex portions 16 and the plurality of concave portions 17 are alternately formed along the Z direction. Furthermore, the plurality of protrusions 16 and the plurality of recesses 17 are alternately formed along the X direction.

FIG. 4 is a cross-sectional view along the ridgeline R of the convex portion 16 in the area A of FIG. The ridgeline R is indicated by a thick solid line in FIG. As shown in FIG. 4 , a switching portion 18 is formed at a location where the convex portion 16 is switched to the concave portion 17 or the concave portion 17 is switched to the convex portion 16 . This switching portion 18 is included in the reference plane M. As shown in FIG.

Here, when the distance from the reference plane M to the top 16a of the projection 16 is defined as a first distance ha, and the distance from the reference plane M to the top 17a of the recess 17 is defined as _a second distance _hb , the first distance h The relationship between _a and the second distance _hb is " _ha > _hb ". This is for reducing the ventilation resistance of the windward heat exchanger 10a and improving the heat exchange performance.

FIG. 5 is a schematic diagram showing an example of the shape of the convex portion 16 in FIG. As shown in FIG. 5, each of the plurality of protrusions 16 is formed with a plurality of surfaces including a protrusion-facing surface 16b that faces the supplied air. In this example, the protrusion 16 has two protrusion attacking surfaces 16b. Also, in the convex portion 16 , a convex portion boundary line is formed at the boundary with the switching portion 18 . Among the convex boundary lines, a convex windward boundary line 16c is formed as a boundary line formed by the convex attacking surface 16b.

FIG. 6 is a schematic diagram showing an example of the shape of the recess 17 in FIG. As shown in FIG. 6, each of the plurality of recesses 17 is formed with a plurality of surfaces including a recess facing surface 17b facing the supplied air. In this example, the recess 17 has one recess attacking surface 17b. Further, in the recess 17 , a recess boundary line is formed at the boundary with the switching portion 18 . Among the recess boundary lines, a recess windward boundary line 17c is formed as a boundary line formed by the recess attack surface 17b.

Here, the angle formed on the leeward side by the air circulation direction and the convex windward boundary line 16c is defined as _a first angle θa, and the angle formed by the air circulation direction and the recessed section windward boundary line 17c on the leeward side is defined as the first angle θa. Assuming two angles θ _b , the relationship between the first angle θ _a and the second angle θ _b is “θ _a <θ _b ”. This is because the air flow is intensively disturbed on the protruding portion 16 side of the fins 15 to promote heat transfer by the fins 15 .

Moreover, it is preferable that the first angle θ _a in the convex portion 16 is set within the range of “10°≦θ _a ≦35°”. By setting the first angle _θa of the convex portion 16 to an acute angle, the gathering and collision of the airflows on the convex portion attacking surface 16b is promoted, and the windward heat exchanger 10a is cooled while reducing the airflow resistance. This is because it is possible to improve the heat exchange performance of

[Air Flow in Fin 15]
Next, air flow in the fins 15 will be described. FIG. 7 is a schematic diagram for explaining the flow of air over the convex portion 16. As shown in FIG. FIG. 8 is a schematic diagram for explaining the flow of air over the recess 17. As shown in FIG. 7 and 8 each show an enlarged view of a portion of the surface 15a of the fin 15. FIG.

As shown in FIG. 7, on the convex portion 16 of the fin 15, the air flowing into the convex portion 16 bends along the convex portion attacking surface 16b and then flows from the convex portion 16 adjacent in the Z direction. collects and collides with the air. As a result, a vortex flow of air flowing in the X direction is formed. On the other hand, as shown in FIG. 8, the air flowing into the recess 17 over the recess 17 of the fin 15 crosses over the recess 17 and flows in the X direction.

When forming the projections 16 and the recesses 17 on the surface 15a of the fin 15, it is preferable that the projections 16 be formed on the upstream side in the air circulation direction. This is because the frost resistance can be improved by reducing the unevenness amplitude on the windward side. Here, the frost resistance indicates the resistance to blockage of air passages in the heat exchanger when frost forms on the heat exchanger.

Further, the description has been made so that the relationship of angle and distance is defined between the convex portion 16 and the concave portion 17. good. This also applies to the modified example and the second embodiment described below.

The shape of the convex portion 16 is not limited to this example, and for example, among the plurality of surfaces forming the convex portion 16, the surface positioned downstream in the air circulation direction may have an attack angle. FIG. 9 is a schematic diagram showing another example of the shape of the convex portion 16 of FIG. FIG. 10 is a schematic diagram showing another example of the shape of the recess 17 in FIG.

For example, as shown in FIG. 9, when the surface of the projection 16 on the downstream side in the direction of air flow has an angle of attack and the projection 16 and the recess 17 are formed adjacent to each other, the recess 17 As shown in FIG. 10, a recess attack surface 17b having an angle corresponding to the attack angle of the projection 16 is formed. As a result, the swirling flow of the air that flows over the tops 16a of the projections 16 and into the recesses 17 is improved, so that the heat exchange performance can be improved while reducing airflow resistance.

[Modification]
The shapes of the protrusions 16 and the recesses 17 formed in the fins 15 are not limited to the triangular pyramid shape described above. _If the relationship between the first distance ha and the second distance _hb and the relationship between the first angle _θa and the second angle _θb are satisfied, the convex portion 16 and the concave portion 17 can be formed in various shapes. can be done. Modified examples of the shape of the convex portion 16 and the concave portion 17 will be described below. Also, in the following description, the same reference numerals are given to the parts common to the examples shown in FIGS. 3 to 6, and detailed description thereof will be omitted.

(First modification)
FIG. 11 is a cross-sectional view showing a main part of a first modification of the windward heat exchanger 10a of the heat exchanger 10 according to the first embodiment. FIG. 11 shows an example of the windward heat exchanger 10a according to the second embodiment in the same observation direction and observation range as in FIG. The solid lines drawn on the surface of the fin 15 in FIG. 11 indicate portions that protrude toward the front side of the paper. In addition, the dashed lines drawn on the surface of the fin 15 in FIG. 11 indicate the portions that are recessed toward the back side of the paper surface.

A plurality of convex portions 16 and a plurality of concave portions 17 are formed on the surfaces 15a of the fins 15 of the windward heat exchanger 10a shown in FIG. In this example, the plurality of protrusions 16 and the plurality of recesses 17 are, for example, continuously formed adjacent to each other.

Each of the plurality of protrusions 16 has a quadrangular pyramid shape protruding in the Y direction, that is, in the thickness direction. Each of the plurality of projections 16 has an apex 16a indicated by black dots in FIG. Each of the plurality of recesses 17 is recessed in the negative Y direction, that is, in the thickness direction, and has a quadrangular pyramid shape protruding from the surface opposite to the surface 15a. Each of the recesses 17 has a top portion 17a indicated by white dots in FIG.

FIG. 12 is a cross-sectional view along the ridgeline R of the convex portion 16 in the area A of FIG. The ridgeline R is indicated by a thick solid line in FIG. As shown in FIG. 12, a switching portion 18 is formed at a location where the convex portion 16 and the concave portion 17 are switched. This switching portion 18 is included in the reference plane M. As shown in FIG. In this example, the relationship between the first distance ha from the reference plane M to the top 16a of the projection 16 and the second distance _hb from the reference plane M to the top 17a of the recess 17 is the same as in the example of _FIG . , "h _a >h _b ".

FIG. 13 is a schematic diagram showing an example of the shape of the projection 16 in FIG. 11. As shown in FIG. In the first modified example, each of the plurality of protrusions 16 includes two protrusion attacking surfaces 16b and two protrusions formed by these protrusion attacking surfaces 16b, respectively, as shown in FIG. It has a boundary line 16c.

FIG. 14 is a schematic diagram showing an example of the shape of the concave portion 17 in FIG. 11. As shown in FIG. In the first modification, each of the plurality of recesses 17 has, as shown in FIG. 14, two recess attacking surfaces 17b and two recess windward boundary lines 17c formed by the respective recess attacking surfaces 17b. have.

Here, a first angle θa formed on the leeward side between the air circulation direction and the convex windward boundary line 16c, and _a second angle _θb formed on the leeward side between the air circulation direction and the concave windward boundary line 17c. , is “θ _a <θ _b ” as in the examples of FIGS. 5 and 6 . Moreover, it is preferable that the first angle θ _a in the convex portion 16 is set within the range of “10°≦θ _a ≦35°” as in the example of FIG. 5 .

The shape of the convex portion 16 is not limited to this example, and for example, among the plurality of surfaces forming the convex portion 16, the surface positioned downstream in the air circulation direction may have an attack angle. FIG. 15 is a schematic diagram showing another example of the shape of the convex portion 16 of FIG. FIG. 16 is a schematic diagram showing another example of the shape of the recess 17 in FIG.

For example, as shown in FIG. 15, when the surface of the projection 16 on the downstream side in the direction of air flow has an angle of attack and the projection 16 and the recess 17 are formed adjacent to each other, the recess 17 , as shown in FIG. 16, a concave attack surface 17b having an angle corresponding to the angle of attack of the convex portion 16 is formed. As a result, the swirling flow of the air that flows over the tops 16a of the projections 16 and into the recesses 17 is improved, so that the heat exchange performance can be improved while reducing airflow resistance.

(Second modification)
FIG. 17 is a cross-sectional view showing a main part of a second modification of the windward heat exchanger 10a of the heat exchanger 10 according to the first embodiment. FIG. 17 shows an example of the windward heat exchanger 10a according to the second embodiment in the same observation direction and observation range as in FIGS. Note that the solid lines drawn on the surface of the fin 15 in FIG. 17 indicate portions that protrude toward the front side of the paper surface. In addition, the dashed lines drawn on the surface of the fin 15 in FIG. 17 indicate the portions that are recessed toward the back side of the paper surface.

A plurality of convex portions 16 and a plurality of concave portions 17 are formed on the surfaces 15a of the fins 15 of the windward heat exchanger 10a shown in FIG. In this example, the plurality of protrusions 16 and the plurality of recesses 17 are, for example, continuously formed adjacent to each other.

Each of the plurality of protrusions 16 has a pentagonal pyramid shape protruding in the Y direction, that is, in the thickness direction. Each of the plurality of projections 16 has an apex 16a indicated by black dots in FIG. Each of the plurality of recesses 17 is recessed in the negative Y direction, that is, in the thickness direction, and has a pentagonal pyramid shape protruding from a surface opposite to the surface 15a. Each of the recesses 17 has a top portion 17a indicated by white dots in FIG.

18 is a cross-sectional view along the ridge line R of the convex portion 16 in the region A of FIG. 17. FIG. The ridgeline R is indicated by a thick solid line in FIG. As shown in FIG. 18, a switching portion 18 is formed at a location where the convex portion 16 and the concave portion 17 are switched. This switching portion 18 is included in the reference plane M. As shown in FIG. In this example, the relationship between the first distance ha from the reference plane M to the top 16a of the projection 16 and the second distance _hb from the reference plane M to the top 17a of the recess 17 is the same as in the example of _FIG . , "h _a >h _b ".

FIG. 19 is a schematic diagram showing an example of the shape of the convex portion 16 of FIG. 17. FIG. In the second modification, each of the plurality of protrusions 16 includes two protrusion attacking surfaces 16b and two protrusions upwind formed by each of the protrusion attacking surfaces 16b, as shown in FIG. It has a boundary line 16c.

FIG. 20 is a schematic diagram showing an example of the shape of the concave portion 17 in FIG. 17. As shown in FIG. In the second modification, each of the plurality of recesses 17 has one recess attacking surface 17b and one recess windward boundary line 17c formed by the recess attacking surface 17b, as shown in FIG. is doing.

Here, a first angle θa formed on the leeward side between the air circulation direction and the convex windward boundary line 16c, and _a second angle _θb formed on the leeward side between the air circulation direction and the concave windward boundary line 17c. , is “θ _a <θ _b ” as in the examples of FIGS. 5 and 6 . Moreover, it is preferable that the first angle θ _a in the convex portion 16 is set within the range of “10°≦θ _a ≦35°” as in the example of FIG. 5 .

The shape of the convex portion 16 is not limited to this example, and for example, among the plurality of surfaces forming the convex portion 16, the surface positioned downstream in the air circulation direction may have an attack angle. FIG. 21 is a schematic diagram showing another example of the shape of the convex portion 16 of FIG. FIG. 22 is a schematic diagram showing another example of the shape of the recess 17 in FIG.

For example, as shown in FIG. 21, when the surface of the convex portion 16 on the downstream side in the direction of air flow has an angle of attack and the convex portion 16 and the concave portion 17 are formed adjacent to each other, the concave portion 17 22, a recess attack surface 17b having an angle corresponding to the attack angle of the projection 16 is formed. As a result, the swirling flow of the air that flows over the tops 16a of the projections 16 and into the recesses 17 is improved, so that the heat exchange performance can be improved while reducing airflow resistance.

As described above, in the windward heat exchanger _10a according to Embodiment 1, the first angle θa at the convex attack surface _16b of the convex portion 16 is equal to the second angle θb at the concave attack surface 17b of the concave portion 17. less than As a result, the vortex flow that has crossed over the apex 16a of the projection 16 flows into the apex 17a of the recess 17, thereby increasing the flow velocity. In addition, interference between airflows generated in each of the convex portion 16 and the concave portion 17 is reduced. Therefore, the ventilation resistance can be reduced while maintaining the heat exchange performance.

In the fins 15 of the windward heat exchanger _10a , the first distance ha from the reference plane M to the tops _16a of the protrusions 16 is longer than the second distance hb from the reference plane M to the tops 17a of the recesses 17. ing. Thereby, while reducing the ventilation resistance of the windward heat exchanger 10a, heat exchange property can be improved.

The convex portion 16 has an angle of attack on the surface on the downstream side in the air circulation direction, and the concave attack surface 17b of the concave portion 17 is formed at a second angle θ _b corresponding to the angle of attack of the convex portion 16. there is As a result, the swirling flow of the air flowing into the concave portion 17 is improved, so that the heat exchange performance can be improved while the ventilation resistance is reduced.

The protrusions 16 are arranged on the windward side of the air relative to the recesses 17 in the fins 15 . As a result, the amplitude of unevenness on the windward side is reduced, so that the frost resistance can be improved.

Further, in Embodiment 1, an example in which the refrigerating cycle device 1 is mounted in an air conditioner has been described, but the device in which the refrigerating cycle device 1 is mounted is not limited to the air conditioner. The refrigerating cycle device 1 can be installed in various devices having a refrigerating cycle circuit, such as refrigerators. That is, the refrigerating cycle device 1 can be installed in various devices having refrigerating cycle circuits.

Note that the number and arrangement of the plurality of protrusions 16 and the plurality of recesses 17 are not limited to this example. For example, each of the plurality of protrusions 16 and the plurality of recesses 17 may be two or more. Further, for example, each of the plurality of protrusions 16 and the plurality of recesses 17 may be arranged so as not to be adjacent to each other.

Further, the plurality of fins 15 may be corrugated fins in which flat portions and curved portions are alternately arranged by bending a plate member. That is, the windward heat exchanger 10a may be a corrugated fin-and-tube heat exchanger. The upwind heat exchanger 10a may also be a microchannel heat exchanger.

Embodiment 2.
Next, Embodiment 2 will be described. Embodiment 2 is different from Embodiment 1 in that the top of recess 17 is formed in a flat shape. It should be noted that, in the second embodiment, the same reference numerals are assigned to the parts that are common to the first embodiment, and detailed description thereof will be omitted.

[Structure of Heat Transfer Tube 14 and Fin 15]
FIG. 23 is a cross-sectional view showing a main part of an example of the windward heat exchanger 10a of the heat exchanger 10 according to the second embodiment. FIG. 23 shows an example of the windward heat exchanger 10a according to the second embodiment in the same observation direction and observation range as in FIG. In addition, the solid lines drawn on the surface of the fin 15 in FIG. 23 indicate portions that protrude toward the front side of the paper surface. In addition, broken lines drawn on the surface of the fin 15 in FIG. 23 indicate portions that are recessed toward the back side of the paper surface.

A plurality of convex portions 16 and a plurality of concave portions 17 are formed on the surfaces 15a of the fins 15 of the windward heat exchanger 10a shown in FIG. In this example, the plurality of protrusions 16 and the plurality of recesses 17 are, for example, continuously formed adjacent to each other.

Since each of the plurality of convex portions 16 is the same as that of the first embodiment, description thereof is omitted. Each of the plurality of recesses 17 is recessed in the negative Y direction, that is, in the thickness direction, protrudes from a surface opposite to the surface 15a, and has a triangular prism shape with a flat portion 17d having a flat projecting end.

Also, in the example shown in FIG. 23, the plurality of convex portions 16 and the plurality of concave portions 17 are alternately formed along the Z direction. Furthermore, the plurality of protrusions 16 and the plurality of recesses 17 are alternately formed along the X direction.

FIG. 24 is a cross-sectional view along the ridgeline R of the convex portion 16 in the area A of FIG. The ridge line R is indicated by a thick solid line in FIG. As shown in FIG. 24, a switching portion 18 is formed at a location where the convex portion 16 and the concave portion 17 are switched. This switching portion 18 is included in the reference plane M. As shown in FIG.

In this example, the relationship between the first distance ha from the reference plane M to the top portion _16a of the projection 16 and the second distance _hb from the reference plane M to the flat portion 17d of the recess 17 is the same as in the first embodiment. Similarly, " _ha > _hb ". Although not shown, the relationship between the first angle θa on the convex attack surface _16b of the convex portion 16 and the second angle _θb on the concave attack surface 17b of the concave portion 17 is the same as in the first embodiment. , “θ _a <θ _b ”.

[Air Flow in Fin 15]
Next, air flow in the fins 15 will be described. 25A and 25B are schematic diagrams for explaining the flow of air over the convex portion 16. FIG. FIG. 26 is a schematic diagram for explaining the flow of air over the recess 17. FIG. As shown in FIG. 25, on the convex portion 16 of the fin 15, the air flowing into the convex portion 16 bends along the convex portion attacking surface 16b and flows in the Z direction, as in the first embodiment. They gather and collide with the air flowing from the adjacent projections 16 . As a result, a vortex flow of air flowing in the X direction is formed. On the other hand, as shown in FIG. 26, the air flowing into the recess 17 over the recess 17 of the fin 15 crosses over the recess 17 and flows in the X direction.

Here, the air flowing into the convex portion 16 passes through the surface of the concave portion 17 on the upstream side on the side of the convex portion 16 . At this time, when the second distance _hb from the reference surface M to the flat portion 17d in the recess 17 is the same as in the first embodiment, the volume of the recess 17 increases compared to the recess 17 in the first embodiment. . By increasing the volume of the concave portion 17 in this way, more air can be introduced into the convex portion 16 on the downstream side, and the heat exchange performance can be improved.

Further, in the present second embodiment, in order to obtain heat exchange performance equivalent to that of the first embodiment, the volume of the recess 17 is made equivalent to that of the recess 17 of the first embodiment. Accordingly, in this case, recessed portion 17 is formed such that second distance _hb is smaller than in the first embodiment.

As described above, in the windward heat exchanger 10a according to the second embodiment, the concave portion 17 is recessed in the direction opposite to the convex portion 16 so that the top portion thereof has a flat shape parallel to the air circulation direction. It has a formed flat portion 17d. Thus, as in the first embodiment, it is possible to reduce ventilation resistance while maintaining heat exchange performance.

Embodiment 3.
Next, the third embodiment will be described. In the third embodiment, a case will be described in which the convex portions 16 and the concave portions 17 described above are applied to the fins of a heat exchanger having a configuration different from that of the heat exchanger 10 described in the first and second embodiments. In the third embodiment, parts common to those in the first and second embodiments are denoted by the same reference numerals, and detailed description thereof will be omitted.

[Configuration of heat exchanger 30A according to first example]
FIG. 27 is a perspective view showing an example of the configuration of a heat exchanger 30A according to the first example of the third embodiment. As shown in FIG. 27, the heat exchanger 30A includes multiple heat transfer tubes 34A, multiple fins 35A, and headers 31A and 32A. In the example shown in FIG. 27, the heat exchanger 30A is a longitudinal heat exchanger.

The plurality of heat transfer tubes 34A are arranged to extend vertically along the Z direction. Also, the plurality of heat transfer tubes 34A are arranged in parallel along the Y direction. Each of the plurality of heat transfer tubes 34A is, for example, a flat tube having a cross-sectional shape that is flat in one direction, and is formed therein with a plurality of fluid passages (not shown) for circulating a refrigerant, which is an internal fluid. Note that the plurality of heat transfer tubes 34A are not limited to flat tubes, and may be circular tubes, for example.

A header 31A is connected to one end in the Z direction of the heat transfer tube 34A. A header 32A is connected to the other end in the Z direction of the heat transfer tube 34A.

The plurality of fins 35A are arranged so as to extend from each of the plurality of heat transfer tubes 34A in the axial direction (Z direction) of the heat transfer tubes 34A and the windward side and the leeward side. The plurality of fins 35A are elongated plate-like members having surfaces 15a (see FIGS. 3 and 23) parallel to the X direction, which is the air circulation direction, as in the first and second embodiments. The plurality of fins 35A are made of a metal material having high thermal conductivity, such as aluminum alloy.

A plurality of convex portions 16 and a plurality of concave portions 17 are formed on the surface 15a of the plurality of fins 35A, as in the first or second embodiment. The plurality of protrusions 16 and the plurality of recesses 17 are, for example, continuously formed adjacent to each other. By forming the convex portions 16 and the concave portions 17 in the plurality of fins 35A in this manner, the heat exchange performance of the heat exchanger 30A is maintained while the airflow resistance is reduced, as in the first and second embodiments. be able to.

[Configuration of heat exchanger 30B according to second example]
FIG. 28 is a perspective view showing an example of the configuration of a heat exchanger 30B according to the second example of the third embodiment. As shown in FIG. 28, the heat exchanger 30B includes multiple heat transfer tubes 34B, multiple fins 35B, and headers 31B and 32B. In the example shown in FIG. 28, the heat exchanger 30B is a longitudinal heat exchanger.

The plurality of heat transfer tubes 34B are arranged to extend vertically along the Z direction. Also, the plurality of heat transfer tubes 34B are arranged in parallel along the Y direction. Each of the plurality of heat transfer tubes 34B is, for example, a flat tube having a cross-sectional shape that is flat in one direction, and is formed therein with a plurality of fluid passages (not shown) for circulating the refrigerant that is the internal fluid.

A header 31B is connected to one end of the heat transfer tube 34B in the Z direction. A header 32B is connected to the other end in the Z direction of the heat transfer tube 34B.

A plurality of fins 35B are corrugated fins and are arranged between adjacent heat transfer tubes 34B. Each of the plurality of fins 35B is made of a plate member made of a metal material having high thermal conductivity, such as an aluminum alloy.

The fins 35B are formed in a shape in which flat portions and curved portions are alternately arranged by bending a plate-like member. The plurality of planar portions are arranged substantially parallel to each other at regular intervals. The curved surface portions of the plurality of fins 35B are connected to the outer wall of the heat transfer tube 34B by brazing, welding, or the like.

A plurality of projections 16 projecting in the thickness direction and a plurality of recesses 17 recessing in the thickness direction are formed on the plane portions of the plurality of fins 35B, as in the first or second embodiment. The plurality of protrusions 16 and the plurality of recesses 17 are, for example, continuously formed adjacent to each other. By forming the convex portions 16 and the concave portions 17 in the plurality of fins 35B in this manner, the heat exchange performance of the heat exchanger 30B is maintained while the airflow resistance is reduced, as in the first and second embodiments. be able to.

As described above, in the third embodiment, the projections 16 and the recesses 17 described in the first and second embodiments are formed in the fins 35A and 35B of the longitudinal heat exchangers 30A and 30B. Thus, as in the first and second embodiments, the airflow resistance can be reduced while maintaining the heat exchange performance of the heat exchangers 30A and 30B.

1 Refrigerating cycle device 2 Compressor 3 Indoor heat exchanger 4 Indoor fan 5 Expansion device 6 Outdoor heat exchanger 7 Outdoor fan 8 Four-way valve 10, 30A, 30B Heat exchanger 10a Windward heat Exchanger 10b Downwind side heat exchanger 11 Upwind header collecting pipe 11a Refrigerant inlet/outlet 12 Downwind header collecting pipe 12a Refrigerant inlet/outlet 13 Connecting member between rows 14, 34A, 34B Heat transfer tube 14a Flow path 15, 35A, 35B fin, 15a surface, 16 protrusion, 16a top, 16b protrusion attacking surface, 16c protrusion windward boundary, 17 recess, 17a top, 17b recess attacking surface, 17c recess windward boundary, 17d Flat part 18 Switching part 31A, 31B, 32A, 32B Header.

Claims (6)

A heat exchanger supplied with air by a blower,
a heat transfer tube extending in a direction intersecting with the direction of circulation of the air supplied from the blower;
A fin connected to the heat transfer tube,
The fins are
a convex portion projecting in the thickness direction of the fin and formed with at least one convex portion-attacking surface facing the supplied air;
a recess formed with at least one recess facing surface that is recessed in a direction opposite to the projection and faces the supplied air;
Having a switching portion where the convex portion and the concave portion are switched,
Among the boundary lines between the convex portion and the switching portion, the one formed by the convex attack surface is defined as the convex windward boundary line, and the boundary line between the concave portion and the switching portion is the concave attack surface. When the one formed by is taken as the windward boundary of the recess,
All first angles formed on the leeward side by the air circulation direction and the windward boundary line of the convex portion are greater than all second angles formed on the leeward side by the air circulation direction and the windward boundary line of the concave portion. A small heat exchanger. 2. The heat exchanger according to claim 1, wherein a first distance from the reference plane including the switching portion to the top of the protrusion is longer than a second distance from the reference plane to the top of the recess. The recess is
3. The heat exchanger according to claim 1, wherein a top formed by recessing in a direction opposite to the projection is formed in a flat shape parallel to the direction of air flow. the protrusion and the recess are provided on the fin adjacent to each other;
The convex portion is
having an angle of attack on the surface on the downstream side in the direction of air flow;
The recess attacking surface of the recess comprises:
The heat exchanger according to any one of claims 1 to 3, wherein the convex portion is formed at the second angle corresponding to the angle of attack. The convex portion is
The heat exchanger according to any one of claims 1 to 4, wherein the fins are arranged on the windward side of the air relative to the recesses. A heat exchanger according to any one of claims 1 to 5;
A refrigeration cycle apparatus comprising: the blower that supplies the air to the heat exchanger in a direction in which the air flows.

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