WO2025169459A1 - Heat exchanger and air conditioning device - Google Patents

Abstract

This heat exchanger is provided with: a first heat exchange unit comprising a first heat transfer tube group and a first header that is connected to lower ends of a plurality of heat transfer tubes constituting the first heat transfer tube group and allows a refrigerant to circulate through the plurality of heat transfer tubes; a second heat exchange unit comprising a second heat transfer tube group and a second header that is connected to lower ends of a plurality of heat transfer tubes constituting the second heat transfer tube group and allows a refrigerant tp circulate through the plurality of heat transfer tubes; and a third header for allowing a refrigerant to circulate between the first heat exchange unit and the second heat exchange unit. The first header and the second header are formed so as to extend along a direction in which the plurality of heat transfer tubes are arranged spaced apart from one another; the first header and the second header are arranged facing each other; and if a gap which is a section constituting the shortest distance between the first header and the second header is defined as an inter-header gap δ (mm), the inter-header gap δ is at least 0.5 (mm).

Description

Heat exchanger and air conditioning device

This disclosure relates to a heat exchanger and air conditioning device in which two headers are arranged side by side.

Conventional heat exchangers include two headers provided at the lower ends of multiple heat transfer tubes extending vertically, with the two headers, one on the inlet side and one on the outlet side of the refrigerant, arranged side by side horizontally (see, for example, Patent Document 1).

Japanese Patent Application Laid-Open No. 2019-215161

When the heat exchanger of Patent Document 1 is installed in an outdoor unit, frost forms on its surface during operation in low-temperature environments. In such cases, hot gas refrigerant is passed through the heat exchanger to defrost it, and the meltwater generated by the defrosting flows toward the bottom of the heat exchanger (which has two headers). The heat exchanger of Patent Document 1 does not take into consideration the freezing of meltwater that flows between the two headers on the refrigerant inlet and outlet sides. If there is insufficient drainage gap between the two headers, or if the shape of the headers causes a lot of meltwater from the corrugated fins located between the heat transfer tubes to flow into the gap between the headers, meltwater may not be properly drained between the headers. If meltwater is not properly drained between two adjacent headers, under low-temperature conditions, the meltwater present between the two adjacent headers may become a source of ice, potentially causing the headers to deform due to the freezing of the meltwater.

The present disclosure is intended to solve the above-mentioned problems by providing a heat exchanger and air conditioning system that prevents header deformation due to freezing of meltwater and improves frost resistance.

The heat exchanger disclosed herein comprises a first heat exchange section having a first heat transfer tube group consisting of a plurality of heat transfer tubes extending in the vertical direction and a first header connected to the lower ends of the plurality of heat transfer tubes constituting the first heat transfer tube group and allowing refrigerant to flow through the plurality of heat transfer tubes; a second heat exchange section having a second heat transfer tube group consisting of a plurality of heat transfer tubes extending in the vertical direction and a second header connected to the lower ends of the plurality of heat transfer tubes constituting the second heat transfer tube group and allowing refrigerant to flow through the plurality of heat transfer tubes; and a third header into which the upper ends of the plurality of heat transfer tubes constituting the first heat exchange section and the second heat exchange section are inserted and allowing refrigerant to flow between the first heat exchange section and the second heat exchange section. , the first header and second header are formed to extend in the direction in which the multiple heat transfer tubes are spaced apart from each other, and where the direction in which the multiple heat transfer tubes extend is defined as a first direction, the direction in which the first header and second header extend is defined as a second direction, and the direction perpendicular to the first and second directions is defined as a third direction, the first header and second header are arranged facing each other in the third direction, and where the gap between the first and second headers at the shortest distance in the third direction is defined as the header gap δ [mm], the header gap δ is configured to be 0.5 [mm] or greater.

The air conditioning apparatus disclosed herein is comprised of a compressor and a heat exchanger of the above-described configuration, and includes a heat exchanger that exchanges heat between outdoor air and the refrigerant flowing inside, a throttle device that reduces the pressure of the refrigerant flowing inside, and an indoor heat exchanger that exchanges heat between indoor air and the refrigerant flowing inside.

This disclosure provides a heat exchanger and air conditioning system that prevents header deformation due to freezing of meltwater and improves frost resistance.

1 is a conceptual diagram showing the configuration of a refrigerant circuit of an air conditioning apparatus according to an embodiment. 1 is a perspective view schematically showing a heat exchanger of an air conditioning apparatus according to Embodiment 1. FIG. 1 is a conceptual diagram of a heat exchanger of an air conditioning apparatus according to Embodiment 1. FIG. 3 is a conceptual diagram showing the positional relationship between a first header and a second header in a heat exchanger of an air conditioning apparatus according to Embodiment 1. FIG. 1 is a perspective view of an outdoor unit of an air conditioning apparatus according to a first embodiment, viewed from the front. 1 is an exploded perspective view of an outdoor unit of an air conditioning apparatus according to Embodiment 1, viewed from the front. 1 is a conceptual plan view of the internal configuration of an outdoor unit of an air conditioning apparatus according to Embodiment 1. FIG. FIG. 10 is a diagram showing the relationship between the gap between headers and the amount of residual water between headers. 10 is a conceptual diagram showing the positional relationship between a first header and a second header in a heat exchanger of an air conditioning apparatus according to Embodiment 2. FIG. 10 is a conceptual diagram of a first header in a heat exchanger of an air conditioning apparatus according to a second embodiment, viewed from the side. FIG. 10 is a conceptual diagram of a partition plate in a heat exchanger of an air conditioning apparatus according to Embodiment 2. FIG. 10 is a conceptual diagram showing the positional relationship between a first header and a second header in a heat exchanger of an air conditioning apparatus according to Embodiment 3. FIG. 11 is a conceptual diagram of a first header in a heat exchanger of an air conditioning apparatus according to a third embodiment, viewed from the side. FIG. 10 is a conceptual diagram showing a partition plate and an inner pipe portion in a heat exchanger of an air conditioning apparatus according to Embodiment 3. FIG.

The heat exchanger and air conditioning device according to the embodiments will be described below with reference to the drawings. Note that in the following drawings, including Figure 1, the relative dimensional relationships and shapes of the components may differ from those in reality. In addition, in the following drawings, items with the same reference numerals are the same or equivalent, and this applies throughout the entire specification. To facilitate understanding, directional terms (e.g., up, down, right, left, front, rear, etc.) will be used as appropriate, but these notations are written in this manner for the convenience of explanation only and do not limit the placement or orientation of the device or parts.

Embodiment 1.
[Air conditioning device 100]
FIG. 1 is a conceptual diagram showing the configuration of a refrigerant circuit 101 of an air conditioning apparatus 100 according to an embodiment. The air conditioning apparatus 100 will be described using FIG. 1. The air conditioning apparatus 100 performs air conditioning by heating or cooling the room by transferring heat between outdoor air and indoor air via a refrigerant. The air conditioning apparatus 100 has an outdoor unit 10 and an indoor unit 20. Note that while FIG. 1 shows one outdoor unit 10 and one indoor unit 20, there may be multiple outdoor units 10 and multiple indoor units 20.

In the air conditioning apparatus 100, the indoor unit 20 and the outdoor unit 10 are connected by refrigerant piping 90 to form a refrigerant circuit 101 through which refrigerant circulates. In the refrigerant circuit 101, the compressor 11, flow switching device 12, indoor heat exchanger 22, throttling device 21, right heat exchanger 30a, rear heat exchanger 30b, left heat exchanger 30c, first flow control valve 13, second flow control valve 14, and accumulator 15 are connected by refrigerant piping 90. Each of the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c is one of multiple heat exchangers 30. Heat exchanger 30 is a collective term for the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c.

As shown in FIG. 1, in the refrigerant circuit 101 of the air conditioning apparatus 100, the rear heat exchanger 30b may be connected in parallel with the right heat exchanger 30a and the left heat exchanger 30c. Furthermore, the air conditioning apparatus 100 may have the right heat exchanger 30a and the left heat exchanger 30c connected in parallel. Note that the configuration of the refrigerant circuit 101 shown in FIG. 1 is one example, and other configurations are also possible. For example, the air conditioning apparatus 100 may not have the flow path switching device 12, and may not have the accumulator 15. Furthermore, the number of heat exchangers 30 may be one or multiple.

[Indoor unit 20]
The indoor unit 20 has an expansion device 21 and an indoor heat exchanger 22. The indoor unit 20 may further have a blower fan (not shown). The indoor unit 20 generates cold air or warm air by exchanging heat between indoor air passing through the indoor heat exchanger 22 and refrigerant flowing inside the indoor heat exchanger 22. The indoor unit 20 blows the cold air or warm air to the outside of the indoor unit 20, and sends conditioned air into the room.

The indoor heat exchanger 22 exchanges heat between the indoor air and the refrigerant. During cooling operation, the indoor heat exchanger 22 functions as an evaporator, evaporating the refrigerant and cooling the indoor air with the heat of vaporization. During heating operation, the indoor heat exchanger 22 functions as a condenser, releasing the heat of the refrigerant into the indoor air to condense the refrigerant.

[Outdoor unit 10]
The outdoor unit 10 has a compressor 11, a flow path switching device 12, a first flow control valve 13, a second flow control valve 14, an accumulator 15, and a plurality of heat exchangers 30. The plurality of heat exchangers 30 are composed of a right heat exchanger 30a, a rear heat exchanger 30b, and a left heat exchanger 30c.

Compressor 11 draws in low-temperature, low-pressure refrigerant, compresses it, and discharges high-temperature, high-pressure refrigerant. Compressor 11 is an inverter compressor whose capacity, which is the amount of refrigeration delivered per unit time, is controlled, for example, by changing the operating frequency.

The flow path switching device 12 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of refrigerant flow. During cooling operation, the flow path switching device 12 switches to the state shown by the solid lines, described below, and connects the discharge side of the compressor 11 to the heat exchanger 30. During heating operation, the flow path switching device 12 switches to the state shown by the dashed lines, and connects the discharge side of the compressor 11 to the indoor heat exchanger 22.

The right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c are heat exchangers 30 that exchange heat between outdoor air and refrigerant. During cooling operation, the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c function as condensers that radiate heat from the refrigerant to the outdoor air to condense the refrigerant. During heating operation, the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c function as evaporators that absorb heat from the outdoor air to evaporate the refrigerant. Details will be described later using Figures 5 to 7, but in embodiment 1, the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c are independent heat exchangers 30 and are located on the right, rear, and left sides of the outdoor unit 10.

The first flow control valve 13 and the second flow control valve 14 are, for example, electronic expansion valves that can adjust the throttle opening. The first flow control valve 13 is provided corresponding to the right heat exchanger 30a and the left heat exchanger 30c, and by changing its opening, it adjusts the flow rate of refrigerant flowing into the right heat exchanger 30a and the left heat exchanger 30c. The second flow control valve 14 is provided corresponding to the rear heat exchanger 30b, and by changing its opening, it adjusts the flow rate of refrigerant flowing into the rear heat exchanger 30b.

The opening degrees of the first flow control valve 13 and the second flow control valve 14 are determined for each site where the outdoor unit 10 is to be installed, for example, during construction of the outdoor unit 10. For example, if the air volume passing through the right heat exchanger 30a and the left heat exchanger 30c is expected to be small, the opening degree of the first flow control valve 13 is set smaller than when the air volume passing through the right heat exchanger 30a and the left heat exchanger 30c is expected to be normal or large. In this case, the opening degree of the second flow control valve 14 may be set larger than when the air volume passing through the right heat exchanger 30a and the left heat exchanger 30c is expected to be normal or large.

By setting the opening degrees of the first flow control valve 13 and the second flow control valve 14 in this manner, even if the air volume passing through the right heat exchanger 30a and the left heat exchanger 30c is small, the flow rate of refrigerant flowing into the right heat exchanger 30a and the left heat exchanger 30c can be reduced, preventing excess refrigerant from flowing through the right heat exchanger 30a and the left heat exchanger 30c. Note that if a wall or another outdoor unit 10 is adjacent to the side of the outdoor unit 10 facing the right heat exchanger 30a or left heat exchanger 30c, the air volume passing through the right heat exchanger 30a and the left heat exchanger 30c is expected to be small. The arrangement of the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c will be described later.

The accumulator 15 is located on the suction side of the compressor 11 and is used to store excess refrigerant that occurs due to differences in operating conditions between cooling and heating, or excess refrigerant caused by transient changes in operation. Furthermore, the accumulator 15 is used to prevent liquid compression in the compressor 11.

The throttling device 21 is, for example, an electronic expansion valve that can adjust the throttle opening, and by adjusting the opening, the pressure of the refrigerant flowing into the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c or the indoor heat exchanger 22 is controlled. In Embodiment 1, the throttling device 21 is provided in the indoor unit 20, but it may also be provided in the outdoor unit 10, and the installation location is not limited.

The air conditioning unit 100 is equipped with a heat exchanger 30 that exchanges heat between the outdoor air and the refrigerant flowing inside, a throttle device 21 that reduces the pressure of the refrigerant flowing inside, and an indoor heat exchanger 22 that exchanges heat between the indoor air and the refrigerant flowing inside.

<Cooling operation>
Here, the operation of the air conditioning apparatus 100 during each operation will be described. In cooling operation, as shown by the solid line in Fig. 2, the flow path switching device 12 is switched so that the discharge side of the compressor 11 is connected to the heat exchanger 30. The high-temperature, high-pressure gas refrigerant discharged from the compressor 11 flows into the right heat exchanger 30a, the rear heat exchanger 30b, and the left heat exchanger 30c via the flow path switching device 12. The high-temperature, high-pressure gas refrigerant that flows into the right heat exchanger 30a, the rear heat exchanger 30b, and the left heat exchanger 30c exchanges heat with the outdoor air, condenses while releasing heat, and flows out as low-temperature, high-pressure liquid refrigerant.

The low-temperature, low-pressure liquid refrigerant flowing out of the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c flows into the throttling device 21, where it is decompressed, becoming a low-temperature, low-pressure two-phase gas-liquid refrigerant, which then flows into the indoor heat exchanger 22. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 22 exchanges heat with the indoor air, absorbing heat and evaporating, becoming a low-temperature, low-pressure gas refrigerant that flows out of the indoor heat exchanger 22. At this time, the indoor air is cooled, and the room is cooled. The low-temperature, low-pressure gas refrigerant flowing out of the indoor heat exchanger 22 is drawn into the compressor 11 via the flow switching device 12 and the accumulator 15, where it again becomes a high-temperature, high-pressure gas refrigerant.

<Heating operation>
In heating operation, as shown by the dashed line in Fig. 1 , the flow path switching device 12 is switched so that the discharge side of the compressor 11 is connected to the indoor heat exchanger 22. The high-temperature, high-pressure gas refrigerant discharged from the compressor 11 flows into the indoor heat exchanger 22 via the flow path switching device 12. The high-temperature, high-pressure gas refrigerant that flows into the indoor heat exchanger 22 exchanges heat with the indoor air, condenses while releasing heat, and becomes low-temperature, high-pressure liquid refrigerant, which flows out of the indoor heat exchanger 22. At this time, the indoor air is heated, and heating is performed in the room. The low-temperature, high-pressure liquid refrigerant that flows out of the indoor heat exchanger 22 flows to the expansion device 21, where it is decompressed to become low-temperature, low-pressure two-phase gas-liquid refrigerant.

Low-temperature, low-pressure two-phase gas-liquid refrigerant flows into the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c exchanges heat with the outdoor air, absorbing heat and evaporating, before flowing out as low-temperature, low-pressure gas refrigerant. The low-temperature, low-pressure gas refrigerant that flows out of the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c is drawn into the compressor 11 via the flow switching device 12 and accumulator 15, where it again becomes high-temperature, high-pressure gas refrigerant.

<Defrosting operation>
FIG. 2 is a perspective view schematically illustrating the heat exchanger 30 of the air conditioning apparatus 100 according to the first embodiment. The arrows in FIG. 2 indicate the inflow and outflow directions of the refrigerant when the heat exchanger 30 functions as a condenser. In a low-temperature environment where the surface temperatures of the heat transfer tubes 32 and fins 33 are below 0°C, frost may form on the heat exchanger 30 during heating operation. When the amount of frost on the heat exchanger 30 exceeds a certain level, the air passage of the heat exchanger 30 through which the air generated by the fan 50 (see FIG. 6 ) passes is blocked, resulting in a decrease in the performance of the heat exchanger 30 and a decrease in heating performance. Therefore, when heating performance is reduced, a defrosting operation is performed to melt the frost on the surface of the heat exchanger 30.

During defrosting operation, the fan 50 (see Figure 6) is stopped, the flow path switching device 12 is switched to the same state as during cooling operation, and high-temperature, high-pressure gas refrigerant flows into the heat exchanger 30. This melts the frost that has adhered to the heat transfer tubes 32 and fins 33. The high-temperature refrigerant that flows into the heat transfer tubes 32 melts the frost that has adhered to the heat transfer tubes 32 and fins 33, turning them into water. The water that is produced when the frost melts is drained below the heat exchanger 30 along the heat transfer tubes 32 or fins 33. Once the frost has melted, defrosting operation ends and heating operation resumes.

[Configuration of heat exchanger 30]
Fig. 3 is a conceptual diagram of the heat exchanger 30 of the air conditioning apparatus 100 according to embodiment 1. The hatched arrows in Fig. 3 indicate the inflow or outflow direction of the refrigerant when the heat exchanger 30 functions as a condenser. The dashed arrows in Fig. 3 indicate an example of the direction of refrigerant flow inside the heat exchanger 30 when the heat exchanger 30 functions as a condenser. The hollow arrows in Fig. 3 indicate an example of the direction of air flow. Note that Fig. 3 omits illustration of a portion of the heat transfer tubes 32 and the fins 33.

Here, the configuration of the heat exchanger 30 will be described in detail using Figures 2 and 3. The right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c all have the same configuration, so they will be described here as heat exchangers 30. The heat exchanger 30 is an air-cooled heat exchanger that exchanges heat between the refrigerant flowing inside and the air. The heat exchanger 30 is, for example, a corrugated fin tube type with parallel piping.

The heat exchanger 30 has a first header 31, heat transfer tubes 32, fins 33, a third header 34, and a second header 35. The first header 31 and the second header 35 correspond to the "headers" in this disclosure. In the heat exchanger 30 according to embodiment 1, a pair of headers consisting of the first header 31 and the third header 34, and the second header 35, are arranged above and below.

The heat exchanger 30 has multiple heat transfer tubes 32 arranged between the first header 31, the second header 35, and the third header 34, with their flat surfaces facing each other and parallel to each other and perpendicular to the first header 31, the second header 35, and the third header 34.

A group of heat transfer tubes 32 (hereinafter also referred to as a flat tube group) consisting of multiple heat transfer tubes 32 is arranged in two rows in the air flow direction. The group of heat transfer tubes 32 in one row is connected to either the first header 31 or the second header 35. In other words, the group of heat transfer tubes 32 is connected to the first header 31 and the second header 35, respectively.

In embodiment 1, the heat exchanger 30 is a corrugated fin tube type heat exchanger in which groups of heat transfer tubes 32 are arranged in two rows, but this is not limited to this, and the heat exchanger may also be a heat exchanger in which groups of heat transfer tubes 32 are arranged in three or more rows.

The first header 31 of the heat exchanger 30 and the heat transfer tubes 32 inserted into the first header 31 are collectively referred to as the first heat exchange section 301. Similarly, the second header 35 of the heat exchanger 30 and the heat transfer tubes 32 inserted into the second header 35 are collectively referred to as the second heat exchange section 302. The first heat exchange section 301 and the second heat exchange section 302 may have fins 33 joined between adjacent heat transfer tubes 32.

The heat exchanger 30 has a first heat exchange section 301 and a second heat exchange section 302. The first heat exchange section 301 is one of the multiple heat exchange sections 300, and the second heat exchange section 302 is one of the multiple heat exchange sections 300. The heat exchange section 300 is a general term for the first heat exchange section 301 and the second heat exchange section 302.

The first heat exchange section 301 has a first heat transfer tube group 32A consisting of a plurality of heat transfer tubes 32 extending in the vertical direction, and a first header 31 connected to the lower ends of the plurality of heat transfer tubes 32 that make up the first heat transfer tube group 32A and circulating refrigerant through the plurality of heat transfer tubes 32.

The second heat exchange section 302 has a second heat transfer tube group 32B consisting of a plurality of heat transfer tubes 32 extending in the vertical direction, and a second header 35 connected to the lower ends of the plurality of heat transfer tubes 32 that make up the second heat transfer tube group 32B and circulating the refrigerant through the plurality of heat transfer tubes 32.

[Detailed configuration of heat exchanger 30]
As described above, the heat exchanger 30 has the first header 31, heat transfer tubes 32, fins 33, third header 34, and second header 35. In other words, the heat exchanger 30 has the first heat exchange section 301, the second heat exchange section 302, and the third header 34. The first header 31 is provided at the bottom of the heat exchanger 30. The first header 31 is connected to other devices that make up the air conditioning apparatus 100, and is a pipe through which the refrigerant flows in and out and through which the refrigerant branches or merges. A refrigerant inlet/outlet pipe 36 through which the refrigerant flows in and out from the outside is connected to the first header 31. The lower ends of the multiple heat transfer tubes 32 that make up the first heat exchange section 301 are inserted into the first header 31.

The first header 31 is formed in a long box shape. The first header 31 is formed to extend in the direction in which the multiple heat transfer tubes 32 are spaced apart from one another. The first header 31 is in communication with the internal spaces of the multiple heat transfer tubes 32. The first header 31 forms a space that distributes the refrigerant that flows in and out of the first heat exchange section 301 to the multiple heat transfer tubes 32. Alternatively, the first header 31 forms a space that merges the refrigerant that flows into the first header 31 from the multiple heat transfer tubes 32. The first header 31 is located below the heat exchanger 30, and hot gas refrigerant flows into it from the refrigerant circuit 101 during defrosting operation.

The multiple heat transfer tubes 32 are arranged in parallel horizontally at intervals so that air generated by the fan 50 (see Figure 6) flows between adjacent heat transfer tubes 32. The multiple heat transfer tubes 32 are arranged at intervals along the extension direction of the first header 31, second header 35, and third header 34. The heat transfer tubes 32 are arranged to extend in the vertical direction, and the refrigerant flows through the tubes along the extension direction of the heat transfer tubes 32. The heat transfer tubes 32 are arranged to extend vertically, for example. As an example, the heat transfer tubes 32 are flat tubes. The heat transfer tubes 32 are not limited to flat tubes, and may be tubes of other shapes, such as circular tubes.

When the heat transfer tubes 32 are flat tubes, the heat transfer tubes 32 have a flat cross section, with the outer surface on the long side of the flat shape along the air flow direction being flat, and the outer surface on the short side perpendicular to the long side being curved. When the heat transfer tubes 32 are flat tubes, the heat transfer tubes 32 are, for example, multi-hole flat tubes with multiple holes inside the tube that serve as refrigerant flow paths. The holes in the heat transfer tubes 32 are formed facing in the vertical direction, as they serve as flow paths between the first header 31, second header 35, and third header 34. Fins 33 are arranged between adjacent heat transfer tubes 32.

The fins 33 are heat transfer promoting members that are arranged between adjacent heat transfer tubes 32 among the multiple heat transfer tubes 32 and are connected to the heat transfer tubes 32. The fins 33 are brazed to the heat transfer tubes 32. The fins 33 are connected between adjacent heat transfer tubes 32 and transfer heat between the connected heat transfer tubes 32. The fins 33 improve the heat exchange efficiency between the air and the refrigerant, and corrugated fins are used as the fins 33, for example. When the fins 33 are corrugated fins, the fins 33 have a wave shape and are arranged between two adjacent heat transfer tubes 32, with multiple apexes joined to the flat surfaces of the heat transfer tubes 32.

The heat exchanger 30 shown in FIG. 2 has flat tubes as the heat transfer tubes 32 and corrugated fins as the fins 33. In the heat exchanger 30, the heat transfer tubes 32 and the fins 33 are arranged alternately in the arrangement direction of the heat transfer tubes 32, i.e., in the axial direction of the third header 34. The fins 33 are not limited to corrugated fins and may be other heat transfer promoting members such as plate fins. Furthermore, because heat exchange between the air and the refrigerant occurs on the surfaces of the heat transfer tubes 32, the heat exchanger 30 may have a so-called finless heat exchange section 300 without fins 33 as long as heat exchange capacity can be ensured.

The third header 34 is a header that acts as a bridge between a group of heat transfer tubes 32 in one row and a group of heat transfer tubes 32 in the other row. The heat exchanger 30 has the third header 34, located above the multiple heat exchange sections 300, into which the upper ends of the multiple heat transfer tubes 32 inserted in the first header 31 and second header 35 are inserted.

The third header 34 is provided at the end of the multiple heat transfer tubes 32 opposite the connection side of the first header 31 and the second header 35. The third header 34 is provided opposite the first header 31 and the second header 35 via the heat transfer tubes 32.

The third header 34 connects the upper part of the first heat exchange section 301 and the upper part of the second heat exchange section 302. The upper ends of the heat transfer tubes 32 that make up the first heat exchange section 301 and the second heat exchange section 302 are inserted into the third header 34, allowing the refrigerant to circulate between the first heat exchange section 301 and the second heat exchange section 302. The third header 34, for example, allows the refrigerant flowing through the first heat exchange section 301 to circulate to the second heat exchange section 302 that faces the first heat exchange section 301 in the short direction. The third header 34 forms a turning point for the refrigerant flow between the first heat exchange section 301 and the second heat exchange section 302.

The third header 34 allows refrigerant to flow between a plurality of heat transfer tubes 32 connected to one of the two headers, the first header 31 and the second header 35, and a plurality of heat transfer tubes 32 connected to the other header. The third header 34 forms a flow path that connects the heat transfer tubes 32 arranged opposite each other in the short direction. The third header 34 connects rows of condensed liquid refrigerant or refrigerant in a gas-liquid two-phase state.

The second header 35 is provided below the heat exchanger 30. The second header 35 is connected to other devices that make up the air conditioning unit 100, and is a pipe through which the refrigerant flows in and out, and through which the refrigerant branches or merges. A refrigerant inlet/outlet pipe 37 through which refrigerant flows in and out from the outside is connected to the second header 35. The lower ends of multiple heat transfer pipes 32 that make up the second heat exchange section 302 are inserted into the second header 35.

The second header 35 is formed in a long box shape. The second header 35 is formed to extend in the direction in which the multiple heat transfer tubes 32 are spaced apart from one another. The second header 35 is in communication with the internal spaces of the multiple heat transfer tubes 32. The second header 35 forms a space where the refrigerant that flows into the interior of the second header 35 from the multiple heat transfer tubes 32 joins together. Alternatively, the second header 35 forms a space where the refrigerant that flows into the interior of the second heat exchange unit 302 from the outside of the second heat exchange unit 302 is distributed to the multiple heat transfer tubes 32 that make up the second heat exchange unit 302.

The second header 35 is arranged parallel to the first header 31. The heat exchanger 30 is arranged so that the first header 31 and the second header 35 are adjacent to each other in the horizontal direction. The heat exchanger 30 is arranged so that the first header 31 and the second header 35 are adjacent to each other in the direction of air flow passing through the heat exchanger 30.

Here, as shown in Figures 2 and 3, the direction in which the multiple heat transfer tubes 32 extend is defined as the first direction D1, the direction in which the first header 31 and the second header 35 extend is defined as the second direction D2, and the direction perpendicular to the first direction D1 and the second direction D2 is defined as the third direction D3. In this case, the first header 31 and the second header 35 are arranged opposite each other in the third direction D3.

The third direction D3 is perpendicular to the extension direction of the heat transfer tubes 32 and perpendicular to the extension direction of the first header 31 and the second header 35, and is the direction in which air flows through the heat exchanger 30. The second direction D2 is also the direction in which the heat transfer tubes 32 are spaced apart from one another, and is also the axial direction of the first header 31 and the second header 35.

Figure 4 is a conceptual diagram showing the positional relationship between the first header 31 and the second header 35 in the heat exchanger 30 of the air conditioning apparatus 100 according to embodiment 1. Figure 4 shows the positional relationship between the first header 31 and the second header 35 when viewed in the axial direction of the heat transfer tube 32, i.e., the vertical direction of the heat exchanger 30. Note that Figure 4 does not show the heat transfer tube 32 and the third header 34, etc.

The heat exchanger 30 is configured so that, when the distance between the first header 31 and the second header 35 in the third direction D3 is the shortest distance between them, the header gap δ [mm] is 0.5 [mm] or greater (header gap δ≧0.5).

[Configuration of outdoor unit 10]
FIG. 5 is a perspective view of the outdoor unit 10 of the air conditioning apparatus 100 according to Embodiment 1, as seen from the front. FIG. 6 is an exploded perspective view of the outdoor unit 10 of the air conditioning apparatus 100 according to Embodiment 1, as seen from the front. FIG. 7 is a conceptual plan view of the internal configuration of the outdoor unit 10 of the air conditioning apparatus 100 according to Embodiment 1. Note that FIG. 6 illustrates a state in which some of the components constituting the outdoor unit 10 have been removed. The hatched arrows in FIG. 7 indicate the flow of air. FIGS. 5 to 7 show an example of the configuration of an outdoor unit 10 equipped with a heat exchanger 30. In the following figures, arrows appropriately indicate directions, with the outdoor unit 10 positioned in a usable state as the reference, with the left being −X, the right being +X, the front being −Y, the rear being +Y, the bottom being −Z, and the top being +Z.

The outdoor unit 10 has a housing 40 that forms the outer shell. The outdoor unit 10 is a top-flow type device with an air outlet 41 formed in the center of the top of the housing 40. The air outlet 41 is an opening through which air blown by the fan 50, which will be described later, is discharged.

The housing 40 has four sides: a right side 40a, a rear side 40b, a left side 40c, and a front side 40d. These four sides form a roughly rectangular parallelepiped shape that rises roughly perpendicularly from a lower surface 40e that forms the bottom of the housing 40. In addition, a removable sealing plate 43 is provided on the front side 40d, which forms the front of the housing 40. The sealing plate 43 is removed during maintenance of the outdoor unit 10, etc.

As shown in Figures 5 and 6, the housing 40 houses the compressor 11, accumulator 15, and other components. A fan 50 is also housed in the upper part of the housing 40, directly below the air outlet 41. The fan 50 supplies outdoor air to the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c, and the airflow rate is adjusted by controlling the rotation speed.

As shown in FIG. 5, the right heat exchanger 30a is generally flat and is positioned so that its entire area faces the right surface 40a, which forms the right part of the housing 40. The rear heat exchanger 30b is generally flat and is positioned so that its entire area faces the rear surface 40b, which forms the rear part of the housing 40. The left heat exchanger 30c is generally flat and is positioned so that its entire area faces the left surface 40c, which forms the left part of the housing 40. Here, the right heat exchanger 30a, rear heat exchanger 30b, and left heat exchanger 30c are each positioned so that, when functioning as a condenser, their refrigerant inlets are inside the housing 40 and their refrigerant outlets are outside the housing 40, upwind of the outdoor air flow.

[Operation of the outdoor unit 10 of the air conditioning apparatus 100]
When the fan 50 of the outdoor unit 10 of the air conditioning apparatus 100 rotates, air around the outdoor unit 10 is drawn into the housing 40. The air drawn into the housing 40 passes through the heat exchanger 30, and as it passes through the heat exchanger 30, it exchanges heat with the refrigerant flowing inside the heat exchanger 30. The air that has passed through the heat exchanger 30 passes through the air outlet 41 and is discharged to the outside of the housing 40.

Figure 8 shows the relationship between the header gap δ and the amount of residual water between headers w. The horizontal axis of Figure 8 represents the header gap δ [mm], and the vertical axis represents the amount of residual water between headers w [g]. The inventors conducted experiments to investigate the relationship between the header gap δ [mm] and the amount of residual water between headers w [g]. Based on the inventors' experimental results, as shown in Figure 8, narrowing the header gap δ [mm] from 1 [mm] to 0.5 [mm] slightly increased the amount of residual water between headers w [g] from approximately 0.1 [g] to approximately 0.3 [g]. In other words, widening the header gap δ [mm] from 0.5 [mm] to 1.0 [mm] decreased the amount of residual water between headers w [g] from approximately 0.3 [g] to approximately 0.1 [g].

Furthermore, as shown in Figure 8, when the header gap δ [mm] was narrowed from 0.5 [mm] to 0.25 [mm], the amount of residual water between the headers w [g] suddenly increased from approximately 0.3 [g] to approximately 1.0 [g]. In other words, when the header gap δ [mm] was widened from 0.25 [mm] to 0.5 [mm], the amount of residual water between the headers w [g] suddenly decreased from approximately 1.0 [g] to approximately 0.3 [g].

As shown in Figure 8, when the header gap δ [mm] is 0.5 mm or more, the rate of increase in the amount of residual water w [g] between the headers when the header gap δ [mm] is narrowed is smaller than when the header gap δ [mm] is less than 0.5 mm. When the header gap δ [mm] is 0.5 mm or less, the rate of increase in the amount of residual water w [g] between the headers when the header gap δ [mm] is narrowed is larger than when the header gap δ [mm] is 0.5 mm or more. Therefore, to improve drainage between the first header 31 and the second header 35, it is desirable that the header gap δ [mm] be 0.5 mm or more (header gap δ≧0.5).

[Function and effect of heat exchanger 30]
In the heat exchanger 30, the first header 31 and the second header 35 are disposed opposite each other in the third direction D3. When the distance between the first header 31 and the second header 35 along the shortest path in the third direction D3 is defined as the header gap δ (mm), the heat exchanger 30 is configured such that the header gap δ is 0.5 mm or greater. This configuration of the heat exchanger 30 ensures an excellent header gap δ, thereby improving drainage in the gap between the first header 31 and the second header 35. Therefore, the heat exchanger 30 can reduce the amount of meltwater retained between the headers to suppress the formation of ice, prevent deformation of the first header 31 and the second header 35 due to freezing of the meltwater, and improve frost resistance.

Because the air conditioning unit 100 has a heat exchanger 30, it can achieve the same effects as the heat exchanger 30. In other words, the air conditioning unit 100 can reduce the amount of meltwater retained between the headers and suppress the formation of ice roots, preventing deformation of the first header 31 and second header 35 due to freezing of meltwater and improving frost resistance.

Embodiment 2.
Fig. 9 is a conceptual diagram showing the positional relationship between the first header 31 and the second header 35 in the heat exchanger 30 of the air conditioning apparatus 100 according to Embodiment 2. Fig. 10 is a conceptual diagram seen from the side of the first header 31 in the heat exchanger 30 of the air conditioning apparatus 100 according to Embodiment 2. Fig. 11 is a conceptual diagram of a partition plate 315 in the heat exchanger 30 of the air conditioning apparatus 100 according to Embodiment 2.

The heat exchanger 30 according to the second embodiment will be described using Figures 9 to 11. Note that the heat exchanger 30 according to the second embodiment is similar to the heat exchanger 30 according to the first embodiment in terms of configuration other than that described below, and components that have the same functions and actions as those in the first embodiment will be assigned the same reference numerals and their description will be omitted. Also, while Figure 10 shows the configuration of the first header 31, the configuration of the second header 35 is similar to that of the first header 31, and therefore a conceptual diagram of the second header 35 viewed from the side will be omitted.

The heat exchanger 30 according to the second embodiment has partition plates 315 inside the first header 31 and the second header 35. Each of the first header 31 and the second header 35 of the heat exchanger 30 has at least one partition plate 315 disposed inside the first header 31 and the second header 35.

The first header 31 and the second header 35 each have at least one partition plate 315 in the axial direction, i.e., in the direction in which the header extends. The outer edge 315b of the partition plate 315 is fixed to the inner wall portion 316 of the first header 31 and the second header 35. The partition plate 315 is used to ensure the strength of the headers such as the first header 31 and the second header 35.

The partition plate 315 is formed in a plate shape. An opening 315a is formed in the partition plate 315. At least one partition plate 315 is formed in a flat plate shape and has an opening 315a that penetrates in the direction in which the first header 31 and the second header 35 extend. The opening 315a constitutes a through hole formed in the partition plate 315. The refrigerant that flows into the inside of the first header 31 and the second header 35 moves through the opening 315a.

In the axial direction of the first header 31 and the second header 35, i.e., in the direction in which the headers extend, the partition plate 315 of the first header 31 and the partition plate 315 of the second header 35 may be arranged in the same position. In other words, in a direction perpendicular to the axial direction of the first header 31 and the second header 35 and perpendicular to the axial direction of the heat transfer tubes 32, the partition plate 315 of the first header 31 and the partition plate 315 of the second header 35 may be arranged in opposing positions.

Note that this configuration is just one example, and the partition plate 315 of the first header 31 and the partition plate 315 of the second header 35 may be positioned at different positions in the axial direction of the first header 31 and the second header 35, i.e., in the direction in which the headers extend.

[Function and effect of heat exchanger 30]
Each of the first header 31 and the second header 35 has at least one partition plate 315 disposed inside the first header 31 and the second header 35. Each of the at least one partition plate 315 is formed in a flat plate shape and has an opening 315a penetrating in the extension direction of the first header 31 and the second header 35. An outer edge portion 315b of the partition plate 315 is fixed to an inner wall portion 316 of the first header 31 and the second header 35.

The heat exchanger 30 according to the second embodiment has a partition plate 315 inside the first header 31 and the second header 35, thereby improving the strength of the first header 31 and the second header 35 compared to a case in which the partition plate 315 is not provided. Therefore, the heat exchanger 30 can ensure the strength of the headers even if ice forms between them, preventing deformation of the headers due to freezing of meltwater.

When refrigerant flows into headers such as the first header 31 and the second header 35, the headers may be subjected to pressure that causes the headers to expand due to the pressure of the refrigerant, resulting in the headers expanding. The heat exchanger 30 according to embodiment 2 has partition plates 315 inside the first header 31 and the second header 35, thereby ensuring the strength of the first header 31 and the second header 35. Therefore, by having partition plates 315 inside the first header 31 and the second header 35, the heat exchanger 30 according to embodiment 2 is able to resist expansion of the headers due to refrigerant pressure.

Depending on the material from which the first header 31 and second header 35 are made, the internal pressure of the refrigerant in the first header 31 and second header 35 may cause the portions of the first header 31 and second header 35 that do not have the partition plate 315 to expand. By providing the partition plate 315 in the first header 31 and second header 35, the heat exchanger 30 is able to suppress expansion of the header in the portion with the partition plate 315, even when affected by the internal pressure of the refrigerant, ensuring the size of the gap between the headers.

Note that when the internal pressure of the refrigerant in the first header 31 and the second header 35 causes the portions not having the partition plate 315 to expand, the header gap δ [mm] is the distance between the first header 31 and the second header 35 that constitutes the shortest distance. In other words, the header gap δ [mm] is the distance between the first header 31 and the second header 35 that constitutes the shortest distance when the heat exchanger 30 is operating.

In the extension direction of the first header 31 and the second header 35, the partition plate 315 of the first header 31 and the partition plate 315 of the second header 35 are arranged in the same position. In the first header 31 and the second header 35, the portions having the partition plate 315 are less likely to deform than portions not having the partition plate 315. Therefore, the portions having the partition plate 315 of the first header 31 and the second header 35 can ensure a larger gap between the headers even if the headers expand, compared to when the partition plate 315 is arranged in a portion where the partition plate 315 is arranged in a different position. Therefore, when the partition plate 315 of the first header 31 and the partition plate 315 of the second header 35 are arranged in the same position in the extension direction of the first header 31 and the second header 35, drainage can be improved compared to when this configuration is not included.

Because the air conditioning unit 100 has a heat exchanger 30, it can achieve the same effects as the heat exchanger 30. That is, the air conditioning unit 100 can reduce the amount of meltwater retained between the headers and suppress the formation of ice roots, preventing deformation of the first header 31 and the second header 35 due to freezing of the meltwater and improving frost resistance. Furthermore, the air conditioning unit 100 can ensure the strength of the first header 31 and the second header 35 by using the partition plate 315, and suppress deformation of the first header 31 and the second header 35.

Embodiment 3.
Fig. 12 is a conceptual diagram showing the positional relationship between the first header 31 and the second header 35 in the heat exchanger 30 of the air conditioning apparatus 100 according to Embodiment 3. Fig. 13 is a conceptual diagram seen from the side of the first header 31 in the heat exchanger 30 of the air conditioning apparatus 100 according to Embodiment 3. Fig. 14 is a conceptual diagram showing the partition plate 315 and the inner pipe portion 312 in the heat exchanger 30 of the air conditioning apparatus 100 according to Embodiment 3.

The heat exchanger 30 according to the third embodiment will be described using Figures 12 to 14. Note that the heat exchanger 30 according to the third embodiment is similar in configuration to the heat exchanger 30 according to the first and second embodiments, except for the configuration described below. Components that have the same functions and actions as those in the first and second embodiments are given the same reference numerals, and their description will be omitted. Furthermore, while Figure 13 shows the configuration of the first header 31, the configuration of the second header 35 is similar to that of the first header 31, and therefore a conceptual diagram of the second header 35 viewed from the side will be omitted.

The first header 31 and the second header 35 each have a cylindrical inner pipe portion 312 that distributes refrigerant to the multiple heat transfer pipes 32, and an outer pipe portion 311 that houses the inner pipe portion 312 and into which the multiple heat transfer pipes 32 are inserted. The inner pipe portion 312 constitutes the cylindrical inner pipe of the first header 31 and the second header 35, and the outer pipe portion 311 constitutes the cylindrical outer pipe of the first header 31 and the second header 35. The first header 31 and the second header 35 each have a double-pipe structure formed by the inner pipe portion 312 and the outer pipe portion 311.

Each of the first header 31 and the second header 35 has a double-pipe structure, including a cylindrical inner pipe portion 312 with a plurality of spaced-apart through holes 314 formed therein, and an outer pipe portion 311 that houses the inner pipe portion 312 and into which a plurality of heat transfer pipes 32 are inserted. Furthermore, each of the first header 31 and the second header 35 has at least one partition plate 315 that divides the intra-cylindrical space between the outer pipe portion 311 and the inner pipe portion 312 in the axial direction of the first header 31 and the second header 35.

(Inner tube part 312)
The inner pipe portion 312 functions as a refrigerant distributor that distributes refrigerant to the multiple heat transfer pipes 32. The inner pipe portion 312 is a long, cylindrical member that is open at both ends and has a space formed therein. The inner pipe portion 312 is housed inside the outer pipe portion 311. The inner pipe portion 312 is disposed inside the outer pipe portion 311 with its pipe axis direction held horizontal. In the axial direction of the inner pipe portion 312, one end is connected to the refrigerant inlet/outlet pipe 36 or the refrigerant inlet/outlet pipe 37, and is connected to the refrigerant piping 90 (see FIG. 1 ) via the refrigerant inlet/outlet pipe 36 or the like, and the other end is sealed with a cap 313.

The inner pipe portion 312 has a plurality of through holes 314 formed therein. The through holes 314 are also called orifices. The plurality of through holes 314 are arranged along the pipe axis direction of the inner pipe portion 312. The plurality of through holes 314 are arranged at intervals in the longitudinal direction of the inner pipe portion 312. The plurality of through holes 314 are arranged in the inner pipe portion 312 in a range that faces at least the plurality of heat transfer tubes 32 inserted into the outer pipe portion 311.

The refrigerant flowing inside the inner pipe section 312 passes through the through-holes 314 and flows out of the inner pipe section 312. Alternatively, if the first header 31 or the second header 35 defines a space where the refrigerant flowing into the first header 31 from multiple heat transfer tubes 32 joins together, the refrigerant flowing outside the inner pipe section 312 passes through the through-holes 314 and flows into the inner pipe section 312.

In the header that distributes the refrigerant, either the first header 31 or the second header 35, the refrigerant passes through the interior of the inner pipe section 312 and flows out into the intra-cylinder space of the outer pipe section 311 through a plurality of through holes 314 that are spaced apart along the longitudinal direction of the inner pipe section 312. By providing a plurality of through holes 314 through which the refrigerant flows that are arranged side by side in the inner pipe section 312, the heat exchanger 30 can ensure that the refrigerant flows evenly through the multiple heat transfer pipes 32 of the heat exchanger 30, thereby improving the performance of the heat exchanger 30.

(Outer tube part 311)
The outer pipe portion 311 is a long, cylindrical member whose both ends are closed except for the connection portion of the refrigerant inlet/outlet pipe 36 or the refrigerant inlet/outlet pipe 37, and a space is formed inside. The outer pipe portion 311 is cylindrically formed with an inner diameter larger than that of the inner pipe portion 312. The outer pipe portion 311 houses the inner pipe portion 312 inside. A plurality of heat transfer pipes 32 are connected to the outer peripheral surface of the outer pipe portion 311. The first header 31 and the second header 35 form a space between the cylindrically formed outer pipe portion 311 and the inner pipe portion 312.

In a cross section perpendicular to the tube axis direction of the outer tube portion 311, the outer tube portion 311 is formed in a rectangular shape. Note that the outer tube portion 311 only needs to be formed in a cylindrical shape, and in a cross section perpendicular to the tube axis direction of the outer tube portion 311, the outer tube portion 311 may be formed in other shapes, such as a perfect circle or a polygonal shape.

Partition plates 315 are provided in the internal spaces of the first header 31 and the second header 35. The partition plates 315 form walls that separate the internal spaces of the headers into multiple spaces in a direction parallel to the axial direction of the first header 31 and the second header 35. The partition plates 315 divide the internal spaces of the first header 31 and the second header 35 in a direction parallel to the axial direction of the headers, forming multiple spaces inside the headers.

The partition plates 315 are formed in a plate shape. At least one partition plate 315 has an opening 315a formed therein, which supports the inner tube portion 312 while allowing the inner tube portion 312 to pass through. The opening 315a constitutes a through-hole formed in the partition plate 315.

In the direction in which the first header 31 and the second header 35 extend, the partition plate 315 of the first header 31 and the partition plate 315 of the second header 35 may be arranged in the same position. In the direction perpendicular to the axial direction of the first header 31 and the second header 35 and perpendicular to the axial direction of the heat transfer tubes 32, the partition plate 315 of the first header 31 and the partition plate 315 of the second header 35 may be arranged in opposing positions.

[Function and effect of heat exchanger 30]
Each of the first header 31 and the second header 35 is a header with a double-pipe structure having a cylindrical inner pipe portion 312 with a plurality of through holes 314 formed at intervals from each other, and an outer pipe portion 311 that houses the inner pipe portion 312 and into which a plurality of heat transfer pipes 32 are inserted. Each of the first header 31 and the second header 35 has at least one plate-shaped partition plate 315 that divides the intra-cylindrical space between the outer pipe portion 311 and the inner pipe portion 312 in the axial direction of the first header 31 and the second header 35. The partition plate 315 has an opening 315a formed therein that supports the inner pipe portion 312 while it passes through.

When the first header 31 performs the distribution function, the refrigerant flows into one end of the inner pipe section 312 through the refrigerant inlet/outlet pipe 36 of the first header 31. The refrigerant that flows into the interior of the inner pipe section 312 flows out of the inner pipe section 312 through the multiple through holes 314 and into the space between the inner pipe section 312 and the outer pipe section 311. The refrigerant that flows out of the inner pipe section 312 and into the space between the inner pipe section 312 and the outer pipe section 311 is distributed to the multiple heat transfer pipes 32. By having the multiple through holes 314 arranged side by side in the inner pipe section 312 through which the refrigerant flows out, the heat exchanger 30 can flow evenly through the multiple heat transfer pipes 32 of the heat exchanger 30 compared to a heat exchanger that does not have this configuration, thereby improving the performance of the heat exchanger 30.

The heat exchanger 30 according to embodiment 3 has a partition plate 315 inside the first header 31 and the second header 35, thereby improving the strength of the first header 31 and the second header 35 compared to when the partition plate 315 is not provided. Therefore, even if ice forms between the headers, the heat exchanger 30 can ensure the strength of the headers, preventing them from deforming due to the freezing of meltwater. Furthermore, the heat exchanger 30 can ensure the strength of the headers using the partition plate 315 and prevent the headers from deforming due to the freezing of meltwater, thereby preventing deformation of the inner pipe portion 312.

The heat exchanger 30 according to embodiment 3 has partition plates 315 inside the first header 31 and second header 35, thereby ensuring the strength of the first header 31 and second header 35. Therefore, by having partition plates 315 inside the first header 31 and second header 35, the heat exchanger 30 according to embodiment 3 is able to resist expansion of the headers due to refrigerant pressure. Furthermore, by having partition plates 315 in the first header 31 and second header 35, the heat exchanger 30 is able to suppress expansion of the headers in the areas where the partition plates 315 are located, even when affected by the internal pressure of the refrigerant, ensuring the size of the gap between the headers.

In the direction in which the first header 31 and the second header 35 extend, the partition plates 315 of the first header 31 and the second header 35 are arranged in the same position. The portions in which the partition plates 315 of the first header 31 and the second header 35 are arranged can ensure a larger gap between the headers even if the headers expand, compared to when the partition plates 315 are arranged in portions in which they are arranged in different positions. Therefore, when the partition plates 315 of the first header 31 and the second header 35 are arranged in the same position in the direction in which the first header 31 and the second header 35 extend, drainage performance can be improved compared to when this configuration is not included.

Because the air conditioning unit 100 has a heat exchanger 30, it can achieve the same effects as the heat exchanger 30. That is, the air conditioning unit 100 can reduce the amount of meltwater retained between the headers and suppress the formation of ice roots, preventing deformation of the first header 31 and the second header 35 due to freezing of the meltwater and improving frost resistance. Furthermore, the air conditioning unit 100 can ensure the strength of the first header 31 and the second header 35 by using the partition plate 315, and suppress deformation of the first header 31 and the second header 35.

Each of the above-described embodiments 1 to 3 can be implemented in combination with one another. Furthermore, the configurations shown in the above-described embodiments are merely examples, and they can be combined with other known technologies. Parts of the configuration can also be omitted or modified without departing from the spirit of the invention.

10 Outdoor unit, 11 Compressor, 12 Flow switching device, 13 First flow control valve, 14 Second flow control valve, 15 Accumulator, 20 Indoor unit, 21 Throttle device, 22 Indoor heat exchanger, 30 Heat exchanger, 30a Right heat exchanger, 30b Rear heat exchanger, 30c Left heat exchanger, 31 First header, 32 Heat transfer tube, 32A First heat transfer tube group, 32B Second heat transfer tube group, 33 Fin, 34 Third header, 35 Second header, 36 Refrigerant inlet/outlet pipe 37 Refrigerant inlet/outlet pipe, 40 Housing, 40a Right side, 40b Rear side, 40c Left side, 40d Front side, 40e Bottom side, 41 Air outlet, 43 Sealing plate, 50 Fan, 90 Refrigerant piping, 100 Air conditioning device, 101 Refrigerant circuit, 300 Heat exchange section, 301 First heat exchange section, 302 Second heat exchange section, 311 Outer pipe section, 312 Inner pipe section, 313 Cap, 314 Through hole, 315 Partition plate, 315a Opening, 315b Outer edge section, 316 Inner wall section.

Claims (5)

a first heat exchange unit including a first heat transfer tube group composed of a plurality of heat transfer tubes extending in the vertical direction, and a first header connected to lower ends of the plurality of heat transfer tubes constituting the first heat transfer tube group and allowing a refrigerant to circulate through the plurality of heat transfer tubes;
a second heat exchange unit including a second heat transfer tube group composed of a plurality of heat transfer tubes extending in the vertical direction, and a second header connected to lower ends of the plurality of heat transfer tubes constituting the second heat transfer tube group and allowing a refrigerant to circulate through the plurality of heat transfer tubes;
a third header into which upper ends of the heat transfer tubes constituting the first heat exchange unit and the second heat exchange unit are inserted, and which allows a refrigerant to circulate between the first heat exchange unit and the second heat exchange unit;
Equipped with
The first header and the second header are
The plurality of heat transfer tubes are formed to extend along a direction in which they are spaced apart from one another,
When a direction in which the plurality of heat transfer tubes extend is defined as a first direction, a direction in which the first header and the second header extend is defined as a second direction, and a direction perpendicular to the first direction and the second direction is defined as a third direction, the first header and the second header are disposed opposite each other in the third direction,
A heat exchanger in which, when the spacing between the parts constituting the shortest distance between the first header and the second header in the third direction is defined as a header gap δ [mm], the header gap δ is configured to be 0.5 [mm] or more. Each of the first header and the second header includes:
at least one partition plate disposed inside the first header and the second header;
Each of the at least one partition plate has:
The plate-shaped opening has an opening extending in the second direction.
2. The heat exchanger according to claim 1, wherein an outer edge of each of the at least one partition plates is fixed to an inner wall of the first header and an inner wall of the second header. Each of the first header and the second header includes:
a header having a double-pipe structure including a cylindrical inner pipe portion having a plurality of through holes formed at intervals from each other, and an outer pipe portion that houses the inner pipe portion and into which the plurality of heat transfer pipes are inserted,
Each of the first header and the second header includes:
a partition plate that divides an inner space between the outer tube portion and the inner tube portion in the second direction;
The at least one partition plate has:
The heat exchanger according to claim 1, wherein an opening is formed through which the inner pipe portion is supported. In the extending direction of the first header and the second header,
4. The heat exchanger according to claim 2, wherein the partition plate of the first header and the partition plate of the second header are arranged at the same position. A compressor;
a heat exchanger configured as the heat exchanger according to any one of claims 1 to 4, which exchanges heat between outdoor air and a refrigerant flowing inside;
a throttle device that reduces the pressure of the refrigerant flowing therein;
an indoor heat exchanger that exchanges heat between indoor air and a refrigerant flowing therein;
An air conditioning device equipped with: