WO2018008134A1

WO2018008134A1 - Heat exchanger

Info

Publication number: WO2018008134A1
Application number: PCT/JP2016/070185
Authority: WO
Inventors: 佑太小宮; 伊東　大輔
Original assignee: 三菱電機株式会社
Priority date: 2016-07-07
Filing date: 2016-07-07
Publication date: 2018-01-11
Also published as: EP3483544A1; EP3483544B1; JP6771557B2; EP3483544A4; JPWO2018008134A1

Abstract

Provided is a heat exchanger, which prevents condensation on the surface of a fin from being dispersed downwind. This heat exchanger comprises at least one heat exchanger tube (2) and a fin (3). The heat exchanger tube (2) includes flow paths (5) therein through which a refrigerant is circulated. The fin (3) is connected to the heat exchanger tube (2). The fin (3) includes a first end, a flat portion (3a), and a second end (3b). The flat portion (3a) has at least one linear rib (15) protruding from the flat portion (3a). The rib (15) includes a rib central portion (15b) and a part that has a straight portion (15a). The rib central portion (15b) is located at the center between the first end and the second end. The aforementioned part is continuous with the rib central portion (15b), and is formed so as to approach the first end or the second end towards the downstream side in the air circulation direction.

Description

Heat exchanger

This invention relates to a heat exchanger having corrugated fins.

Conventionally, heat exchangers having corrugated fins (hereinafter also referred to as fins) are known. For example, as shown in FIG. 1, as an example of a conventional heat exchanger, a parallel flow heat exchanger in which heat is exchanged between a refrigerant flowing in a flat tube and air outside the flat tube is well known. In the heat exchanger shown in FIG. 1, a plurality of flat tubes oriented in the vertical direction are arranged in parallel in the horizontal direction. Headers are provided at both ends of the flat tube in the vertical direction. Corrugated fins are provided between the plurality of flat tubes.

Here, conventionally, a heat exchanger incorporated in an air conditioner, in particular, a heat exchanger incorporated in an indoor unit of a separate type air conditioner is disposed so as to surround the cross flow fan inside the indoor unit (for example, Patent Document 1: Japanese Patent Application Laid-Open No. 2011-47600). Also when incorporating in the indoor unit using the parallel flow heat exchanger described above, the heat exchanger is disposed so as to surround the cross flow fan.

When the heat exchanger described above is used as an evaporator, the temperature of the flat tube and the surface of the fin is lower than the temperature of air. For this reason, when air passes through the heat exchanger, moisture in the air is condensed on the surfaces of the flat tubes and the fins, and condensed water is generated.

Condensed water generated on the fin surface of the heat exchanger includes gravity, the force given by the air passing through the heat exchanger, the surface tension between the flat tube and the condensed water, and the surface tension between the fin and the condensed water. , Act. Due to the above-described force relationship, the dew condensation water flows down the flat tube to the lower part of the heat exchanger, drops from the heat exchanger to the leeward side, or is held and retained between the fins. Take.

In the indoor unit described above, a drain pan is generally disposed below the heat exchanger. Condensed water flowing down from the lower part of the heat exchanger is received by the drain pan and discharged outside the room. However, the condensed water dripping from the heat exchanger to the leeward side is not received by the drain pan and may be discharged from the inside of the indoor unit to the outside of the indoor unit (for example, indoors).

In order to prevent the release of condensed water into the room, a configuration has been proposed in which one end surface of the flat tube is protruded from the end portion of the corrugated fin and the protruding portion is a drainage channel (for example, Patent Document 2: Japanese Patent Application Laid-Open No. 2004-177082). A configuration in which a drainage groove is provided in a flat tube has also been proposed (see, for example, Patent Document 3: Japanese Patent Laid-Open No. 7-190661). With such a configuration, it is supposed that drainage of condensed water in the heat exchanger can be promoted.

JP2011-47600A JP 2004-177082 A Japanese Patent Laid-Open No. 7-190661

Here, the dew condensation water generated on the fin surface of the heat exchanger may flow in the leeward direction along the fin surface due to gravity and the force given by the air passing through the heat exchanger. In addition, when condensed water flows down the fin surface in the leeward direction between the flat tubes arranged in parallel, not along the side surface portion or the fin curved surface portion of the flat tube, the condensed water is drained from the flat tube, or Spatter to the leeward side without obtaining the effect of drainage. As a result, the scattered condensed water may be discharged from the inside of the indoor unit to the outside (indoor).

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger that does not scatter the condensed water generated on the fin surface to the leeward side.

The heat exchanger according to this embodiment includes at least one heat transfer tube and fins. The heat transfer tube is provided so as to extend along one direction, and the refrigerant circulates therein. The fin is connected to at least one heat transfer tube. The fin includes a first end portion, a planar portion, and a second end portion. The first end is connected to the heat transfer tube. The flat surface portion is continuous with the first end portion. The second end portion is connected to the flat portion, and is located on the opposite side of the first end portion as viewed from the flat portion. The planar portion has at least one linear rib projecting from the planar portion. The at least one rib includes a rib center portion located in the center between the first end portion and the second end portion. The at least one rib includes a portion continuous with the rib central portion. The said part is formed so that it may approach either one of a 1st end part and a 2nd end part as it goes to the downstream of the distribution direction of air.

In the heat exchanger according to the present invention, when the dew condensation water generated on the flat portion of the fin moves to the downstream side (downward side) in the air flow direction, the fin contacts the rib and is guided by the rib. It flows in the direction of either the end or the second end. As a result, the condensed water flows to the surface of the heat transfer tube through the first end portion or flows along the second end portion of the fin, and finally the surface of the heat transfer tube and the second end portion of the fin It is collected in a drain pan. Therefore, it is possible to reduce the possibility that the condensed water flows as it is on the flat portion of the fin and is scattered on the leeward side.

1 is a schematic perspective view showing a heat exchanger according to Embodiment 1. FIG. 3 is a schematic side view showing the heat exchanger according to Embodiment 1. FIG. FIG. 3 is a schematic perspective view of a main part of the heat exchanger according to Embodiment 1. It is a principal part longitudinal cross-section schematic diagram of the heat exchanger which has a U-shaped rib which concerns on Embodiment 1. FIG. 3 is an enlarged schematic diagram of a U-shaped rib according to Embodiment 1. FIG. FIG. 6 is a schematic cross-sectional view taken along line VI-VI in FIG. 5. 6 is a schematic cross-sectional view of a modification of the U-shaped rib according to Embodiment 1. FIG. It is a cross-sectional schematic diagram of the indoor unit of the separate type air conditioner which concerns on Embodiment 1. FIG. It is a longitudinal cross-sectional schematic diagram of the dew condensation water adhering to the heat exchanger which concerns on Embodiment 1. FIG. 3 is a schematic cross-sectional view of condensed water adhering to the heat exchanger according to Embodiment 1. FIG. It is a principal part longitudinal cross-section schematic diagram of the heat exchanger which has a V-shaped rib which concerns on Embodiment 1. FIG. 3 is an enlarged schematic diagram of a V-shaped rib according to Embodiment 1. FIG. 3 is a schematic vertical sectional view of a main part of a heat exchanger having linear ribs according to Embodiment 1. FIG. 3 is an enlarged schematic view of a linear rib according to Embodiment 1. FIG. It is a summary perspective schematic diagram of the heat exchanger according to the second embodiment. 6 is a schematic perspective schematic view of a heat exchanger according to Embodiment 3. FIG. FIG. 6 is a summary perspective schematic diagram of a heat exchanger according to Embodiment 4. FIG. 9 is a summary perspective schematic view of a heat exchanger according to Embodiment 5.

Hereinafter, embodiments of the present invention will be described 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. Moreover, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

Embodiment 1 FIG.
<Configuration of heat exchanger>
FIG. 1 is a schematic perspective view showing a heat exchanger according to the present embodiment. FIG. 2 is a schematic side view showing the heat exchanger according to the present embodiment. FIG. 3 is a schematic perspective view of an essential part of the heat exchanger shown in FIGS. 1 and 2. 4 is a schematic vertical sectional view of an essential part of the heat exchanger shown in FIG. 2 and FIG. FIG. 5 is an enlarged schematic view of the rib shown in FIG. 6 is a schematic sectional view taken along line VI-VI in FIG. FIG. 7 is a schematic sectional view of a modification of the rib shown in FIG. FIG. 8 is a schematic cross-sectional view of an indoor unit of an air conditioner to which the heat exchanger according to the present embodiment is applied. FIG. 9 is a schematic vertical cross-sectional view for explaining the condensed water adhering to the heat exchanger. FIG. 10 is a schematic cross-sectional view for explaining the condensed water adhering to the heat exchanger. The configuration of the heat exchanger according to the present embodiment will be described with reference to FIGS.

As shown in FIGS. 1 to 3, the heat exchanger 1 according to the present embodiment includes a heat transfer tube 2 that is a plurality of flat tubes that are arranged to extend in the vertical direction and are arranged in parallel in the horizontal direction, and a plate. A fin 3 which is a corrugated fin formed of a member and disposed between the heat transfer tubes 2, and an inlet side header 4a and an outlet side header 4b which are disposed so as to extend horizontally and are connected to both ends of the heat transfer tube 2. Prepare.

The heat transfer tube 2 is formed with one or a plurality of flow paths 5 through which a refrigerant flows. In the heat transfer tube 2, a plurality of flow paths 5 are arranged in parallel. For this reason, the heat transfer tube 2 is a flat tube whose cross-sectional shape is not circular but rectangular. Further, the fin 3 is configured as a corrugated fin in which the flat surface portions 3a and the curved surface portions 3b are alternately arranged by bending the plate-like member, and the plurality of flat surface portions 3a are arranged substantially in parallel at predetermined intervals. is doing.

For example, the refrigerant flows from the refrigerant inlet / outlet 6 into the inlet header 4a. The refrigerant flowing into the inlet header 4a flows into the outlet header 4b through the flow path 5 inside the pipe. The refrigerant that has flowed into the outlet header 4b flows out of the refrigerant inlet / outlet 6 of the outlet header 4b. In addition, the distribution direction of a refrigerant | coolant is not limited to this, A reverse direction may be sufficient.

The heat transfer tube 2 and the fin 3 are brazed between the side surface portion 2 a of the outer wall of the heat transfer tube 2 and the curved surface portion 3 b of the fin 3. Air passes through the space between the adjacent flat portions 3 a in the fin 3. With such a configuration, in the heat exchanger 1, the refrigerant flowing through the flow path 5 inside the heat transfer tube 2 and the air passing between the fins 3 exchange heat.

As shown in FIGS. 4 and 5, the heat exchanger 1 (see FIG. 1) according to the present embodiment includes at least one linear rib 15 (hereinafter referred to as “vertical upward”) projecting vertically on the flat portion 3 a of the fin 3. Rib 15) is formed so as to straddle the center line of the space between the heat transfer tubes 2 arranged in parallel, that is, the center line of the flat portion 3 a of the fin 3. The rib 15 includes a rib central portion 15b disposed at a position overlapping the center line of the flat surface portion 3a, and a linear portion 15a at least at a part connected to the rib central portion 15b. The straight portion 15a of the rib 15 is formed to be inclined from the leeward direction indicated by the arrow in FIG. 5 toward the side surface portion 2a. A louver 16 may be formed on the flat surface portion 3 a of the fin 3.

As shown in FIGS. 4 and 5, at least a part of the linear rib 15 is a straight portion 15a, and the planar shape may be a U-shaped rib (also referred to as a U-shaped rib). . In the U-shaped rib 15, as shown in FIGS. 4 and 5, the central portion (rib central portion 15 b) connecting the linear portions 15 a at both ends is located on the windward side from the linear portion 15 a. The straight portion 15a is formed by being inclined by an angle θ from the leeward direction toward the side surface portion 2a (see FIG. 3). From a different point of view, the straight portion 15 a is inclined by an angle θ with respect to the center line of the flat portion 3 a of the fin 3.

The angle θ, which is the inclination angle of the straight portion 15a with respect to the leeward direction or the center line of the plane portion 3a, may be, for example, 10 ° to 80 °. The lower limit of the angle θ may be 20 ° or 30 °. Further, the upper limit of the angle θ may be 70 ° or 60 °.

As shown in FIG. 6, the cross-sectional shape of the rib 15 may be triangular. Moreover, as shown in FIG. 7, the cross-sectional shape of the rib 15 may be semicircular. In addition, the cross-sectional shape of the rib 15 is not limited to the shape shown in FIGS. 6 and 7, and any shape that can form a convex portion protruding from the surface of the flat portion 3 a can be employed.

<Configuration of air conditioner to which heat exchanger is applied>
FIG. 8 shows a case where the heat exchanger 1 of the present embodiment is applied to an indoor unit 7 of a separate type air conditioner used in a general household. As shown in FIG. 8, the indoor unit 7 includes a casing 8 that forms an outer shell, a heat exchanger 1 disposed inside the casing 8, and a cross flow fan 12. The casing 8 is provided with an inlet 9 and an outlet 10. In the indoor unit 7 shown in FIG. 8, two suction ports 9 are formed, but the number of the suction ports 9 may be three or more. An air passage 11 is formed from the inlet 9 to the outlet 10. In the indoor unit 7, the air taken in from the suction port 9 is heat-exchanged by the heat exchanger 1. When the cross flow fan 12 is driven, the heat-exchanged air is discharged into the room from the air outlet 10. For example, when the heat exchanger 1 is used as an evaporator during heat exchange of air, moisture of air passing between the fins 3 adheres to the surface of the heat transfer tube 2 and the surface of the fin 3 as dew. There are things to do. Therefore, the indoor unit 7 includes a drain pan 13 for receiving dew condensation water generated in the heat exchanger 1.

As shown in FIG. 8, the heat exchanger 1 may be arranged to be inclined from the vertical direction toward the cross flow fan 12 so as to surround the upper part of the cross flow fan 12. The heat exchanger 1 is installed in a state where the inlet header 4a is disposed on the lower side and the outlet header 4b is disposed on the upper side. The arrangement of the inlet header 4a and the outlet header 4b may be reversed. When the heat exchanger 1 is inclined and arranged toward the crossflow fan 12, the condensed water generated in the heat exchanger 1 has a force acting in the leeward direction given from the air passing through the heat exchanger 1, and The force given by gravity acts. Therefore, it is conceivable that the dew condensation water drops on the cross flow fan located on the leeward side of the heat exchanger 1 and is discharged into the room from the air outlet 10.

<Condensation water behavior in heat exchangers>
As shown in FIGS. 9 and 10, the condensed water adhering to the fin 3 (see FIG. 4) can be classified into three types depending on the adhering location. That is, the dew condensation water is the dew condensation water 14a that contacts the side surface 2a of the heat transfer tube 2, the dew condensation water 14b that contacts the curved surface portion 3b of the fin 3, the side surface 2a of the heat transfer tube 2, and the curved surface portion 3b of the fin 3. And dew condensation water 14c that is in contact with only the flat surface portion 3a of the fin 3 can be classified.

As shown in FIG. 8, a configuration is considered in which the heat exchanger 1 is disposed to be inclined from the vertical direction toward the cross flow fan 12 so as to surround the upper part of the cross flow fan 12. In this case, a force Fa given from the air passing through the heat exchanger 1 and a force Fg given by a gravitational force in the direction along the plane portion 3a act in the leeward direction on the dew condensation water. On the other hand, the surface tension F1 between the condensed water and the flat portion 3a of the fin acts in the windward direction. Moreover, the surface tension F2 between the dew condensation water 14a and the side surface part 2a acts on the dew condensation water 14a in contact with the side surface part 2a in the windward direction. Further, the surface tension F3 between the condensed water 14b and the curved surface portion 3b of the fin acts on the condensed water 14b in contact with the curved surface portion 3b of the fin in the windward direction.

In the condensed water 14a to 14c, the total force acting in the leeward direction is f1, and the total force acting in the leeward direction is f2.

When f1> f2 (when the force acting in the leeward direction is larger than the force acting in the leeward direction), the dew condensation waters 14a to 14c flow down the leeward direction along the surfaces of the fins 3 and the like, and the heat exchanger 1 May scatter to the leeward side.

When f1 ≦ f2 (when the force acting in the windward direction is larger than the force acting in the leeward direction), the dew condensation water 14a to 14c stays on the surface of the fin 3 and is scattered on the leeward side of the heat exchanger 1. do not do.

Hereinafter, for the condensed water 14a to 14c, the total sums f1 and f2 of the forces are expressed by the following equations.

Sum of forces acting in the leeward direction on the condensed water 14a to 14c f1 = Fa + Fg
Total force f2a = F1 + F2 acting in the windward direction on the condensed water 14a
Total force f2b = F1 + F3 acting in the windward direction on the condensed water 14b
Total force f2c = F1 acting in the windward direction on the condensed water 14c
As is clear from the above formula, the relations f2a> f2c and f2b> f2c are established. Therefore, the dew condensation water 14c is more likely to flow down in the leeward direction than the

dew condensation waters

14a and 14b, and is likely to be scattered on the leeward side.

In the condensed water 14c, when f1> f2c, the condensed water 14c flows down in the leeward direction. And the dew condensation water 14c collides with the linear rib 15 which protruded perpendicularly upwards shown in FIG. 4 and FIG. The dew condensation water 14c that has collided with the linear rib 15 flows along the linear portion 15a of the rib 15 along the extending direction of the linear portion 15a. For this reason, the said dew condensation water 14c contacts with the side part 2a of the heat exchanger tube 2, or the curved surface part 3b of the fin 3, and becomes dew condensation water 14a or dew condensation water 14b. That is, after the condensed water 14c is guided to the linear rib 15, it becomes the condensed water 14a or the condensed water 14b, so that the total force f2 acting in the windward direction on the condensed water is f2c (= F1). To f2a (= F1 + F2) or f2b (= F1 + F3). Thus, since the ratio of the

condensed water

14a, 14b having a relatively large sum of the forces acting on the condensed water in the windward direction increases, the ratio of the condensed water staying between the fins 3 increases, Condensed water is less likely to scatter on the leeward side of the exchanger 1.

In the case of f1> f2a in the condensed water 14a, that is, when the condensed water 14a flows down in the leeward direction, the condensed water 14a flows down in the leeward direction through the side surface portion 2a of the heat transfer tube 2. In the case of f1> f2b in the condensed water 14b, that is, when the condensed water 14b flows down in the leeward direction, the condensed water 14b flows down in the leeward direction along the curved surface portion 3b of the fin 3.

When the dew condensation water 14a flows down in the leeward direction along the side surface portion 2a of the heat transfer tube 2, the front portion 2b (hereinafter also referred to as a tube front portion) of the outer wall surface of the heat transfer tube 2 shown in FIG. Available. For this reason, the dew condensation water 14 a flows down to the lower part of the heat exchanger 1 through the front part 2 b (drainage channel) of the heat transfer tube 2. Moreover, also when the dew condensation water 14b flows down in the leeward direction along the curved surface part 3b of the fin 3, it similarly passes along the front part 2b (drainage channel) of the heat exchanger tube 2 adjacent to the curved surface part 3b. Condensed water 14b flows downward.

<Effects of heat exchanger>
Speaking from a different point of view, the heat exchanger 1 includes at least one heat transfer tube 2 and fins 3. The heat transfer tube 2 is provided so as to extend along one direction as shown in FIGS. 1 and 2. One direction is, for example, the direction of gravity. The heat transfer tube 2 includes a flow path 5 through which a refrigerant flows. The fin 3 is connected to at least one heat transfer tube 2. The fin 3 includes a first end (a portion joined to the heat transfer tube 2 in the curved surface portion 3b of the fin 3 in contact with the condensed water 14a in FIG. 9), a flat portion 3a, and a second end (in FIG. 9). And the curved surface portion 3b) of the fin 3 in contact with the condensed water 14b. The first end is connected to the heat transfer tube 2. The flat surface portion 3a is continuous with the first end portion. The second end portion (curved surface portion 3b) is located on the opposite side to the first end portion when viewed from the plane portion 3a. The flat portion 3a has at least one linear rib 15 protruding from the flat portion 3a. At least one rib 15 includes a rib center portion 15b located at the center between the first end portion and the second end portion (curved surface portion 3b). The at least one rib 15 is connected to the rib central portion 15b and is formed so as to approach either the first end portion or the second end portion (curved surface portion 3b) toward the downstream side in the air flow direction. Part (the part from the rib center part 15b to the end part of the rib 15). The said part contains the linear part 15a.

In addition, in the rib 15, the part formed so that either one of the said 1st end part and a 2nd end part may be made into the shape which does not include the linear part 15a shown in FIG. 5 in the planar shape. For example, the planar shape of the entire part may be curved. More specifically, the planar shape of the entire portion may be a curved shape that is convex toward the leeward side, or may be a curved shape that is convex toward the leeward side. The shape may be an arbitrary combination of convex curves and straight lines. That is, if the said part is extended so that it may approach either one of a 1st end part and a 2nd end as it goes to the leeward side from the rib center part 15b, arbitrary plane shapes can be employ | adopted.

Further, from a different point of view, as shown in FIG. 5, a virtual straight line 15c from the rib central portion 15b toward the end of the rib 15 is inclined from the leeward direction to the heat transfer tube 2 side. From a different point of view, the rib 15 is formed so that the virtual straight line 15c approaches either the first end or the second end as it goes downstream in the air flow direction. From another point of view, a part of the at least one rib 15 (rib central portion 15b) is located at the center of the plane portion 3a in the direction intersecting with the air flow direction. At least one rib 15 includes a straight portion 15a. The straight portion 15a is inclined by an angle θ with respect to the flow direction so as to approach either one of the first end portion and the second end portion (curved surface portion 3b) as it goes downstream in the air flow direction. Yes.

The at least one heat transfer tube 2 includes a first heat transfer tube (heat transfer tube 2 located on the right side in FIG. 4) and a second heat transfer tube (heat transfer tube 2 located on the left side in FIG. 4). The first heat transfer tube and the second heat transfer tube are arranged so as to sandwich the fin 3 therebetween. The first heat transfer tube and the second heat transfer tube are arranged to extend in parallel to each other. The first end of the fin 3 is connected to the first heat transfer tube. The outer peripheral surface of the second end portion (curved surface portion 3b) of the fin 3 is connected to the second heat transfer tube.

In this way, when the condensed water 14c adhering to the flat portion 3a of the fin 3 flows down to the leeward side, the condensed water 14c collides with the rib 15 and the flow direction thereof is changed, and the side surface portion of the heat transfer tube 2 is changed. It flows to the 2a side or the curved surface portion 3b side of the fin 3. As a result, the dew condensation water 14c comes into contact with the side surface part 2a of the heat transfer tube 2 or the curved surface part 3b of the fin 3, and becomes the dew condensation water 14a or the dew condensation water 14b shown in FIG. As a result, since the ratio of the

dew condensation water

14a and 14b remaining in the heat exchanger 1 can be increased, the possibility that the dew condensation water is scattered on the downstream side of the heat exchanger 1 can be reduced.

<Modification of heat exchanger>
FIG. 11 is a schematic cross-sectional view of an essential part showing a first modification of the heat exchanger shown in FIGS. 1 to 10, and FIG. 12 is an enlarged schematic view of a rib of the heat exchanger shown in FIG. The heat exchanger shown in FIGS. 11 and 12 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 10, except that the planar shape of the rib 15 is the same as that shown in FIGS. It is different from the exchanger. Specifically, as shown in FIG. 12, the linear rib 15 is a rib 15 having a V-shaped planar shape having a straight portion 15 a at least partially. The V-shaped rib 15 shown in FIGS. 11 and 12 has a central portion connecting the straight portions 15a at both ends positioned on the windward side of the straight portions 15a. The straight portion 15a included in the V-shaped rib 15 is formed so as to be inclined by an angle θ from the leeward direction toward the side surface portion 2a of the heat transfer tube 2. Even with the heat exchanger having such a configuration, the same effects as those of the heat exchanger shown in FIGS. 1 to 10 can be obtained.

FIG. 13 is a schematic cross-sectional view of an essential part showing a second modification of the heat exchanger shown in FIGS. 1 to 10, and FIG. 14 is an enlarged schematic view of a rib of the heat exchanger shown in FIG. The heat exchanger shown in FIG. 13 and FIG. 14 basically has the same configuration as the heat exchanger shown in FIG. 1 to FIG. 10, but the planar shape of the rib 15 is the heat shown in FIG. 1 to FIG. It is different from the exchanger. Specifically, as illustrated in FIG. 14, the linear rib 15 is a rib 15 having a linear planar shape. The linear rib 15 is formed so as to be inclined by an angle θ from the leeward direction toward the side surface portion 2 a of the heat transfer tube 2. Further, the plurality of linear ribs 15 are formed so that the inclination directions with respect to the center line of the flat surface portion 3a are different from each other. As shown in FIG. 13, the ribs 15 are formed so that the inclination directions with respect to the center line of the plane portion 3 a are alternately reversed with respect to the plurality of linear ribs 15 formed from the windward side toward the leeward side. May be. Even with the heat exchanger having such a configuration, the same effects as those of the heat exchanger shown in FIGS. 1 to 10 can be obtained.

Embodiment 2. FIG.
<Configuration of heat exchanger>
FIG. 15 is a schematic perspective view of a main part of the heat exchanger 1 according to the present embodiment. The heat exchanger shown in FIG. 15 basically has the same configuration as the heat exchanger shown in FIGS. 1 to 10, except that the leeward front portion 2b of the heat transfer tube 2 is the end of the fin 3 on the leeward side. The heat exchanger shown in FIGS. 1 to 10 is different from the heat exchanger shown in FIGS. If it says from a different viewpoint, the at least 1 heat exchanger tube 2 will contain the downstream edge part (part located in the downstream of the fin 3 in the heat exchanger tube 2) located in the downstream of the fin 3 in the distribution direction of air.

<Effects of heat exchanger>
As shown in FIG. 15, it is located between the front portion 2 b of the heat transfer tube 2 projecting further leeward than the end surface on the leeward side of the fin 3 and from the front portion 2 b to the downstream end of the fin 3. A part of the side surface portion 2 a of the heat transfer tube 2 can be used as the drainage channel 17. Therefore, the area that can be used as the drainage channel 17 is larger than that of the heat exchanger shown in FIGS. Therefore, even when the amount of the dew condensation water 14a to 14c generated in the heat exchanger 1 is large, the dew condensation water that has flowed to the drainage channel 17 through the surface of the heat transfer tube 2 or the curved surface portion 3b of the fin 3 is used as the heat exchanger 1. It can be made to flow down to the bottom. For this reason, the amount of condensed water scattered on the leeward side of the heat exchanger 1 can be reduced.

Embodiment 3 FIG.
<Configuration of heat exchanger>
FIG. 16 is a schematic perspective view of an essential part of the heat exchanger 1 according to the present embodiment. The heat exchanger shown in FIG. 16 basically has the same configuration as the heat exchanger shown in FIG. 15, but the portion (drainage channel) located on the leeward side of the fin 3 in the side surface portion 2 a of the heat transfer tube 2. 15 is different from the heat exchanger shown in FIG. 15 in that a recess 2c is formed in a region functioning as 17). The recess 2 c is formed so as to extend along the extending direction of the heat transfer tube 2.

<Effects of heat exchanger>
In the heat exchanger shown in FIG. 16, a side surface portion 2 a in which a concave portion 2 c is formed at an end portion of the heat transfer tube 2 projecting further leeward than the end surface on the leeward side of the fin 3, a front surface portion 2 b of the heat transfer tube 2, However, it can be used as the drainage channel 17. That is, the area of the portion that can be used as the drainage channel 17 is wider than that of the heat exchanger shown in FIG. 15 by forming the recess 2c. Therefore, even when the amount of dew condensation water 14a to 14c generated in the heat exchanger 1 is larger than when the heat exchanger shown in FIG. 15 is used, the heat transfer tube 2 and the curved surface portion 3b of the fin 3 are transmitted. Thus, the dew condensation water that has flowed into the drainage channel 17 can flow down to the lower part of the heat exchanger 1. For this reason, the amount of condensed water scattered on the leeward side of the heat exchanger 1 can be reduced.

Embodiment 4 FIG.
<Configuration of heat exchanger>
FIG. 17 is a schematic perspective view of a main part of the heat exchanger 1 according to the present embodiment. The heat exchanger shown in FIG. 17 basically has the same configuration as that of the heat exchanger shown in FIG. 16, but the portion (drainage channel) located on the leeward side of the fin 3 in the side surface portion 2 a of the heat transfer tube 2. 16 is different from the heat exchanger shown in FIG. 16 in that a convex portion 2d is further formed on the downstream side of the concave portion 2c. The convex portion 2 d is formed so as to extend along the extending direction of the heat transfer tube 2.

<Effects of heat exchanger>
In the heat exchanger shown in FIG. 17, the side surface portion 2 a in which the concave portion 2 c and the convex portion 2 d are formed at the end portion of the heat transfer tube 2 projecting further leeward than the end surface on the leeward side of the fin 3, The front portion 2 b can be used as the drainage channel 17. That is, the area of the portion that can be used as the drainage channel 17 is further increased by forming the convex portion 2d as compared with the heat exchanger shown in FIG. Therefore, even when the amount of condensed water 14a to 14c generated in the heat exchanger 1 is larger than when the heat exchanger shown in FIG. 16 is used, the heat transfer pipe 2 and the curved surface portion 3b of the fin 3 are transmitted. Thus, the dew condensation water that has flowed into the drainage channel 17 can flow down to the lower part of the heat exchanger 1. For this reason, the amount of condensed water scattered on the leeward side of the heat exchanger 1 can be reduced.

Embodiment 5 FIG.
<Configuration of heat exchanger>
FIG. 18 is a schematic perspective view of a main part of the heat exchanger 1 according to the present embodiment. The heat exchanger shown in FIG. 18 basically has the same configuration as the heat exchanger shown in FIG. 15, but the portion (drainage channel) located on the leeward side of the fin 3 in the side surface portion 2 a of the heat transfer tube 2. 15 is different from the heat exchanger shown in FIG. 15 in that the water absorbing member 18 is disposed in the area functioning as The water absorbing member 18 is fixed to the side surface portion 2 a of the heat transfer tube 2. The water absorbing member 18 is formed so as to extend along the extending direction of the heat transfer tube 2.

<Effects of heat exchanger>
In the heat exchanger shown in FIG. 18, from the leeward side end surface of the fin 3 further comprising a water absorbing member 18 connected to the downstream side end portion of the heat transfer tube 2 (portion located on the downstream side of the fin 3 in the heat transfer tube 2). Moreover, the side part 2a to which the water absorption member 18 was fixed in the edge part of the heat exchanger tube 2 which protrudes to the leeward side, and the front part 2b of the heat exchanger tube 2 can be utilized as a drainage channel. That is, the ability to hold the condensed water in a portion that can be used as a drainage channel by arranging the water absorbing member 18 is higher than that of the heat exchanger shown in FIG. 15 than the heat exchanger shown in FIG. Therefore, even when the amount of dew condensation water 14a to 14c generated in the heat exchanger 1 is larger than when the heat exchanger shown in FIG. 15 is used, the heat transfer tube 2 and the curved surface portion 3b of the fin 3 are transmitted along the surface. The condensed water that has flowed to the water absorbing member 18 can flow down to the lower part of the heat exchanger 1. For this reason, the amount of condensed water scattered on the leeward side of the heat exchanger 1 can be reduced.

Note that any material can be used as the material of the water absorbing member 18 as long as it is a material having water absorption. For example, a sponge-like resin or a porous material can be used. Moreover, in FIG. 18, although the water absorption member 18 is arrange | positioned in the surface of the side part 2a of the heat exchanger tube 2, a groove | channel may be formed in the said side part 2a and the water absorption member 18 may be arrange | positioned inside the said groove | channel. . In this case, since the height at which the water absorbing member 18 protrudes into the air flow passage can be reduced, an increase in air flow resistance due to the water absorbing member 18 can be suppressed. Moreover, you may make the thickness of the water absorption member 18 and the depth of a groove | channel so that the surface of the water absorption member 18 may be located on the same surface as the part in which the groove | channel is not formed in the side part 2a.

Although the embodiments of the present invention have been described above, the above-described embodiments can be variously modified. The scope of the present invention is not limited to the above-described embodiment. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

The present invention is effectively used for a parallel flow heat exchanger and an air conditioner equipped with the parallel flow heat exchanger.

1 heat exchanger, 2 heat transfer tube, 2a side surface, 2b front surface, 2c concave, 2d convex, 3 fin, 3a flat surface, 3b curved surface, 4a inlet side header, 4b outlet side header, 5 flow path, 6 Refrigerant inlet / outlet, 7 indoor unit, 8 casing, 9 inlet, 10 outlet, 11 air passage, 12 cross flow fan, 13 drain pan, 14a, 14b, 14c condensed water, 15 rib, 15a straight part, 15b rib central part, 16 louvers, 17 drainage channels, 18 water-absorbing members.

Claims

At least one heat transfer tube through which refrigerant flows;
A fin connected to the at least one heat transfer tube;
The fin is
A first end connected to the heat transfer tube;
A plane portion connected to the first end;
A second end located on the opposite side of the first end as viewed from the plane,
The plane portion is
Having at least one linear rib projecting from the planar portion;
The at least one rib is
A rib central portion located in the center between the first end portion and the second end portion;
A heat exchanger that includes a portion that is connected to the rib central portion and is formed so as to approach either the first end portion or the second end portion toward the downstream side in the air flow direction.
The heat exchanger according to claim 1, wherein the portion of the at least one rib includes a straight portion.
The heat exchanger according to claim 1 or 2, wherein the at least one heat transfer tube includes a downstream end located on the downstream side of the fin.
The heat exchanger according to claim 3, wherein a surface of the downstream end includes a recess.
The heat exchanger according to claim 4, wherein the surface of the downstream end includes a convex portion located downstream of the concave portion in the flow direction.
The heat exchanger according to claim 3, further comprising a water absorbing member connected to the downstream end.
The at least one heat transfer tube includes a first heat transfer tube and a second heat transfer tube,
The first heat transfer tube and the second heat transfer tube are disposed so as to sandwich the fin therebetween,
The first end of the fin is connected to the first heat transfer tube;
The heat exchanger according to any one of claims 1 to 6, wherein the second end portion of the fin is connected to the second heat transfer tube.