WO2021001953A1

WO2021001953A1 - Heat exchanger and refrigeration cycle device

Info

Publication number: WO2021001953A1
Application number: PCT/JP2019/026420
Authority: WO
Inventors: 暁八柳; 前田　剛志; 石橋　晃
Original assignee: 三菱電機株式会社
Priority date: 2019-07-03
Filing date: 2019-07-03
Publication date: 2021-01-07
Also published as: CN114041037B; CN114041037A; EP3995775B1; JPWO2021001953A1; EP3995775A4; JP7166458B2; EP3995775A1

Abstract

A heat exchanger comprises: a plurality of heat exchanger modules arranged in parallel in a first direction at intervals from each other; and a header connected to the plurality of heat exchanger modules at the ends of the plurality of heat exchanger modules in a second direction that intersects with the first direction, wherein the plurality of heat exchanger modules comprise a heat transfer tube that extends in the second direction and a fin that extends in a third direction, the third direction intersecting with a plane parallel to the first and second directions, from a side edge portion of the heat transfer tube in the third direction, and in the fin, a plurality of convex portions that protrude in the first direction are formed on the front surface and the plurality of convex portions are respectively formed so as to configure a surface having an inclination angle with respect to the second direction and the third direction.

Description

Heat exchanger and refrigeration cycle equipment

The present invention relates to a heat exchanger and a refrigeration cycle apparatus provided with the heat exchanger, and particularly to a structure of fins connected to a heat transfer tube.

Conventionally, a heat exchange module having fin-shaped fins formed at the end in the ventilation direction of a heat transfer tube has been provided for the purpose of achieving both heat transfer performance under dry and wet conditions of the heat exchanger and defrosting property. A heat exchanger in which the heat exchange modules are arranged at intervals from each other is known (see, for example, Patent Document 1).

By arranging such a heat exchanger so that the direction of the pipe axis coincides with the direction of gravity, there is no resistor that hinders the sliding of condensed water or frost-melted water, so drainage is fast. That is, such a heat exchanger can reduce the liquid film thickness under wet conditions, and can quickly discharge the frost-melted water in the defrosting operation. Further, in such a heat exchanger, the heat transfer tube diameter is reduced and the heat exchange modules are arranged at high density, or the contact area between the refrigerant and the heat transfer tube is expanded by forming the inside into a multi-hole structure. The heat transfer performance can be improved. Therefore, such a heat exchanger can achieve both heat transfer performance under dry and wet conditions and defrosting property.

Japanese Unexamined Patent Publication No. 2008-202896

However, in the above-mentioned conventional heat exchanger, in the ventilation direction of the air passing through the heat exchanger, the dead water area generated downstream of the heat transfer tube is arranged so that the fins on the downstream side cover the dead water area. There is a problem that the flow velocity is low and the heat transfer coefficient between the fins and air is low.

The present invention is for solving the above-mentioned problems, and an object of the present invention is to provide a heat exchanger and a refrigeration cycle device capable of improving the heat transfer coefficient between fins and air.

The heat exchanger according to the present invention has a plurality of heat exchange modules arranged in parallel in the first direction at intervals from each other, and a plurality of end portions of the plurality of heat exchange modules in the second direction intersecting the first direction. A header connected to a heat exchange module is provided, and a plurality of heat exchange modules include a heat transfer tube extending in a second direction and a heat transfer tube in a third direction intersecting a plane parallel to the first direction and the second direction. A fin extending from a side edge portion in a third direction is provided, and the fin is formed with a plurality of convex portions projecting in the first direction on the surface, and the plurality of convex portions are formed in the second direction and the third direction, respectively. It is formed so as to form a surface having an inclination angle with respect to the relative.

The refrigeration cycle apparatus according to the present invention is provided with the heat exchanger according to the present invention.

According to the present invention, the heat exchanger is formed so that a plurality of convex portions form a surface having an inclination angle with respect to the second direction and the third direction, respectively. In the heat exchanger, the air flow is agitated by the collision of the air flow with the surfaces inclined with respect to the second direction and the third direction. Therefore, in the heat exchanger, air also flows into the surface of the fins on the downstream side of the heat transfer tube, and the flow velocity of air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

It is a refrigerant circuit diagram which shows the structure of the refrigeration cycle apparatus provided with the heat exchanger according to Embodiment 1. FIG. It is a perspective view which shows schematic structure of the heat exchanger which concerns on Embodiment 1. FIG. It is a conceptual diagram which looked at the heat exchanger which concerns on Embodiment 1 from the side. FIG. 5 is a cross-sectional view schematically showing a cross section taken along line AA of the heat exchange module shown in FIG. FIG. 5 is an enlarged view of a heat exchange module constituting the heat exchanger according to the first embodiment. FIG. 5 is a cross-sectional view schematically showing a cross section taken along line BB of the fin shown in FIG. FIG. 5 is a cross-sectional view schematically showing a cross section taken along line CC of the fin shown in FIG. It is an enlarged view of the fin of the heat exchange module shown in FIG. FIG. 5 is a cross-sectional view schematically showing the configuration of the DD line cross-sectional position of the fin shown in FIG. 8 is a cross-sectional view schematically showing the configuration of the EE line cross section of the fins shown in FIGS. 8 and 9. FIG. 5 is an enlarged view of a heat exchange module of a modified example constituting the heat exchanger according to the first embodiment. It is an enlarged view of the heat exchange module which constitutes the heat exchanger which concerns on Embodiment 2. FIG. It is an enlarged view of the heat exchange module which comprises the heat exchanger which concerns on Embodiment 3. FIG. It is an enlarged view of the heat exchange module which comprises the heat exchanger which concerns on Embodiment 4. FIG. FIG. 5 is a cross-sectional view schematically showing a cross section of fins of a heat exchange module constituting the heat exchanger according to the fifth embodiment. FIG. 5 is a cross-sectional view schematically showing a cross section of fins of a heat exchange module constituting the heat exchanger according to the sixth embodiment. FIG. 5 is a cross-sectional view schematically showing a cross section of a heat exchange module fin of another example constituting the heat exchanger according to the sixth embodiment. FIG. 5 is a cross-sectional view schematically showing a cross section of fins of a heat exchange module constituting the heat exchanger according to the seventh embodiment. FIG. 5 is an enlarged view of a heat exchange module constituting the heat exchanger according to the eighth embodiment. FIG. 5 is a cross-sectional view schematically showing a cross section taken along line FF of the fin shown in FIG. FIG. 5 is a cross-sectional view schematically showing a GG line cross section of the fin shown in FIG. FIG. 5 is an enlarged view of a heat exchange module constituting the heat exchanger according to the ninth embodiment. FIG. 6 is a cross-sectional view schematically showing a cross section of the fin shown in FIG. 22 along the line HH. FIG. 2 is a cross-sectional view schematically showing a cross section of the fin shown in FIG. 22 along the line I-I.

Hereinafter, the heat exchanger 50 according to the first embodiment will be described with reference to the drawings and the like. In the following drawings including FIG. 1, the relative dimensional relationships and shapes of the constituent members may differ from the actual ones. Further, in the following drawings, those having the same reference numerals are the same or equivalent thereof, and this shall be common to the entire text of the specification. In addition, terms that indicate directions (for example, "top", "bottom", "right", "left", "front", "rear", etc.) are used as appropriate for ease of understanding. For convenience of explanation, it is described as such, and does not limit the arrangement and orientation of the device or component. In the specification, the positional relationship between the constituent members, the extending direction of each constituent member, and the arrangement direction of each constituent member are, in principle, those when the heat exchanger 50 is installed in a usable state. ..

Embodiment 1.
[Refrigeration cycle device 100]
FIG. 1 is a refrigerant circuit diagram showing a configuration of a refrigeration cycle device 100 provided with a heat exchanger 50 according to the first embodiment. In FIG. 1, the arrow indicated by the dotted line indicates the direction in which the refrigerant flows in the refrigerant circuit 110 during the cooling operation, and the arrow indicated by the solid line indicates the direction in which the refrigerant flows during the heating operation. .. First, the refrigeration cycle apparatus 100 provided with the heat exchanger 50 will be described with reference to FIG. In the present embodiment, the air conditioner is illustrated as the refrigerating cycle device 100, but the refrigerating cycle device 100 is, for example, refrigerating a refrigerator or a freezer, a vending machine, an air conditioner, a refrigerating device, a water heater, or the like. Used for applications or air conditioning applications. The illustrated refrigerant circuit 110 is an example, and the configuration of circuit elements and the like is not limited to the contents described in the embodiment, and can be appropriately changed within the scope of the technique according to the embodiment. ..

The refrigerating cycle device 100 has a refrigerant circuit 110 in which a compressor 101, a flow path switching device 102, an indoor heat exchanger 103, a decompression device 104, and an outdoor heat exchanger 105 are cyclically connected via a refrigerant pipe. .. A heat exchanger 50, which will be described later, is used for at least one of the outdoor heat exchanger 105 and the indoor heat exchanger 103. The refrigeration cycle device 100 has an outdoor unit 106 and an indoor unit 107. The outdoor unit 106 includes a compressor 101, a flow path switching device 102, an outdoor heat exchanger 105 and a decompression device 104, and an outdoor blower 108 that supplies outdoor air to the outdoor heat exchanger 105. The indoor unit 107 includes an indoor heat exchanger 103 and an indoor blower 109 that supplies air to the indoor heat exchanger 103. The outdoor unit 106 and the indoor unit 107 are connected to each other via two

extension pipes

111 and 112 which are a part of the refrigerant pipe.

The compressor 101 is a fluid machine that compresses and discharges the sucked refrigerant. The flow path switching device 102 is, for example, a four-way valve, and is a device that switches the flow path of the refrigerant between the cooling operation and the heating operation by controlling the control device (not shown).

The indoor heat exchanger 103 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the indoor air supplied by the indoor blower 109. The indoor heat exchanger 103 functions as a condenser during the heating operation and as an evaporator during the cooling operation.

The pressure reducing device 104 is, for example, an expansion valve, which is a device for reducing the pressure of the refrigerant. As the pressure reducing device 104, an electronic expansion valve whose opening degree is adjusted by the control of the control device can be used.

The outdoor heat exchanger 105 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the air supplied by the outdoor blower 108. The outdoor heat exchanger 105 functions as an evaporator during the heating operation and as a condenser during the cooling operation.

[Operation of refrigeration cycle device]
Next, an example of the operation of the refrigeration cycle device 100 will be described with reference to FIG. During the heating operation of the refrigeration cycle device 100, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the indoor heat exchanger 103 via the flow path switching device 102, and the air supplied by the indoor blower 109. Heat exchange with and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out of the indoor heat exchanger 103, and is in a low-pressure gas-liquid two-phase state by the vacuum distillation device 104. The low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 105 and evaporates by heat exchange with the air supplied by the outdoor blower 108. The evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101.

During the cooling operation of the refrigeration cycle device 100, the refrigerant flowing through the refrigerant circuit 110 flows in the opposite direction to that during the heating operation. That is, during the cooling operation of the refrigeration cycle device 100, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the outdoor heat exchanger 105 via the flow path switching device 102 and is supplied by the outdoor blower 108. It exchanges heat with the air and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out of the outdoor heat exchanger 105, and is in a low-pressure gas-liquid two-phase state by the vacuum distillation device 104. The low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 103 and evaporates by heat exchange with the air supplied by the indoor blower 109. The evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101.

[Heat exchanger 50]
FIG. 2 is a perspective view schematically showing the configuration of the heat exchanger 50 according to the first embodiment. FIG. 3 is a conceptual diagram of the heat exchanger 50 according to the first embodiment as viewed from the side. The heat exchanger 50 according to the first embodiment will be described with reference to FIGS. 2 to 3. The X-axis direction shown in the figure indicates the first direction, the Y-axis direction indicates the second direction, and the Z-axis direction indicates the third direction.

As shown in FIG. 3, the heat exchanger 50 has a plurality of headers 70 and a plurality of heat exchange modules 10 connected between the plurality of headers 70.

(Header 70)
The header 70 is connected to the ends of the plurality of heat exchange modules 10 in the stretching direction. The header 70 is formed so as to extend along the arrangement direction of the plurality of heat exchange modules 10. The header 70 functions as a fluid distribution mechanism in the heat exchanger 50 that distributes the refrigerant flowing into the heat exchanger 50 to the plurality of heat exchange modules 10. The header 70 also functions as a fluid merging mechanism in the heat exchanger 50, in which the refrigerant flowing out of the heat exchanger 50 flows out of the plurality of heat exchange modules 10 and merges.

The header 70 has a first header 71 and a second header 72. One of the first header 71 and the second header 72 functions as a fluid distribution mechanism, and the other functions as a fluid merging mechanism. The first header 71 is connected to one end of each of the plurality of heat exchange modules 10 in the stretching direction, and the second header 72 is connected to the other end of each of the plurality of heat exchange modules 10 in the stretching direction. .. That is, the first header 71 and the second header 72 are attached to both ends of the plurality of heat exchange modules 10 in the stretching direction. That is, the header 70 is connected to the plurality of heat exchange modules 10 at the ends of the plurality of heat exchange modules 10 in the second direction (Y-axis direction) intersecting the first direction (X-axis direction). More specifically, the first header 71 and the second header 72 are attached to both ends of the heat transfer tubes 20 constituting the plurality of heat exchange modules 10 in the extending direction. The first header 71 and the second header 72 are connected to the heat transfer tube 20 of the heat exchange module 10 so that the inside of the header 70 and the inside of the conduit of the heat transfer tube 20 communicate with each other.

The header 70 shown in FIGS. 2 and 3 is formed in a rectangular parallelepiped shape so as to form a longitudinal direction along the arrangement direction of the plurality of heat exchange modules 10. However, the shape of the header 70 is not limited to the rectangular parallelepiped shape, and may be another shape such as a cylindrical shape.

The first header 71 is formed with an inflow port (not shown) for the refrigerant flowing into the first header 71, or an outflow port (not shown) for the refrigerant flowing out from the first header 71. ing. Similarly, the second header 72 is formed with an inlet (not shown) of the refrigerant flowing into the second header 72, or an outlet of the refrigerant flowing out of the second header 72 (not shown). Is formed.

(Heat exchange module 10)
FIG. 4 is a cross-sectional view schematically showing a cross section taken along line AA of the heat exchange module 10 shown in FIG. The heat exchange module 10 exchanges heat between the air flowing along the heat exchange module 10 and the refrigerant flowing in the heat exchange module 10. The plurality of heat exchange modules 10 are arranged in parallel in the first direction (X-axis direction) at intervals from each other. The plurality of heat exchange modules 10 are arranged at predetermined intervals P along the longitudinal direction (X-axis direction) of the header 70. The heat exchange module 10 has a heat transfer tube 20 extending in the second direction (Y-axis direction). Further, the heat exchange module 10 has a first side edge portion of a heat transfer tube 20 in a third direction (Z-axis direction) that intersects a plane parallel to the first direction (X-axis direction) and the second direction (Y-axis direction). It has fins 30 extending in a third direction (Z-axis direction) from 20a and a second side edge portion 20b.

(Heat transfer tube 20)
Each of the plurality of heat transfer tubes 20 allows the refrigerant to flow inside. Each of the plurality of heat transfer tubes 20 extends between the first header 71 and the second header 72. Each of the plurality of heat transfer tubes 20 is arranged at intervals from each other, and is parallel to the axial direction which is the extending direction of the header 70. The plurality of heat transfer tubes 20 are arranged so as to face each other. A gap serving as an air flow path is formed between two adjacent heat transfer tubes 20 among the plurality of heat transfer tubes 20.

In the heat exchanger 50, the arrangement direction of the plurality of heat transfer tubes 20 which is the first direction is the horizontal direction. However, the arrangement direction of the plurality of heat transfer tubes 20 which is the first direction is not limited to the horizontal direction, and may be a vertical direction or a direction inclined with respect to the vertical direction. Similarly, in the heat exchanger 50, the extending direction of the plurality of heat transfer tubes 20 is the vertical direction. However, the extending direction of the plurality of heat transfer tubes 20 is not limited to the vertical direction, and may be a horizontal direction or a direction inclined with respect to the vertical direction.

In the heat transfer tubes 20 adjacent to each other among the plurality of heat transfer tubes 20, the heat transfer tubes 20 are not connected to each other by the heat transfer promoting member. The heat transfer promoting member is, for example, a plate fin, a corrugated fin, or the like.

When the heat exchanger 50 functions as an evaporator of the refrigeration cycle device 100, in each of the plurality of heat transfer tubes 20, the refrigerant flows inside the heat transfer tubes 20 from one end to the other end in the extension direction of the heat transfer tubes 20. Further, when the heat exchanger 50 functions as a condenser of the refrigeration cycle device 100, in each of the plurality of heat transfer tubes 20, the refrigerant flows inside the heat transfer tubes 20 from the other end in the extending direction of the heat transfer tubes 20 toward one end. It flows.

As shown in FIG. 4, the heat transfer tube 20 is a flat tube having a rectangular cross-sectional shape. The shape of the heat transfer tube 20 is not limited, and may be, for example, a flat tube having a flat cross-sectional shape in one direction such as an oval shape. The heat transfer tube 20 has a pair of first side edge portions 20a and a second side edge portion 20b, and a pair of flat surfaces 20c and flat surfaces 20d. In the cross section shown in FIG. 6, the first side edge portion 20a is formed so as to be flat between one end portion of the flat surface 20c and one end portion of the flat surface 20d. In the same cross section, the second side edge portion 20b is formed so as to be flat between the other end portion of the flat surface 20c and the other end portion of the flat surface 20d. The first side edge portion 20a and the second side edge portion 20b are not limited to the shape thereof, and are, for example, convex outward between the end portion of the flat surface 20c and the end portion of the flat surface 20d. It may be formed so as to become.

The first side edge portion 20a is a side edge portion arranged on the windward side, that is, on the front edge side in the flow of air passing through the heat exchanger 50. The second side edge portion 20b is a side edge portion arranged on the leeward side, that is, on the trailing edge side in the flow of air passing through the heat exchanger 50. In the following description, the direction perpendicular to the extending direction of the heat transfer tube 20 and along the flat surface 20c and the flat surface 20d may be referred to as the semimajor axis direction of the heat transfer tube 20. In FIG. 4, the long axis direction of the heat transfer tube 20 is the vertical direction, and the short axis direction is the horizontal direction. The major axis direction of the heat transfer tube 20 is the third direction.

The heat transfer tube 20 is formed with a plurality of refrigerant passages 22 arranged between the first side edge portion 20a and the second side edge portion 20b along the long axis direction. The heat transfer tube 20 is a flat perforated tube in which a plurality of refrigerant passages 22 through which the refrigerant flows are arranged in the air flow direction. Each of the plurality of refrigerant passages 22 is formed so as to extend in parallel with the second direction, which is the extending direction of the heat transfer tube 20. Each of the partition walls 23 between the adjacent refrigerant passages 22 is continuous to both ends in the extending direction of the heat transfer tube 20. The cross-sectional shape and the number of formed refrigerant passages 22 are not limited to the illustrated embodiment, and may be formed in various shapes such as a circular shape or a triangular shape, and may be formed by one or a plurality of formed numbers. Also good.

(Fin 30)
The fin 30 protrudes from the end of the heat transfer tube 20 in the long axis direction. The fin 30 is a plate-shaped portion provided so as to project from the first side edge portion 20a and the second side edge portion 20b and extend in the major axis direction of each of the plurality of heat transfer tubes 20. The fin 30 extends in the long axis direction of the heat transfer tube 20, but is not limited to this form. For example, the fins 30 may be formed in a state of being tilted at a predetermined angle in the arrangement direction of the plurality of heat transfer tubes 20 with respect to the major axis direction. The fin 30 may be formed by joining with the heat transfer tube 20, or may be integrally molded with the heat transfer tube 20. As described above, in the heat transfer tubes 20 adjacent to each other among the plurality of heat transfer tubes 20, the heat transfer tubes 20 are not connected to each other by the heat transfer promoting member. Therefore, each of the plurality of heat transfer tubes 20 is not connected to the heat transfer tubes 20 arranged adjacent to each other via the fins 30.

FIG. 5 is an enlarged view of the heat exchange module 10 constituting the heat exchanger 50 according to the first embodiment. The arrow shown in FIG. 5 represents the airflow FL. Further, FIG. 5 is a perspective view of a part of the heat exchange module 10, and a part of the heat exchange module 10 is not shown. The configuration of the fin 30 will be described in more detail with reference to FIG. A plurality of convex portions 40 projecting in the first direction (X-axis direction) are formed on the surface of the fin 30. The convex portion 40 is formed so as to project in a quadrangular pyramid shape. The shape of the convex portion 40 is not limited to the shape of a quadrangular pyramid. For example, the convex portion 40 may be formed in a hemispherical shape. The convex portion 40 is formed so that one surface in the first direction (X-axis direction) is projected and the other surface is recessed. The convex portions 40 are formed in parallel in the second direction (Y-axis direction) and in parallel in the third direction (Z-axis direction). The plurality of convex portions 40 are formed so that the ridge lines 41 are continuous in the third direction.

The plurality of convex portions 40 have a first convex portion 40a projecting from one surface and a second convex portion 40b projecting from the other surface in the first direction (X-axis direction). The first convex portion 40a is formed in parallel in the second direction (Y-axis direction) and in parallel in the third direction (Z-axis direction). Similarly, the second convex portion 40b is formed in parallel in the second direction (Y-axis direction) and in parallel in the third direction (Z-axis direction). The plurality of first convex portions 40a are formed so that the ridge line 41 is continuous in the third direction (Z-axis direction). Further, the plurality of second convex portions 40b are formed so that the ridge line 41 is continuous in the third direction (Z-axis direction). The plurality of first convex portions 40a and the plurality of second convex portions 40b are formed alternately in a direction oblique to a second direction (Y-axis direction) and a third direction (Z-axis direction).

FIG. 6 is a cross-sectional view schematically showing the BB line cross section of the fin 30 shown in FIG. The BB line cross section is a cross section of the fin 30 when viewed from the second direction (Y-axis direction) when the fin 30 is cut along the third direction (Z-axis direction). Further, FIG. 6 is a cross-sectional view of a part of the heat exchange module 10, and a part of the heat exchange module 10 is not shown. As shown in FIG. 6, each of the plurality of first convex portions 40a of the fins 30 is formed so as to form an inclined surface 42 having an inclination angle α with respect to the third direction (Z-axis direction). The inclined surface 42 is a surface on the side of the convex portion 40 located in the protruding direction, and is an inclined surface facing upstream with respect to the flow direction of the air flow.

FIG. 7 is a cross-sectional view schematically showing the CC line cross section of the fin 30 shown in FIG. The CC line cross section is a cross section of the fin 30 when viewed from the third direction (Z-axis direction) when the fin 30 is cut along the second direction (Y-axis direction). Further, FIG. 7 is a cross-sectional view of a part of the heat exchange module 10, and a part of the heat exchange module 10 is not shown. As shown in FIG. 7, each of the plurality of first convex portions 40a of the fins 30 is formed so as to form an inclined surface 43 having an inclination angle β with respect to the second direction (Y-axis direction).

[Operation example of heat exchanger 50]
The operation of the heat exchanger 50 according to the first embodiment will be described by exemplifying the operation when the heat exchanger 50 functions as an evaporator of the refrigeration cycle device 100. The gas-liquid two-phase refrigerant decompressed by the decompression device 104 flows into the heat exchanger 50 that functions as an evaporator. At this time, the refrigerant flows in from the first header 71 of the heat exchanger 50 and is separated into the same path as the number of the plurality of heat transfer tubes 20. Then, the refrigerant flows through the refrigerant passages 22 of the plurality of heat transfer tubes 20, absorbs heat and evaporates, flows out from the second header 72, and circulates in the refrigerant circuit 110.

[Effect of heat exchanger 50]
FIG. 8 is an enlarged view of the fins 30 of the heat exchange module 10 shown in FIG. FIG. 9 is a cross-sectional view schematically showing the configuration of the DD line cross-sectional position of the fin 30 shown in FIG. FIG. 10 is a cross-sectional view schematically showing the configuration of the EE line cross section of the fin 30 shown in FIGS. 8 and 9. The arrows shown in FIGS. 8 to 9 represent the airflow FL. 9 and 10 are cross-sectional views of a part of the heat exchange module 10, and a part of the heat exchange module 10 is not shown. In the heat exchanger 50, the airflow FL passes between the plurality of heat exchange modules 10. As shown in FIG. 8, in the heat exchanger 50, when the airflow FL collides with the first convex portion 40a formed on the fins 30, the airflow FL does not flow linearly but flows in a vortex. More specifically, the airflow FL collides with the inclined surface 42 of the first convex portion 40a shown in FIG. 6 to form a vortex rotating in the third direction (Z-axis direction) as shown in FIG. The airflow FL forming this vortex generates a high-speed flow HL that flows at high speed toward the recessed portion HA between the first convex portions 40a. Further, the airflow FL collides with the inclined surface 43 of the first convex portion 40a shown in FIG. 7, and forms a vortex rotating in the second direction (Y-axis direction) as shown in FIG. Therefore, the first convex portion 40a of the fin 30 forms a vortex that rotates in the second direction and the third direction with respect to the air flow FL, and agitates the air flow.

As described above, the plurality of convex portions 40 are formed so as to form surfaces having inclination angles with respect to the second direction (Y-axis direction) and the third direction (Z-axis direction), respectively. In the heat exchanger 50, the air flow is agitated by the collision of the air flow with the surfaces inclined in the second direction (Y-axis direction) and the third direction (Z-axis direction). Therefore, in the heat exchanger 50, air also flows into the surface of the fin 30 on the downstream side of the heat transfer tube 20, and the flow velocity of the air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

Further, each of the plurality of first convex portions 40a is formed in a quadrangular pyramid shape, and the ridge line 41 of the first convex portion 40a is formed so as to be continuous in the third direction (Z-axis direction). Therefore, in the heat exchanger 50, the airflow FL in which the vortex is formed tends to flow in the third direction (Z-axis direction) along the peak-shaped portion formed by the ridgeline 41 as a whole.

Further, the fin 30 has a plurality of convex portions 40 on the surface. Therefore, the surface area of the fin 30 can be increased as compared with the case where the convex portion 40 is not formed. As a result, the heat exchanger 50 can increase the efficiency of heat exchange between the refrigerant and air.

FIG. 11 is an enlarged view of the heat exchange module 1010I of a modified example constituting the heat exchanger 50 according to the first embodiment. Note that FIG. 11 is a perspective view of a part of the heat exchange module 10I, and a part of the heat exchange module 10I is not shown. As shown in FIG. 11, the heat transfer tube 120 of the heat exchange module 10 may be a circular tube instead of the flat tube described above. The fins 30 are provided so as to extend in the radial direction of the heat transfer tube 120 which is a circular tube.

Embodiment 2.
FIG. 12 is an enlarged view of the heat exchange module 10A constituting the heat exchanger 50 according to the second embodiment. The arrow shown in FIG. 12 represents the airflow FL. FIG. 13 is a perspective view of a part of the heat exchange module 10A, and the illustration of a part of the heat exchange module 10A is omitted. Further, the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. The heat exchange module 10A constituting the heat exchanger 50 according to the second embodiment has a different fin 30 configuration from the heat exchange module 10 constituting the heat exchanger 50 according to the first embodiment. More specifically, the configuration of the convex portion 140 of the heat exchange module 10A is different from the configuration of the convex portion 40 of the heat exchange module 10. The configuration of the convex portion 140 provided on the fin 30 will be described in more detail with reference to FIG.

The heat exchange module 10A has fins 30 provided on both sides of the heat transfer tube 20 with the heat transfer tube 20 interposed therebetween in the third direction (Z-axis direction). A plurality of convex portions 140 protruding in the first direction (X-axis direction) are formed on the surface of the fin 30. The convex portion 140 is formed in a columnar shape so as to extend along the plane of the fin 30. The convex portion 140 shown in FIG. 12 is formed in a pentagonal columnar shape, but the shape of the convex portion 140 is not limited to the shape. The convex portion 140 may be formed in a columnar shape whose side surface extends along the plane of the fin 30, and may be formed in a semi-cylindrical shape, for example.

The convex portion 140 is formed in parallel in the second direction (Y-axis direction) and in parallel in the third direction (Z-axis direction). In FIG. 12, in each fin 30, two convex portions 140 are formed in the third direction (Z-axis direction), but the number of convex portions 140 formed in the third direction (Z-axis direction) is two. It is not limited to, and may be one or three or more. Since it is preferable that there are many starting points for forming the vortex of the airflow FL described above, it is desirable that the number of convex portions 140 formed in the third direction (Z-axis direction) is large. Similarly, in FIG. 12, in each fin 30, 12 convex portions 140 are formed in the second direction (Y-axis direction), but the number of convex portions 140 formed in the second direction (Y-axis direction) is large. , Not limited to twelve. Since it is preferable that there are many starting points for forming the vortex of the airflow FL described above, it is desirable that the number of convex portions 140 formed in the second direction (Y-axis direction) is large.

The direction D1 in which the longitudinal direction of the convex portion 140 extends is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends. In other words, the direction D1 in which the longitudinal direction of the convex portion 140 extends is inclined with respect to the third direction (Z-axis direction). The direction D1 in which the longitudinal direction of the plurality of convex portions 140 extends extends in the same direction. The convex portion 140 is formed in a columnar shape and is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends, and is formed so as to form the inclined surface 42 and the inclined surface 43 described above. In the above description, the direction D1 is the direction in which the longitudinal direction of the convex portion 140 extends, but the direction D1 may be the direction in which the ridge line formed by the top of the convex portion 140 extends.

[Effect of heat exchanger 50]
As described above, each of the plurality of convex portions 140 is formed so as to form a surface having an inclination angle with respect to the third direction (Z-axis direction). In the heat exchanger 50, the air flow is agitated by the collision of the air flow with the surfaces inclined in the second direction (Y-axis direction) and the third direction (Z-axis direction). Therefore, in the heat exchanger 50, air also flows into the surface of the fin 30 on the downstream side of the heat transfer tube 20, and the flow velocity of the air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

Further, the fin 30 has a plurality of convex portions 140 on the surface. Therefore, the surface area of the fin 30 can be increased as compared with the case where the convex portion 140 is not formed. As a result, the heat exchanger 50 can increase the efficiency of heat exchange between the refrigerant and air.

Embodiment 3.
FIG. 13 is an enlarged view of the heat exchange module 10B constituting the heat exchanger 50 according to the third embodiment. The white arrows shown in FIG. 13 represent the airflow FL. Further, FIG. 13 is a perspective view of a part of the heat exchange module 10B, and a part of the heat exchange module 10B is not shown. Further, the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. The heat exchange module 10B constituting the heat exchanger 50 according to the third embodiment has a different fin 30 configuration from the heat exchange module 10A constituting the heat exchanger 50 according to the second embodiment. More specifically, the heat exchange module 10B has a convex portion 240 configuration different from that of the heat exchange module 10A convex portion 140. The configuration of the convex portion 240 provided on the fin 30 will be described in more detail with reference to FIG.

The heat exchange module 10B has fins 30 provided on both sides of the heat transfer tube 20 with the heat transfer tube 20 interposed therebetween in the third direction (Z-axis direction). A plurality of convex portions 240 protruding in the first direction (X-axis direction) are formed on the surface of the fin 30. The convex portion 240 is formed in a columnar shape so as to extend in the longitudinal direction along the plane of the fin 30. The convex portion 240 shown in FIG. 13 is formed in a pentagonal columnar shape, but the shape of the convex portion 240 is not limited to the shape. The convex portion 240 may be formed in a columnar shape so as to extend in the longitudinal direction along the plane of the fin 30, and may be formed in a semi-cylindrical shape, for example.

The convex portion 240 is formed in parallel in the second direction (Y-axis direction) and in parallel in the third direction (Z-axis direction). In FIG. 13, in each fin 30, two convex portions 240 are formed in the third direction (Z-axis direction), but the number of convex portions 240 formed in the third direction (Z-axis direction) is two. It is not limited to, and may be one or three or more. Since it is preferable that there are many starting points for forming the vortex of the airflow FL described above, it is desirable that the number of convex portions 240 formed in the third direction (Z-axis direction) is large. Similarly, in FIG. 13, 12 convex portions 240 are formed in each fin 30 in the second direction (Y-axis direction), but the number of convex portions 240 formed in the second direction (Y-axis direction) is large. , Not limited to twelve. Since it is preferable that there are many starting points for forming the vortex of the airflow FL described above, it is desirable that the number of convex portions 240 formed in the second direction (Y-axis direction) is large.

The fin 30 of the heat exchange module 10B has a first fin 30a and a second fin 30b. The first fin 30a is provided so as to extend from the first side edge portion 20a of the heat transfer tube 20 in the third direction (Z-axis direction), and the second fin 30b is provided from the second side edge portion 20b in the third direction. It is provided so as to extend in the (Z-axis direction). The first fin 30a is a fin 30 located on the upstream side of the airflow FL with respect to the heat transfer tube 20, and the second fin 30b is a fin 30 located on the downstream side of the airflow FL with respect to the heat transfer tube 20.

The direction D1 in which the longitudinal direction of the convex portion 240 provided on the first fin 30a extends is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends. In other words, the direction D1 in which the longitudinal direction of the convex portion 240 extends is inclined with respect to the third direction (Z-axis direction). The directions D1 in which the plurality of convex portions 240 provided in the first fin 30a extend in the longitudinal direction extend in the same direction. The convex portion 240 provided on the first fin 30a is formed in a columnar shape and is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends, and is formed so as to form the inclined surface 42 and the inclined surface 43 described above. ing. In the above description, the direction D1 is the direction in which the longitudinal direction of the convex portion 240 extends, but the direction D1 may be the direction in which the ridge line formed by the top of the convex portion 240 extends.

The direction D2 in which the longitudinal direction of the convex portion 240 provided on the second fin 30b extends is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends. In other words, the direction D2 in which the longitudinal direction of the convex portion 240 extends is inclined with respect to the third direction (Z-axis direction). The directions D2 in which the plurality of convex portions 240 provided in the second fin 30b extend in the longitudinal direction extend in the same direction, respectively. The convex portion 240 provided on the second fin 30b is formed in a columnar shape and is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends, and is formed so as to form the inclined surface 42 and the inclined surface 43 described above. ing. In the above description, the direction D2 is the direction in which the longitudinal direction of the convex portion 240 extends, but for example, the direction D2 may be the direction in which the ridge line formed by the top of the convex portion 240 extends.

Here, in the direction in which the longitudinal direction of the convex portion 240 extends, the end portion located on the heat transfer tube 20 side is referred to as the first end portion 240a, and the end portion located on the side opposite to the heat transfer tube 20 is referred to as the second end portion 240b. Define. The fins 30 are formed so that the first end portion 240a of the convex portion 240 provided on the first fin 30a and the second fin 30b is located on one end portion T1 side of the heat transfer tube 20. The fins 30 are formed so that the second end 240b of the convex portion 240 provided on the first fin 30a and the second fin 30b is located on the other end T2 side of the heat transfer tube 20.

As shown in FIG. 13, the direction D1 in which the convex portion 240 provided on the first fin 30a extends in the longitudinal direction and the direction D2 in which the convex portion 240 provided on the second fin 30b extends in the longitudinal direction are the third. It is formed so as to be tilted at a different angle with respect to the direction (Z-axis direction). That is, the fins 30 are provided on both sides of the heat transfer tube 20 with the heat transfer tube 20 interposed therebetween in the third direction (Z-axis direction). Then, the fins 30 have a direction D1 in which the longitudinal direction of the convex portion 240 provided on the fin 30 arranged on one side extends and a longitudinal direction of the convex portion 240 provided on the fin 30 arranged on the other side. Is formed so that the extending direction D2 is inclined in a direction different from the third direction (Z-axis direction).

In the aspect shown in FIG. 13, the direction D1 in which the convex portion 240 provided on the first fin 30a extends in the longitudinal direction and the direction D2 in which the convex portion 240 provided on the second fin 30b extends in the longitudinal direction are the heat transfer tubes. It is tilted symmetrically around 20. That is, in the heat exchange module 10, the inclination of the direction D1 with respect to the third direction (Z-axis direction) and the inclination of the direction D2 with respect to the third direction (Z-axis direction) are symmetrical with respect to the heat transfer tube 20. It is formed. The direction D1 in which the convex portion 240 provided in the first fin 30a extends in the longitudinal direction and the direction D2 in which the convex portion 240 provided in the second fin 30b extends in the longitudinal direction are symmetrical with respect to the heat transfer tube 20. It is not limited to the configuration that leans toward.

[Effect of heat exchanger 50]
The fins 30 are provided on both sides of the heat transfer tube 20 with the heat transfer tube 20 interposed therebetween in the third direction (Z-axis direction). Then, the direction D1 in which the longitudinal direction of the convex portion 240 provided on the fin 30 arranged on one side extends and the direction D2 in which the longitudinal direction of the convex portion 240 provided on the fin 30 arranged on the other side extends. And are formed so as to be inclined in different directions with respect to the third direction (Z-axis direction). Therefore, in the heat exchanger 50, the inclination direction of the convex portion 240 is different between the upstream side and the downstream side of the air flow with respect to the heat transfer tube 20, and the air flow is further agitated. Therefore, in the heat exchanger 50, air also flows into the surface of the fin 30 on the downstream side of the heat transfer tube 20, and the flow velocity of the air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

Further, the fins 30 are provided on both sides of the heat transfer tube 20 in the direction D1 in which the longitudinal direction of the convex portion 240 provided on the fins 30 arranged on one side extends and the fins 30 arranged on the other side. The convex portion 240 is formed so that the direction D2 in which the longitudinal direction extends is symmetrical with respect to the heat transfer tube 20. Therefore, in the heat exchanger 50, the inclination direction of the convex portion 240 is different between the upstream side and the downstream side of the air flow with respect to the heat transfer tube 20, and the air flow is further agitated. Therefore, in the heat exchanger 50, air also flows into the surface of the fin 30 on the downstream side of the heat transfer tube 20, and the flow velocity of the air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

Further, each of the plurality of convex portions 240 is formed so as to form a surface having an inclination angle with respect to the third direction (Z-axis direction). In the heat exchanger 50, the air flow is agitated by the collision of the air flow with the surfaces inclined in the second direction (Y-axis direction) and the third direction (Z-axis direction). Therefore, in the heat exchanger 50, air also flows into the surface of the fin 30 on the downstream side of the heat transfer tube 20, and the flow velocity of the air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

Further, the fin 30 has a plurality of convex portions 240 on the surface. Therefore, the surface area of the fin 30 can be increased as compared with the case where the convex portion 240 is not formed. As a result, the heat exchanger 50 can increase the efficiency of heat exchange between the refrigerant and air.

Embodiment 4.
FIG. 14 is an enlarged view of the heat exchange module 10C constituting the heat exchanger 50 according to the fourth embodiment. The white arrows shown in FIG. 14 represent the airflow FL. Further, FIG. 14 is a perspective view of a part of the heat exchange module 10C, and the illustration of a part of the heat exchange module 10C is omitted. Further, the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. The heat exchange module 10C constituting the heat exchanger 50 according to the fourth embodiment has a different fin 30 configuration from the heat exchange module 10A constituting the heat exchanger 50 according to the second embodiment. More specifically, the heat exchange module 10C has a convex portion 340 configuration different from that of the heat exchange module 10A convex portion 140. The configuration of the convex portion 340 provided on the fin 30 will be described in more detail with reference to FIG.

The heat exchange module 10C has fins 30 provided on both sides of the heat transfer tube 20 with the heat transfer tube 20 interposed therebetween in the third direction (Z-axis direction). A plurality of convex portions 340 protruding in the first direction (X-axis direction) are formed on the surface of the fin 30. The convex portion 340 is formed in a columnar shape so as to extend along the plane of the fin 30. The convex portion 340 shown in FIG. 14 is formed in a pentagonal columnar shape, but the shape of the convex portion 340 is not limited to the shape. The convex portion 340 may be formed in a columnar shape so as to extend along the plane of the fin 30, and may be formed in a semi-cylindrical shape, for example.

The convex portion 340 has a first convex portion 341 and a second convex portion 342. The first convex portion 341 and the second convex portion 342 are formed so as to be spaced apart from each other in the second direction (Y-axis direction). Here, in the direction in which the longitudinal direction of the convex portion 340 extends, the end portion located on the heat transfer tube 20 side is referred to as the first end portion 340a, and the end portion located on the side opposite to the heat transfer tube 20 is referred to as the second end portion 340b. Define.

The fin 30 is formed so that the first end portion 340a of the first convex portion 341 is located on the one end portion T1 side of the heat transfer tube 20. Further, the fin 30 is formed so that the second end portion 340b of the first convex portion 341 is located on the other end portion T2 side of the heat transfer tube 20.

In the first fin 30a, the direction D1 in which the longitudinal direction of the first convex portion 341 extends is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends. In other words, in the first fin 30a, the direction D1 in which the longitudinal direction of the first convex portion 341 extends is inclined with respect to the third direction (Z-axis direction). In the first fin 30a, the directions D1 in which the plurality of first convex portions 341 provided on the fin 30 extend in the longitudinal direction extend in the same direction. The first convex portion 341 is formed in a columnar shape and is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends, and is formed so as to form the inclined surface 42 and the inclined surface 43 described above.

In the second fin 30b, the direction D2 in which the longitudinal direction of the first convex portion 341 extends is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends. In other words, in the second fin 30b, the direction D2 in which the longitudinal direction of the first convex portion 341 extends is inclined with respect to the third direction (Z-axis direction). In the second fin 30b, the directions D2 in which the plurality of first convex portions 341 provided on the fin 30 extend in the longitudinal direction extend in the same direction.

The fin 30 is formed so that the first end portion 340a of the second convex portion 342 is located on the other end portion T2 side of the heat transfer tube 20. Further, the fin 30 is formed so that the second end portion 340b of the second convex portion 342 is located on the one end portion T1 side of the heat transfer tube 20.

In the first fin 30a, the direction D2 in which the longitudinal direction of the second convex portion 342 extends is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends. In other words, in the first fin 30a, the direction D2 in which the longitudinal direction of the second convex portion 342 extends is inclined with respect to the third direction (Z-axis direction). In the first fin 30a, the directions D2 in which the plurality of second convex portions 342 provided on the fin 30 extend in the longitudinal direction extend in the same direction. The second convex portion 342 is formed in a columnar shape and is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends, and is formed so as to form the inclined surface 42 and the inclined surface 43 described above.

In the second fin 30b, the direction D1 in which the longitudinal direction of the second convex portion 342 extends is inclined with respect to the direction in which the longitudinal direction of the heat transfer tube 20 extends. In other words, in the second fin 30b, the direction D1 in which the longitudinal direction of the second convex portion 342 extends is inclined with respect to the third direction (Z-axis direction). In the second fin 30b, the directions D1 in which the plurality of second convex portions 342 provided on the fin 30 extend in the longitudinal direction extend in the same direction.

In the convex portion 340, the first convex portion 341 is formed in parallel with the third direction (Z-axis direction). Further, in the convex portion 340, the second convex portion 342 is formed in parallel with the third direction (Z-axis direction). Further, the convex portion 340 is formed by continuously arranging the first convex portion 341 and the second convex portion 342 alternately in the second direction (Y-axis direction).

As shown in FIG. 14, the convex portions 340 have different inclinations with respect to the third direction (Z-axis direction), and the first convex portions formed at intervals from each other in the second direction (Y-axis direction). It has a portion 341 and a second convex portion 342. Then, the convex portion 340 is angled at regular intervals in the second direction (Y-axis direction) by the combination of the first convex portion 341 and the second convex portion 342 having different inclinations, and is folded back each time. It is formed in a linear shape that bends in the opposite direction. That is, the convex portion 340 is formed in a sawtooth shape or a wavy line shape in the second direction (Y-axis direction). Since it is preferable that there are many starting points for forming the vortex of the airflow FL described above, it is desirable that the number of convex portions 340 formed in the second direction (Y-axis direction) and the third direction (Z-axis direction) is large.

[Effect of heat exchanger 50]
The convex portions 340 have different inclinations with respect to the third direction (Z-axis direction), and the first convex portion 341 and the second convex portion formed at intervals from each other in the second direction (Y-axis direction). It has 342 and. Then, the convex portion 340 is angled at regular intervals in the second direction (Y-axis direction) by the combination of the first convex portion 341 and the second convex portion 342, and is folded back in the opposite direction each time. It is formed in a bent linear shape. Therefore, in the convex portion 340, a wall having a narrow width is formed in the third direction (Z-axis direction) in which the air flow flows, the air flowing in the third direction (Z-axis direction) easily collides with each other, and the air flow further. Is agitated. Therefore, in the heat exchanger 50, air also flows into the surface of the fin 30 on the downstream side of the heat transfer tube 20, and the flow velocity of the air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

Further, each of the plurality of convex portions 340 is formed so as to form a surface having an inclination angle with respect to the third direction (Z-axis direction). In the heat exchanger 50, the air flow is agitated by the collision of the airflow with the surfaces inclined in the second direction (Y-axis direction) and the third direction (Z-axis direction). Therefore, in the heat exchanger 50, air also flows into the surface of the fin 30 on the downstream side of the heat transfer tube 20, and the flow velocity of the air in the vicinity of the surface increases, so that the heat transfer coefficient is improved.

Further, the fin 30 has a plurality of convex portions 340 on the surface. Therefore, the surface area of the fin 30 can be increased as compared with the case where the convex portion 340 is not formed. As a result, the heat exchanger 50 can increase the efficiency of heat exchange between the refrigerant and air.

Embodiment 5.
FIG. 15 is a cross-sectional view schematically showing a cross section of fins 30 of the heat exchange module 10D constituting the heat exchanger 50 according to the fifth embodiment. The cross section shown in FIG. 15 is a schematic view of the BB line cross section of the fin 30 shown in FIG. Further, FIG. 15 is a cross-sectional view of a part of the heat exchange module 10D, and the illustration of a part of the heat exchange module 10D is omitted. The convex portion 40 shown on the fin 30 is an example, and any one of the convex portion 40 described above and the convex portion 440 described later is applied to the configuration described as the convex portion 40. In the following description, components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

The heat exchanger 50 includes a heat exchange module 10D having a heat transfer tube 20 and fins 30. In the heat exchange module 10D of the heat exchanger 50, the root portion 31 of the fin 30 which is the base for the heat transfer tube 20 is first with respect to the central portion 21 of the thickness of the heat transfer tube 20 in the first direction (X-axis direction). In the direction (X-axis direction), the plurality of convex portions 40 are arranged so as to be biased toward the protruding side.

[Effect of heat exchanger 50]
The root portion 31 of the fin 30 is arranged so as to be biased toward the protruding side of the convex portion 40 in the first direction (X-axis direction) with respect to the central portion 21 of the thickness of the heat transfer tube 20 in the first direction (X-axis direction). As shown in FIG. 15, the area of the fin 30 exposed from the dead water area DA becomes large. Therefore, in the heat exchanger 50, the airflow easily collides with the surface of the convex portion 40 of the fin 30 in the heat exchange module 10D. As a result, in the heat exchanger 50, the flow velocity of air in the vicinity of the surface of the fin 30 is increased, so that the heat transfer coefficient is improved. Further, in the heat exchange module 10D of the heat exchanger 50, since the air flow sufficiently collides with the surface of the fin 30, the height of the required convex portion 40 can be reduced, and the moldability is improved.

Embodiment 6.
FIG. 16 is a cross-sectional view schematically showing a cross section of fins 30 of the heat exchange module 10E constituting the heat exchanger 50 according to the sixth embodiment. FIG. 17 is a cross-sectional view schematically showing a cross section of fins 30 of another example heat exchange module 10E constituting the heat exchanger 50 according to the sixth embodiment. The cross sections shown in FIGS. 16 and 17 are schematic views of the BB line cross sections of the fins 30 shown in FIG. 16 and 17 are cross-sectional views of a part of the heat exchange module 10E, and a part of the heat exchange module 10E is not shown. The white arrows shown in FIGS. 16 and 17 represent the airflow FL. The convex portion 40 shown on the fin 30 is an example, and any one of the convex portion 40 described above and the convex portion 440 described later is applied to the configuration described as the convex portion 40. In the following description, components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

The heat exchanger 50 includes a heat exchange module 10E having a heat transfer tube 20 and fins 30. In the heat exchange module 10E of the heat exchanger 50, the top 45 of at least one of the plurality of convex portions 40 is arranged outside the heat transfer tube 20 in the first direction (X-axis direction). It is configured as follows. The top portion 45 is a portion of the convex portion 40 located at the tip in the protruding direction.

As described above, the second fin 30b is a fin 30 located on the downstream side of the airflow FL with respect to the heat transfer tube 20. In the heat exchange module 10E of the heat exchanger 50, the top 45 of at least one convex portion 40 located downstream of the heat transfer tube 20 is outside the width WT of the heat transfer tube 20 in the first direction (X-axis direction). It is arranged so that it is easily exposed to the air.

In the heat exchange module 10E of the heat exchanger 50, as shown in FIG. 16, the root portion 31 of the fin 30 is arranged at the position of the central portion 21 of the thickness of the heat transfer tube 20 in the first direction (X-axis direction). May be good. Alternatively, in the heat exchange module 10E of the heat exchanger 50, as shown in FIG. 17, the root portion 31 of the fin 30 is relative to the central portion 21 of the thickness of the heat transfer tube 20 in the first direction (X-axis direction). In the first direction (X-axis direction), the plurality of convex portions 40 may be arranged so as to be biased toward the protruding side.

[Effect of heat exchanger 50]
In the heat exchange module 10E of the heat exchanger 50, the top 45 of at least one of the plurality of convex portions 40 is arranged outside the heat transfer tube 20 in the first direction (X-axis direction). It is configured as follows. By having the heat exchange module 10E of the heat exchanger 50, the airflow easily collides with the second fin 30b downstream of the heat transfer tube 20, and a stronger vortex flow of the airflow can be generated. As a result, in the heat exchanger 50, the flow velocity of air in the vicinity of the surface of the fins 30 located downstream of the air flow with respect to the heat transfer tube 20 increases, so that the heat transfer coefficient is further improved.

Embodiment 7.
FIG. 18 is a cross-sectional view schematically showing a cross section of fins 30 of the heat exchange module 10F constituting the heat exchanger 50 according to the seventh embodiment. The cross section shown in FIG. 18 is a schematic view of the BB line cross section of the fin 30 shown in FIG. Further, FIG. 18 is a cross-sectional view of a part of the heat exchange module 10F, and the illustration of a part of the heat exchange module 10F is omitted. The white arrows shown in FIG. 18 represent the airflow FL. The convex portion 40 shown on the fin 30 is an example, and any one of the convex portion 40 described above and the convex portion 440 described later is applied to the configuration described as the convex portion 40. In the following description, components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

The heat exchanger 50 includes a heat exchange module 10F having a heat transfer tube 20 and fins 30. Fins 30 of the heat exchange module 10F of the heat exchanger 50 are provided on both sides of the heat transfer tube 20 with the heat transfer tube 20 interposed therebetween in the third direction (Z-axis direction). Then, all of the plurality of convex portions 40 provided on the fins 30 arranged on one side are arranged in the width WT of the heat transfer tube 20 in the first direction (X-axis direction).

As described above, the first fin 30a is a fin 30 located on the upstream side of the airflow FL with respect to the heat transfer tube 20, and the second fin 30b is located on the downstream side of the airflow FL with respect to the heat transfer tube 20. Fin 30. Each of the plurality of heat exchange modules 10F has a plurality of convex portions 40 provided on the first fin 30a arranged on the other side of the second fin 30b in the first direction (X-axis direction). Is arranged in the width WT of the heat transfer tube 20 in the above. In the heat exchange module 10F, the top 45 of the convex portion 40 located upstream of the heat transfer tube 20 is arranged inside the width WT of the heat transfer tube 20 in the first direction (X-axis direction) from the heat transfer tube. Is also configured so that it is not easily exposed to the air.

[Effect of heat exchanger 50]
In the plurality of heat exchange modules 10F, all of the plurality of convex portions 40 provided on the first fin 30a arranged on the downstream side of the air flow FL with respect to the heat transfer tube 20 are in the first direction (X-axis direction). It is arranged in the width WT of the heat transfer tube 20. Therefore, the plurality of heat exchange modules 10F of the heat exchanger 50 can generate agitation of air upstream of the heat transfer tube 20 in a region close to the heat exchange module 10F. As a result, in the plurality of heat exchange modules 10F of the heat exchanger 50, the air flow easily flows into the heat transfer tube 20 or the second fin 30b located on the downstream side of the heat transfer tube 20, and the heat transfer coefficient is further improved.

Embodiment 8.
FIG. 19 is an enlarged view of the heat exchange module 10G constituting the heat exchanger 50 according to the eighth embodiment. FIG. 20 is a cross-sectional view schematically showing the FF line cross section of the fin 30 shown in FIG. FIG. 21 is a cross-sectional view schematically showing the GG line cross section of the fin 30 shown in FIG. Further, FIG. 19 is a perspective view of a part of the heat exchange module 10G, and the illustration of a part of the heat exchange module 10G is omitted. 20 and 21 are cross-sectional views of a part of the heat exchange module 10G, and a part of the heat exchange module 10G is not shown. The white arrows shown in FIGS. 19 to 21 represent the airflow FL. The convex portion 40 shown on the fin 30 is an example, and any one of the convex portion 40 described above and the convex portion 440 described later is applied to the configuration described as the convex portion 40. In the following description, components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

The heat exchanger 50 includes a heat exchange module 10G having a heat transfer tube 20 and fins 30. The heat exchange module 10G of the heat exchanger 50 has a flat portion 36 configured such that the surfaces of both ends of the fins 30 along the second direction (Y-axis direction) or the third direction (Z-axis direction) are flat. Have. More specifically, the heat exchange module 10G of the heat exchanger 50 has a first flat portion 35 configured such that the surfaces of both end portions of the fin 30 along the second direction (Y-axis direction) are flat. .. The first flat portion 35 is formed at the edge portion of the fin 30, and is formed along the second direction (Y-axis direction). Alternatively, the heat exchange module 10G of the heat exchanger 50 has a second flat portion 37 configured so that the surfaces of both end portions of the fin 30 along the third direction (Z-axis direction) are flat. The second flat portion 37 is formed at the edge portion of the fin 30, and is formed along the third direction (Z-axis direction).

[Effect of heat exchanger 50]
The heat exchange module 10G of the heat exchanger 50 has a flat portion 36 configured such that the surfaces of both ends of the fins 30 along the second direction (Y-axis direction) or the third direction (Z-axis direction) are flat. Have. Since the heat exchange module 10G of the heat exchanger 50 has the flat portion 36, it is possible to secure a holding portion as a reference surface when forming the uneven shape of the convex portion 40. Since the heat exchange module 10G of the heat exchanger 50 has a flat portion 36 as a holding portion, wear of the molding machine can be suppressed and the manufacturing cost can be reduced.

Embodiment 9.
FIG. 22 is an enlarged view of the heat exchange module 10H constituting the heat exchanger 50 according to the ninth embodiment. Note that FIG. 22 is a perspective view of a part of the heat exchange module 10H, and a part of the heat exchange module 10H is not shown. The white arrow shown in FIG. 22 represents the airflow FL. In the following description, components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

A plurality of convex portions 440 protruding in the first direction (X-axis direction) are formed on the surface of the fin 30. The convex portion 440 has a triangular pyramid shape, and projects so as to form a side surface 441 of the triangular pyramid. The convex portion 440 is formed so that the side surface 441 of the triangular pyramid faces the upstream side of the airflow FL. That is, the convex portion 440 is formed so that the apex 442 side is located on the upstream side of the air flow. The convex portion 440 is formed so that the side side 443 located on the tip end side in the first direction (X-axis direction) is along the third direction (Z-axis direction). The shape of the convex portion 440 described above is an example, and the shape of the convex portion 440 is not limited to the shape. For example, the convex portion 440 may be formed in another shape such as a pyramidal shape, a conical shape, or a hemispherical shape.

The convex portion 440 is formed in parallel with the second direction (Y-axis direction). The rows of convex portions 440 parallel in the second direction (Y-axis direction) are formed in parallel in the third direction (Z-axis direction). At this time, the odd-numbered columns and the even-numbered columns are arranged so as to be offset from each other in the second direction (Y-axis direction). Then, in the third direction (Z-axis direction), the convex portion 440 in the rear row is formed so as to be located between the convex portions 440 in the front row.

FIG. 23 is a cross-sectional view schematically showing the OH line cross section of the fin 30 shown in FIG. The HH line cross section is a cross section of the fin 30 when viewed from the second direction (Y-axis direction) when the fin 30 is cut along the third direction (Z-axis direction). Further, FIG. 23 is a cross-sectional view of a part of the heat exchange module 10H, and the illustration of a part of the heat exchange module 10H is omitted. As shown in FIG. 23, the plurality of convex portions 440 of the fins 30 are formed so as to form an inclined surface 46 having an inclination angle α with respect to the third direction (Z-axis direction). The inclined surface 46 is a surface on the side of the convex portion 440 that is located in the protruding direction, and is an inclined surface that faces upstream with respect to the flow direction of the airflow FL. That is, the inclined surface 46 is a surface on the side of the convex portion 440 located in the protruding direction, and is not a surface on the tip end side of the fin 30 but a surface on the root portion 31 side on which the heat transfer tube 20 is arranged.

FIG. 24 is a cross-sectional view schematically showing the I-I line cross section of the fin 30 shown in FIG. 22. The I-I line cross section is a cross section of the fin 30 when viewed from the third direction (Z-axis direction) when the fin 30 is cut along the second direction (Y-axis direction). Further, FIG. 24 is a cross-sectional view of a part of the heat exchange module 10H, and the illustration of a part of the heat exchange module 10H is omitted. As shown in FIG. 24, the plurality of convex portions 440 of the fins 30 are formed so as to form an inclined surface 47 having an inclination angle β with respect to the second direction (Y-axis direction).

As described above, the angle formed by the plurality of convex portions 440 with respect to the third direction (Z-axis direction) is defined as the inclination angle α, and the angle formed with respect to the second direction (Y-axis direction) is the inclination angle β. When defined as, it is formed so that the tilt angle α <tilt angle β. That is, each of the plurality of convex portions 440 is formed so that the inclination angle α is smaller than the inclination angle β.

[Effect of heat exchanger 50]
The plurality of convex portions 440 are formed so that the inclination angle α <inclination angle β. The heat exchange module 10H of the heat exchanger 50 forms a convex portion 440 at a high density along the second direction (Y-axis direction) in the configuration, and bends the airflow angle in the third direction (Z-axis direction). Can be made smaller. Therefore, the heat exchanger 50 can improve the balance between the heat transfer performance and the ventilation resistance, and can improve the heat exchanger performance.

[Action and effect of refrigeration cycle device 100]
The refrigeration cycle device 100 described above includes the heat exchanger according to any one of the first to third embodiments. Therefore, in the refrigeration cycle apparatus 100, the same effect as that of any one of the first and second embodiments can be obtained. Therefore, the refrigeration cycle device 100 can improve the energy efficiency of the air conditioning system by mounting a heat exchanger having high heat transfer performance.

Each of the above embodiments 1 to 9 can be implemented in combination with each other. Further, the configuration shown in the above embodiment is an example, and can be combined with another known technique, and a part of the configuration is omitted or changed without departing from the gist. It is also possible.

10 heat exchange module, 10A heat exchange module, 10B heat exchange module, 10C heat exchange module, 10D heat exchange module, 10E heat exchange module, 10F heat exchange module, 10G heat exchange module, 10H heat exchange module, 10I heat exchange module, 20 heat transfer tube, 20a 1st side edge, 20b 2nd side edge, 20c flat surface, 20d flat surface, 21 central part, 22 refrigerant passage, 23 partition wall, 30 fins, 30a 1st fin, 30b 2nd fin , 31 root part, 35 first flat part, 36 flat part, 37 second flat part, 40 convex part, 40a first convex part, 40b second convex part, 41 ridgeline, 42 inclined surface, 43 inclined surface, 45 top , 46 inclined surface, 47 inclined surface, 50 heat exchanger, 70 header, 71 first header, 72 second header, 100 refrigeration cycle device, 101 compressor, 102 flow path switching device, 103 indoor heat exchanger, 104 decompression Equipment, 105 outdoor heat exchanger, 106 outdoor unit, 107 indoor unit, 108 outdoor blower, 109 indoor blower, 110 refrigerant circuit, 111 extension pipe, 112 extension pipe, 120 heat transfer tube, 140 convex part, 240 convex part, 240a 1 end, 240b 2nd end, 340 convex, 340a 1st end, 340b 2nd end, 341 1st convex, 342 2nd convex, 440 convex, 441 side, 442 apex, 443 side Side.

Claims

Multiple heat exchange modules arranged in parallel in the first direction at intervals from each other,
At the ends of the plurality of heat exchange modules in the second direction intersecting the first direction, a header connected to the plurality of heat exchange modules is provided.
The plurality of heat exchange modules
The heat transfer tube extending in the second direction and
A fin extending in the third direction from a side edge of the heat transfer tube in the third direction intersecting a plane parallel to the first direction and the second direction.
With
The fins
A plurality of convex portions protruding in the first direction are formed on the surface thereof.
Each of the plurality of convex portions
A heat exchanger formed so as to form a surface having an inclination angle with respect to the second direction and the third direction.
Each of the plurality of convex portions is formed in a quadrangular pyramid shape.
The heat exchanger according to claim 1, wherein the side sides of the plurality of convex portions are formed so as to be continuous in the third direction.
Each of the plurality of convex portions is formed in a columnar shape so as to extend along the plane of the fin.
The direction in which the longitudinal direction of the plurality of convex portions extends is
The heat exchanger according to claim 1, which is tilted with respect to the third direction.
The plurality of convex portions
The heat exchange according to claim 3, wherein the heat exchange is formed in parallel in the second direction and in parallel with the third direction, and the directions of inclination with respect to the third direction are all the same. vessel.
The fins
It is provided on both sides of the heat transfer tube so as to sandwich the heat transfer tube in the third direction.
A direction in which the longitudinal direction of the plurality of convex portions provided on the fins arranged on one side extends and a direction in which the longitudinal directions of the plurality of convex portions provided on the fins arranged on the other side extend. The heat exchanger according to claim 3, wherein the heat exchanger is formed so as to be inclined in a direction different from that of the third direction.
The fins
The direction in which the longitudinal direction of the plurality of protrusions provided on the fins arranged on one side extends and the direction in which the longitudinal directions of the plurality of protrusions provided on the fins arranged on the other side extend. The heat exchanger according to claim 5, wherein the heat exchanger is formed so as to be symmetrical with respect to the heat transfer tube.
The plurality of convex portions
It has a first convex portion and a second convex portion formed at intervals from each other in the second direction while having different inclinations with respect to the third direction.
3. Claim 3 in which the combination of the first convex portion and the second convex portion forms an angle in the second direction at regular intervals, and each time the first convex portion is folded back and bent in the opposite direction. The heat exchanger described in.
The fins
The root of the fin, which is the base for the heat transfer tube,
The invention according to any one of claims 1 to 7, wherein the heat transfer tube is arranged so as to be biased toward the protruding side of the plurality of convex portions in the first direction with respect to the central portion of the thickness of the heat transfer tube in the first direction. Heat exchanger.
The fins
It is provided on both sides of the heat transfer tube so as to sandwich the heat transfer tube in the third direction.
Each of the plurality of heat exchange modules
Of the plurality of convex portions provided on the fins arranged on one side, the top of at least one convex portion is configured to be arranged outside the heat transfer tube in the first direction. The heat exchanger according to any one of claims 1 to 8.
Each of the plurality of heat exchange modules
The heat exchanger according to claim 9, wherein the plurality of protrusions provided on the fins arranged on the other side are arranged within the width of the heat transfer tube in the first direction.
The heat exchange module
The heat exchanger according to any one of claims 1 to 10, wherein the surface of both ends of the fin along the second direction or the third direction has a flat portion configured to be flat.
The plurality of convex portions
When the angle formed with respect to the third direction is defined as the tilt angle α and the angle formed with respect to the second direction is defined as the tilt angle β, the tilt angle α <tilt angle β is formed. The heat exchanger according to any one of claims 1 to 11.
A refrigeration cycle device provided with the heat exchanger according to any one of claims 1 to 12.