JP2021008982A - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

To provide a heat exchanger and a refrigeration cycle device that can restrain a decrease in an amount of heat exchange.SOLUTION: A heat exchanger according to an embodiment comprises a plurality of heat exchange tubes, headers, and a partition member. The plurality of heat exchange tubes are arranged in parallel at intervals in a first direction. The headers are formed in a cylindrical shape, each have a central axis extending in the first direction, and are arranged in parallel separately from each other in a second direction orthogonal to the first direction. End parts of the plurality of heat exchange tubes are opened inside at least two of the headers. The partition member partitions the inside of at least one of the headers. The partition member comprises a heat insulating layer having lower heat conductivity than that of a forming material of the headers.SELECTED DRAWING: Figure 5

Description

Embodiments of the present invention relate to heat exchangers and refrigeration cycle devices.

A heat exchanger that exchanges heat between the refrigerant and the outside air is used. The header type heat exchanger has a plurality of heat exchange tubes and a header. The plurality of heat exchange tubes are arranged in parallel at intervals in the vertical direction. Inside the header, the ends of the plurality of heat exchange tubes are opened. In order to increase the amount of heat exchange, there is a heat exchanger in which the refrigerant is folded back and circulated in the header. In this heat exchanger, the internal space of the header is partitioned into a plurality of small chambers by a partition member. When heat is exchanged between adjacent small chambers via a partition member, the amount of heat exchanged with the outside air of the heat exchanger is reduced. There is a need for a heat exchanger that can suppress a decrease in the amount of heat exchange.

Japanese Unexamined Patent Publication No. 2017-155993

An object to be solved by the present invention is to provide a heat exchanger and a refrigeration cycle device capable of suppressing a decrease in the amount of heat exchange.

The heat exchanger of the embodiment has a plurality of heat exchange tubes, a header, and a partition member. The plurality of heat exchange tubes are arranged in parallel at intervals in the first direction. The header is formed in a tubular shape, the central axis extends in the first direction, and the headers are arranged side by side so as to be separated from each other in the second direction orthogonal to the first direction. Inside at least two headers, the ends of the plurality of heat exchange tubes are open. The partition member partitions at least one inside of the header in the first direction. The partition member has a heat insulating layer having a lower thermal conductivity than the material for forming the header.

The schematic block diagram of the refrigerating cycle apparatus in 1st Embodiment. The front view of the heat exchanger in the first embodiment. FIG. 2 is a side sectional view taken along line F3-F3 of FIG. Perspective view of the partition member. The front sectional view around the partition member in line F5-F5 of FIG. FIG. 5 is a plan sectional view of the periphery of the partition member along the line F6-F6 of FIG. The front sectional view around the partition member in the modified example of 1st Embodiment. The perspective view of the partition member in 2nd Embodiment.

Hereinafter, the heat exchanger and the refrigeration cycle apparatus of the embodiment will be described with reference to the drawings.
In the present application, the X direction, the Y direction and the Z direction are defined as follows. The Z direction (first direction) is the central axis direction (extending direction) of the first header and the second header. For example, the Z direction is the vertical direction, and the + Z direction is the upward direction. The X direction (second direction) is the central axis direction (extending direction) of the heat exchange tube. For example, the X direction is the horizontal direction, and the + X direction is the direction from the first header to the second header. The Y direction is a direction perpendicular to the X and Z directions.

(First Embodiment)
FIG. 1 is a schematic configuration diagram of the refrigeration cycle device of the first embodiment.
As shown in FIG. 1, the refrigeration cycle device 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger (heat exchanger) 4, an expansion device 5, and an indoor heat exchanger (heat exchanger). 6 and. The components of the refrigeration cycle device 1 are sequentially connected by a pipe 7. In FIG. 1, the flow direction of the refrigerant during the cooling operation is indicated by a solid line arrow, and the flow direction of the refrigerant during the heating operation is indicated by a broken line arrow.

The compressor 2 has a compressor main body 2A and an accumulator 2B. The compressor body 2A compresses the low-pressure gas refrigerant taken into the inside into a high-temperature, high-pressure gas refrigerant. The accumulator 2B separates the gas-liquid two-phase refrigerant and supplies the gas refrigerant to the compressor main body 2A.

The four-way valve 3 reverses the flow direction of the refrigerant and switches between cooling operation and heating operation. During the cooling operation, the refrigerant flows in the order of the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6. At this time, the refrigeration cycle device 1 causes the outdoor heat exchanger 4 to function as a condenser and the indoor heat exchanger 6 to function as an evaporator to cool the room. During the heating operation, the refrigerant flows in the order of the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4. At this time, the refrigeration cycle device 1 causes the indoor heat exchanger 6 to function as a condenser and the outdoor heat exchanger 4 to function as an evaporator to heat the room.

The condenser makes a high-pressure liquid refrigerant by radiating high-temperature and high-pressure gaseous refrigerant discharged from the compressor 2 to the outside air and condensing it.
The expansion device 5 lowers the pressure of the high-pressure liquid refrigerant sent from the condenser to obtain a low-temperature / low-pressure gas-liquid two-phase refrigerant.
The evaporator makes a low-temperature gas-liquid two-phase refrigerant sent from the expansion device 5 into a low-temperature gaseous refrigerant by absorbing heat from the outside air and vaporizing it.

In this way, in the refrigeration cycle device 1, the refrigerant as the working fluid circulates between the gas refrigerant and the liquid refrigerant while changing the phase. The refrigerant dissipates heat in the process of phase change from gas refrigerant to liquid refrigerant, and absorbs heat in the process of phase change from liquid refrigerant to gas refrigerant. The refrigeration cycle device 1 performs heating, cooling, defrosting, etc. by utilizing heat dissipation or endothermic of the refrigerant.

FIG. 2 is a front view of the heat exchanger of the first embodiment. The heat exchanger 4 of the embodiment is used for one or both of the outdoor heat exchanger 4 and the indoor heat exchanger 6 of the refrigeration cycle device 1. Hereinafter, the case where the heat exchanger 4 of the embodiment is used as the outdoor heat exchanger 4 of the refrigeration cycle device 1 will be described as an example.

As shown in FIG. 2, the heat exchanger 4 has a first header 10, a second header 20, a heat exchange tube (heat transfer tube) 30, and fins 40.
The first header 10 is formed of a material having a high thermal conductivity and a low specific gravity, such as aluminum or an aluminum alloy. The first header 10 is formed in a tubular shape, for example, a cylindrical shape having a circular cross section perpendicular to the Z direction. The central axis of the first header 10 extends in the Z direction. Both ends of the first header 10 in the Z direction are closed. A plurality of through holes into which the heat exchange tube 30 is inserted are formed on the outer peripheral surface of the first header 10.
The second header 20 is formed in the same manner as the first header 10. The first header 10 and the second header 20 are arranged side by side so as to be separated from each other in the X direction.

FIG. 3 is a partial cross-sectional view taken along the line F4-F4 of FIG. The heat exchange tube 30 is made of a material having a high thermal conductivity and a low specific gravity, such as aluminum or an aluminum alloy. The heat exchange tube 30 is formed in a flat tubular shape. That is, the heat exchange tube 30 has a predetermined width in the Y direction, is thin in the Z direction, and extends long in the X direction.

The outer shape of the heat exchange tube 30 is formed in an oval shape. Inside the heat exchange tube 30, a plurality of refrigerant flow paths 34 are formed side by side in the Y direction. The adjacent refrigerant flow paths 34 are partitioned by a flow path wall 35 parallel to the XZ plane. The plurality of refrigerant flow paths 34 penetrate the heat exchange tube 30 in the X direction.

As shown in FIG. 2, a plurality of heat exchange tubes 30 are arranged in parallel at intervals in the Z direction. Both ends of the heat exchange tube 30 are inserted into through holes formed in the outer peripheral surfaces of the first header 10 and the second header 20. As a result, both ends of the refrigerant flow path 34 of the heat exchange tube 30 are opened inside the first header 10 and the second header 20.

The gap between the first header 10 and the second header 20 and the heat exchange tube 30 is sealed by brazing or the like. The specific procedure for brazing is as follows. Wax is applied to the inner surfaces of the first header 10 and the second header 20. The heat exchange tube 30 is inserted into the first header 10 and the second header 20, and the heat exchanger 4 is assembled. The assembled heat exchanger 4 is heated in the furnace. The heating melts the wax on the inner surfaces of the first header 10 and the second header 20. The molten wax closes the gap between the first header 10 and the second header 20 and the heat exchange tube 30. After that, the heat exchanger 4 is cooled and the wax solidifies. As a result, the first header 10 and the second header 20 and the heat exchange tube 30 are fixed.

The fin 40 is formed of a material having a high thermal conductivity and a low specific gravity, such as aluminum or an aluminum alloy. For example, the fin 40 is a plate fin formed in a flat plate shape. The fins 40 are arranged parallel to the YZ plane. The fin 40 may be a corrugated fin. The corrugated fins are wavy and are arranged between adjacent heat exchange tubes 30.

As shown in FIG. 3, the width of the fin 40 in the Y direction is larger than the width of the heat exchange tube 30 in the Y direction. A notch 43 is formed from the + Y direction end edge of the fin 40 to the −Y direction. A heat exchange tube 30 is inserted into the notch 43. The heat exchange tube 30 and the fin 40 are fixed by the brazing described above.
As shown in FIG. 2, a plurality of fins 40 are arranged at intervals in the X direction.

An outside air flow path extending in the Y direction is formed between the adjacent heat exchange tubes 30 and between the adjacent fins 40. The heat exchanger 4 circulates the outside air through the outside air flow path by a blower fan (not shown) or the like. The heat exchanger 4 exchanges heat between the outside air flowing through the outside air flow path and the refrigerant flowing through the refrigerant flow path 34. The heat exchange is indirectly performed via the heat exchange tube 30 and the fins 40.

The structure of the header will be described.
As shown in FIG. 2, the first header 10 has partition members 15 and 16. The partition members 15 and 16 are arranged in parallel with the XY plane, and partition the internal space of the first header 10 in the Z direction. The partition members 15 and 16 divide the internal space of the first header 10 into a plurality of small chambers. In the example of FIG. 2, two partition members 15 and 16 divide the internal space into three small chambers 11, 12 and 13. The two partition members 15 and 16 are a first partition member 15 on the + Z side and a second partition member 16 on the −Z side. The three chambers 11, 12, and 13 are the first chamber 11 on the + Z side, the second chamber 12 in the center, and the third chamber 13 on the −Z side. In the example of FIG. 2, the heights of the first chamber 11 and the third chamber 13 in the Z direction are the same, and the height of the second chamber 12 in the Z direction is higher than that of the first chamber 11 and the third chamber 13.

The second header 20 has a partition member 25 similar to that of the first header 10. The partition member 25 divides the internal space of the second header 20 into a plurality of small chambers. In the example of FIG. 2, one partition member 25 divides the internal space into two small chambers 21 and 22. The two chambers 21 and 22 are a first chamber 21 on the + Z side and a second chamber 22 on the −Z side. In the example of FIG. 2, the heights of the two chambers 21 and 22 in the Z direction are the same.

The first end of the heat exchange tube 30 in the −X direction opens inside the first header 10. A plurality of heat exchange tubes 30 are opened in the three chambers 11, 12, and 13 formed in the first header 10. In the example of FIG. 2, the same number of heat exchange tubes 30 are opened in the first chamber 11 and the third chamber 13, respectively, and the second chamber 12 is twice as large as the first chamber 11 and the third chamber 13. The number of heat exchange tubes 30 is opened.
The second end of the heat exchange tube 30 in the + X direction opens inside the second header 20. A plurality of heat exchange tubes 30 are opened in the two chambers 21 and 22 formed in the second header 20. In the example of FIG. 2, the same number of heat exchange tubes 30 are opened in each of the two chambers 21 and 22.

Refrigerant ports 18 and 19 are opened inside the first header 10. Refrigerant ports 18 and 19 are inlets and outlets for refrigerants between the outside and the heat exchanger. A first refrigerant port 18 opens at the end of the first small chamber 11 of the first header 10 in the −Z direction. The first refrigerant port 18 may be opened at the end of the first chamber 11 in the + Z direction. A second refrigerant port 19 opens at the end of the third small chamber 13 of the first header 10 in the −Z direction.

When the refrigeration cycle device 1 shown in FIG. 1 performs a cooling operation, the outdoor heat exchanger 4 functions as a condenser. In this case, the gaseous refrigerant flowing out of the compressor 2 flows into the outdoor heat exchanger 4. The refrigerant flows into the first small chamber 11 of the first header 10 from the first refrigerant port 18 shown in FIG. The refrigerant flows through the heat exchange tube 30 in the + X direction and flows into the upper half of the first small chamber 21 of the second header 20. The refrigerant moves to the lower half of the first chamber 21 of the second header 20. The refrigerant flows through the heat exchange tube 30 in the −X direction and flows into the upper half of the second chamber 12 of the first header 10. The refrigerant moves to the lower half of the second chamber 12 of the first header 10. The refrigerant flows through the heat exchange tube 30 in the + X direction and flows into the upper half of the second small chamber 22 of the second header 20. The refrigerant moves to the lower half of the second chamber 22 of the second header 20. The refrigerant flows through the heat exchange tube 30 in the −X direction and flows into the third chamber 13 of the first header 10.

The gaseous refrigerant flowing into the first small chamber 11 of the first header 10 dissipates heat to the outside air and condenses in the process of flowing through the heat exchange tube 30. The condensed refrigerant becomes a liquid refrigerant and flows into the third chamber 13 of the first header 10. The refrigerant flows out of the heat exchanger 4 from the second refrigerant port 19.
When the refrigeration cycle device 1 shown in FIG. 1 performs a heating operation, the refrigerant flows in the opposite direction to the above. That is, the liquid refrigerant flows from the second refrigerant port 19 into the third small chamber 13 of the first header, and the gas-liquid two-phase refrigerant flows out from the first refrigerant port 18.

In the heat exchanger 4, in the portion where the refrigerant flows in a gas-liquid two-phase state, the amount of heat exchanged with the outside air is used for the phase change of the refrigerant, so that the temperature change of the refrigerant is small. In the portion where the refrigerant flows in a single-phase state, the amount of heat exchanged with the outside air is used for the temperature change of the refrigerant, so that the temperature change of the refrigerant is large. The first chamber 11 of the first header 10 through which the gaseous refrigerant flows and the third chamber 13 of the first header 10 through which the liquid refrigerant flows are portions in which the refrigerant flows in a single-phase state. On the other hand, the second small chamber 12 of the first header 10 is a portion where the refrigerant flows in a gas-liquid two-phase state. Therefore, the temperature difference between the first chamber 11 and the second chamber 12 of the first header 10 is large. The same applies to the temperature difference between the second chamber 12 and the third chamber 13 of the first header 10.

As described above, the temperature difference between the first chamber 11 and the second chamber 12 of the first header 10 is large. Therefore, there is a possibility that heat exchange is performed between the refrigerant flowing through the first small chamber 11 and the refrigerant flowing through the second small chamber 12 via the first partition member 15. When heat exchange is performed via the first partition member 15, the amount of heat exchanged between the refrigerant and the outside air decreases. As a result, the amount of heat exchanged by the heat exchanger 4 is reduced. The same applies to the second partition member 16. Further, when heat exchange is performed via the first partition member 15, the temperature of the refrigerant flowing through the small chambers 11 and 12 changes from the temperature of the refrigerant flowing through the immediately preceding heat exchange tube 30. If a temperature sensor is arranged in the first header 10 in order to detect the temperature of the refrigerant flowing through the heat exchange tube 30, there is a possibility that an erroneous refrigerant temperature is detected. Along with this, there is a possibility that the opening degree control of the expansion device 5 (see FIG. 1) may be erroneous.

The first partition member 15 will be described in detail. The second partition member 16 is the same as the first partition member 15. In the following description, the first partition member 15 is simply referred to as a partition member 50.
FIG. 4 is a perspective view of the partition member. The partition member 50 has a pair of end plates 51, 51 and a heat insulating layer 52.

The end plate 51 is made of the same material as the material for forming the first header 10. That is, the end plate 51 is formed of a material such as aluminum or an aluminum alloy.

The end plate 51 is formed in a substantially circular shape in a plan view. The radius of the first semicircular portion 54 in the −X direction and the second semicircular portion 56 in the + X direction of the end plate 51 are different. The radius of the first semicircular portion 54 is equivalent to the radius of the outer peripheral surface of the first header 10. The radius of the second semicircular portion 56 is equivalent to the radius of the inner peripheral surface of the first header 10. A step portion 55 is formed between the first semicircular portion 54 and the second semicircular portion 56 of the end plate 51. The step portion 55 has a flat surface facing in the + X direction. A protrusion 57 is formed at the end of the second semicircular portion 56 in the + X direction. The protrusion 57 protrudes from the second semicircular portion 56 in the + X direction.

A pair of end plates 51, 51 are arranged in parallel at intervals in the Z direction. The shapes of the pair of end plates 51, 51 are the same. The partition member 50 has a connecting portion 58 that connects a pair of end plates 51, 51 in the Z direction. The connecting portion 58 connects the pair of end plates 51, 51 to each other at the step portion 55, the outer peripheral portion of the second semicircular portion 56, and the protrusion 57. The pair of end plates 51, 51 and the connecting portion 58 of the partition member 50 are integrally formed by injection molding or the like.

The heat insulating layer 52 is formed between a pair of end plates 51, 51 in the Z direction. That is, a pair of end plates 51, 51 are arranged on both sides of the heat insulating layer 52 in the Z direction. As shown in FIG. 4, the heat insulating layer 52 is formed as a hollow portion by opening the space between the pair of end plates 51, 51 to the outside from the opening 10w of the first header 10. Therefore, the heat insulating layer 52 is an air layer. The thermal conductivity of aluminum or an aluminum alloy, which is a material for forming the first header 10, is about 240 W / mk. The thermal conductivity of air is about 0.2 W / mk. That is, the heat insulating layer 52 has a smaller thermal conductivity than the material for forming the first header 10.

FIG. 5 is a front sectional view of the periphery of the partition member in line F5-F5 of FIG. FIG. 6 is a plan sectional view of the periphery of the partition member in line F6-F6 (line F6-F6 in FIG. 2) of FIG.
As shown in FIG. 5, the first header 10 is formed with an opening 10w that penetrates the peripheral wall. The partition member 50 is inserted into the inside of the first header 10 from the outside (−X direction) in the radial direction of the first header 10 through the opening 10w. The height of the opening 10w in the Z direction is equivalent to the height of the partition member 50 in the Z direction. As shown in FIG. 6, the opening 10w of the first header 10 is formed in the −X direction from the central axis of the first header 10. The opening 10w is formed over a half circumference in the circumferential direction of the first header 10.

As shown in FIG. 6, a hole 10h penetrating the peripheral wall is formed at the end of the first header 10 in the + X direction. The protrusion 57 of the partition member 50 is inserted into the hole 10h of the first header 10. As a result, the partition member 50 is positioned in the circumferential direction of the first header 10. The outer circumference of the second semicircular portion 56 of the partition member 50 abuts on the inner peripheral surface of the first header 10. The step portion 55 of the partition member 50 comes into contact with the end portion of the opening 10w in the circumferential direction of the first header 10. The outer circumference of the first semicircular portion 54 of the partition member 50 is arranged along the outer peripheral surface of the first header 10. The gap between the partition member 50 and the first header 10 is sealed by the brazing described above.

As shown in FIG. 5, the partition member 50 partitions the inside of the first header 10 into a first chamber 11 and a second chamber 12. The partition member 50 has a heat insulating layer 52 at the center in the Z direction. The heat insulating layer 52 is formed of a material having a lower thermal conductivity than the material for forming the first header 10.
As a result, it is possible to suppress heat exchange between the refrigerant flowing through the first small chamber 11 and the refrigerant flowing through the second small chamber 12 via the partition member 50. Therefore, the refrigerant exchanges heat with the outside air. Therefore, it is possible to suppress a decrease in the amount of heat exchange in the heat exchanger.

The partition member 50 has end plates 51 on both sides of the heat insulating layer 52 in the Z direction. The end plate 51 is made of the same material as the material for forming the first header 10.
The partition member 50 abuts on the first header 10 to partition the inside of the first header 10. Since the first header 10 and the end plate 51 are made of the same material, electrolytic corrosion of both is suppressed. Since the expansion coefficient of both is the same, the generation of gaps due to heating during brazing is suppressed. Since the melting points of both are the same, deformation of the end plate 51 due to heating during brazing is suppressed.

In the first embodiment, the partition member 50 is applied to the first partition member 15 and the second partition member 16 of the first header 10. On the other hand, the partition member 50 may be applied to the partition member 25 of the second header 20.

In the first embodiment, the first header 10 is divided into three chambers 11, 12, 13 by the two partition members 15, 16. The second header 20 is divided into two small chambers 21 and 22 by one partition member 25. On the other hand, the first header 10 and the second header 20 may be divided into a different number of small chambers by a different number of partition members.

The first header 10 has a first refrigerant port 18 and a second refrigerant port 19 as an inflow port for the refrigerant from the outside of the heat exchanger 4 and an outflow port for the refrigerant to flow out to the outside of the heat exchanger 4. The partition member 50 partitions the first chamber 11 and the third chamber 13 inside the first header 10 through which the first refrigerant port 18 and the second refrigerant port 19 open.
The first chamber 11 and the third chamber 13 through which the inlet and outlet of the heat exchanger 4 are opened are portions through which the refrigerant flows in a single-phase state. The temperature difference between the first chamber 11 and the second chamber 12 is large, and the temperature difference between the second chamber 12 and the third chamber 13 is large. The partition member 50 partitions between the first chamber 11 and the second chamber 12 and between the second chamber 12 and the third chamber 13. As a result, it is possible to suppress heat exchange via the partition member 50. Therefore, it is possible to suppress a decrease in the amount of heat exchange in the heat exchanger.

In the first embodiment, the first refrigerant port 18 and the second refrigerant port 19 are opened inside the first header 10. On the other hand, one or both of the first refrigerant port 18 and the second refrigerant port 19 may be opened inside the second header 20. In either case, the partition member 50 of the first embodiment is applied as a partition member for a small chamber in which the first refrigerant port 18 and the second refrigerant port 19, which are the inlet and outlet of the refrigerant, open.

The partition member 50 of the above-described embodiment is inserted from the outside of the first header 10 to the inside through the opening 10w. On the other hand, the partition member may be inserted inside from the axial end of the first header 10. In this case, the opening 10w of the first header 10 becomes unnecessary.

In the partition member 50 of the above-described embodiment, the pair of end plates 51, 51 are connected by the connecting portion 58. The partition member 50 integrally formed in this way is inserted into the opening 10w of the first header 10. On the other hand, the partition member may be formed of only a pair of end plates 51, 51. In this case, the pair of end plates 51, 51 are separately inserted into the opening 10w of the first header 10 at intervals in the Z direction. Holes 10h are formed in the first header 10 at the positions of the end plates 51 and 51, respectively.

A modified example of the first embodiment will be described.
FIG. 7 is a front sectional view of the periphery of the partition member in the modified example of the first embodiment. FIG. 7 is a cross-sectional view of a portion corresponding to the line F5-F5 in FIG. The partition member 150 of the modified example is different from the first embodiment in that the heat insulating layer 152 is formed of a solid material. The description of the modified example regarding the same points as in the first embodiment will be omitted.

The heat insulating layer 152 is made of a solid material. For example, the solid material is an epoxy-based or silicon-based resin material. The thermal conductivity of these resin materials is about 1 to 10 W / mk, which is smaller than the thermal conductivity of aluminum or an aluminum alloy which is a material for forming the first header 10. Therefore, heat exchange via the partition member 150 is suppressed.
For example, the heat insulating layer 152 is formed by filling the air layer, which is the heat insulating layer 52 of the first embodiment, with a resin putty agent and curing it. The filling of the resin putty agent is carried out after the partition member 150 and the first header 10 are fixed by brazing.

The partition member 50 of the first embodiment is inserted into the inside through the opening 10w on the outer peripheral surface of the first header 10. The heat insulating layer 52 of the first embodiment is exposed to the outside through the opening 10w of the first header 10. Therefore, rainwater and dew condensation water adhere to the end plates 51 on both sides of the heat insulating layer 52. As a result, the partition member 50 may be corroded.
The heat insulating layer 152 of the modified example is formed of a solid material. As a result, rainwater and dew condensation water do not adhere to the end plates 51 on both sides of the heat insulating layer 152, so that corrosion of the partition member 150 is suppressed.

(Second Embodiment)
FIG. 8 is a perspective view of the partition member according to the second embodiment. The partition member 250 of the second embodiment is different from the first embodiment in that the connecting portion 258 connects the pair of end plates 51, 51 at the outer peripheral portion of the first semicircular portion 54. The description of the second embodiment with respect to the same points as the first embodiment is omitted.

The partition member 250 has a connecting portion 258 that connects a pair of end plates 51, 51 in the Z direction. The connecting portion 258 connects the pair of end plates 51, 51 to each other at the first semicircular portion 54 and the step portion 55. The opening 10w of the first header 10 (see FIGS. 5 and 6) is covered by a pair of end plates 51, 51 and a connecting portion 258. Therefore, the air layer, which is the heat insulating layer 52, is not exposed to the outside through the opening 10w. As a result, adhesion of rainwater and dew condensation water to the end plates 51 on both sides of the heat insulating layer 52 is suppressed. Therefore, corrosion of the partition member 250 is suppressed.

According to at least one embodiment described above, the first header 10 of the heat exchanger 4 has a partition member 50 having a heat insulating layer 52. As a result, it is possible to suppress a decrease in the amount of heat exchange in the heat exchanger 4.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, as well as in the scope of the invention described in the claims and the equivalent scope thereof.

1 ... Refrigeration cycle device, 4 ... Outdoor heat exchanger (heat exchanger), 10 ... 1st header (header), 10w ... Opening, 15 ... 1st partition member (partition member), 16 ... 2nd partition member (partition) Members), 18 ... 1st refrigerant port (inflow port, outflow port), 19 ... 2nd refrigerant port (outlet, inflow port), 30 ... heat exchange tube, 50, 150, 250 ... partition member, 51 ... end plate , 52, 152 ... Insulation layer.

Claims (5)

Multiple heat exchange tubes arranged in parallel at intervals in the first direction,
It is formed in a tubular shape, the central axis extends in the first direction, and is arranged side by side so as to be separated from each other in the second direction orthogonal to the first direction, and the ends of the plurality of heat exchange tubes are inside. At least two headers to open and
At least one inside of the header is partitioned in the first direction, and the header has a partition member having a heat insulating layer having a lower thermal conductivity than the material for forming the header.
Heat exchanger. The partition member has end plates on both sides of the heat insulating layer in the first direction.
The end plate is made of the same material as the header forming material.
The heat exchanger according to claim 1. The heat insulating layer is made of a solid material and is exposed to the outside through an opening on the outer peripheral surface of the header.
The heat exchanger according to claim 1 or 2. At least one of the headers has an inflow port for the refrigerant to flow in from the outside of the heat exchanger and an outflow port for the refrigerant to flow out to the outside of the heat exchanger.
The partition member partitions the inside of the header through which the inlet and the outlet open.
The heat exchanger according to any one of claims 1 to 3. The heat exchanger according to any one of claims 1 to 4.
Refrigeration cycle equipment.

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