WO2022244232A1

WO2022244232A1 - Air conditioner

Info

Publication number: WO2022244232A1
Application number: PCT/JP2021/019355
Authority: WO
Inventors: 直紀中川; 尚史池田; 啓地村; 暁八柳; 和英山本; 洋平小柳; 將太須貝
Original assignee: 三菱電機株式会社
Priority date: 2021-05-21
Filing date: 2021-05-21
Publication date: 2022-11-24

Abstract

This air conditioner comprises a heat exchanger that exchanges heat between a refrigerant flowing through a heat exchanger tube and air, and a blower that sends air to the heat exchanger tube. The heat exchanger is equipped with: a plurality of plate-shaped fins that extend in the extension direction that intersects with the ventilation direction of air sent by the blower to the heat exchanger; a plurality of cut-and-raised portions that are formed on the plate surface of each of the plurality of fins; and a fin collar that is provided between the fins adjacent to each other among the plurality of fins and into which the heat exchanger tube is inserted. The plurality of cut-and-raised portions include a downstream cut-and-raised portion located downstream of the fin collar in the ventilation direction. One end of the downstream cut-and-raised portion in the extension direction is disposed overlapping the fin collar when viewed in the ventilation direction.

Description

air conditioner

The present disclosure relates to air conditioners.

Patent Documents

1 and 2 describe conventional air conditioners. An air conditioner includes a heat exchanger having a plurality of fins and heat transfer tubes, and a blower such as a cross-flow fan. A plurality of cut-and-raised slits are formed in the plurality of fins by cutting and raising part of the surfaces of the fins.

Japanese Patent Application Laid-Open No. 2009-127882 Japanese Patent Application Laid-Open No. 2003-247794

In the heat exchangers disclosed in

Patent Documents

1 and 2, pressure fluctuation occurs on the blade surface of the rotating cross-flow fan, abnormal blower noise is generated, and abnormal noise cannot be sufficiently suppressed. There is

The present disclosure has been made to solve the above problems, and aims to provide an air conditioner equipped with a heat exchanger capable of suppressing the generation of abnormal noise.

An air conditioner according to the present disclosure includes a heat transfer tube through which a refrigerant flows, a heat exchanger that exchanges heat between the refrigerant flowing in the heat transfer tube and air, and a blower that sends air to the heat transfer tube; Prepare. The heat exchanger is formed in a plate shape, and has a plurality of fins extending in an extending direction intersecting with a ventilation direction of the air sent to the heat exchanger by the blower, and a plate surface of each of the plurality of fins. and a fin collar provided between adjacent fins among the plurality of fins and through which the heat transfer tube is inserted. The plurality of cut-and-raised portions include a downstream cut-and-raised portion located downstream of the fin collar in the airflow direction. One end in the extending direction of the downstream cut-and-raised portion is arranged to overlap the fin collar when viewed in the ventilation direction.

According to the air conditioner according to the present disclosure, it is possible to suppress the occurrence of abnormal noise.

1 is a fluid circuit diagram showing an air conditioner according to Embodiment 1. FIG. 1 is a schematic cross-sectional view showing an indoor unit according to Embodiment 1. FIG. 1 is a schematic cross-sectional view showing a heat exchanger according to Embodiment 1; FIG. 4 is a side view showing a structure in which a plurality of fins forming the heat exchanger according to Embodiment 1 are laminated; FIG. 4 is a side view showing a structure in which a plurality of fins forming the heat exchanger according to Embodiment 1 are laminated; FIG. FIG. 4 is a plan view partially showing the fins forming the heat exchanger according to the first embodiment, showing the arrangement of the cut-and-raised portions; It is a figure which shows the wind speed distribution in the heat exchanger which concerns on a comparative example. FIG. 10 is a plan view showing the wind speed distribution in the heat exchanger according to the example, showing a case where both open ends of two cut-and-raised portions adjacent to each other are located downstream of the fin collar in the ventilation direction. be. 7B is a graph corresponding to the wind speed distribution shown in FIG. 7A; FIG. 10 is a plan view showing the wind speed distribution in a heat exchanger according to a comparative example, showing a case where both open ends of two cut-and-raised portions adjacent to each other are not located downstream of the fin collar in the ventilation direction; be. 8B is a graph corresponding to the wind speed distribution shown in FIG. 8A; FIG. 10 is a plan view showing the wind speed distribution in a heat exchanger according to a comparative example, in which only one of the open ends of two adjacent cut-and-raised portions is positioned downstream of the fin collar in the ventilation direction; FIG. 10 is a diagram showing a case; 9B is a graph corresponding to the wind speed distribution shown in FIG. 9A; FIG. 10 is a plan view partially showing a fin constituting a heat exchanger according to a comparative example, showing a case where the cut-and-raised portion is divided; FIG. 10 is a plan view showing the wind velocity distribution in a heat exchanger according to a comparative example, showing a case where the cut-and-raised portion is divided; 11B is a graph corresponding to the wind speed distribution shown in FIG. 11A; FIG. 5 is a perspective view showing simulation results of wind speed distribution in the heat exchanger according to the example. FIG. 7 is a perspective view showing a simulation result of wind speed distribution in a heat exchanger according to a comparative example;

Embodiment 1.
Hereinafter, the air conditioner 1 according to Embodiment 1 will be described with reference to the drawings.
In the description to be given later, the vertical direction (gravity direction, vertical direction) is defined as the Z direction, the width direction of the indoor unit 2 is defined as the Y direction, and the front-rear direction of the indoor unit 2 is defined as the X direction (Y direction and Z direction). orthogonal direction). A tilt direction G is defined as a direction tilted in the X direction and the Y direction. A direction perpendicular to the tilt direction G is defined as a direction P.

(Air conditioner 1)
FIG. 1 is a fluid circuit diagram showing an air conditioner 1 according to Embodiment 1. FIG.
As shown in FIG. 1 , the air conditioner 1 has an indoor unit 2 , an outdoor unit 3 and refrigerant pipes 4 . Although one indoor unit 2 is shown in the example shown in FIG. 1, the number of indoor units 2 constituting the air conditioner 1 may be two or more.

(Refrigerant pipe 4)
The refrigerant pipe 4 (pipe) connects the flow switching valve 11 , the indoor heat exchanger 7 , the expansion valve 9 and the outdoor heat exchanger 8 . A coolant flows inside the coolant pipe 4 . As the refrigerant, for example, a refrigerant such as R32 or a refrigerant having a global warming potential GWP of 675 or less is used. The refrigerant pipe 4 and the above-described devices connected to the refrigerant pipe 4 constitute a refrigerant circuit.

(Outdoor unit 3)
The outdoor unit 3 has an air blower 6 , an outdoor heat exchanger 8 , an expansion valve 9 , a compressor 10 and a channel switching valve 11 .
The blower 6 is a device that sends outdoor air to the outdoor heat exchanger 8 .
The outdoor heat exchanger 8 includes a heat exchanger that exchanges heat between refrigerant and outdoor air. The outdoor heat exchanger 8 is, for example, a fin-and-tube heat exchanger. The outdoor heat exchanger 8 functions as a condenser during cooling operation. The outdoor heat exchanger 8 functions as an evaporator during heating operation.

The expansion valve 9 is a valve that decompresses and expands the refrigerant. The expansion valve 9 is, for example, an electronic expansion valve.
The compressor 10 sucks a low-temperature, low-pressure refrigerant, compresses the sucked refrigerant, and converts it into a high-temperature, high-pressure refrigerant.
The channel switching valve 11 is a valve that switches the flow direction of the refrigerant in the refrigerant circuit, and is, for example, a four-way valve.

(Indoor unit 2)
The indoor unit 2 has an air blower 5 and an indoor heat exchanger 7 .
The blower 5 is a device that sends indoor air to the indoor heat exchanger 7, and is a cross-flow fan 22, for example.
The indoor heat exchanger 7 includes a heat exchanger 18 that exchanges heat between the indoor air and the refrigerant. The indoor heat exchanger 7 functions as an evaporator during cooling operation. The indoor heat exchanger 7 functions as a condenser during heating operation.

(Cooling operation in air conditioner 1)
Next, the operation of the air conditioner 1 having the configuration described above will be described.
First, the cooling operation will be explained. The air conditioner 1 performs cooling operation by switching the flow path switching valve 11 so that the discharge portion of the compressor 10 and the outdoor heat exchanger 8 are connected.
In the cooling operation, the refrigerant sucked into the compressor 10 is compressed by the compressor 10 into a high-temperature and high-pressure gas state. The gaseous refrigerant is discharged toward the outdoor heat exchanger 8 . The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 10 passes through the flow path switching valve 11 and flows into the outdoor heat exchanger 8 functioning as a condenser.

The refrigerant that has flowed into the outdoor heat exchanger 8 exchanges heat with the outdoor air sent by the blower 6, condenses, and liquefies. The liquid refrigerant flows into the expansion valve 9 and is decompressed and expanded to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant flows into the indoor heat exchanger 7 functioning as an evaporator. The refrigerant that has flowed into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the blower 5, evaporates, and gasifies. At that time, the room air is cooled to cool the room. Thereafter, the vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow path switching valve 11 and is sucked into the compressor 10 .

(Heating operation in air conditioner 1)
Next, the heating operation will be explained. The air conditioner 1 performs heating operation by switching the flow path switching valve 11 so that the discharge portion of the compressor 10 and the indoor heat exchanger 7 are connected.
In the heating operation, the refrigerant sucked into the compressor 10 is compressed by the compressor 10 into a high-temperature, high-pressure gas state. The gaseous refrigerant is discharged toward the indoor heat exchanger 7 . The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 10 passes through the flow path switching valve 11 and flows into the indoor heat exchanger 7 functioning as a condenser.

The refrigerant that has flowed into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the blower 5, condenses, and liquefies. At that time, the room air is warmed, and the room is heated. The liquid refrigerant flows into the expansion valve 9 and is decompressed and expanded to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 8 that functions as an evaporator. The refrigerant that has flowed into the outdoor heat exchanger 8 exchanges heat with the outdoor air sent by the blower 6 to evaporate and gasify. Thereafter, the vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow path switching valve 11 and is sucked into the compressor 10 .

(Configuration of indoor unit 2)
FIG. 2 is a schematic cross-sectional view showing the indoor unit 2 according to Embodiment 1, showing a cross section of the indoor unit 2 along the Z direction.
As shown in FIG. 2, the indoor unit 2 has a housing 12, an air filter 14, a heat exchanger 18, a drain pan 19, a flap 20, and a cross-flow fan 22 (blower 5).
The housing 12 has a cover 12A, a support portion 12B, a base portion 16, a top panel 15, and a front panel 13. As shown in FIG. The housing 12 constitutes the outer shell of the indoor unit 2 .

The cover 12A has an air outlet 21 . The outlet 21 is formed in the lower portion of the cover 12A.
The support portion 12B and the base portion 16 are attached to a wall surface W or the like in the room to support the cover 12A. The base 16 is positioned above the support 12B in the Z direction.

The top panel 15 is connected to the base 16 and constitutes the top surface 2T of the indoor unit 2. The top panel 15 is open in a grid pattern. The front panel 13 constitutes the front surface of the indoor unit 2 in the X direction. The air filter 14 is attached to the top panel 15 and removes dust from the air drawn from the top panel 15 .

(Cross flow fan 22)
The cross-flow fan 22 is housed inside the housing 12 and sends air to the heat transfer tubes 17 constituting the heat exchanger 18, which will be described later. The cross-flow fan 22 extends in the Y direction of the housing 12 in FIG. The heat exchanger 18 is housed inside the housing 12 and has a first heat exchange section 18A and a second heat exchange section 18B. Cross-flow fan 22 faces heat exchanger 18 .

In addition, in Embodiment 1, as an example, a structure in which the heat exchanger 18 is not arranged in the back area (area facing the wall surface W) of the cross flow fan 22 is described. A structure in which the heat exchanger 18 is arranged in the back area of the cross flow fan 22 may be adopted.

The first heat exchange section 18A has an upper end 18AU and a lower end 18AL. The lower end 18AL faces the drain pan 19 . The first heat exchange section 18A extends, for example, along the Z direction. The first heat exchange portion 18A faces a front area 22A of the cross-flow fan 22 located on the opposite side of the wall surface W in the X direction.
In other words, the first heat exchange section 18A is arranged to face the cross flow fan 22 via the front region 22A.

The second heat exchange section 18B is positioned above the first heat exchange section 18A in the Z direction. The second heat exchange section 18B has an upper end 18BU and a lower end 18BL. The upper end 18BU faces the support portion 12B. The lower end 18BL is connected to the upper end 18AU of the first heat exchange section 18A.
The second heat exchange portion 18B extends along an inclination direction G that is inclined in the X direction and the Z direction. The tilt direction G is a direction perpendicular to the Y direction. The second heat exchange portion 18B extends upward and obliquely rearward from the upper end 18AU of the first heat exchange portion 18A when viewed in the Y direction.

The second heat exchange section 18B faces the upper region 22B of the crossflow fan 22. The upper area 22B means an area extending from the upper portion 22C of the cross-flow fan 22 toward the front area 22A in the Z direction. In other words, the second heat exchange section 18B is arranged to face the cross flow fan 22 via the upper region 22B.

The drain pan 19 is arranged below the first heat exchange section 18A. The drain pan 19 stores water dripped from the heat exchanger 18 .
The flap 20 is attached to the lower portion of the cover 12A. The flap 20 is rotatable around a rotary shaft 20A and adjusts the blowing direction of air blown from the blower port 21 . The rotating shaft 20A is an axis extending in the Y direction.

(Air flow in indoor unit 2)
The air flow in the indoor unit 2 will be described.
First, by driving the cross-flow fan 22 , the indoor air is sucked into the housing 12 through the opening of the top panel 15 . The air drawn into the housing 12 passes through the heat exchanger 18 and is drawn into the cross-flow fan 22 . Then, the air sucked into the cross-flow fan 22 is blown out from the outlet 21. - 特許庁

(Configuration of heat exchanger 18)
FIG. 3 is a schematic cross-sectional view showing the main part of the indoor unit 2 shown in FIG. 2 and showing the heat exchanger 18 according to the first embodiment. In FIG. 3, only the heat exchanger 18 is shown among the members constituting the indoor unit 2, and the other constituent members are omitted.
4A and 4B are side views showing a structure in which a plurality of fins 24 constituting heat exchanger 18 according to Embodiment 1 are laminated. 4A and 4B show only the fins 24, the cut-and-raised portions 23, and the fin collars 25 among the members constituting the heat exchanger 18, and the other constituent members are omitted.

FIG. 5 is a plan view partially showing the fins 24 that constitute the heat exchanger 18 according to the first embodiment. FIG. 5 is a diagram showing the arrangement of the cut-and-raised portions 23, showing an enlarged view of the fins 24 of the heat exchanger 18 shown in FIG. The structure shown in FIG. 5 is applied to each of the first heat exchange section 18A and the second heat exchange section 18B shown in FIG.

As shown in FIG. 3, the heat exchanger 18 (the first heat exchange section 18A and the second heat exchange section 18B) includes a plurality of fins 24 arranged in the Y direction and a plurality of fins 24 that are inserted into the heat exchanger 18. and a heat transfer tube 17 extending in the Y direction. Each of the plurality of fins 24 is formed in a plate shape having a plate surface 24F (surface) extending in the Y direction.
In FIG. 3, the positions where the heat transfer tubes 17 are fixed, that is, the positions of the plurality of fin collars 25 are indicated by reference numeral 25P. Hereinafter, it is called fixed position 25P.

(fin 24)
Each of the plurality of fins 24 forming the first heat exchange section 18A extends in the Z direction.
Each of the plurality of fins 24 forming the second heat exchange portion 18B extends in the tilt direction G. As shown in FIG.
The plurality of fins 24 are arranged side by side in the width direction (Y direction) of the housing 12 in FIGS. 3, 4A, and 4B. Each of the plurality of fins 24 is plate-shaped, for example, made of aluminum.

In a structure in which the heat exchanger 18 is also arranged in the back area of the cross-flow fan 22, the number of fins 24 facing the front area 22A and the upper area 22B is the number facing the back area of the cross-flow fan 22. fins may be greater than the number of fins.
Since each of the plurality of fins 24 has the same structure, only one fin 24 will be described in the following description, and description of each of the plurality of fins 24 may be omitted.

The arrangement pattern of the plurality of fixed positions 25P on each fin 24 (the fixed position pattern of the positions where the heat transfer tubes 17 are fixed on each fin 24) is, for example, a zigzag pattern as shown in FIG. Here, the zigzag pattern will be specifically described.
A plurality of fixed positions 25P are arranged along a first row labeled a and a second row labeled b.
Reference 24K is the boundary between the first column a and the second column b. The boundary line 24K corresponds to the centerline of each of the first heat exchange section 18A and the second heat exchange section 18B.

The first row a of the plurality of fixed positions 25P is the row located on the upstream side (upwind side) in the flow of air passing through the fins 24 . The second row b of the plurality of fixed positions 25P is the row positioned downstream (downwind side) in the flow of air passing through the fins 24 .

In the first heat exchange section 18A, the arrangement pitch of the plurality of fixed positions 25P in the first row a and the arrangement pitch of the plurality of fixed positions 25P in the second row b are the same.
In the first heat exchanging portion 18A, a central position between two adjacent fixed positions 25P (for example, 25PAa) that constitute the first row a is denoted by 25CAa. The central position 25CAa overlaps with one fixed position 25P (for example, 25PAb) forming the second row b when viewed from the X direction (the direction perpendicular to the direction of the first row a).

Similarly, the central position between two fixed positions 25P (for example, 25PAb) that constitute the second row b and are adjacent to each other is indicated by 25CAb. The central position 25CAb overlaps with one fixed position 25P (for example, reference numeral 25PAa) that forms the first row a when viewed from the X direction.
Thus, in the first heat exchange section 18A, the heat transfer tubes 17 are arranged at positions corresponding to the zigzag pattern in which the plurality of fixed positions 25P are arranged in two rows.

In the second heat exchange section 18B, the arrangement pitch of the plurality of fixed positions 25P in the first row a and the arrangement pitch of the plurality of fixed positions 25P in the second row b are the same.
In the second heat exchange section 18B, the central position between two adjacent fixed positions 25P (for example, 25PBa) that constitute the first row a is indicated by 25CBa. The central position 25CBa overlaps with one fixed position 25P (for example, 25PBb) forming the second row b when viewed from the direction P (the direction orthogonal to both the tilt direction G and the Y direction).

Similarly, the central position between two adjacent fixed positions 25P (for example, 25PBb) forming the second row b is designated 25CBb. The center position 25CBb overlaps the position of one fixed position 25P (for example, 25PBa) that forms the first row a when viewed from the direction P. As shown in FIG.
Thus, in the second heat exchange section 18B, the heat transfer tubes 17 are arranged at positions corresponding to the zigzag pattern in which the plurality of fixed positions 25P are arranged in two rows.

By arranging the heat transfer tubes 17 at each of the plurality of fixed positions 25P having the zigzag pattern as described above, it is possible to improve the heat exchange efficiency between the refrigerant flowing inside the heat transfer tubes 17 and the air. becomes.

(Cut-and-raised portion 23)
As shown in FIG. 5 , a plurality of cut-and-raised portions 23 are formed on plate surfaces 24F of the plurality of fins 24 . The plurality of cut-and-raised portions 23 are located upstream UP and downstream DW in the ventilation direction FL of the air flowing through the heat exchanger 18 (the ventilation direction of the air sent to the heat exchanger 18 by the cross-flow fan 22).

The ventilation direction FL is a direction orthogonal to the arrangement direction of the plurality of fins 24 arranged in the Y direction shown in FIG. A ventilation direction FL is a direction perpendicular to the direction in which the fins 24 extend.

Each of the plurality of cut-and-raised portions 23 is raised upward from the plate surface 24F of the fin 24 from a cut portion formed in a portion of the plate surface 24F. The plurality of cut-and-raised portions 23 are formed by, for example, a known sheet metal working method.

A method for forming each of the cut-and-raised portions 23 will be described.
First, as shown in FIG. 5, on the plate surface 24F, notches are formed at locations corresponding to the upper side and two oblique sides of the trapezoid while leaving a location corresponding to the lower side (base) of the trapezoid. This cut portion is formed so as to penetrate the plate surface 24F.

After that, raise (lift) the trapezoidal part so as to bend the part corresponding to the lower side of the trapezoidal shape. As a result, a bent portion is formed at a location corresponding to the lower side of the trapezoidal shape. A cut-and-raised portion 23 is formed to extend obliquely upward from the bent portion.

On the plate surface 24F of the plurality of fins 24, there are a plurality of upstream cut-and-raised portions 23U formed on the upstream side UP in the airflow direction FL and a plurality of downstream cut-and-raised portions 23D formed on the downstream side DW in the airflow direction FL. is formed.
Each of the plurality of upstream cut-and-raised portions 23U has an opening 23UH and an opening end 23UE (apex, one end). The opening 23UH is formed between the upper end 23T (see FIGS. 4A and 4B) of the upstream cut-and-raised portion 23U and the plate surface 24F. The opening 23UH opens in the ventilation direction. The opening end 23UE is located at the boundary between the plate surface 24F on which the opening 23UH is not formed and the opening 23UH. That is, the opening ends 23UE are located on both sides of the opening 23UH in the extending direction (Z direction) of the opening 23UH.

Each of the plurality of downstream cut-and-raised portions 23D has an opening 23DH and an opening end 23DE (apex, one end). The opening 23DH is formed between the upper end 23T (see FIGS. 4A and 4B) of the downstream cut-and-raised portion 23D and the plate surface 24F. The opening 23DH opens in the ventilation direction. The opening end 23DE is located at the boundary between the plate surface 24F on which the opening 23DH is not formed and the opening 23DH. That is, the opening ends 23DE are positioned on both sides of the opening 23DH in the extending direction (Z direction) of the opening 23DH.

The opening ends 23UE and 23DE can also be referred to as starting points (opening starting points) from which the formation of the openings 23UH and 23DH starts when the cut-and-raised portions 23 are formed by cutting a part of the plate surface 24F of the fin 24.

The openings 23UH and 23DH of the cut-and-raised portions 23 (23U and 23D) are open in the ventilation direction FL. By forming the plurality of cut-and-raised portions 23 on the fins 24 that constitute the heat exchanger 18, the heat transfer performance between the fins 24 and the air flowing between the plurality of fins 24 can be improved.

Next, the height of the cut-and-raised portion 23 will be described.
As shown in FIGS. 3, 4A, and 4B, the plurality of fins 24 are arranged along the Y direction. A space between two fins 24 facing each other among the plurality of fins 24 is maintained by fin collars 25 .
In Embodiment 1, the height of the space 30 formed between the fins 24 adjacent to each other in the direction in which the plurality of fins 24 overlap is defined as F, and the height of each of the plurality of cut-and-raised portions 23 is defined as H. , the height of each of the plurality of cut-and-raised portions 23 is set so as to satisfy the relationship H≦1/2×F.

Here, the height F of the space 30 is the distance between the two fins 24 facing each other. The height H of the cut-and-raised portion 23 is the distance from the plate surface 24F of the fin 24 on which the cut-and-raised portion 23 is formed to the upper end 23T of the cut-and-raised portion 23 .

FIG. 4A shows a case where the height H of the cut-and-raised portion 23 is half the height F of the space 30. FIG. FIG. 4B shows a case where the height H of the cut-and-raised portion 23 is smaller than half the height F of the space 30 .

(Fin collar 25)
A plurality of fin collars 25 are formed on the plate surface 24</b>F of each of the plurality of fins 24 . The plurality of fin collars 25 maintains the spacing between adjacent fins 24 among the plurality of fins 24 arranged in the Y direction shown in FIG. Heat transfer tubes 17 are inserted through a plurality of fin collars 25 , and the heat transfer tubes 17 are fixed to the fins 24 at the fin collars 25 .

The plurality of fin collars 25 are positioned upstream UP and downstream DW in the ventilation direction FL. In other words, on the plate surface 24F of the plurality of fins 24, a plurality of upstream fin collars 25U formed on the upstream side UP in the airflow direction FL and a plurality of downstream fin collars 25D formed on the downstream side DW in the airflow direction FL. and are formed.

The fin collars 25 (25U, 25D) have hole diameters about 4 to 7% larger than the diameter of the heat transfer tubes 17 in order to insert the heat transfer tubes 17 therein. Specifically, the hole diameter of the fin collar 25 is preferably 5.35 mm or less.

5 correspond to the first column a and the second column b shown in FIG. 3, respectively. That is, the plurality of fixing positions 25P at which the heat transfer tubes 17 are fixed to the fin collars 25 are arranged in two rows.
Specifically, the first row a is composed of a plurality of upstream cut-and-raised portions 23U and a plurality of upstream fin collars 25U. In the first row a, one upstream fin collar 25U is arranged between two upstream cut-and-raised portions 23U. In other words, one upstream cut-and-raised portion 23U is arranged between two upstream fin collars 25U.

The second row b is composed of a plurality of downstream cut-and-raised portions 23D and a plurality of downstream fin collars 25D. In the first row a, one downstream fin collar 25D is arranged between two downstream cut-and-raised portions 23D. In other words, one downstream cut-and-raised portion 23D is arranged between two downstream fin collars 25D.

The upstream fin collar 25U forming the first row a and the downstream cut-and-raised portion 23D forming the second row b are aligned in the ventilation direction FL.
In the second row b, the downstream fin collar 25D and the downstream cut-and-raised portion 23D are arranged in the longitudinal direction of the fin 24 (extending direction of the second row b).
Furthermore, in the ventilation direction FL, the opening end 23DE of the downstream cut-and-raised portion 23D is located behind the downstream fin collar 25D. That is, in the ventilation direction FL, the opening end 23DE of the downstream cut-and-raised portion 23D is located downstream of the downstream fin collar 25D.

Here, "the opening end 23DE is located behind the downstream fin collar 25D" means that the downstream fin collar 25D and the opening end 23DE overlap when viewed from the upstream side UP in the ventilation direction FL and It means that the fin collar 25D is arranged in front of the open end 23DE. In other words, it means that the heat transfer tube 17 and the open end 23DE overlap when viewed from the upstream side UP in the air flow direction FL, and that the heat transfer tube 17 is arranged in front of the open end 23DE.

Furthermore, in the second row b, a first downstream cut-and-raised portion 23D1 and a second downstream cut-and-raised portion 23D2, which are the downstream cut-and-raised portion 23D, are arranged in the extending direction of the second row b. Each of the first downstream cut-and-raised portion 23D1 and the second downstream cut-and-raised portion 23D2 is one of the plurality of cut-and-raised portions 23 positioned on the downstream side DW in the ventilation direction FL.

The first downstream cut-and-raised portion 23D1 includes a first opening 23DH1, a first opening end 23DE1 (first end part).
The second downstream cut-and-raised portion 23D2 has a second opening 23DH2, a second opening end 23DE2 (second end part).

The downstream fin collar 25D is positioned between the first downstream cut-and-raised portion 23D1 and the second downstream cut-and-raised portion 23D2. The first opening end 23DE1 and the second opening end 23DE2 are formed so as to face each other and be adjacent to each other. In the ventilation direction FL, the first opening end 23DE1 and the second opening end 23DE2 are located behind the downstream fin collar 25D. That is, in the ventilation direction FL, the first opening end 23DE1 and the second opening end 23DE2 are located downstream of the downstream fin collar 25D.

Here, "the first opening end 23DE1 and the second opening end 23DE2 are positioned behind the downstream fin collar 25D" means that the downstream fin collar 25D and the first opening end are positioned behind the downstream fin collar 25D when viewed from the upstream side UP in the ventilation direction FL. 23DE1 and the second open end 23DE2 overlap, and the downstream fin collar 25D is arranged in front of the first open end 23DE1 and the second open end 23DE2. In other words, when viewed from the upstream side UP in the ventilation direction FL, the heat transfer tubes 17 overlap the first opening end 23DE1 and the second opening end 23DE2, and the heat transfer tubes 17 are arranged in front of the opening end 23DE. means that

(Heat transfer tube 17)
The heat transfer tubes 17 are housed inside the housing 12 . The heat transfer tube 17 is inserted through a plurality of fin collars 25 formed on each of the plurality of fins 24 . In each of the plurality of fins 24, the heat transfer tubes 17 are fixed to the plurality of fin collars 25 by caulking by a tube expanding method. Therefore, the heat transfer tubes 17 are fixed to the fins 24 in a state where the adhesion between the heat transfer tubes 17 and the plurality of fins 24 is enhanced. A refrigerant flows inside the heat transfer tube 17 . The heat transfer tube 17 is, for example, copper or aluminum piping.

In FIG. 5, symbol B indicates the distance between the first open end 23DE1 and the second open end 23DE2, symbol C indicates the hole diameter of the fin collar 25, and symbol D indicates the outer diameter of the heat transfer tube 17. indicates the diameter.
In this case, the first downstream cut-and-raised portion 23D1 and the second downstream cut-and-raised portion 23D2 are arranged so as to satisfy the relationship B≦0.75×C.
Moreover, the outer diameter D of the heat transfer tube 17 is 5.0 mm.

Furthermore, as shown in FIGS. 3 to 5, between two adjacent downstream fin collars (a first fin collar and a second fin collar) among the plurality of downstream fin collars 25D, the downstream cut-and-raised portion 23D is It is formed by one cut-and-raised portion that is not divided in the longitudinal direction of the fin 24 .
Specifically, the first fin collar is provided between the fins 24 adjacent to each other among the plurality of fins 24 and is a fin collar through which the heat transfer tubes 17 are inserted.
The second fin collar is provided between the fins 24 adjacent to each other among the plurality of fins 24 and is a fin collar through which the heat transfer tubes 17 are inserted.

In the heat exchanger 18 including the cut-and-raised portions 23 having the above-described configuration, when the air passes through the space around the heat transfer tubes 17 inserted through the downstream fin collars 25D in the air ventilation direction FL, the air flows downstream of the heat transfer tubes 17. The growth of the air flow (pipe wake) occurs on the side. Specifically, a low-velocity air flow resulting from the pipe wake flow and a constricted air flow flowing from between the fin collar 25 and the cut-and-raised portion 23 are generated. Such airflow reaches the blade surfaces of the cross-flow fan 22 .

The heat exchanger 18 according to Embodiment 1 has a configuration in which the opening end 23DE of the downstream cut-and-raised portion 23D is positioned behind the downstream fin collar 25D. In particular, the downstream fin collar 25D is positioned between the first downstream cut-and-raised portion 23D1 and the second downstream cut-and-raised portion 23D2.

As a result, the first open end 23DE1 and the second open end 23DE2 hinder the growth of the air flow. In other words, the first opening end 23DE1 and the second opening end 23DE2 can suppress an increase in the width of the low-velocity air flow caused by the pipe wake flow. Therefore, it is possible to prevent the slow-speed airflow from reaching the cross-flow fan. Here, the "width of the air flow" means the width in the direction intersecting with the ventilation direction FL.

As a result, around the blade surfaces of the cross-flow fan 22, the speed difference between the slow-speed air and the constricted air can be uniformly reduced. It is possible to suppress the occurrence of drift, reduce the pressure difference, and obtain a uniform air flow. Furthermore, by reducing the air velocity difference, air pressure fluctuations can be suppressed, and as a result, the occurrence of noise such as abnormal fan noise can be suppressed.

Furthermore, since the first opening end 23DE1 and the second opening end 23DE2 are positioned behind the downstream fin collar 25D in the airflow direction FL, the airflow direction from the portion between the downstream fin collar 25D and the downstream cut-and-raised portion 23D in the airflow direction FL It becomes possible to suppress the amount of flowing heat exchange air. As a result, it is possible to suppress the occurrence of a contracted air flow having a high flow velocity that flows out from the portion between the downstream fin collar 25D and the downstream cut-and-raised portion 23D.

Further, as described above, when the distance between the first opening end 23DE1 and the second opening end 23DE2 is defined as B, and the hole diameter of the fin collar 25 is defined as C, B≤0.75. The arrangement of the first downstream cut-and-raised portion 23D1 and the second downstream cut-and-raised portion 23D2 is determined so as to satisfy the relationship xC. This effect will be described below.

First, conventional heat exchangers used heat transfer tubes having an outer diameter of, for example, 7.2 mm or 7.0 mm. The outer diameter of the heat transfer tubes 17 constituting the heat exchanger 18 according to Embodiment 1 is 5.0 mm, which is smaller than the outer diameter of conventional heat transfer tubes. It is known that when the outer diameter of the heat transfer tube 17 becomes smaller, a pipe wake, which is an air flow occurring on the downstream side of the heat transfer tube 17 in the ventilation direction FL, is generated and the pipe wake grows along the ventilation direction FL. ing. Furthermore, it is generally known that the pipe wake reaches the cross-flow fan 22 .

By positioning the first opening end 23DE1 and the second opening end 23DE2 behind the downstream fin collar 25D with respect to the ventilation direction FL, constricted air is generated between the downstream cut-and-raised portion 23D and the downstream fin collar 25D. It is possible to suppress This constricted air is a flow of air that has been constricted and increased in speed.

If the above distance B is not specified, the growth of the pipe wake 27 cannot be suppressed in the heat exchanger provided with the heat transfer tubes 17 having an outer diameter of 5.0 mm, and the pipe wake 27 will be displaced by the cross flow fan 22. plunge into. Therefore, there is a difference between the speed of the slow air around the blade surface of the cross-flow fan 22 and the speed of the pipe wake 27, and this speed difference causes a pressure difference, resulting in abnormal blower noise. There is fear.

On the other hand, the heat exchanger 18 having the heat transfer tube 17 having an outer diameter of 5.0 mm (that is, the hole diameter C of the fin collar 25 is 5.0 mm) satisfies the relationship B≦0.75×C Thus, the distance B between the first open end 23DE1 and the second open end 23DE2 is determined. As a result, the growth of the pipe wake 27 is reliably suppressed, and the pipe wake 27 does not directly flow into the cross flow fan 22, so that the occurrence of abnormal fan noise can be suppressed.

In Embodiment 1, the structure in which the cut-and-raised portions 23 and the fin collars 25 are arranged in each of the two first rows a and second rows b has been described. The effect obtained by the first embodiment can be obtained not only in the heat exchanger 18 having the two-row structure, but also in a heat exchanger having three or more rows. Similar or similar effects can also be obtained with structures having different column widths.

(Principle of generation of abnormal fan noise)
Next, before describing more specifically the effects obtained by the first embodiment, the principle of generation of abnormal fan noise generated in a conventional heat exchanger will be described.

The cross-flow fan 22 has wings with blade surfaces. As the cross-flow fan 22 is driven to rotate, the air flowing in the space around the blade surface is affected by pressure when passing through the blade surface from the front to the rear. Rotation noise is generated from the cross flow fan 22 by the action of this pressure.

In addition, abnormal fan noise occurs due to periodic changes in the flow of air in the heat exchanger in the ventilation direction. In order to eliminate the abnormal blower noise, it is preferable to reduce the speed difference and pressure difference of the air flowing in the space around the blade surfaces of the cross-flow fan 22 to obtain a uniform flow.

In addition, in the field of air conditioners, from the viewpoint of curbing global warming, there is a demand for conversion from refrigerants such as R410a to low GWP refrigerants such as R32. A refrigerant with a low GWP has mild flammability, so an air conditioner using a low GWP refrigerant is designed to operate with a reduced amount of refrigerant.

Regarding this point, in conventional heat exchangers, for example, heat transfer tubes having an outer diameter of 7.2 mm or 7.0 mm, which were the mainstream in the past, were used, but the heat exchanger 18 according to Embodiment 1 is The outer diameter of the constituting heat transfer tube 17 is 5.0 mm. As a result, the diameter of the heat transfer tube 17 is reduced, which is suitable for the operation of the air conditioner with a reduced amount of refrigerant.

Next, Examples 1 and 2 and Comparative Examples 1 to 5 will be described with reference to FIGS. 6 to 13. FIG.
Examples 1 and 2 described below show the results obtained by the air conditioner 1 including the heat exchanger 18 according to Embodiment 1 described above. Comparative Examples 1 to 4 differ from Example 1 in the structures of the cut-and-raised portion 23 and the fin collar 25 . Comparative Example 5 differs from Example 2 in the relationship between the height F of the space 30 and the height H of the cut-and-raised portion 23 .

(Comparative example 1)
FIG. 6 is a diagram showing the wind velocity distribution in the heat exchanger 50 according to Comparative Example 1. As shown in FIG.
In the structure shown in Comparative Example 1, the opening end 23DE of the downstream cut-and-raised portion 23D is not located behind (downstream) of the downstream fin collar 25D in the ventilation direction FL. Furthermore, in the heat exchanger 50 according to Comparative Example 1, the heat transfer tubes 17 having an outer diameter of 5.0 mm are used, and the diameters of the heat transfer tubes 17 are reduced. In such a heat exchanger 50 , when air flows along the ventilation direction FL, the pipe wake 27 tends to grow on the downstream side of the heat transfer pipe 17 .

The velocity of this pipe wake 27 is lower than the velocity of the air flow that would not have reached the cross-flow fan 22 if heat transfer tubes with an outer diameter of 7.2 mm were mounted in the heat exchanger.
In the heat exchanger 50 , such pipe wake flow 27 directly reaches the cross flow fan 22 . Therefore, due to the generation of the pipe wake 27, a speed difference and a pressure difference occur in the air flowing in the space around the blade surfaces of the cross-flow fan 22, and abnormal fan noise is likely to occur.

Furthermore, it is conceivable that the heat transfer tube 17 having a reduced diameter is applied while maintaining the conventional arrangement of the cut-and-raised portions 23 . In this case, constricted air 26 is generated between the fin collar 25 provided with the heat transfer tube 17 and the cut-and-raised portion 23 . The constricted air 26 is an air flow generated by constricted air, and has a high velocity. If the constricted air 26 directly flows into the cross flow fan 22, a significant difference in speed will occur between the constricted air 26 and the pipe wake 27, making abnormal fan noise more likely to occur.

(Example 1)
FIG. 7A is a plan view showing the wind speed distribution in the heat exchanger 18 according to the first embodiment, in which both open ends 23DE of two cut-and-raised portions 23D adjacent to each other extend behind the fin collar 25 with respect to the ventilation direction. It is a figure which shows the case where it is located in.
FIG. 7B is a graph corresponding to the wind speed distribution shown in FIG. 7A. In FIG. 7B, the vertical axis indicates the position of the fin in the longitudinal direction, and the horizontal axis indicates the flow velocity (m/s) at the end of the fin on the downstream side DW in the airflow direction FL.

The plan view shown in FIG. 7A corresponds to FIG. That is, the opening end 23DE of the downstream cut-and-raised portion 23D is located behind the downstream fin collar 25D. In particular, the downstream fin collar 25D is positioned between the first downstream cut-and-raised portion 23D1 and the second downstream cut-and-raised portion 23D2.
Reference numeral 100 in FIG. 7B indicates the velocity difference between the constricted air flow and the pipe wake 27 . This speed difference was about 0.8 m/s. 7B corresponds to the position of the pipe wake 27 shown in FIG. 7A.

As shown in FIGS. 7A and 7B, the opening end 23DE of the downstream cut-and-raised portion 23D is positioned behind the downstream fin collar 25D, thereby inhibiting the growth of the pipe wake flow 27 having a slow speed, and causing the pipe wake flow 27 to grow. shortened in length. The pipe wake 27 does not reach the blade surface of the cross-flow fan 22, which is the surface on which abnormal fan noise is generated. Therefore, the difference in speed between the constricted air flow and the pipe wake 27 can be reduced, and abnormal fan noise can be suppressed.

(Comparative example 2)
FIG. 8A is a plan view showing the wind speed distribution in the heat exchanger 51 according to Comparative Example 2, in which both open ends 23DE of two cut-and-raised portions 23D adjacent to each other are located behind the fin collar 25 with respect to the ventilation direction. It is a figure which shows the case where it is not located in. In FIG. 8A, the same members as those shown in FIG. 7A are denoted by the same reference numerals, and the description thereof will be omitted or simplified.

FIG. 8B is a graph corresponding to the wind speed distribution shown in FIG. 8A. In FIG. 8B, the vertical axis indicates the position of the fin in the longitudinal direction, and the horizontal axis indicates the flow velocity (m/s) at the end of the fin on the downstream side DW in the air flow direction FL.
Reference numeral 101 in FIG. 8B indicates the velocity difference between the constricted air flow and the pipe wake 27 . This speed difference was about 3.0 m/s. 8B corresponds to the position of the pipe wake 27 shown in FIG. 8A.

As shown in FIGS. 8A and 8B, when the opening end 23DE of the cut-and-raised portion 23D is not located behind the fin collar 25 with respect to the ventilation direction FL, from between the fin collar 25 and the cut-and-raised portion 23D, Constricted air 26 is generated. This constricted air 26 is an air flow in which the air is constricted and the speed is increased. For this reason, a significant difference in speed occurs between the constricted air 26 and the pipe wake 27 . In this state, when the contracted air 26 and the pipe wake 27 reach the blade surface of the cross-flow fan 22, an abnormal blower noise is generated.

Furthermore, the following point is clear when Example 1 shown in FIG. 7A and Comparative Example 2 shown in FIG. 8A are compared.
First, comparing the shape of the pipe wake 27 shown in FIG. 7A with the shape of the pipe wake 27 shown in FIG. 8A, the width of the pipe wake 27 shown in FIG. is smaller than the width of the pipe wake 27 shown in FIG.
Also, it can be seen that the length of the pipe wake 27 shown in FIG. 7A (the length in the direction along the ventilation direction FL) is smaller than the length of the pipe wake 27 shown in FIG. 8A.
From such a comparison result, in comparison with Comparative Example 2, in Example 1, it is possible to suppress an increase in the width of the low-velocity air flow caused by the wake of the piping. In other words, compared with Comparative Example 2, in Example 1, it is possible to prevent the air flow having a low speed from reaching the cross-flow fan.

(Comparative Example 3)
FIG. 9A is a plan view showing the wind speed distribution in the heat exchanger 52 according to Comparative Example 3, in which only one open end 23DE1 of the open ends 23DE of the two cut-and-raised portions 23D adjacent to each other is 10 is a diagram showing a case where the fin collar 25 is located behind the fin collar 25. FIG. In other words, only the opening end 23DE2 is not located behind the fin collar 25 with respect to the ventilation direction. In FIG. 9A, the same members as those shown in FIG. 7A are denoted by the same reference numerals, and the description thereof will be omitted or simplified.

FIG. 9B is a graph corresponding to the wind speed distribution shown in FIG. 9A. In FIG. 9B, the vertical axis indicates the position of the fin in the longitudinal direction, and the horizontal axis indicates the flow velocity (m/s) at the end of the fin on the downstream side DW in the air flow direction FL.

Reference numeral 102 in FIG. 9B indicates the velocity difference between the constricted air flow and the pipe wake 27 . This speed difference was about 3.5 m/s. 9B corresponds to the position of the pipe wake 27 shown in FIG. 9A.
As shown in FIGS. 9A and 9B, when the opening end 23DE1 is positioned behind the fin collar 25 with respect to the airflow direction and the opening end 23DE2 is not positioned behind the fin collar 25 with respect to the airflow direction, Compressed air 26 is generated from the open end 23DE2. Therefore, the growth of the pipe wake 27 cannot be sufficiently suppressed. Furthermore, a significant difference in velocity between the constricted air 26 and the pipe wake 27 occurs. In this state, when the contracted air 26 and the pipe wake 27 reach the blade surface of the cross-flow fan 22, an abnormal blower noise is generated.

(Comparative Example 4)
FIG. 10 is a plan view partially showing a fin constituting a heat exchanger according to Comparative Example 4, showing a case where the cut-and-raised portion is divided.
The heat exchanger fins may be cut to a required length depending on the specifications and design of the indoor unit 2 . When cutting the fins 24 of this heat exchanger, a part of the cut-and-raised portion 23 may be broken. If a portion of the cut-and-raised portion 23 is broken, the broken cut-and-raised portion 23 may protrude from the outer shell of the heat exchanger 18 . In this case, the condensed water generated in the evaporator may drop into the ventilation passage via the broken cut-and-raised portion 23 . Therefore, the cut-and-raised portion 23 may be divided and provided on the fin 24 so as not to be broken.
FIG. 10 shows a case where the fin 24 is provided with the first split portion 23F and the second split portion 23S. The cut-and-raised portion 23 is not formed in the boundary portion 23X located between the first divided portion 23F and the second divided portion 23S.

FIG. 11A is a plan view showing the wind velocity distribution in the heat exchanger 53 according to Comparative Example 4, and shows the case where the cut-and-raised portion 23 is divided.
FIG. 11B is a graph corresponding to the wind speed distribution shown in FIG. 11A. In FIG. 11B, the vertical axis indicates the position of the fin in the longitudinal direction, and the horizontal axis indicates the flow velocity (m/s) at the end of the fin on the downstream side DW in the air flow direction FL.

As shown in FIG. 11A, in the case where the cut-and-raised portion 23 is divided into the first divided portion 23F and the second divided portion 23S, the air is released from the position of the boundary portion 23X along the ventilation direction FL. put away. Further, since the flow path of the boundary portion 23X is narrow, the flow velocity of the air is high, and the constricted air 26 is generated. Specifically, the position indicated by reference numeral 103 in FIG. 11B corresponds to the boundary portion 23X shown in FIGS. 10 and 11A. The flow velocity of the constricted air 26 generated from the boundary 23X was approximately 1.6 m/s.

When this contracted air 26 reaches the blade surfaces of the cross-flow fan 22, an abnormal blower noise is generated. Therefore, each of the plurality of downstream cut-and-raised portions 23D forming the most downstream second row b in the ventilation direction FL is required to be one continuous portion (cut-and-raised portion). In other words, the downstream cut-and-raised portion 23</b>D must be formed by one cut-and-raised portion that is not divided in the longitudinal direction of the fin 24 .
For the reason described above, it is necessary to form the cut-and-raised portion 23 in the fin 24 so that the first divided portion 23F and the second divided portion 23S are not formed.

(Example 2)
FIG. 12 is a perspective view showing simulation results of wind speed distribution in the heat exchanger 18 according to the second embodiment.
In the heat exchanger 18 according to the second embodiment, the height of the space 30 formed between the fins 24 adjacent to each other in the overlapping direction of the plurality of fins 24 is defined as F, and each of the plurality of cut-and-raised portions 23 is defined as H, the height of each of the plurality of cut-and-raised portions 23 is set so as to satisfy the relationship H≦1/2×F (see FIGS. 4A and 4B).

By setting the height of each of the plurality of cut-and-raised portions 23 so as to satisfy the relationship H≦1/2×F, a flow area (spatial area ) becomes wider. This makes it easier for the air to circulate in the space 30 .

Therefore, as shown in FIG. 12, the constricted air 29 flowing between the fin collar 25 and the cut-and-raised portion 23 can be reduced. As a result, the influence of pressure on the blade surfaces of the cross-flow fan 22 can be minimized.

(Comparative Example 5)
FIG. 13 is a perspective view showing a simulation result of the wind speed distribution in the heat exchanger 18 according to Comparative Example 5. As shown in FIG. Unlike Example 2 shown in FIG. 12, Comparative Example 5 does not satisfy the relationship H≦1/2×F. That is, in Comparative Example 5, the height of the space 30 and the height H of the cut-and-raised portion are set so as to satisfy the relationship of H>1/2×F.

In the case of the relationship H>1/2×F, the flow area (spatial area) in which the air 29 flows between the fins 24 adjacent to each other becomes narrow. Therefore, the flow velocity of the air 29 flowing between the fin collar 25 and the cut-and-raised portion 23 increases. When the air 29 with a high flow velocity reaches the cross-flow fan 22, the pressure on the blade surfaces of the cross-flow fan 22 increases. As a result, abnormal noise is likely to occur.
Therefore, in the case of the relationship of H>1/2×F, the effects described in the second embodiment cannot be obtained.

1...Air conditioner 2...Indoor unit 2T...Ceiling 3...Outdoor unit 4...Refrigerant pipe 5...Blower 6...Blower 7...Indoor heat exchanger 8...Outdoor heat exchanger 9...Expansion valve 10...Compressor 11...Flow Path switching valve 12...Case 12A...Cover (case) 12B...Support portion (case) 13...Front panel 14...Air filter 15...Top panel 16...Base 17...

Heat transfer tube

18, 50, 51, 52, 53 ...Heat exchanger 18A...First heat exchange section 18AL, 18BL...Lower end 18AU...Upper end 18B...Second heat exchange section 18BU...Upper end 19...Drain pan 20...Flap 20A...Rotating shaft 21...Outlet 22...Cross flow fan (blower ) 22A... Front area 22B... Upper area 22C... Upper part 23... Cut-and-raised part 23D... Downstream cut-and-raised part (cut-and-raised part) 23D1... First downstream cut-and-raised part (cut-and-raised part) 23D2... Second downstream cut-and-raised part (Cut and raised portion) 23DE, 23UE...Open end 23DE1...First open end (open end) 23DE2...Second open end (open end) 23DH, 23UH...Opening 23DH1...First opening 23DH2...Second opening 23F 1st division 23S 2nd division 23T Upper end 23U Upper cut-and-raised portion (cut-and-raised portion) 23X Boundary 24 Fin 24F Plate surface (surface) 24K Boundary 25 Fin collar 25CAa Center Position 25CAb...Central position 25CBa...Central position 25CBb...Central position 25D...Downstream fin collar (fin collar) 25P...Fixed position 25U...Upstream fin collar (fin collar) 26...Constricted air 27...Piping downstream 29...Air 30... Space a... 1st row b... 2nd row DW... downstream side UP... upstream side W... wall surface

Claims

a heat exchanger having a heat transfer tube through which a refrigerant flows and performing heat exchange between the refrigerant flowing through the heat transfer tube and air;
a blower that blows air to the heat transfer tubes;
with
The heat exchanger is
a plurality of plate-shaped fins extending in an extending direction intersecting with a ventilation direction of air sent by the blower to the heat exchanger;
a plurality of cut-and-raised portions formed on the plate surface of each of the plurality of fins;
a fin collar provided between the fins adjacent to each other among the plurality of fins and through which the heat transfer tubes are inserted;
with
The plurality of cut-and-raised portions include a downstream cut-and-raised portion located downstream of the fin collar in the airflow direction,
One end in the extending direction of the downstream cut-and-raised portion is arranged so as to overlap the fin collar when viewed in the ventilation direction,
Air conditioner.
The plurality of cut-and-raised portions include a first downstream cut-and-raised portion and a second downstream cut-and-raised portion located downstream of the fin collar in the airflow direction,
The first downstream cut-and-raised portion has a first end in the extending direction,
The second downstream cut-and-raised portion has a second end in the extending direction,
The fin collar is positioned between the first downstream cut-and-raised portion and the second downstream cut-and-raised portion,
The first end and the second end are formed so as to face each other and be adjacent to each other,
The first end and the second end are arranged to overlap the fin collar when viewed in the airflow direction.
The air conditioner according to claim 1.
defining the distance between the first end and the second end as B;
When the hole diameter of the fin collar is defined as C,
To satisfy the relationship B ≤ 0.75 × C,
The first downstream cut-and-raised part and the second downstream cut-and-raised part are arranged,
The air conditioner according to claim 2.
a first fin collar provided between adjacent fins among the plurality of fins and through which the heat transfer tubes are inserted;
a second fin collar provided between adjacent fins among the plurality of fins and through which the heat transfer tubes are inserted;
has
The first fin collar and the second fin collar are arranged adjacent to each other,
Between the first fin collar and the second fin collar, the downstream cut-and-raised portion is formed by one cut-and-raised portion that is not divided in the longitudinal direction.
The air conditioner according to any one of claims 1 to 3.
The height of the space formed between the fins adjacent to each other in the direction in which the plurality of fins overlap is defined as F,
When the height of each of the plurality of cut-and-raised parts is defined as H,
so as to satisfy the relationship H ≤ 1/2 × F,
a height of each of the plurality of cut-and-raised parts is set;
The air conditioner according to any one of claims 1 to 4.
The hole diameter of each of the plurality of fin collars through which the heat transfer tubes are inserted is 5.35 mm or less.
The air conditioner according to any one of claims 1 to 5.