JP7372777B2 - Heat exchangers and air conditioners - Google Patents

Description

The present invention relates to a heat exchanger and an air conditioner.

BACKGROUND ART Air conditioners configured to perform both cooling and heating operations have become popular as home and commercial air conditioners. There are also air conditioners that perform only cooling operation without heating operation.

For example, Patent Document 1 discloses a side flow type parallel flow heat exchanger that includes two header pipes and a plurality of flat tubes that connect the header pipes. A partition plate is provided inside the header pipe to divide the plurality of flat tubes into a plurality of groups. The heat exchanger disclosed in Patent Document 1 is a heat exchanger installed in an air conditioner that performs both cooling operation and heating operation.

Patent No. 5858478

In an air conditioner, in order to increase its operating efficiency, it is required to increase the amount of heat exchanged in a heat exchanger.

The present invention provides a heat exchanger capable of increasing the amount of heat exchange, and an air conditioner equipped with the heat exchanger.

Further, the present invention provides a heat exchanger that can save space, and an air conditioner equipped with the heat exchanger.

A heat exchanger according to an embodiment of the present invention includes a first header pipe and a second header pipe arranged apart from each other, and a plurality of flat pipes connected to the first header pipe and the second header pipe. , a plurality of heat radiation fins arranged between adjacent flat tubes of the plurality of flat tubes, and an interior of each of the first header pipe and the second header pipe are divided into a plurality of spaces, and the plurality of A heat exchanger comprising a plurality of partition plates that divide flat tubes into a plurality of groups, wherein the first header pipe divided into the plurality of spaces is supplied with a refrigerant from outside the heat exchanger. one of the first and second header pipes divided into the plurality of spaces has an outlet section through which the refrigerant is discharged to the outside of the heat exchanger; The cross-sectional area of the internal space of the inlet part in the direction perpendicular to the extending direction is 1.5-3.0 times the cross-sectional area of the internal space of the outlet part.

According to an embodiment, the plurality of groups include a group located most upstream with respect to the flow of the refrigerant and a group located most downstream with respect to the flow of the refrigerant, and the plurality of groups include a group located most downstream with respect to the flow of the refrigerant, A plurality of flat tubes belonging to a group located on the side may be connected to the inlet portion, and a plurality of flat tubes belonging to a group located on the most downstream side may be connected to the outlet portion.

According to an embodiment, the plurality of groups include a group located second upstream with respect to the flow of the refrigerant and a group located third upstream with respect to the flow of the refrigerant. , the first header pipe divided into the plurality of spaces is divided into a plurality of flat pipes belonging to the group located on the second upstream side and a plurality of flat pipes belonging to the group located on the third upstream side. The cross-sectional area of the internal space of the inlet in the direction perpendicular to the direction in which the first header pipe extends is 1.5 to 3.0 times the cross-sectional area of the internal space of the turn. It may be.

According to an embodiment, the first header pipe may include the outlet section.

According to an embodiment, the inner diameter of the inlet section may be 1.3-1.7 times the inner diameter of the outlet section.

According to an embodiment, the cross-sectional area of the internal space of the inlet section in the direction perpendicular to the direction in which the first header pipe extends is 2.0 to 2.5 times the cross-sectional area of the internal space of the outlet section. There may be.

An air conditioner according to an embodiment of the present invention includes any of the heat exchangers described above.

A heat exchanger according to an embodiment of the present invention includes a first header pipe and a second header pipe arranged apart from each other, and a plurality of flat pipes connected to the first header pipe and the second header pipe. , a plurality of heat radiation fins arranged between adjacent flat tubes of the plurality of flat tubes, and an interior of each of the first header pipe and the second header pipe are divided into a plurality of spaces, and the plurality of a plurality of partition plates that divide flat tubes into a plurality of groups, the first header pipe divided into the plurality of spaces is supplied with refrigerant from outside the heat exchanger. The heat exchanger further includes a third header pipe connected to the inlet part, and the heat exchanger further includes a third header pipe connected to the inlet part, and the inner space of the third header pipe in a direction perpendicular to the direction in which the first header pipe extends. The cross-sectional area is 0.5-1.5 times the cross-sectional area of the internal space of the inlet.

In one embodiment, the plurality of groups include a group located most upstream with respect to the flow of the refrigerant, and the third header pipe includes a plurality of groups belonging to the inlet section and the group located most upstream. The inlet portion and the plurality of flat tubes belonging to the group located most upstream may be connected via the third header pipe.

In one embodiment, the third header pipe may be arranged on a side opposite to the plurality of flat tubes with respect to the inlet portion.

In one embodiment, one of the first and second header pipes divided into the plurality of spaces may include an outlet portion through which the refrigerant is discharged to the outside of the heat exchanger.

In some embodiments, the first header pipe may include the outlet section.

In one embodiment, the cross-sectional area of the internal space of the inlet section and the cross-sectional area of the internal space of the outlet section in a direction perpendicular to the direction in which the first header pipe extends may be the same.

In one embodiment, the volume of the internal space of the third header pipe may be 0.5 to 1.5 times the volume of the internal space of the inlet.

In one embodiment, the inner diameter of the third header pipe may be 0.8-1.2 times the inner diameter of the inlet.

In one embodiment, the cross-sectional area of the internal space of the third header pipe in the direction perpendicular to the direction in which the first header pipe extends is 0.8 to 1.2 times the cross-sectional area of the internal space of the inlet. There may be.

An air conditioner according to an embodiment of the present invention includes any of the heat exchangers described above.

A heat exchanger according to an embodiment of the present invention includes a first header pipe and a second header pipe arranged apart from each other, and a plurality of flat pipes connected to the first header pipe and the second header pipe. , a plurality of heat radiation fins arranged between adjacent flat tubes of the plurality of flat tubes, and an interior of each of the first header pipe and the second header pipe are divided into a plurality of spaces, and the plurality of A heat exchanger comprising: a plurality of partition plates that divide the flat tubes into a plurality of groups; and a side sheet fixed to the first header pipe and the second header pipe, the heat exchanger comprising: The divided first header pipe includes an inlet portion through which refrigerant is supplied from outside the heat exchanger, and the plurality of groups include a first group located most upstream with respect to the flow of the refrigerant; The second header pipe, which includes a second group located on the second upstream side and is divided into the plurality of spaces, includes a plurality of flat pipes belonging to the first group and a plurality of flat pipes belonging to the second group. The side seat has a structure with a space inside, and the internal space of the side seat is connected to the internal space of the turn part.

In one embodiment, the interior space of the side sheet may be separated from the interior space of the entrance section.

In one embodiment, the side sheet may be arranged above the plurality of flat tubes belonging to the first group.

In one embodiment, one of the first and second header pipes divided into the plurality of spaces may include an outlet portion through which the refrigerant is discharged to the outside of the heat exchanger.

In some embodiments, the first header pipe may include the outlet section.

In one embodiment, the volume of the inner space of the side sheet may be 0.5 to 1.5 times the volume of the inner space of the turn part.

An air conditioner according to an embodiment of the present invention includes any of the heat exchangers described above.

A heat exchanger according to an embodiment of the present invention includes a first header pipe and a second header pipe arranged apart from each other, and a plurality of flat pipes connected to the first header pipe and the second header pipe. , a plurality of heat radiation fins arranged between adjacent flat tubes of the plurality of flat tubes, and an interior of each of the first header pipe and the second header pipe are divided into a plurality of spaces, and the plurality of a plurality of partition plates that divide flat tubes into a plurality of groups, the first header pipe divided into the plurality of spaces is supplied with refrigerant from outside the heat exchanger. the heat exchanger in a direction perpendicular to the direction in which the plurality of flat tubes extend, the plurality of groups including a first group located most upstream with respect to the flow of the refrigerant; When the total cross-sectional area of the internal spaces of all the flat tubes included in is A _e , and the total cross-sectional area of the internal spaces of all the flat tubes belonging to the first group is _A1 , the total cross-sectional area The ratio of the total cross-sectional area A ₁ to A _e is 0.40-0.80.

In one embodiment, the flat tube is a multi-hole tube having a plurality of holes, and the cross-sectional area of the internal space of the flat tube may be the sum of the cross-sectional areas of the plurality of holes.

In one embodiment, the plurality of groups includes a second group located second upstream with respect to the flow of the refrigerant, and the plurality of flat tubes of one of the plurality of flat tubes belonging to the first group include When the cross-sectional area of the internal space is _A11 , and the cross-sectional area of the internal space of one of the flat tubes belonging to the second group is _A21 , the cross-sectional area _A11 is the cross-sectional area It may be 1.25-1.75 times _A21 .

In one embodiment, the cross-sectional area of the internal space of one of the plurality of flat tubes belonging to the first group is _A11 , and the plurality of flat tubes belonging to a group other than the first group among the plurality of groups When the cross-sectional area of the internal space of one of the flat tubes is A _O1 , the cross-sectional area A ₁₁ may be 1.25 to 1.75 times the cross-sectional area A _O1 .

In one embodiment, a plurality of flat tubes belonging to the first group may be connected to the inlet portion.

In one embodiment, one of the first and second header pipes divided into the plurality of spaces includes an outlet portion through which the refrigerant is discharged to the outside of the heat exchanger, A plurality of flat tubes belonging to one of the groups other than the first group may be connected to the outlet section.

In some embodiments, the first header pipe may include the outlet section.

An air conditioner according to an embodiment of the present invention includes any of the heat exchangers described above.

A heat exchanger according to an embodiment of the present invention includes a first header pipe and a second header pipe arranged apart from each other, and a plurality of flat pipes connected to the first header pipe and the second header pipe. , a plurality of heat radiation fins arranged between adjacent flat tubes of the plurality of flat tubes, and an interior of each of the first header pipe and the second header pipe are divided into a plurality of spaces, and the plurality of A heat exchanger comprising: a plurality of partition plates that divide the flat tubes into a plurality of groups; and a side sheet fixed to the first header pipe and the second header pipe, the heat exchanger comprising: The divided first header pipe includes an inlet portion through which refrigerant is supplied from outside the heat exchanger, and one of the first and second header pipes divided into the plurality of spaces is provided with an inlet portion to which a refrigerant is supplied from outside the heat exchanger. The refrigerant is provided with an outlet section through which the refrigerant is discharged to the outside of the container, and the side sheet has a structure with a space inside, and the inner space of the side sheet is connected to the inner space of the outlet section.

In one embodiment, the plurality of groups include a group located most downstream with respect to the flow of the refrigerant and a group located second most downstream, and the first and second groups divided into the plurality of spaces The other side of the second header pipe includes a turn portion connected to a plurality of flat pipes belonging to the group located most downstream and a plurality of flat pipes belonging to the group located second most downstream, The interior space of the seat may be separated from the interior space of the turn portion.

In one embodiment, the side sheet may be arranged below a plurality of flat tubes belonging to the group located on the most downstream side.

In some embodiments, the first header pipe may include the outlet section.

In one embodiment, the first header pipe may include the outlet section, and the second header pipe may include the turn section.

In one embodiment, the volume of the internal space of the side sheet may be 0.5 to 1.5 times the volume of the internal space of the output section.

An air conditioner according to an embodiment of the present invention includes any of the heat exchangers described above.

According to a heat exchanger according to an embodiment of the present invention, the cross-sectional area of the internal space of the inlet part is 1.5-3.0 times the cross-sectional area of the internal space of the outlet part. By increasing the cross-sectional area of the inlet, the internal volume on the upstream side of the heat exchanger can be increased. Gaseous refrigerant mainly flows on the upstream side of the heat exchanger. By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the amount of heat exchanged by the heat exchanger can be increased.

Moreover, according to the heat exchanger according to an embodiment of the present invention, the third header pipe is connected to the inlet portion of the first header pipe. The cross-sectional area of the internal space of the third header pipe is 0.5 to 1.5 times the cross-sectional area of the internal space of the inlet. By adding a header pipe to the inlet, the internal volume on the upstream side of the heat exchanger can be increased. Gaseous refrigerant mainly flows on the upstream side of the heat exchanger. By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the amount of heat exchanged by the heat exchanger can be increased.

Moreover, according to the heat exchanger according to an embodiment of the present invention, the side seat has a space inside, and the interior space of the turn portion of the second header pipe is connected to the interior space of the side seat. Thereby, the internal volume on the upstream side of the heat exchanger can be increased. Gaseous refrigerant mainly flows on the upstream side of the heat exchanger. By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the amount of heat exchanged by the heat exchanger can be increased.

Moreover, according to the heat exchanger according to an embodiment of the present invention, the internal space of all the flat tubes belonging to the first group is The ratio of the total cross-sectional area is 0.40-0.80. By increasing the cross-sectional area of the internal space of the upstream flat tube, the internal volume of the upstream side of the heat exchanger can be increased. Gaseous refrigerant mainly flows on the upstream side of the heat exchanger. By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the amount of heat exchanged by the heat exchanger can be increased.

Moreover, according to the heat exchanger according to an embodiment of the present invention, the side seat has a space inside, and the interior space of the outlet portion is connected to the interior space of the side seat. Thereby, the side sheet can be used as a liquid receiver. By using the side sheet as a liquid receiver, there is no need to separately provide a liquid receiver. This makes it possible to save space in the air conditioner. In a configuration in which the heat exchanger is mounted on the outdoor unit, space saving of the outdoor unit can be realized.

FIG. 1 is a diagram showing a heat exchanger according to a first embodiment of the present invention. FIG. 2 is a diagram showing a plurality of flat tubes 2 divided into a plurality of groups according to a first embodiment of the present invention. It is a figure showing the cross section of the entrance part, the exit part, and the 2nd turn part concerning a 1st embodiment of the present invention. It is a figure showing the heat exchanger concerning a 2nd embodiment of the present invention. It is a figure which shows the cross section of the inlet part and 3rd header pipe based on 2nd Embodiment of this invention. It is a figure which shows the modification of the heat exchanger based on 2nd Embodiment of this invention. It is a figure which shows the heat exchanger based on 3rd Embodiment of this invention. It is a figure showing the heat exchanger concerning a 4th embodiment of the present invention. It is a figure showing the heat exchanger concerning a 5th embodiment of the present invention. It is a figure which shows the cross section of the flat tube based on 5th Embodiment of this invention. It is a figure which shows the modification of the heat exchanger based on 5th Embodiment of this invention. It is a figure showing an air conditioner concerning a 6th embodiment of the present invention.

Hereinafter, a heat exchanger and an air conditioner according to embodiments of the present invention will be described with reference to the drawings. Similar components are given the same reference numerals, and repeated detailed descriptions will be omitted. Moreover, the following embodiments are illustrative, and the present invention is not limited to the following embodiments.

In order to explain the embodiments in an easy-to-understand manner, the shape of each member and the positional relationship between the members may be described with the x direction in the drawings as the left-right direction, the y direction as the depth direction, and the z-axis direction as the up-down direction. . When a device including a heat exchanger is installed on a horizontal plane, the up-down direction may be approximately parallel to the vertical direction, and the left-right direction and the depth direction may be approximately parallel to the horizontal direction. However, the present invention is not limited to the up-down direction, the left-right direction, and the depth direction, and may be inclined with respect to the vertical direction and the horizontal direction.

In order to explain the embodiments in an easy-to-understand manner, the inside of various components of the heat exchanger may be shown transparently in the drawings.

(First embodiment)
FIG. 1 is a front view showing a heat exchanger 1 according to the first embodiment. The heat exchanger 1 according to the first embodiment is a so-called parallel flow type heat exchanger. The explanation will be made assuming that the upper side in FIG. 1 is the upper side of the heat exchanger 1, and the lower side is the lower side of the heat exchanger 1.

The heat exchanger 1 includes a first header pipe 10, a second header pipe 20, a plurality of flat tubes 2, a plurality of heat radiation fins 3, partition plates 51, 52, 53, and side sheets 61, 62. Be prepared.

Each of the first header pipe 10 and the second header pipe 20 has a cylindrical shape with a space inside. The first header pipe 10 and the second header pipe 20 are arranged apart from each other in the left-right direction. Each of the first header pipe 10 and the second header pipe 20 is arranged such that its longitudinal direction extends along the up-down direction.

The first header pipe 10 is provided with a cap 55 that closes its upper end and a cap 57 that closes its lower end. The second header pipe 20 is provided with a cap 56 that closes its upper end and a cap 58 that closes its lower end. The caps 55, 56, 57, and 58 prevent the refrigerant from flowing out from both ends of the first header pipe 10 and the second header pipe 20, respectively.

Each of the plurality of flat tubes 2 is arranged so that its longitudinal direction extends along the left-right direction. Each of the flat tubes 2 has one end connected to the first header pipe 10 and the other end connected to the second header pipe 20. The number of flat tubes 2 can be appropriately set depending on the required heat exchange amount and pressure loss, and is, for example, 30 to 160, but is not limited thereto. In FIG. 1, the number of flat tubes 2 is limited to 20 in order to make the structure of the heat exchanger 1 easier to understand.

Inside the flat tube 2, there is a through hole that serves as a refrigerant passage through which the refrigerant flows. The flat tube 2 of this embodiment is a multi-hole tube, and one flat tube 2 has a plurality of through holes. The internal space of each of the plurality of through holes is connected to the internal space of the first header pipe 10 and the internal space of the second header pipe 20. The plurality of flat tubes 2 and the first and second header pipes 10 and 20 may be joined by brazing or welding.

The plurality of flat tubes 2 are arranged at intervals in the vertical direction. The plurality of heat radiation fins 3 are arranged between adjacent flat tubes 2 among the plurality of flat tubes 2. Further, the radiation fins 3 are arranged above the flat tube 2 located at the uppermost side, and are also arranged below the flat tube 2 located at the lowermost side. The radiation fins 3 of this embodiment are corrugated fins, but are not limited thereto. The radiation fins 3 may be plate fins, for example. The flat tube 2 and the radiation fins 3 may be joined by brazing or welding.

A side sheet 61 is arranged above the radiation fin 3 located at the uppermost side. A side sheet 62 is arranged below the radiation fin 3 located at the lowest position.

Each of the side sheets 61 and 62 is arranged such that its longitudinal direction runs along the left-right direction. The side sheet 61 has one end fixed to the upper part of the first header pipe 10 and the other end fixed to the upper part of the second header pipe 20. The side sheet 62 has one end fixed to the lower part of the first header pipe 10 and the other end fixed to the lower part of the second header pipe 20. The side sheets 61 and 62 and the first and second header pipes 10 and 20 may be joined by brazing or welding. The side sheets 61 and 62 may be joined to the radiation fins 3 by brazing or welding. The core 4 is constituted by a set of the flat tube 2, the radiation fins 3, and the side sheets 61 and 62.

As materials for each of the first header pipe 10, second header pipe 20, flat tube 2, radiation fin 3, and side sheets 61 and 62, a metal material with high thermal conductivity such as aluminum or aluminum alloy may be used.

The partition plates 51, 52, and 53 divide the insides of the first header pipe 10 and the second header pipe 20 into a plurality of spaces. The partition plates 51 and 53 are provided inside the first header pipe 10. The partition plate 52 is provided inside the second header pipe 20. The first and second header pipes 10 and 20 and the partition plates 51, 52, and 53 may be joined by brazing or welding.

The partition plate 51 is located above the partition plate 53. In the vertical direction, the partition plate 52 is located at a height between the partition plates 51 and 53. The partition plates 51 and 53 divide the first header pipe 10 into three chambers: an inlet section 11, a second turn section 12, and an outlet section 13. The partition plate 52 divides the second header pipe 20 into two chambers, a first turn section 21 and a third turn section 23.

Refrigerant is supplied to the inlet portion 11 from outside the heat exchanger 1 . At the first turn portion 21, the refrigerant flowing leftward turns back rightward. At the second turn portion 12, the refrigerant that was flowing rightward turns back to the left. At the third turn portion 23, the refrigerant flowing leftward turns back to the right. The refrigerant is discharged from the outlet portion 13 to the outside of the heat exchanger 1 .

The partition plates 51, 52, and 53 also divide the plurality of flat tubes 2 into a plurality of groups. FIG. 2 is a diagram showing a plurality of flat tubes 2 divided into a plurality of groups. In this embodiment, the plurality of flat tubes 2 are divided into four groups: a first group 71, a second group 72, a third group 73, and a fourth group 74. The number of groups is arbitrary, and may be 3 or less, or 5 or more.

The flat tubes 2 located above the partition plate 51 belong to the first group 71. The flat tubes 2 located between the partition plates 51 and 52 in the vertical direction belong to the second group 72. The flat tubes 2 located between the partition plates 52 and 53 in the vertical direction belong to the third group 73. The flat tubes 2 located below the partition plate 53 belong to the fourth group 74.

Referring to FIGS. 1 and 2, each of the flat tubes 2 belonging to the first group 71 has one end connected to the inlet portion 11 and the other end connected to the first turn portion 21. The internal space of each of the flat tubes 2 belonging to the first group 71 is connected to the internal space 31 of the inlet portion 11 . Further, the internal space of each of the flat tubes 2 belonging to the first group 71 is connected to the internal space 41 of the first turn portion 21 .

Each of the flat tubes 2 belonging to the second group 72 has one end connected to the second turn section 12 and the other end connected to the first turn section 21. The internal space of each of the flat tubes 2 belonging to the second group 72 is connected to the internal space 41 of the first turn portion 21 . Furthermore, the internal space of each of the flat tubes 2 belonging to the second group 72 is connected to the internal space 32 of the second turn portion 12 .

Each of the flat tubes 2 belonging to the third group 73 has one end connected to the second turn section 12 and the other end connected to the third turn section 23. The internal space of each of the flat tubes 2 belonging to the third group 73 is connected to the internal space 32 of the second turn portion 12 . Furthermore, the internal space of each of the flat tubes 2 belonging to the third group 73 is connected to the internal space 43 of the third turn portion 23 .

Each of the flat tubes 2 belonging to the fourth group 74 has one end connected to the outlet section 13 and the other end connected to the third turn section 23. The internal space of each of the flat tubes 2 belonging to the fourth group 74 is connected to the internal space 33 of the outlet section 13 . Further, each internal space of the flat tubes 2 belonging to the fourth group 74 is connected to the internal space 43 of the third turn portion 23.

Based on the flow of refrigerant, the first group 71 is the group located on the most upstream side. The second group 72 is the second group located on the upstream side. The third group 73 is the third group located on the upstream side. The fourth group 74 is the group located on the most downstream side. The third group 73 can also be expressed as the second downstream group.

A refrigerant supply pipe 5 is provided in the inlet portion 11 . A refrigerant discharge pipe 6 is provided at the outlet portion 13 . A refrigerant is supplied to the inlet portion 11 from outside the heat exchanger 1 via the refrigerant supply pipe 5 . For example, refrigerant is supplied to the inlet portion 11 from a compressor described later.

The refrigerant supplied to the inlet portion 11 passes through the flat tubes 2 belonging to the first group 71 and flows into the first turn portion 21 . That is, the refrigerant flows inside the flat tubes 2 belonging to the first group 71 from right to left. The refrigerant that has flowed into the first turn portion 21 then flows into the second turn portion 12 through the flat tubes 2 belonging to the second group 72 . The refrigerant flows inside the flat tubes 2 belonging to the second group 72 from left to right.

The refrigerant that has flowed into the second turn portion 12 then flows into the third turn portion 23 through the flat tubes 2 belonging to the third group 73 . The refrigerant flows inside the flat tubes 2 belonging to the third group 73 from right to left. The refrigerant that has flowed into the third turn section 23 then flows into the outlet section 13 through the flat tubes 2 belonging to the fourth group 74 . The refrigerant flows inside the flat tubes 2 belonging to the fourth group 74 from left to right. The refrigerant that has flowed into the outlet portion 13 passes through the refrigerant discharge pipe 6 and is discharged to the outside of the heat exchanger 1 . While flowing through the heat exchanger 1, the refrigerant exchanges heat with gas outside the heat exchanger 1. The refrigerant discharged to the outside of the heat exchanger 1 is supplied to, for example, an expansion valve described below.

In this embodiment, the cross-sectional area of the internal space 31 of the inlet part 11 in the direction perpendicular to the vertical direction in which the first header pipe 10 extends is larger than the cross-sectional area of the internal space 33 of the outlet part 13. As the first header pipe 10 of this embodiment, a single pipe having a different cross-sectional area depending on the internal position may be used, or two or more pipes having different cross-sectional areas may be combined to form the first header pipe 10. may be configured.

FIG. 3 is a diagram showing a cross section of the inlet section 11 and the outlet section 13. The cross section shown in FIG. 3 is a cross section in a direction perpendicular to the up-down direction. In other words, it is a cross section parallel to the plane formed by the left-right direction and the depth direction. In FIG. 3, a cross-sectional portion of the internal space is shown with diagonal lines.

As shown in FIG. 3, the cross-sectional area of the internal space 31 of the inlet section 11 is larger than the cross-sectional area of the internal space 33 of the outlet section 13. In this embodiment, the cross-sectional area of the internal space 31 of the inlet part 11 is 1.5-3.0 times the cross-sectional area of the internal space 33 of the outlet part 13.

When the inlet section 11 and the outlet section 13 each have a circular cross section, the inner diameter D ₁₁ of the inlet section 11 is 1.3 to 1.7 times the inner diameter D ₁₃ of the outlet section 13 . Note that the cross-sectional shapes of the inlet portion 11 and the outlet portion 13 are not limited to a perfect circle. Their cross-sectional shape may be, for example, an ellipse or a rectangle. Comparison of cross-sectional areas is performed by comparing cross-sectional areas at arbitrary positions of each member. For example, the cross-sectional areas of each member at the position where the cross-sectional area is the largest may be compared. Furthermore, for example, the cross-sectional areas at approximately the center of each member in the vertical direction may be compared.

In this way, by increasing the cross-sectional area of the inlet portion 11, the internal volume on the upstream side of the heat exchanger 1 can be increased. A gaseous refrigerant mainly flows on the upstream side of the heat exchanger 1 . By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the heat exchange amount of the heat exchanger 1 can be increased.

Depending on various factors such as the required heat exchange amount and pressure loss, the cross-sectional area of the internal space 31 of the inlet section 11 is 2.0 to 2.5 times the cross-sectional area of the internal space 33 of the outlet section 13. It's okay. Similarly to the above, by increasing the cross-sectional area of the inlet portion 11, the internal volume on the upstream side of the heat exchanger 1 can be increased, and the amount of heat exchanged by the heat exchanger 1 can be increased.

Further, the cross-sectional area of the internal space 31 of the entrance portion 11 may be larger than the cross-sectional area of the internal space 32 of the second turn portion 12. FIG. 3 further shows a cross section of the second turn portion 12. As shown in FIG. In the example shown in FIG. 3, the cross-sectional area of the internal space 32 of the second turn part 12 is the same as the cross-sectional area of the internal space 33 of the outlet part 13, but they may be different from each other.

In this embodiment, the cross-sectional area of the internal space 31 of the inlet portion 11 is 1.5 to 3.0 times the cross-sectional area of the internal space 32 of the second turn portion 12. When each of the entrance portion 11 and the second turn portion 12 has a circular cross section, the inner diameter D ₁₁ of the entrance portion 11 is 1.3 to 1.7 times the inner diameter D ₁₂ of the second turn portion 12 . Note that the cross-sectional shapes of the entrance portion 11 and the second turn portion 12 are not limited to a perfect circle. Their cross-sectional shape may be, for example, an ellipse or a rectangle.

Depending on various factors such as the required heat exchange amount and pressure loss, the cross-sectional area of the internal space 31 of the inlet section 11 is 2.0 to 2.5 times the cross-sectional area of the internal space 32 of the second turn section 12. It may be.

By increasing the cross-sectional area of the inlet portion 11, the internal volume on the upstream side of the heat exchanger 1 can be increased, and the amount of heat exchanged by the heat exchanger 1 can be increased.

In addition, in this embodiment, although the outlet part 13 was provided in the 1st header pipe 10, it may be provided in the 2nd header pipe 20. For example, if the number of groups of flat tubes 2 is odd, the outlet part 13 may be provided at the lower part of the second header pipe 20.

(Second embodiment)
FIG. 4 is a front view showing the heat exchanger 1 according to the second embodiment. Compared to the heat exchanger 1 according to the first embodiment, the heat exchanger 1 according to the second embodiment includes a third header pipe 15 connected to the inlet portion 11 of the first header pipe 10.

In the example shown in FIG. 4, the cross-sectional area of the internal space 31 of the inlet part 11 in the direction perpendicular to the vertical direction is the same as the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. may be different from each other. For example, in the heat exchanger 1 according to the first embodiment, the cross-sectional area of the internal space 31 of the inlet part 11 is larger than the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. It's okay.

In the example shown in FIG. 4, the third header pipe 15 is arranged on the opposite side of the plurality of flat tubes 2 with respect to the inlet portion 11. That is, the third header pipe 15 is arranged outside the inlet portion 11 of the heat exchanger 1. The third header pipe 15 is provided with a cap 55a that closes its upper end and a cap 57a that closes its lower end. The internal space 31 of the inlet portion 11 and the internal space 35 of the third header pipe 15 are connected via a connecting pipe 16. The number of connecting pipes 16 is arbitrary and may be one or more. In the example shown in FIG. 4, the number of connecting pipes 16 is three. In the example shown in FIG. 4, the third header pipe 15 is provided with a refrigerant supply pipe 5. Note that the internal space 31 of the inlet portion 11 and the internal space 35 of the third header pipe 15 may be directly connected to each other without using the connecting pipe 16.

A refrigerant is supplied to the third header pipe 15 from outside the heat exchanger 1 via the refrigerant supply pipe 5 . The refrigerant supplied to the third header pipe 15 flows into the inlet portion 11 through the connecting pipe 16. The refrigerant that has entered the inlet section 11 passes through the flat tubes 2 (FIG. 2) belonging to the first group 71 and flows into the first turn section 21 . The flow of the refrigerant thereafter is the same as in the first embodiment.

In this embodiment, the cross-sectional area of the internal space 35 of the third header pipe 15 in the direction perpendicular to the vertical direction is 0.5 to 1.5 times the cross-sectional area of the internal space 31 of the inlet portion 11.

FIG. 5 is a diagram showing a cross section of the inlet portion 11 and the third header pipe 15. In FIG. 5, a cross-sectional portion of the internal space is shown with diagonal lines.

In the example shown in FIG. 5 , the cross-sectional area of the internal space 35 of the third header pipe 15 is smaller than the cross-sectional area of the internal space 31 of the inlet portion 11 . Depending on various factors such as the required amount of heat exchange and pressure loss, the cross-sectional area of the internal space 35 may be larger or smaller than the cross-sectional area of the internal space 31.

The volume of the internal space 35 of the third header pipe 15 is, for example, 0.5 to 1.5 times the volume of the internal space 31 of the inlet portion 11. For example, when the vertical lengths of the internal space 31 and the internal space 35 are approximately the same, the volume of the internal space 35 is 0.5 to 1.5 times the volume of the internal space 31.

When the inlet section 11 and the third header pipe 15 each have a circular cross section, the inner diameter D ₁₅ of the third header pipe 15 is 0.8 to _1.2 times the inner diameter D 11 of the inlet section 11. Note that the cross-sectional shapes of the inlet portion 11 and the third header pipe 15 are not limited to a perfect circle. Their cross-sectional shape may be, for example, an ellipse or a rectangle.

In this way, by adding the third header pipe 15 to the inlet section 11 and increasing the cross-sectional area of the entire inlet section that receives refrigerant from the outside, it is possible to increase the internal volume on the upstream side of the heat exchanger 1. can. A gaseous refrigerant mainly flows on the upstream side of the heat exchanger 1 . By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the heat exchange amount of the heat exchanger 1 can be increased.

Depending on various factors such as the required heat exchange amount and pressure loss, the cross-sectional area of the internal space 35 of the third header pipe 15 is 0.8 to 1.2 times the cross-sectional area of the internal space 31 of the inlet section 11. It may be. Similarly to the above, the internal volume on the upstream side of the heat exchanger 1 can be increased, and the amount of heat exchanged by the heat exchanger 1 can be increased.

Note that the third header pipe 15 may be arranged between the first header pipe 10 and the flat tube 2. That is, the third header pipe 15 may be arranged inside the inlet section 11 of the heat exchanger 1.

FIG. 6 is a front view showing the heat exchanger 1 with the third header pipe 15 disposed inside. In the example shown in FIG. 6, the third header pipe 15 is arranged between the inlet portion 11 of the first header pipe 10 and the flat tubes 2 belonging to the first group 71. The flat tubes 2 belonging to the first group 71 are connected to the third header pipe 15. The inlet portion 11 and the flat tubes 2 belonging to the first group 71 are connected via the third header pipe 15. The refrigerant supply pipe 5 is provided at the inlet portion 11 of the first header pipe 10.

A refrigerant is supplied to the inlet portion 11 from outside the heat exchanger 1 via the refrigerant supply pipe 5 . The refrigerant supplied to the inlet portion 11 passes through the connecting pipe 16 and flows into the third header pipe 15 . The refrigerant that has flowed into the third header pipe 15 passes through the flat tubes 2 belonging to the first group 71 and flows into the first turn portion 21 . The flow of the refrigerant thereafter is the same as in the first embodiment.

Also in the form shown in FIG. 6, the internal volume on the upstream side of the heat exchanger 1 can be increased, and the amount of heat exchanged by the heat exchanger 1 can be increased.

(Third embodiment)
FIG. 7 is a front view showing the heat exchanger 1 according to the third embodiment. Compared to the heat exchanger 1 according to the first embodiment, the heat exchanger 1 according to the third embodiment has a structure in which the side sheet 61 has a space 63 inside. The side sheet 61 is a side sheet disposed above the flat tubes 2 (FIG. 2) belonging to the first group 71.

In the example shown in FIG. 7, the cross-sectional area of the internal space 31 of the inlet part 11 in the direction perpendicular to the vertical direction is the same as the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. may be different from each other. For example, in the heat exchanger 1 according to the first embodiment, the cross-sectional area of the internal space 31 of the inlet part 11 is larger than the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. It's okay.

In this embodiment, the internal space 63 of the side seat 61 is connected to the internal space 41 of the first turn portion 21 of the second header pipe 20. The internal space 63 of the side seat 61 is not connected to the internal space 31 of the inlet portion 11 of the first header pipe 10. That is, the internal space 63 of the side seat 61 is separated from the internal space 31 of the entrance portion 11.

Since the internal space 41 is connected to the internal space 63, the volume of the portion functioning as the first turn portion can be increased. Thereby, the internal volume on the upstream side of the heat exchanger 1 can be increased. A gaseous refrigerant mainly flows on the upstream side of the heat exchanger 1 . By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the heat exchange amount of the heat exchanger 1 can be increased.

The volume of the internal space 63 of the side seat 61 is, for example, 0.5 to 1.5 times the volume of the internal space 41 of the first turn portion 21. The volume of the internal space 63 of the side seat 61 can be set depending on various factors such as the required amount of heat exchange and pressure loss.

Note that the internal space 63 of the side seat 61 may have an inclination such that the first turn portion 21 side is located lower than the entrance portion 11 side. As a result, more refrigerant can be prevented from accumulating on the inlet portion 11 side of the internal space 63 than on the first turn portion 21 side.

(Fourth embodiment)
FIG. 8 is a front view showing the heat exchanger 1 according to the fourth embodiment. Compared to the heat exchanger 1 according to the first embodiment, in the heat exchanger 1 according to the fourth embodiment, the side sheet 62 has a structure with a space 64 inside. The side sheet 62 is a side sheet disposed below the flat tubes 2 (FIG. 2) belonging to the fourth group 74.

In the example shown in FIG. 8, the cross-sectional area of the internal space 31 of the inlet part 11 in the direction perpendicular to the vertical direction is the same as the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. may be different from each other. For example, in the heat exchanger 1 according to the first embodiment, the cross-sectional area of the internal space 31 of the inlet part 11 is larger than the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. It's okay.

In this embodiment, the internal space 64 of the side seat 62 is connected to the internal space 33 of the outlet portion 13 of the first header pipe 10 . The internal space 64 of the side seat 62 is not connected to the internal space 43 of the third turn portion 23 of the second header pipe 20. That is, the internal space 64 of the side seat 62 is separated from the internal space 43 of the third turn portion 23.

Since the internal space 33 is connected to the internal space 64, the side sheet 62 can be used as a liquid receiver. The liquid receiver is a tank that stores liquid refrigerant inside, and cushions fluctuations in the amount of refrigerant due to load fluctuations. By using the side sheet 62 as a liquid receiver, there is no need to separately provide a liquid receiver. This makes it possible to save space in the air conditioner. In a configuration in which the heat exchanger 1 is mounted on the outdoor unit, space saving of the outdoor unit can be realized.

The volume of the internal space 64 of the side seat 62 is, for example, 0.5 to 1.5 times the volume of the internal space 33 of the outlet section 13. The volume of the internal space 64 of the side seat 62 can be set depending on various factors such as the required amount of heat exchange and pressure loss.

Note that the internal space 64 of the side seat 62 may have an inclination such that the outlet portion 13 side is located lower than the third turn portion 23 side. Thereby, it is possible to suppress more refrigerant from accumulating on the third turn portion 23 side than on the outlet portion 13 side of the internal space 64.

(Fifth embodiment)
FIG. 9 is a front view showing the heat exchanger 1 according to the fifth embodiment. In the heat exchanger 1 according to the fifth embodiment, the cross-sectional area of the internal space of the flat tubes 2 belonging to the first group 71 is larger than the heat exchanger 1 according to the first embodiment.

In the example shown in FIG. 9, the cross-sectional area of the internal space 31 of the inlet part 11 in the direction perpendicular to the vertical direction is the same as the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. may be different from each other. For example, in the heat exchanger 1 according to the first embodiment, the cross-sectional area of the internal space 31 of the inlet part 11 is larger than the cross-sectional area of the internal space 32 of the second turn part 12 and the internal space 33 of the outlet part 13. It's okay.

FIG. 10 is a diagram showing a cross section of a flat tube according to the fifth embodiment. The flat tube 121 shown in FIG. 10 is the flat tube 2 belonging to the first group 71. The flat tube 122 is a flat tube 2 that belongs to at least one group other than the first group 71. The flat tube 122 is, for example, the flat tube 2 belonging to the second to fourth groups 72 to 74.

As mentioned above, the flat tube 2 is a multi-hole tube, and one flat tube 2 has a plurality of through holes. A plurality of through holes 125 are opened in one flat tube 121. Due to the plurality of through holes 125, a plurality of internal spaces 127 exist in one flat tube 121. A plurality of through holes 126 are opened in the flat tube 122 . Due to the plurality of through holes 126, a plurality of internal spaces 128 exist in one flat tube 122.

The cross section shown in FIG. 10 is a cross section in a direction perpendicular to the left-right direction in which the flat tube 2 extends. In other words, it is a cross section parallel to the plane formed by the vertical direction and the depth direction. In FIG. 10, the cross-sectional portion of the internal space is indicated by diagonal lines. The total value of the cross-sectional area of the internal space 127 of one flat tube 121 is larger than the total value of the cross-sectional area of the internal space 127 of one flat tube 122.

The first group 71 includes a plurality of flat tubes 121. Each of the second to fourth groups 72 to 74 may include a plurality of flat tubes 121.

The cross-sectional area of the internal space of one flat tube 2 is the cross-sectional area that is the sum of the cross-sectional areas of the plurality of through holes. Here, the total cross-sectional area of the internal spaces of all the flat tubes 2 included in the heat exchanger 1 is defined as A _e . All the flat tubes 2 are the flat tubes 2 included in the first to fourth groups 71 to 74. Further, the sum of the cross-sectional areas of the internal spaces of all the flat tubes 2 belonging to the first group 71 is defined as A ₁ . At this time, the ratio of the total cross-sectional area A ₁ to the total cross-sectional area A _e is 0.40-0.80. That is, the ratio of the total cross-sectional area of the internal spaces of all the flat tubes 2 belonging to the first group 71 to the total cross-sectional area of the internal spaces of all the flat tubes 2 included in the heat exchanger 1 is 0. 40-0.80. By increasing the cross-sectional area of the internal space of the flat tube 2 on the upstream side, the internal volume on the upstream side of the heat exchanger 1 can be increased. A gaseous refrigerant mainly flows on the upstream side of the heat exchanger 1 . By increasing the internal volume on the upstream side through which the gaseous refrigerant flows, the heat exchange amount of the heat exchanger 1 can be increased.

Here, the total cross-sectional area of the internal space 127 of one flat tube 121 is defined as A ₁₁ , and the total cross-sectional area of one flat tube 122 is defined as A ₂₁ . The ratio between A ₁₁ and A ₂₁ is appropriately set depending on the number of flat tubes 2 included in the heat exchanger 1. For example, A ₁₁ is 1.25-1.75 times as large as A ₂₁ . By increasing the cross-sectional area of the internal space of the flat tubes 2 belonging to the first group 71, the internal volume on the upstream side of the heat exchanger 1 can be increased. Thereby, the amount of heat exchanged by the heat exchanger 1 can be increased.

Note that the through holes of the flat tubes 2 in the second to fourth groups 72 to 74 may be provided with protrusions that protrude inward. The presence of the protrusion inside the through hole allows the contact area between the flat tube 2 and the refrigerant to be increased. The through holes of the flat tubes 2 of the first group 71 may or may not be provided with protrusions. In a configuration in which the through hole is not provided with a protrusion, the internal space of the through hole can be increased by the amount of the absence of the protrusion.

FIG. 11 is a front view showing a modification of the heat exchanger 1 according to the fifth embodiment. Compared to the heat exchanger 1 shown in FIG. 9, in the heat exchanger 1 shown in FIG. 11, the number of flat tubes 2 belonging to the first group 71 is reduced. As the size of the flat tubes 2 in the first group 71 increases, the area for ventilation can be secured by reducing the number of flat tubes 2 in the first group 71. It is possible to both increase the internal volume on the upstream side of the heat exchanger 1 and secure an area for ventilation.

The features of the heat exchangers 1 according to the first to fifth embodiments described above can be combined as appropriate. For example, a heat exchanger that combines two or more of the features of each of the heat exchangers 1 according to the first to fifth embodiments is also included in the scope of the embodiments of the present invention. Furthermore, a heat exchanger that combines all the features of the heat exchangers 1 according to the first to fifth embodiments is also included in the scope of the embodiments of the present invention.

(Sixth embodiment)
FIG. 12 is a block diagram showing an air conditioner 200 according to the sixth embodiment.

Air conditioner 200 includes an outdoor unit 210 and an indoor unit 220. The outdoor unit 210 is installed outdoors, and the indoor unit 220 is installed indoors. The outdoor unit 210 includes a heat exchanger 211, a compressor 212, an expansion valve 213, and a blower 214. The indoor unit 220 includes a heat exchanger 221 and a blower 222.

As the heat exchanger 211, any of the heat exchangers 1 according to the first to fifth embodiments can be used. As the heat exchanger 211, a heat exchanger that appropriately combines the characteristics of the heat exchangers 1 according to the first to fifth embodiments may be used.

In the example shown in FIG. 12, the air conditioner 200 is an air conditioner that does not perform heating operation but only performs cooling operation. However, the present invention is not limited thereto, and the air conditioner 200 may be an air conditioner that can perform both cooling operation and heating operation.

The compressor 212 compresses the refrigerant and outputs it as a high-temperature, high-pressure gas. The refrigerant output from the compressor 212 flows into the heat exchanger 211 and passes through the heat exchanger 211 . The refrigerant condenses by exchanging heat with outdoor air. The airflow generated by the blower 214 facilitates heat exchange between the refrigerant and the outdoor air. The liquefied refrigerant flows from the heat exchanger 211 to the expansion valve 213. The refrigerant is depressurized by the expansion valve 213 to become a gas-liquid two-phase state, and is output from the outdoor unit 210.

The refrigerant output from the outdoor unit 210 flows into the indoor unit 220 through piping and passes through the heat exchanger 221 . The refrigerant vaporizes by exchanging heat with the indoor air. The airflow generated by the blower 222 facilitates heat exchange between the refrigerant and the indoor air. The vaporized refrigerant is output from the indoor unit 220 and flows into the compressor 212 through piping. The compressor 212 compresses the refrigerant and outputs it as a high-temperature, high-pressure gas.

By repeating such operations, the air conditioner 200 can perform cooling operation.

The embodiments of the present invention have been described above. The above description of the embodiments is an illustration of the present invention and is not intended to limit the present invention. Furthermore, embodiments in which the respective constituent elements described in the above-mentioned embodiments are appropriately combined are also possible. The present invention can be modified, replaced, added, omitted, etc. within the scope of the claims or equivalents thereof.

The invention is particularly useful in the field of heat exchangers and air conditioners.

1: Heat exchanger 2: Flat tube 3: Radiation fin 4: Core 5: Refrigerant supply pipe 6: Refrigerant discharge pipe 10: First header pipe 11: Inlet section 12: Second turn section 13: Outlet section 15: Third Header pipe 16: Connecting pipe 20: Second header pipe 21: First turn section 23: Third turn section 31: Internal space of inlet section 32: Internal space of second turn section 33: Internal space of outlet section 35: Third turn section 3 Internal space of header pipe 41: Internal space of first turn portion 43: Internal space of third turn portion 51, 52, 53: Partition plate 55, 56, 57, 58: Cap 61, 62: Side seat 63, 64 : Internal space of side seat 71: 1st group 72: 2nd group 73: 3rd group 74: 4th group D ₁₁ : Inner diameter of inlet part D ₁₂ : Inner diameter of second turn part D ₁₃ : Inner diameter of outlet part D ₁₅ : Inner diameter of the third header pipe 121: Flat tube belonging to the first group 122: Flat tube belonging to the second to fourth groups 125, 126: Through holes 127, 128: Internal space of the flat tube 200: Air conditioner 210 : Outdoor unit 211: Heat exchanger 212: Compressor 213: Expansion valve 214: Blower 220: Indoor unit 221: Heat exchanger 222: Blower

Claims (6)

a first header pipe and a second header pipe arranged apart from each other;
a plurality of flat pipes connected to the first header pipe and the second header pipe;
a plurality of radiation fins arranged between adjacent flat tubes of the plurality of flat tubes;
a plurality of partition plates that divide the interior of each of the first header pipe and the second header pipe into a plurality of spaces and divide the plurality of flat tubes into a plurality of groups;
A heat exchanger comprising:
The first header pipe divided into the plurality of spaces includes an inlet portion to which a refrigerant is supplied from outside the heat exchanger,
One of the first and second header pipes divided into the plurality of spaces includes an outlet portion through which the refrigerant is discharged to the outside of the heat exchanger,
The cross-sectional area of the internal space of the inlet section in the direction perpendicular to the direction in which the first header pipe extends is 1.5 to 3.0 times the cross-sectional area of the internal space of the outlet section,
The plurality of groups are
a group located second upstream with respect to the flow of the refrigerant;
a group located third upstream with respect to the flow of the refrigerant;
including;
The first header pipe divided into the plurality of spaces is connected to the plurality of flat pipes belonging to the group located on the second upstream side and the plurality of flat pipes belonging to the group located on the third upstream side. Equipped with a turned part,
In the heat exchanger, a cross-sectional area of the internal space of the inlet section in a direction perpendicular to the direction in which the first header pipe extends is 1.5 to 3.0 times as large as a cross-sectional area of the internal space of the turn section. a first header pipe and a second header pipe arranged apart from each other;
a plurality of flat pipes connected to the first header pipe and the second header pipe;
a plurality of radiation fins arranged between adjacent flat tubes of the plurality of flat tubes;
a plurality of partition plates that divide the interior of each of the first header pipe and the second header pipe into a plurality of spaces and divide the plurality of flat tubes into a plurality of groups;
A heat exchanger comprising:
The first header pipe divided into the plurality of spaces includes an inlet portion to which a refrigerant is supplied from outside the heat exchanger,
The first header pipe divided into the plurality of spaces includes an outlet portion through which the refrigerant is discharged to the outside of the heat exchanger,
A cross-sectional area of the internal space of the inlet section in a direction perpendicular to the direction in which the first header pipe extends is 1.5 to 3.0 times as large as a cross-sectional area of the internal space of the outlet section. The plurality of groups are
a group located most upstream with respect to the flow of the refrigerant;
a group located most downstream with respect to the flow of the refrigerant;
including;
A plurality of flat tubes belonging to the group located most upstream are connected to the inlet portion,
The heat exchanger according to claim 1 or 2 , wherein a plurality of flat tubes belonging to the group located on the most downstream side are connected to the outlet section. The heat exchanger according to any of claims 1 to 3 , wherein the inner diameter of the inlet section is 1.3-1.7 times the inner diameter of the outlet section. Claims 1 to 4 , wherein the cross-sectional area of the internal space of the inlet section in a direction perpendicular to the direction in which the first header pipe extends is 2.0 to 2.5 times the cross-sectional area of the internal space of the outlet section. The heat exchanger described in any of the above. An air conditioner comprising the heat exchanger according to any one of claims 1 to 5 .

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