JP7296264B2 - Heat exchanger and refrigeration cycle equipment - Google Patents

Description

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

A heat exchanger is used to exchange heat between the refrigerant and the outside air. A 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. Ends of a plurality of heat exchange tubes open into the interior of the header. In order to increase the amount of heat exchanged, there is a heat exchanger that circulates the refrigerant by folding it inside the header. In this heat exchanger, the internal space of the header is partitioned into a plurality of small chambers by partition members. When heat is exchanged between the adjacent small chambers through the partition member, the amount of heat exchanged between the heat exchanger and the outside air is reduced. A heat exchanger capable of suppressing a decrease in heat exchange amount is required.

JP 2017-155993 A

The problem to be solved by the present invention is to provide a heat exchanger and a refrigeration cycle device that can suppress a decrease in heat exchange amount.

A heat exchanger of an embodiment has a plurality of heat exchange tubes, headers, and partition members. The plurality of heat exchange tubes are arranged side by side at intervals in the first direction. The headers are formed in a cylindrical shape, have central axes extending in a first direction, and are arranged side by side in a second direction orthogonal to the first direction, spaced apart from each other. Ends of a plurality of heat exchange tubes open into the at least two headers. The partition member partitions the interior of at least one of the headers in the first direction. The partition member has a heat insulating layer with a lower thermal conductivity than the material forming the header. The partition member includes a pair of end plates, connecting portions, and projections. A pair of end plates are provided on both sides in the first direction. The connecting portion connects the pair of end plates. The projections are inserted into holes penetrating the peripheral wall of the header. The heat insulating layer is formed between the pair of end plates and exposed to the outside through an opening in the outer peripheral surface of the header. The heat insulating layer is formed to have a thickness in the first direction greater than the thickness of the end plate in the first direction.

BRIEF DESCRIPTION OF THE DRAWINGS The schematic block diagram of the refrigerating-cycle apparatus in 1st Embodiment. The front view of the heat exchanger in 1st Embodiment. FIG. 3 is a side cross-sectional view taken along line F3-F3 of FIG. 2; The perspective view of a partition member. FIG. 7 is a front cross-sectional view of the periphery of the partition member taken along line F5-F5 in FIG. 6; FIG. 6 is a cross-sectional plan view of the periphery of the partition member taken along line F6-F6 of FIG. 5; FIG. 4 is a front cross-sectional view of the periphery of a partition member in a modified example of the first embodiment; The perspective view of the partition member in 2nd Embodiment.

Hereinafter, a heat exchanger and a refrigeration cycle device according to embodiments will be described with reference to the drawings.
In the present application, the X direction, Y direction and 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 vertical and the +Z direction is upward. The X direction (second direction) is the central axis direction (extending direction) of the heat exchange tubes. 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 the direction perpendicular to the X and Z directions.

(First embodiment)
FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus of a 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 constituent elements of the refrigeration cycle apparatus 1 are connected in sequence by pipes 7 . In FIG. 1 , the direction of refrigerant flow during cooling operation is indicated by solid line arrows, and the direction of refrigerant flow during heating operation is indicated by broken line arrows.

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

The four-way valve 3 reverses the flow direction of the refrigerant to switch between cooling operation and heating operation. During cooling operation, the refrigerant flows through the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6 in this order. 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 heating operation, the refrigerant flows through the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4 in this order. 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 converts the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 2 into a high-pressure liquid refrigerant by radiating heat to the outside air and condensing the refrigerant.
The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant sent from the condenser to convert it into a low-temperature, low-pressure gas-liquid two-phase refrigerant.
The evaporator absorbs heat from the outside air and evaporates the low-temperature, low-pressure gas-liquid two-phase refrigerant fed from the expansion device 5, thereby converting it into a low-pressure gaseous refrigerant.

Thus, in the refrigeration cycle device 1, the refrigerant, which is the working fluid, circulates while changing the phase between the gas refrigerant and the liquid refrigerant. The refrigerant releases heat during the phase change from the gas refrigerant to the liquid refrigerant, and absorbs heat during the phase change from the liquid refrigerant to the gas refrigerant. The refrigerating cycle device 1 performs heating, cooling, defrosting, etc. by utilizing the heat radiation or heat absorption of the refrigerant.

FIG. 2 is a front view of the heat exchanger of the first embodiment; FIG. 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, a case where the heat exchanger 4 of the embodiment is used as the outdoor heat exchanger 4 of the refrigeration cycle apparatus 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 , heat exchange tubes (heat transfer tubes) 30 and fins 40 .
The first header 10 is made of a material with high thermal conductivity and low specific gravity, such as aluminum or an aluminum alloy. The first header 10 is formed in a tubular shape, for example, in a cylindrical shape with a circular cross section perpendicular to the Z direction. A 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 tubes 30 are inserted are formed in the outer peripheral surface of the first header 10 .
The second header 20 is formed similarly to the first header 10 . The first header 10 and the second header 20 are arranged side by side while being spaced apart from each other in the X direction.

3 is a partial cross-sectional view taken along line F4-F4 of FIG. 2. FIG. The heat exchange tube 30 is made of a material with high thermal conductivity and 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 elliptical shape. Inside the heat exchange tube 30, a plurality of refrigerant flow paths 34 are formed side by side in the Y direction. Adjacent coolant channels 34 are partitioned by channel walls 35 parallel to the XZ plane. A plurality of refrigerant flow paths 34 pass through the heat exchange tubes 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 tubes 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 paths 34 of the heat exchange tubes 30 are opened inside the first header 10 and the second header 20 .

The gaps between the first header 10 and the second header 20 and the heat exchange tubes 30 are sealed by brazing or the like. A specific procedure for brazing is as follows. Braze is applied to the inner surfaces of the first header 10 and the second header 20 . The heat exchange tubes 30 are inserted into the first header 10 and the second header 20 to assemble the heat exchanger 4 . The assembled heat exchanger 4 is heated in a furnace. The heating melts the wax on the inner surfaces of the first header 10 and the second header 20 . The melted wax fills the gaps between the first header 10 and the second header 20 and the heat exchange tubes 30 . The heat exchanger 4 is then cooled and the wax solidifies. Thereby, the first header 10 and the second header 20 and the heat exchange tubes 30 are fixed.

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

As shown in FIG. 3, the width of the fins 40 in the Y direction is greater than the width of the heat exchange tubes 30 in the Y direction. A notch 43 is formed from the edge of the fin 40 in the +Y direction to the -Y direction. The heat exchange tube 30 is inserted into the notch 43 . The heat exchange tube 30 and the fins 40 are fixed by the above-described brazing.
As shown in FIG. 2, a plurality of fins 40 are spaced apart in the X direction.

Outside air flow paths extending in the Y direction are formed between adjacent heat exchange tubes 30 and between adjacent fins 40 . The heat exchanger 4 circulates outside air through an outside air flow path using a fan (not shown) or the like. The heat exchanger 4 exchanges heat between the outside air flowing through the outside air passage and the refrigerant flowing through the refrigerant passage 34 . Heat exchange is performed indirectly through heat exchange tubes 30 and fins 40 .

Describe the structure of the header.
As shown in FIG. 2, the first header 10 has partition members 15 and 16 . The partition members 15 and 16 are arranged parallel to the XY plane and partition the internal space of the first header 10 in the Z direction. Partition members 15 and 16 partition the internal space of first header 10 into a plurality of small chambers. In the example of FIG. 2 , two partition members 15 and 16 partition the internal space into three small chambers 11 , 12 and 13 . The two partition members 15 and 16 are the first partition member 15 on the +Z side and the second partition member 16 on the -Z side. The three chambers 11, 12, 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 first chamber 11 and the third chamber 13 have the same height in the Z direction, and the second chamber 12 is higher than the first chamber 11 and the third chamber 13 in the Z direction.

The second header 20 has partition members 25 similar to the first header 10 . A 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. In the example of FIG. The two chambers 21 and 22 are the first chamber 21 on the +Z side and the second chamber 22 on the -Z side. In the example of FIG. 2, the two chambers 21 and 22 have the same height in the Z direction.

A 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 to the three small chambers 11, 12, 13 formed in the first header 10, respectively. In the example of FIG. 2, the same number of heat exchange tubes 30 are opened to the first small chamber 11 and the third small chamber 13, respectively, and the number of heat exchange tubes 30 to the second small chamber 12 is twice that of the first small chamber 11 and the third small chamber 13. number of heat exchange tubes 30 are opened.
A 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 to the two small chambers 21 and 22 formed in the second header 20, respectively. In the example of FIG. 2, the same number of heat exchange tubes 30 are opened to the two small chambers 21 and 22, respectively.

Refrigerant ports 18 and 19 are opened inside the first header 10 . Refrigerant ports 18, 19 are the inlet and outlet of the refrigerant between the outside and the heat exchanger. A first refrigerant port 18 opens at the -Z direction end of the first small chamber 11 of the first header 10 . The first coolant port 18 may open at the +Z direction end of the first small chamber 11 . A second refrigerant port 19 opens at the -Z direction end of the third small chamber 13 of the first header 10 .

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

The gaseous refrigerant that has flowed into the first small chambers 11 of the first header 10 radiates heat to the outside air and condenses while flowing through the heat exchange tubes 30 . The condensed refrigerant becomes liquid refrigerant and flows into the third small chambers 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 heating operation, the refrigerant flows in the direction opposite 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 the gas-liquid two-phase state, the amount of heat exchanged with the outside air is used for the phase change of the refrigerant, so 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 the temperature change of the refrigerant is large. The first small chamber 11 of the first header 10 through which the gas refrigerant flows and the third small chamber 13 of the first header 10 through which the liquid refrigerant flows are portions through 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 through which the refrigerant flows in a gas-liquid two-phase state. Therefore, the temperature difference between the first small chamber 11 and the second small chamber 12 of the first header 10 is large. The same applies to the temperature difference between the second small chamber 12 and the third small 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, heat exchange may occur 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 as well. 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 heat exchange tube 30 immediately before. If a temperature sensor is placed in the first header 10 to detect the temperature of the refrigerant flowing through the heat exchange tubes 30, the wrong temperature of the refrigerant may be detected. Along with this, there is a possibility that the opening control of the expansion device 5 (see FIG. 1) is erroneous.

The first partition member 15 will be described in detail. The second partition member 16 is similar to the first partition member 15 . In the following description, the first partition member 15 is simply referred to as partition member 50 .
FIG. 4 is a perspective view of a 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 that of the first header 10 . That is, the end plate 51 is made of a material such as aluminum or an aluminum alloy.

The end plate 51 is formed in a substantially circular shape in plan view. A first semicircular portion 54 in the -X direction of the end plate 51 and a second semicircular portion 56 in the +X direction have different radii. The radius of the first semicircular portion 54 is the same as the radius of the outer peripheral surface of the first header 10 . The radius of the second semicircular portion 56 is the same as the radius of the inner peripheral surface of the first header 10 . A stepped 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 plane facing the +X direction. A protrusion 57 is formed at the +X direction end of the second semicircular portion 56 . 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 with a gap in the Z direction. The shape of the pair of end plates 51, 51 is the same. The partition member 50 has a connecting portion 58 that connects the 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 stepped portion 55 , the outer peripheral portion of the second semicircular portion 56 and the projection 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 the 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 in which the space between the pair of end plates 51, 51 is opened to the outside from the opening 10w of the first header 10. As shown in FIG. Therefore, the heat insulating layer 52 is an air layer. The thermal conductivity of aluminum or an aluminum alloy, which is the 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 lower thermal conductivity than the material forming the first header 10 .

5 is a front cross-sectional view of the periphery of the partition member taken along line F5-F5 of FIG. 6. FIG. 6 is a plan cross-sectional view of the periphery of the partition member taken along line F6-F6 in FIG. 5 (line F6-F6 in FIG. 2).
As shown in FIG. 5, the first header 10 is formed with an opening 10w passing through the peripheral wall. The partition member 50 is inserted inside the first header 10 from the radially outer side (−X direction) of the first header 10 through the opening 10w. The height of the opening 10w in the Z direction is the same as 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. As shown in FIG. The opening 10w is formed over a half circumference of the first header 10 in the circumferential direction.

As shown in FIG. 6, a hole 10h is formed through the peripheral wall at the +X direction end of the first header 10 . The projections 57 of the partition member 50 are inserted into the holes 10h of the first header 10. As shown in FIG. Thereby, 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 the inner circumferential surface of the first header 10 . The stepped portion 55 of the partition member 50 abuts on the end portion of the opening 10w of the first header 10 in the circumferential direction. The outer periphery 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 above-described brazing.

As shown in FIG. 5 , the partition member 50 partitions the inside of the first header 10 into the first small chamber 11 and the second small chamber 12 . The partition member 50 has a heat insulating layer 52 in the central portion in the Z direction. The heat insulating layer 52 is made of a material having a lower thermal conductivity than the material of the first header 10 .
Accordingly, 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, a decrease in the amount of heat exchanged by the heat exchanger can be suppressed.

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 that of 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, electric corrosion of both is suppressed. Since both have the same coefficient of expansion, the generation of gaps due to heating during brazing is suppressed. Since both have the same melting point, deformation of the end plate 51 due to heating during brazing is suppressed.

In a 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 . Alternatively, 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 compartments 11, 12, 13 by two partition members 15, 16. As shown in FIG. 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 other numbers of compartments by other numbers of partition members.

The first header 10 has a first refrigerant port 18 and a second refrigerant port 19 as an inlet through which the refrigerant flows from the outside of the heat exchanger 4 and an outlet through which the refrigerant flows out of the heat exchanger 4 . The partition member 50 partitions the first small chamber 11 and the third small chamber 13 inside the first header 10 to which the first refrigerant port 18 and the second refrigerant port 19 open.
The first small chamber 11 and the third small chamber 13 to which the inflow port and the outflow port of the heat exchanger 4 are open 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 small chamber 11 and the second small chamber 12 and between the second small chamber 12 and the third small chamber 13 . Thereby, heat exchange via the partition member 50 can be suppressed. Therefore, a decrease in the amount of heat exchanged by the heat exchanger can be suppressed.

In the first embodiment, the first refrigerant port 18 and the second refrigerant port 19 open inside the first header 10 . Alternatively, one or both of the first refrigerant port 18 and the second refrigerant port 19 may open inside the second header 20 . In either case, the partition member 50 of the first embodiment is applied as the partition member of the small chambers 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 embodiment described above is inserted from the outside of the first header 10 to the inside through the opening 10w. Alternatively, the partition member may be inserted into the first header 10 from its axial end. In this case, the opening 10w of the first header 10 becomes unnecessary.

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

A modification of the first embodiment will be described.
FIG. 7 is a front cross-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 line F5-F5 in FIG. The modified partition member 150 differs from the first embodiment in that the heat insulating layer 152 is made of a solid material. The description of the modified example that is the same as the first embodiment is omitted.

Thermal insulation layer 152 is formed 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 aluminum alloy, which is the material 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 the resin putty agent. The filling of the resin putty is performed 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 first header 10 through an opening 10w on the outer peripheral surface thereof. The heat insulating layer 52 of the first embodiment is exposed to the outside through the opening 10w of the first header 10. As shown in FIG. Therefore, rainwater and condensed water adhere to the end plates 51 on both sides of the heat insulating layer 52 . This may cause the partition member 50 to corrode.
The modified thermal insulation layer 152 is formed of a solid material. As a result, rainwater and condensed water do not adhere to the end plates 51 on both sides of the heat insulating layer 152, so corrosion of the partition member 150 is suppressed.

(Second embodiment)
FIG. 8 is a perspective view of a partition member in the second embodiment. A partition member 250 of the second embodiment differs from that of the first embodiment in that a 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 as to what is the same as the first embodiment is omitted.

The partition member 250 has a connecting portion 258 that connects the 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 stepped portion 55 . The opening 10w (see FIGS. 5 and 6) of the first header 10 is covered with a pair of end plates 51, 51 and a connecting portion 258. As shown in FIG. Therefore, the air layer, which is the heat insulating layer 52, is not exposed to the outside from the opening 10w. As a result, adhesion of rainwater and condensed 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 with an insulating layer 52 . Thereby, a decrease in the amount of heat exchanged by the heat exchanger 4 can be suppressed.

While several embodiments of the invention have been described, these embodiments have been presented by way of example 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 modifications can be made without departing from the scope of the invention. These embodiments and their modifications are included in the scope and spirit of the invention, as well as the scope of the invention described in the claims and equivalents thereof.

DESCRIPTION OF SYMBOLS 1... Refrigeration cycle apparatus, 4... Outdoor heat exchanger (heat exchanger), 10... 1st header (header), 10w... Opening, 15... 1st partition member (partition member), 16... 2nd partition member (partition Member), 18... First refrigerant port (inlet, outlet), 19... Second refrigerant port (outlet, inlet), 30... Heat exchange tube, 50, 150, 250... Partition member, 51... End plate , 52, 152 . . . Thermal insulation layer.

Claims (5)

a plurality of heat exchange tubes arranged in parallel and spaced apart in a first direction;
It is formed in a cylindrical shape, has a central axis extending in the first direction, is arranged side by side in a second direction perpendicular to the first direction, and is spaced apart from each other. at least two open headers;
a partition member that partitions the inside of at least one of the headers in the first direction and has a heat insulating layer with a lower thermal conductivity than the material forming the header ;
The partition member includes a pair of end plates provided on both sides in the first direction, a connecting portion connecting the pair of end plates, and a projection inserted into a hole penetrating the peripheral wall of the header,
the heat insulating layer is formed between the pair of end plates and exposed to the outside from an opening in the outer peripheral surface of the header;
The heat insulating layer has a thickness in the first direction greater than the thickness of the end plate in the first direction ,
Heat exchanger. The end plates are made of the same material as that of which the header is made.
A heat exchanger according to claim 1. The heat insulating layer is formed of a solid material,
A heat exchanger according to claim 1 or 2. at least one of the headers has an inlet through which the refrigerant flows from the outside of the heat exchanger and an outlet through which the refrigerant flows out of the heat exchanger;
The partition member partitions the inside of the header where the inlet and the outlet open,
A heat exchanger according to any one of claims 1 to 3. Having a heat exchanger according to any one of claims 1 to 4,
Refrigeration cycle equipment.

Images