Heat exchanger and refrigeration cycle device

Abstract

To provide a heat exchanger and a refrigeration cycle device capable of adjusting an amount of a refrigerant flowing through a heat transfer tube.SOLUTION: A heat exchanger according to an embodiment includes: one or a plurality of heat transfer tubes having a refrigerant flow path through which a refrigerant flows; and a header connected to at least one end of the plurality of heat transfer tubes. The header includes: a first plate material to which a refrigerant inlet pipe having an inlet port for guiding the refrigerant is connected; one or a plurality of intermediate plate materials having a spatial flow path through which the refrigerant is introduced; and a second plate material to which the heat transfer tubes are connected. The spatial flow path has an introduction space, a first space, and a second space. The refrigerant is introduced into the introduction space from the introduction port. The refrigerant flows into the first space from the introduction space. The refrigerant flows into the second space from the introduction space. On the intermediate plate material, a first wall portion that increases the flow resistance of the refrigerant from the introduction space to the first space, and a second wall portion that increases the flow resistance of the refrigerant from the introduction space to the second space are formed.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] An embodiment of the present invention relates to a heat exchanger and a refrigeration cycle apparatus. [Background technology]

[0002] Heat exchangers are used in air conditioners, refrigeration equipment, and the like. For example, a heat exchanger includes a plurality of heat transfer tubes and a header. The heat transfer tubes have a refrigerant flow path. The header is provided at an end of the heat transfer tube. In a heat exchanger having the above structure, it may be necessary to adjust the amount of refrigerant flowing through the heat transfer tube. For example, in a heat exchanger, the refrigerant may be distributed from one refrigerant port to a plurality of heat transfer tubes. In a heat exchanger having the above structure, there may be a bias in the amount of refrigerant or the state of the refrigerant distributed to the plurality of heat transfer tubes. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent Publication No. 2021-179308 Summary of the Invention [Problem to be solved by the invention]

[0004] An object of the present invention is to provide a heat exchanger and a refrigeration cycle device capable of adjusting the amount or state of a refrigerant flowing through a heat transfer tube. [Means for solving the problem]

[0005] The heat exchanger of the embodiment includes one or more heat transfer tubes having a refrigerant flow path through which a refrigerant flows, and a header connected to at least one end of the heat transfer tubes. The header includes a first plate material to which a refrigerant inlet pipe having an inlet port for introducing the refrigerant is connected, one or more intermediate plate materials having a spatial flow path into which the refrigerant is introduced, and a second plate material to which the heat transfer tubes are connected. The spatial flow path has an introduction space, a first space, and a second space. The introduction space is introduced from the introduction port. The first space is formed adjacent to one side of the introduction space. The refrigerant flows into the first space from the introduction space. The second space is formed adjacent to the other side of the introduction space. The refrigerant flows into the second space from the introduction space. The intermediate plate material is formed with a first wall portion that increases the flow resistance of the refrigerant from the introduction space to the first space, and a second wall portion that increases the flow resistance of the refrigerant from the introduction space to the second space. [Brief description of the drawings]

[0006] [Figure 1] 1 is a schematic configuration diagram of a refrigeration cycle device according to an embodiment; [Diagram 2] FIG. 2 is a perspective view of the heat exchanger according to the first embodiment. [Diagram 3] FIG. 4 is a perspective view showing an internal structure of a first header in the first embodiment. [Figure 4] FIG. 4 is a cross-sectional view showing an internal structure of a first header in the first embodiment. [Diagram 5] FIG. 4 is a side view showing the internal structure of the first header in the first embodiment. [Figure 6] FIG. 11 is a perspective view showing an internal structure of a first header according to a second embodiment. [Figure 7] FIG. 11 is a side view showing the internal structure of the first header in the second embodiment. [Figure 8] FIG. 13 is a side view showing the internal structure of the first header in the third embodiment. [Figure 9] FIG. 13 is a side view showing the internal structure of the first header in the fourth embodiment. [Figure 10] FIG. 13 is an exploded perspective view of a heat exchanger according to a fifth embodiment. [Figure 11] FIG. 13 is a side view showing the internal structure of the first header in the fifth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0007] Hereinafter, a heat exchanger and a refrigeration cycle device according to an embodiment will be described with reference to the drawings.

[0008] (First embodiment) FIG. 1 is a schematic configuration diagram of a refrigeration cycle device according to an embodiment. As shown in Fig. 1, the refrigeration cycle apparatus 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. The components of the refrigeration cycle apparatus 1 are connected by piping 7. In Fig. 1, the flow direction of the refrigerant (heat medium) during cooling operation is indicated by solid arrows. The flow direction of the refrigerant during heating operation is indicated by dashed arrows.

[0009] The compressor 2 includes a compressor body 2A and an accumulator 2B. The compressor body 2A compresses the low-pressure gas refrigerant taken in to produce high-temperature, high-pressure gas refrigerant. The accumulator 2B separates the gas-liquid two-phase refrigerant and supplies the gas refrigerant to the compressor body 2A.

[0010] The four-way valve 3 reverses the flow direction of the refrigerant to switch between cooling 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 that order. At this time, the outdoor heat exchanger 4 functions as a condenser, and the indoor heat exchanger 6 functions as an evaporator.

[0011] 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 that order. At this time, the indoor heat exchanger 6 functions as a condenser, and the outdoor heat exchanger 4 functions as an evaporator.

[0012] The condenser converts the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 into high-pressure liquid refrigerant by dissipating heat into the outside air and condensing it. The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant sent from the condenser, converting it into a low-temperature, low-pressure two-phase gas-liquid refrigerant. The evaporator converts the low-temperature, low-pressure two-phase gas-liquid refrigerant sent from the expansion device 5 into a low-pressure gas refrigerant by absorbing heat from the outside air and vaporizing it.

[0013] In the refrigeration cycle device 1, the refrigerant, which is the working fluid, circulates while changing phase between gaseous refrigerant and liquid refrigerant. The refrigerant releases heat during the phase change from gaseous refrigerant to liquid refrigerant. The refrigerant absorbs heat during the phase change from liquid refrigerant to gaseous refrigerant. The refrigeration cycle device 1 performs heating, cooling, defrosting, etc. by utilizing the heat release or absorption of the refrigerant.

[0014] Fig. 2 is a perspective view of the heat exchanger of the first embodiment. For example, the heat exchanger of the embodiment is used as one or both of the outdoor heat exchanger 4 and the indoor heat exchanger 6 (see Fig. 1) of the refrigeration cycle device 1. Hereinafter, a case where the heat exchanger of the embodiment is used as the outdoor heat exchanger 4 (see Fig. 1) of the refrigeration cycle device 1 will be described as an example. The outdoor heat exchanger 4 will be simply referred to as "heat exchanger 4".

[0015] The X direction, Y direction, and Z direction are defined as follows: The Z direction is the longitudinal direction (extension direction) of the first header. The Z direction is the height direction. For example, the Z direction is the vertical direction. +Z is upward. -Z is downward. The X direction is the central axis direction (extension direction) of the heat transfer tube. The X direction is perpendicular to the Z direction. For example, the X direction is the horizontal direction. +X is the direction from the heat transfer tube toward the first header. -X is the opposite direction to +X.

[0016] The Y direction is perpendicular to the X direction and the Z direction. The Y direction is the left-right direction. +Y is one direction of the Y direction. -Y is the other direction of the Y direction. For example, the Y direction is the horizontal direction. The Y direction is the width direction of the first header 10. The Y direction is the first direction. The X direction is the second direction. The Z direction is the third direction. The YZ plane is the plane formed by the Y direction and the Z direction.

[0017] As shown in FIG. 2, the heat exchanger 4 has a first header 10, a plurality of heat transfer tubes 30, a plurality of fins (not shown), and a second header (not shown). The first header 10 is connected to an end (one end) on the +X side of the heat transfer tube 30. The second header is connected to an end (the other end) on the -X side of the heat transfer tube 30. A plurality of fins are formed on the heat transfer tube 30. The fins are perpendicular to the heat transfer tube 30.

[0018] The first header 10 is formed in a flat plate shape parallel to the YZ plane. For example, when viewed from the X direction, the first header 10 is rectangular. The shape of the first header 10 is a rectangle whose longitudinal direction is along the Z direction. The first header 10 is formed of a material with high thermal conductivity and low specific gravity. For example, the first header 10 is formed of a metal such as aluminum or an aluminum alloy.

[0019] The first header 10 (header) includes a first plate material 11, a first intermediate plate material 12, a second intermediate plate material 13, a third intermediate plate material 14, and a second plate material 15. The first plate material 11, the first intermediate plate material 12, the second intermediate plate material 13, the third intermediate plate material 14, and the second plate material 15 are stacked in this order.

[0020] The first intermediate plate 12 is superimposed on the -X side surface of the first plate 11. The second intermediate plate 13 is superimposed on the -X side surface of the first intermediate plate 12. The third intermediate plate 14 is superimposed on the -X side surface of the second intermediate plate 13. The second plate 15 is superimposed on the -X side surface of the third intermediate plate 14. The first plate 11, the first intermediate plate 12, the second intermediate plate 13, the third intermediate plate 14 and the second plate 15 are substantially rectangular when viewed from the thickness direction (X direction). The first intermediate plate 12, the second intermediate plate 13 and the third intermediate plate 14 can be collectively referred to as "intermediate plate 12-14". The intermediate plate 12-14 are examples of "intermediate plate".

[0021] The first plate material 11 is formed in a flat plate shape. One or more connection ports 50 are formed in the first plate material 11. The connection port 50 is an opening for introducing the refrigerant into the spatial flow path 16. For example, the connection port 50 is circular. A tubular refrigerant port 51 (refrigerant introduction pipe) is inserted into the connection port 50. The gap between the periphery of the connection port 50 and the refrigerant port 51 is sealed by, for example, brazing. The refrigerant port 51 is attached to the first plate material 11. With this structure, the refrigerant port 51 is connected to the connection port 50. The refrigerant port 51 has a flow path through which the refrigerant flows. For example, the refrigerant port 51 is perpendicular to the first plate material 11.

[0022] The inlet 51a at the -X side end of the refrigerant port 51 faces the spatial flow path 16 (see FIG. 4). The refrigerant port 51 guides the refrigerant. The inlet 51a serves as an inlet for introducing the refrigerant into the spatial flow path 16. When viewed from the X direction, the inlet 51a is located at a position corresponding to the portion (middle portion 24) between the first compartment 22 and the second compartment 23 of the second intermediate plate member 13. When viewed from the X direction, the center of the inlet 51a is located lower than the center of the spatial flow path 16 (see FIG. 5).

[0023] Fig. 3 is a perspective view showing the internal structure of the first header 10. Fig. 4 is a cross-sectional view showing the internal structure of the first header 10. Fig. 5 is a side view showing the internal structure of the first header 10.

[0024] 3, one or more spatial flow paths 16 are formed in the intermediate plate members 12-14. For example, the multiple spatial flow paths 16 are formed side by side at intervals in the Z direction. An opening on the outer surface side (+X side) of the spatial flow path 16 is closed by the first plate member 11. An opening on the inner surface side (-X side) of the spatial flow path 16 is closed by the second plate member 15.

[0025] As shown in FIGS. 3 and 4, the spatial flow path 16 has an introduction chamber 21, a first compartment 22, and a second compartment . The introduction chamber 21 is formed by a through hole that penetrates the first intermediate plate 12 in the thickness direction. The introduction chamber 21 has an elliptical shape when viewed from the X direction. The "elliptical shape" is composed of two straight lines that are parallel to and face each other, and two curved lines that connect the ends of the two straight lines. The two curved lines are curved shapes (e.g., semicircular, elliptical, etc.) that are convex on the sides that move away from each other.

[0026] The major axis direction (long axis direction) of the introduction chamber 21 is parallel to the Y direction. The opening on the +X side of the introduction chamber 21 is closed by the first plate material 11. The refrigerant is introduced into the introduction chamber 21 from a refrigerant port 51. The through hole that becomes the introduction chamber 21 can be formed in the first intermediate plate material 12 by cutting or the like.

[0027] The first sub-chamber 22 and the second sub-chamber 23 are formed by through holes that penetrate the second intermediate plate 13 and the third intermediate plate 14 in the thickness direction. In the illustrated example, the first sub-chamber 22 and the second sub-chamber 23 have approximately the same shape. The first sub-chamber 22 and the second sub-chamber 23 are formed at different positions in the Y direction. The first sub-chamber 22 and the second sub-chamber 23 are formed at an interval in the Y direction. The first sub-chamber 22 and the second sub-chamber 23 are aligned in the Y direction. The first sub-chamber 22 and the second sub-chamber 23 are formed independently. The first sub-chamber 22 and the second sub-chamber 23 can be collectively referred to as "chambers 22, 23". The through holes that become the sub-chambers 22, 23 can be formed in the second intermediate plate 13 and the third intermediate plate 14 by cutting or the like.

[0028] The sub-chambers 22, 23 are elliptical when viewed from the X direction. The major axis direction of the sub-chambers 22, 23 is parallel to the Y direction. The major axis of the sub-chambers 22, 23 is shorter than half the major axis of the introduction chamber 21. For example, the minor axis of the sub-chambers 22, 23 is equal to the minor axis of the introduction chamber 21.

[0029] The -Y side end of the first sub-chamber 22 is located at a position overlapping with the -Y side end of the introduction chamber 21 when viewed from the X direction. The +Y side end of the second sub-chamber 23 is located at a position overlapping with the +Y side end of the introduction chamber 21 when viewed from the X direction. The sub-chambers 22, 23 overlap with the introduction chamber 21 when viewed from the X direction. The +X sides of the sub-chambers 22, 23 are open to the introduction chamber 21. The sub-chambers 22, 23 communicate with the introduction chamber 21. The openings on the -X side of the sub-chambers 22, 23 are closed by the second plate member 15. The refrigerant is introduced into the sub-chambers 22, 23 from the introduction chamber 21.

[0030] A plurality of outlet ports 41 are formed in the second plate member 15. The outlet ports 41 are slit-shaped along the Y direction. The plurality of outlet ports 41 include a first outlet port 41A formed at a position corresponding to the first compartment 22 and a second outlet port 41B formed at a position corresponding to the second compartment 23.

[0031] 3 to 5, wall portions 61 and 62 are formed on the inner surface of the introduction chamber 21. The wall portions 61 and 62 are a first wall portion 61 and a second wall portion 62.

[0032] The walls 61, 62 are formed on the bottom surface 21a (lower surface) of the introduction chamber 21. The walls 61, 62 are plate-shaped along a plane intersecting with the Y direction. For example, the walls 61, 62 are rectangular plate-shaped perpendicular to the Y direction. The walls 61, 62 protrude upward from the bottom surface 21a. When viewed from the X direction, the walls 61, 62 are positioned so that at least a portion of them overlaps with the middle portion 24. For example, the walls 61, 62 are positioned so that at least the base ends (lower ends) overlap with the middle portion 24. The height of the walls 61, 62 may be half or more of the height of the introduction chamber 21 (dimension in the Z direction) or less than half of the height of the introduction chamber 21.

[0033] When viewed from the X direction, the first wall portion 61 is located on the -Y side of the inlet 51a of the refrigerant port 51. When viewed from the X direction, the second wall portion 62 is located on the +Y side of the inlet 51a of the refrigerant port 51.

[0034] The tips (upper ends) of the wall portions 61, 62 are at the same height as the top of the inlet 51a of the refrigerant port 51, or at a higher position than this top. Therefore, the wall portions 61, 62 are formed to correspond to the entire height range of the inlet 51a. In other words, the wall portions 61, 62 are formed in a height range that covers the entire range from the bottom to the top of the inlet 51a. Therefore, the refrigerant introduced from the inlet 51a and flowing to the -Y side or +Y side hits the wall portions 61, 62 and is easily adjusted in flow rate.

[0035] The walls 61, 62 may be formed integrally with the first intermediate plate 12. The walls 61, 62 can be formed when the introduction chamber 21 is formed in the first intermediate plate 12.

[0036] The introduction chamber 21 has an introduction space 21A, a first space 21B, and a second space 21C. The introduction space 21A is a space including the center in the Y direction within the internal space of the introduction chamber 21. The introduction space 21A is partitioned by wall portions 61 and 62. The introduction space 21A is a space that is on the +Y side of the first wall portion 61 and on the -Y side of the second wall portion 62. The introduction space 21A faces the intermediate portion 24.

[0037] The first space 21B is a space formed adjacent to the -Y side (one side) of the introduction space 21A. The first space 21B is a space on the -Y side of the first wall portion 61. The first space 21B communicates with the first compartment 22. The second space 21C is a space formed adjacent to the +Y side (the other side) of the introduction space 21A. The second space 21C is a space on the +Y side of the second wall portion 62. The second space 21C communicates with the second compartment 23.

[0038] The first wall portion 61 can increase the flow resistance of the refrigerant from the inlet space 21A to the first space 21B. The second wall portion 62 can increase the flow resistance of the refrigerant from the inlet space 21A to the second space 21C.

[0039] As shown in Fig. 4, the tip of the refrigerant port 51 is located within the introduction space 21A. The wall portions 61, 62 are located close to the tip of the refrigerant port 51, and therefore can restrict the tilt of the refrigerant port 51 by being close to the outer surface of the refrigerant port 51. Furthermore, the wall portions 61, 62 extend further toward the +X side than the tip of the refrigerant port 51, and therefore can more easily restrict the tilt of the refrigerant port 51. The wall portions 61, 62 can restrict the tilt of the refrigerant port 51 in the Y direction. The wall portions 61, 62 may be separated from the outer surface of the refrigerant port 51 or may be in contact with the outer surface of the refrigerant port 51.

[0040] For example, the heat transfer tube 30 is a flat tube formed in a flat shape. The heat transfer tube 30 has a larger outer dimension (outer diameter) in the Y direction than the outer dimension (outer diameter) in the Z direction. For example, the outer diameter of the heat transfer tube 30 in the Y direction is at least twice as large as the outer diameter in the Z direction. For example, the shape of a cross section (YZ cross section) perpendicular to the extension direction (X direction) of the heat transfer tube 30 is a substantially oval shape or a substantially elliptical shape.

[0041] One or more refrigerant flow paths 34 are formed inside the heat transfer tube 30. A refrigerant flows through the refrigerant flow paths 34. In the internal space of the heat transfer tube 30, a plurality of refrigerant flow paths 34 arranged in the Y direction (width direction) may be formed by one or more partition walls. The heat transfer tube 30 is made of a material having high thermal conductivity and low specific gravity. For example, the heat transfer tube 30 is made of a metal such as aluminum or an aluminum alloy.

[0042] The plurality of heat transfer tubes 30 include a first heat transfer tube 30A and a second heat transfer tube 30B. The first heat transfer tube 30A and the second heat transfer tube 30B are arranged at different positions in the Y direction. The first heat transfer tube 30A and the second heat transfer tube 30B are adjacent to each other in the Y direction. The first heat transfer tube 30A and the second heat transfer tube 30B are formed with an interval between them in the Y direction. The first heat transfer tube 30A and the second heat transfer tube 30B constitute a heat transfer tube group 30C.

[0043] A portion of the heat transfer tube 30 including the end in the +X direction is inserted into the outlet 41 of the first header 10. A gap between the periphery of the outlet 41 and the heat transfer tube 30 is sealed by, for example, brazing. The heat transfer tube 30 is attached to the second plate material 15. With this structure, the heat transfer tube 30 is connected to the outlet 41.

[0044] The first heat transfer tube 30A is connected to the first outlet 41A. The +X direction end of the refrigerant flow path 34 of the first heat transfer tube 30A opens to the first compartment 22. The refrigerant flow path 34 of the first heat transfer tube 30A communicates with the first compartment 22. The first heat transfer tube 30A discharges the refrigerant from the first compartment 22.

[0045] The second heat transfer tube 30B is connected to the second outlet 41B. The +X direction end of the refrigerant flow path 34 of the second heat transfer tube 30B opens to the second compartment 23. The refrigerant flow path 34 of the second heat transfer tube 30B communicates with the second compartment 23. The second heat transfer tube 30B discharges the refrigerant from the second compartment 23.

[0046] 2, for example, the heat transfer tubes 30 include a plurality of heat transfer tube groups 30C. The heat transfer tube groups 30C are arranged at different height positions. The heat transfer tube groups 30C are arranged in parallel at intervals in the Z direction.

[0047] Between vertically adjacent heat transfer tubes 30, an outside air flow path is formed along the Y direction. For example, the heat exchanger 4 circulates 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 performed indirectly via the heat transfer tubes 30 and fins (not shown).

[0048] The flow of the refrigerant will be described in detail below. 3 and 4, the refrigerant is introduced into the introduction space 21A of the first header 10 from the inlet 51a of the refrigerant port 51. For example, the refrigerant is a two-phase gas-liquid refrigerant. The refrigerant that has flowed into the introduction space 21A changes its flow direction when it hits the intermediate portion 24, and flows mainly toward the -Y side and the +Y side.

[0049] The refrigerant (liquid) flowing toward the -Y side passes over the first wall portion 61 and flows into the first space 21B. The refrigerant that flows into the first space 21B enters the refrigerant flow path 34 of the first heat transfer tube 30A from the first compartment 22. The refrigerant (liquid) flowing toward the +Y side passes over the second wall portion 62 and flows into the second space 21C. The refrigerant that flows into the second space 21C enters the refrigerant flow path 34 of the second heat transfer tube 30B from the second compartment 23.

[0050] The heat exchanger 4 of this embodiment has walls 61 and 62. The first wall 61 increases the flow resistance of the refrigerant from the introduction space 21A toward the -Y side. The second wall 62 increases the flow resistance of the refrigerant from the introduction space 21A toward the +Y side. Therefore, even when the refrigerant port 51 cannot be installed vertically in the introduction space 21A, the refrigerant does not flow biased toward the -Y side or the +Y side, but flows in both directions. In detail, when the refrigerant tends to flow biased toward one direction, the walls 61 and 62 increase the flow resistance in the direction in which the refrigerant tends to flow more, and the amount of refrigerant flowing in the direction with relatively smaller flow resistance increases. Therefore, compared to the case where there are no walls, the bias between the flow rate of the refrigerant from the introduction space 21A to the first space 21B and the flow rate of the refrigerant from the introduction space 21A to the second space 21C can be reduced. Therefore, the bias in the amount of refrigerant distributed to the multiple heat transfer tubes 30 (30A, 30B) can be reduced. In this manner, in the heat exchanger 4, the amount of refrigerant flowing through the heat transfer tubes 30 can be adjusted.

[0051] In the heat exchanger 4 of this embodiment, the inlet 51a of the refrigerant port 51 is located at a position corresponding to the middle portion 24 when viewed from the X direction. Therefore, the refrigerant that flows into the introduction space 21A hits the middle portion 24 and moves toward the -Y side and +Y side. This makes it possible to optimize the flow rate of the refrigerant from the introduction space 21A to the first space 21B and the second space 21C. Furthermore, when the refrigerant that flows in from the inlet 51a of the refrigerant port 51 is a gas-liquid two-phase refrigerant, the refrigerant is stirred in the introduction space 21A and distributed to the first space 21B and the second space 21C. This makes it possible to suppress the bias between the amount of gas refrigerant and the amount of liquid refrigerant, and to appropriately divide the gas-liquid two-phase refrigerant.

[0052] In the heat exchanger 4 of the present embodiment, the wall portions 61, 62 are close to the outer surface of the refrigerant port 51, thereby restricting tilting of the refrigerant port 51, so that the refrigerant port 51 can be assembled in a vertical position relative to the first header 10. Therefore, the refrigerant port 51 can be connected to the first header 10 easily and accurately.

[0053] The walls 61, 62 of this embodiment are formed to correspond to the entire height range of the inlet 51a. That is, the walls 61, 62 are formed in a height range that covers the entire inlet 51a from the bottom to the top. Therefore, the refrigerant introduced from the inlet 51a and flowing to the -Y side or +Y side is likely to be adjusted in flow rate by hitting the walls 61, 62.

[0054] Second embodiment Fig. 6 is a perspective view showing the internal structure of the first header 110 of the heat exchanger 104 of the second embodiment. Fig. 7 is a side view showing the internal structure of the first header 110. The same reference numerals are used for the same components as those of the heat exchanger 4 of the first embodiment, and the description thereof will be omitted.

[0055] 6 and 7, in the heat exchanger 104, the center of the inlet 51a of the refrigerant port 51 coincides with the center of the spatial flow path 16 when viewed from the X direction. Therefore, the inlet 51a is located at the center of the spatial flow path 16 when viewed from the X direction.

[0056] Instead of the walls 61, 62 (see FIGS. 3 to 5), walls 161-164 (narrowing walls) are formed on the inner surface of the introduction chamber 21. The walls 161-164 are a first wall 161, a second wall 162, a third wall 163, and a fourth wall 164.

[0057] The walls 161, 162 are formed on the bottom surface 21a (lower surface) of the introduction chamber 21. The walls 161, 162 are plate-shaped along a plane intersecting with the Y direction. For example, the walls 161, 162 are rectangular plate-shaped perpendicular to the Y direction. The walls 161, 162 protrude upward from the bottom surface 21a. When viewed from the X direction, the walls 161, 162 are positioned so that at least a portion of them overlaps with the middle portion 24. For example, the walls 161, 162 are positioned so that at least a base end (lower end) of the walls 161, 162 overlaps with the middle portion 24. For example, the height of the walls 161, 162 is lower than half the height of the introduction chamber 21.

[0058] When viewed from the X direction, the first wall portion 161 is located on the -Y side of the inlet 51a of the refrigerant port 51. When viewed from the X direction, the second wall portion 162 is located on the +Y side of the inlet 51a of the refrigerant port 51.

[0059] The walls 163, 164 are formed on the upper surface 21b (top surface) of the introduction chamber 21. The walls 163, 164 are plate-shaped along a plane intersecting with the Y direction. For example, the walls 163, 164 are rectangular plate-shaped perpendicular to the Y direction. The walls 163, 164 protrude downward from the upper surface 21b. When viewed from the X direction, the walls 163, 164 are positioned so that at least a portion of them overlaps with the middle portion 24. For example, the walls 163, 164 are positioned so that at least the base end (upper end) of each of the walls 163, 164 overlaps with the middle portion 24. The height of the walls 163, 164 is lower than half the height dimension of the introduction chamber 21.

[0060] When viewed from the X direction, the third wall portion 163 is located on the -Y side with respect to the inlet 51a of the refrigerant port 51. The third wall portion 163 is located opposite to the first wall portion 161. A tip (lower end) of the third wall portion 163 and a tip (upper end) of the first wall portion 161 are disposed with a vertical gap between them. When viewed from the X direction, the fourth wall portion 164 is located on the +Y side with respect to the inlet 51a of the refrigerant port 51. The fourth wall portion 164 is located opposite the second wall portion 162. A tip (lower end) of the fourth wall portion 164 and a tip (upper end) of the second wall portion 162 are disposed with a vertical gap between them.

[0061] The tips (upper ends) of the wall portions 161, 162 are located higher than the lowermost part of the inlet 51a of the refrigerant port 51. The tips (upper ends) of the wall portions 161, 162 are located lower than the uppermost part of the inlet 51a of the refrigerant port 51. Therefore, the wall portions 161, 162 are formed to correspond to a part of the height range of the inlet 51a.

[0062] The tips (lower ends) of the wall portions 163, 164 are located lower than the uppermost part of the inlet 51a of the refrigerant port 51. The tips (lower ends) of the wall portions 163, 164 are located higher than the lowermost part of the inlet 51a of the refrigerant port 51. Therefore, the wall portions 163, 164 are formed so as to correspond to a part of the height range of the inlet 51a.

[0063] The introduction chamber 21 has an introduction space 21A, a first space 21B, and a second space 21C. The introduction space 21A is a space including the center in the Y direction of the internal space of the introduction chamber 21. The introduction space 21A is partitioned by walls 161-164. The introduction space 21A is a space on the +Y side of the walls 161, 163 and on the -Y side of the walls 162, 164. The first space 21B is a space on the -Y side of the walls 161, 163. The second space 21C is a space on the +Y side of the walls 162, 164.

[0064] The first wall portion 161 and the third wall portion 163 can increase the flow resistance of the refrigerant from the introduction space 21A to the first space 21B. The second wall portion 162 and the fourth wall portion 164 can increase the flow resistance of the refrigerant from the introduction space 21A to the second space 21C. The walls 161 to 164 are disposed close to the outer surface of the refrigerant port 51, thereby restricting the refrigerant port 51 from tilting.

[0065] The flow of the refrigerant will be described in detail below. 6, the refrigerant is introduced into the introduction space 21A of the first header 110 from the inlet 51a of the refrigerant port 51. For example, the refrigerant is a two-phase gas-liquid refrigerant. The refrigerant that has flowed into the introduction space 21A hits the intermediate portion 24 and flows toward the -Y side and the +Y side.

[0066] The refrigerant (liquid) flowing toward the -Y side flows into the first space 21B through the gap between the walls 161, 163. The refrigerant that has flowed into the first space 21B enters the refrigerant flow path 34 of the first heat transfer tube 30A from the first compartment 22. The refrigerant (liquid) flowing toward the +Y side flows into the second space 21C through the gap between the walls 162, 164. The refrigerant that has flowed into the second space 21C enters the refrigerant flow path 34 of the second heat transfer tube 30B from the second compartment 23.

[0067] In the heat exchanger 104 of this embodiment, the walls 161-164 increase the flow resistance of the refrigerant. Therefore, even if the refrigerant port 51 cannot be installed vertically in the introduction space 21A, the refrigerant does not flow biased to the -Y side or +Y side, but flows in both directions. In detail, when the refrigerant tends to flow biased in one direction, the walls 161-164 increase the flow resistance in the direction in which the refrigerant tends to flow more, and the amount of refrigerant flowing in the direction with relatively smaller flow resistance increases. Therefore, compared to a case where there are no walls, the bias between the flow rate of the refrigerant from the introduction space 21A to the first space 21B and the flow rate of the refrigerant from the introduction space 21A to the second space 21C can be reduced. Therefore, the bias in the amount of refrigerant distributed to the multiple heat transfer tubes 30 (30A, 30B) can be reduced. In this way, the heat exchanger 104 can adjust the amount of refrigerant flowing through the heat transfer tubes 30.

[0068] In the heat exchanger 104 of this embodiment, the walls 163 and 164 are formed on the upper surface 21b of the introduction chamber 21, so that not only the refrigerant flowing through the bottom surface 21a but also the flow of the refrigerant near the upper surface 21b can be adjusted. Therefore, the bias between the flow rate of the refrigerant to the first space 21B and the flow rate of the refrigerant to the second space 21C can be reduced. Furthermore, when the refrigerant flowing in from the introduction port 51a of the refrigerant port 51 is a gas-liquid two-phase refrigerant, the refrigerant is stirred in the introduction space 21A and passes through the gaps between the walls 161 and 163 and the gaps between the walls 162 and 164, and is distributed to the first space 21B and the second space 21C, so that the bias between the amount of gas refrigerant and the amount of liquid refrigerant can be suppressed, and the gas-liquid two-phase refrigerant can be optimally divided.

[0069] (Third embodiment) 8 is a side view showing the internal structure of the first header of the heat exchanger 204 of the third embodiment. The same reference numerals are used for the components common to the heat exchangers of the other embodiments, and the description thereof will be omitted.

[0070] As shown in FIG. 8, in the heat exchanger 204, the center of the inlet 51a is located slightly lower than the center of the spatial flow path 16 when viewed from the X direction.

[0071] 5 in that the heat exchanger 204 has a third wall portion 263 in addition to the walls 61 and 62. The heat exchanger 204 may have the same configuration as the heat exchanger 4 shown in FIG.

[0072] The third wall portion 263 is formed on the upper surface 21b (top surface) of the introduction chamber 21. The third wall portion 263 is in the shape of a plate along a plane intersecting with the upper surface 21b. For example, the third wall portion 263 is in the shape of a rectangular plate perpendicular to the upper surface 21b. The wall portion 263 protrudes downward from the upper surface 21b. The third wall portion 263 is formed so as to protrude into the first space 21B. The third wall portion 263 faces the first space 21B. The third wall portion 263 is located on the -Y side compared to the first wall portion 61. The wall portion 263 is located on the -Y side of the +Y side end of the first heat transfer tube 30A. The wall portion 263 is located on the +Y side of the -Y side end of the first heat transfer tube 30A.

[0073] The flow of the refrigerant will be described in detail below. 8, the refrigerant is introduced into the introduction space 21A of the first header from the inlet 51a of the refrigerant port 51. For example, the refrigerant is a two-phase gas-liquid refrigerant. The refrigerant that has flowed into the introduction space 21A hits the intermediate portion 24 and flows toward the -Y side and the +Y side.

[0074] The refrigerant flowing toward the -Y side passes over the first wall portion 61 and flows into the first space 21B. The refrigerant passes from the first space 21B through the first compartment 22 and enters the refrigerant flow path 34 of the first heat transfer tube 30A. At that time, in the first space 21B, the third wall portion 263 increases the flow resistance of the refrigerant, so that more of the refrigerant flows into the +Y side portion of the first heat transfer tube 30A than when there is no wall portion. On the other hand, the refrigerant flowing from the introduction space 21A toward the +Y side passes over the second wall portion 62 and flows into the second space 21C, and enters the refrigerant flow path 34 of the second heat transfer tube 30B from the second compartment 23.

[0075] In the outside air flow path formed between the multiple heat transfer tubes 30, it is assumed that the +Y side is the windward side in the flow direction of the outside air (i.e., the outside air flows from the +Y side to the -Y side). In this case, the first space 21B is a "space on the leeward side in the flow direction of the outside air" with respect to the second space 21C. The +Y side portions of the first space 21B and the second space 21C are windward partial spaces on the windward side of each. The -Y side portions of the first space 21B and the second space 21C are leeward partial spaces on the leeward side of each. The third wall portion 263 increases the flow resistance of the refrigerant from the windward partial space to the leeward partial space in the first space 21B.

[0076] The windward partial space is a partial space located on the upstream side in the flow direction of the outside air in the first space 21B and the second space 21C. For example, the windward partial space of the first space 21B is a portion including the end of the first space 21B on the +Y side. The leeward partial space is a partial space located on the downstream side in the flow direction of the outside air in the first space 21B and the second space 21C. For example, the leeward partial space of the first space 21B is a portion including the end of the first space 21B on the -Y side. The third wall portion 263 divides the first space 21B into the windward partial space and the leeward partial space.

[0077] The refrigerant that flows from the introduction space 21A into the first space 21B tends to gather in the -Y side of the first space 21B due to inertial force, but since the third wall portion 263 is formed in the first space 21B, the refrigerant tends to remain in the +Y side (windward space). Therefore, the amount of refrigerant flowing into the windward portion of the first heat transfer tube 30A can be increased. The refrigerant that flows from the introduction space 21A into the second space 21C tends to gather in the +Y side of the second space 21C due to inertial force. Therefore, the amount of refrigerant flowing into the windward portion of the second heat transfer tube 30B can be increased.

[0078] In the heat exchanger 204 of this embodiment, the flow resistance of the refrigerant is increased by the walls 61, 62. This makes it possible to reduce the bias between the flow rate of the refrigerant from the introduction space 21A to the first space 21B and the flow rate of the refrigerant from the introduction space 21A to the second space 21C. This makes it possible to reduce the bias in the amount of refrigerant distributed to the multiple heat transfer tubes 30 (30A, 30B). In this way, in the heat exchanger 204, the amount of refrigerant flowing through the heat transfer tubes 30 can be adjusted.

[0079] In the heat exchanger 204 of this embodiment, the third wall portion 263 is formed on the upper surface 21b of the introduction chamber 21, and therefore the flow of the refrigerant toward the -Y side near the upper surface 21b can be adjusted. For example, in the heat exchanger 204 shown in FIG. 8, when the +Y side is the windward side, the amount of refrigerant flowing into the windward side of the heat transfer tube 30 can be increased. Since the temperature difference between the outside air and the refrigerant is large on the windward side, the amount of heat exchange can be increased. Therefore, the heat transfer efficiency can be improved.

[0080] (Fourth embodiment) 9 is a side view showing the internal structure of the first header of the heat exchanger 304 of the fourth embodiment. The same reference numerals are used for the components common to the heat exchangers of the other embodiments, and the description thereof will be omitted.

[0081] 9, in the heat exchanger 304, the long axis of the introduction chamber 21 is inclined with respect to the Y direction. More specifically, the long axis of the introduction chamber 21 is inclined so as to descend toward the +Y side. Therefore, the second space 21C is a low-level space located lower than the first space 21B.

[0082] A second wall portion 162 and a third wall portion 163 are formed on the inner surface of the introduction chamber 21. The second wall portion 162 is formed on the bottom surface 21a of the introduction chamber 21. The third wall portion 163 is formed on the upper surface 21b of the introduction chamber 21. The heat exchanger 304 differs from the heat exchanger 104 shown in FIG. 7 in that the first wall portion 161 and the fourth wall portion 164 are not formed.

[0083] The flow of the refrigerant will be described in detail below. 9, the refrigerant is introduced into the introduction space 21A of the first header from the inlet 51a of the refrigerant port 51. For example, the refrigerant is a two-phase gas-liquid refrigerant. The refrigerant that has flowed into the introduction space 21A hits the intermediate portion 24 and flows toward the -Y side and the +Y side.

[0084] The refrigerant flowing toward the -Y side passes through the third wall portion 163 and flows into the first space 21B. The refrigerant in the first space 21B enters the refrigerant flow path 34 of the first heat transfer tube 30A from the first compartment 22. The refrigerant flowing toward the +Y side passes over the second wall portion 162 and flows into the second space 21C. The refrigerant in the second space 21C enters the refrigerant flow path 34 of the second heat transfer tube 30B from the second compartment 23.

[0085] The second wall portion 162 can increase the flow resistance of the refrigerant from the introduction space 21A to the second space 21C (lower space). The third wall portion 163 can increase the flow resistance of the refrigerant from the introduction space 21A to the first space 21B.

[0086] In the heat exchanger 304 of this embodiment, since the introduction chamber 21 is inclined with respect to the Y direction, the refrigerant easily flows into the second space 21C (low space), but since the second wall portion 162 is formed on the bottom surface 21a of the introduction chamber 21, the flow resistance of the refrigerant into the second space 21C (low space) can be increased. Therefore, the bias between the flow rate of the refrigerant from the introduction space 21A to the first space 21B and the flow rate of the refrigerant from the introduction space 21A to the second space 21C can be reduced. Therefore, the bias in the amount of the refrigerant distributed to the multiple heat transfer tubes 30 (30A, 30B) can be reduced. In this way, in the heat exchanger 304, the amount of the refrigerant flowing through the heat transfer tubes 30 can be adjusted.

[0087] Furthermore, when the heat exchanger 304 shown in FIG. 9 is used as a condenser, the refrigerant flows from the heat transfer tube 30 to the refrigerant port 51. For example, the refrigerant is a liquid refrigerant. The refrigerant from the second heat transfer tube 30B flows from the second space 21C through the second wall portion 162 into the introduction space 21A. The refrigerant in the introduction space 21A flows to the inlet 51a of the refrigerant port 51. The refrigerant from the first heat transfer tube 30A flows from the first space 21B through the third wall portion 163 into the introduction space 21A. The refrigerant in the introduction space 21A flows to the inlet 51a of the refrigerant port 51.

[0088] In the heat exchanger 304 of this embodiment, since the introduction chamber 21 is inclined with respect to the Y direction, the refrigerant easily flows from the first space 21B to the introduction space 21A (low space), but the third wall portion 163 can increase the flow resistance of the refrigerant to the introduction space 21A (low space). Therefore, it is possible to reduce the bias between the flow rate of the refrigerant from the first space 21B to the introduction space 21A and the flow rate of the refrigerant from the second space 21C to the introduction space 21A. Therefore, it is possible to reduce the bias in the amount of refrigerant flowing into the introduction space 21A. In this way, in the heat exchanger 304, it is possible to adjust the bias of the refrigerant flowing into the refrigerant port 51.

[0089] Fifth embodiment 10 is an exploded perspective view of the heat exchanger 404. Components common to the heat exchangers of the other embodiments are given the same reference numerals and will not be described.

[0090] As shown in FIG. 10, the heat exchanger 404 includes a first header 410 and a plurality of heat transfer tubes 30. The first header 410 includes a first plate member 411, an intermediate plate member 412, and a second plate member 413. The first plate member 411 is formed with a connection port 50 to which a refrigerant port is connected. The intermediate plate member 412 is formed with a plurality of spatial channels 416 aligned in the Z direction.

[0091] The second plate member 413 has a plurality of outlet ports 41 formed at positions corresponding to the spatial flow paths 416. The plurality of outlet ports 41 are formed aligned in the Z direction. The plurality of heat transfer tubes 30 are connected to the outlet ports 41. The plurality of heat transfer tubes 30 are arranged aligned in the Z direction.

[0092] FIG. 11 is a side view showing the internal structure of the first header 410 of the heat exchanger 404. As shown in FIG. 11, the spatial flow path 416A located at the bottom among the plurality of spatial flow paths 416 has an elliptical introduction chamber 21. The major axis direction of the introduction chamber 21 is parallel to the Y direction.

[0093] A first wall portion 61 and a second wall portion 462 are formed on the inner surface of the introduction chamber 21. When viewed from the X direction, the first wall portion 61 is located on the -Y side of the introduction port 51a of the refrigerant port 51. The second wall portion 462 is located on the +Y side of the introduction port 51a. The second wall portion 462 is formed lower than the first wall portion 61.

[0094] In the heat exchanger 404 of this embodiment, since the second wall portion 462 is lower than the first wall portion 61, the flow resistance of the refrigerant from the introduction space 21A toward the +Y side is lower than the flow resistance of the refrigerant toward the -Y side. Therefore, the flow rate of the refrigerant from the introduction space 21A toward the +Y side is greater than the flow rate of the refrigerant toward the -Y side. In this way, the heat exchanger 404 can adjust the amount of refrigerant flowing through the heat transfer tube 30. For example, when the +Y side is the windward side (when outside air flows from the +Y side to the -Y side), the inflow amount of the refrigerant to the windward side can be increased. Since the temperature difference between the outside air and the refrigerant is large on the windward side, the heat exchange amount can be increased. Therefore, the heat transfer efficiency can be improved.

[0095] Although the heat exchanger and the refrigeration cycle apparatus according to the embodiment have been described above, the configurations of the embodiments are not limited to the above examples. For example, in the heat exchanger 4 shown in Fig. 2, a first header 10 is provided at the end of the heat transfer tube 30 on the +X side. The heat exchanger 4 may be provided with a second header at the end of the heat transfer tube 30 on the -X side. The first header 10 has three intermediate plate members 12 to 14, but the number of intermediate plate members may be one or more (any number equal to or greater than two). That is, the number of intermediate plate members may be one or more.

[0096] The first header 10 shown in Fig. 4 includes a first intermediate plate 12 in which an introduction chamber 21 is formed, and intermediate plates 13, 14 in which sub-chambers 22, 23 are formed. The first header can also be configured without the intermediate plates 13, 14. In this case, the first header is made up of a first plate 11, a first intermediate plate 12, and a second plate 15. The spatial flow path in this example does not have sub-chambers 22, 23 formed therein, and is made up of only the introduction chamber 21.

[0097] In the first header 10 shown in FIG. 4, the walls 61, 62 are formed only in the first intermediate plate 12, but the number of intermediate plates on which the walls are formed is not limited to one and may be multiple (any number equal to or greater than two). For example, the first header may include two first intermediate plate members 12. For example, the first header may have a structure in which a first plate member 11, two first intermediate plate members 12, a second intermediate plate member 13, and a second plate member 15 are stacked in this order. The first header may have a structure in which a first plate member 11, three first intermediate plate members 12, and a second plate member 15 are stacked.

[0098] In the first header 10 shown in FIG. 4, two heat transfer tubes 30 are connected to one spatial flow path 16, but the number of heat transfer tubes connected to one spatial flow path may be one or more (any number greater than or equal to two).

[0099] In heat exchanger 304 shown in FIG. 9, wall portion 162 and wall portion 163 are provided on the inner surface of introduction chamber 21, but wall portion 162 may be the only wall portion formed on the inner surface of introduction chamber 21.

[0100] Although the heat exchangers 4, 104, 204, 304, and 404 described above each have two to four walls, the number of walls is not limited to this. The number of walls may be one or more (any number equal to or greater than two).

[0101] 6 and 7, a third wall portion 163 (narrowing wall portion) facing the first wall portion 161 and a fourth wall portion 164 (narrowing wall portion) facing the second wall portion 162 are formed, but the configuration of the narrowing wall portion is not limited to this. The narrowing wall portion may be formed facing at least one of the first wall portion and the second wall portion.

[0102] In the heat exchanger 204 shown in FIG. 8, it is assumed that the first space 21B is located on the leeward side of the second space 21C, but the second space 21C may be located on the leeward side of the first space 21B. In that case, the third wall portion 263 is formed in the second space 21C. The +Y side portions of the first space 21B and the second space 21C are respectively leeward partial spaces. The -Y side portions of the first space 21B and the second space 21C are respectively windward partial spaces. The third wall portion 263 increases the flow resistance of the refrigerant from the windward partial space to the leeward partial space in the second space 21C.

[0103] 9, it is assumed that the second space 21C is located lower than the first space 21B, but the first space 21B may be located lower than the second space 21C. In that case, the first space 21B becomes the low-level space.

[0104] According to at least one of the embodiments described above, the first wall portion increases the flow resistance of the refrigerant from the inlet space to the first space. The second wall portion increases the flow resistance of the refrigerant from the inlet space to the second space. This makes it possible to adjust the flow rate of the refrigerant flowing through the heat transfer tube.

[0105] 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, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope of the invention and its equivalents described in the claims, as well as in the scope and spirit of the invention. [Explanation of symbols]

[0106] 1...refrigeration cycle device, 4,104,204,304,404...heat exchanger, 10,110,410...first header (header), 11,411...first plate material, 12...first intermediate plate material (intermediate plate material), 13...second intermediate plate material (intermediate plate material), 14...third intermediate plate material (intermediate plate material), 15,413...second plate material, 16,416,416A...space flow path, 21...introduction chamber, 21A...introduction space, 21B ...first space, 21C...second space, 22...first compartment, 23...second compartment, 30...heat transfer tube, 30A...first heat transfer tube, 30B...second heat transfer tube, 34...refrigerant flow path, 51...refrigerant port (refrigerant inlet tube), 51a...inlet, 61, 161...first wall portion, 62, 162, 462...second wall portion, 163...third wall portion (narrowed wall portion), 164...fourth wall portion (narrowed wall portion), 263...third wall portion, 412...intermediate plate material

Claims

1. One or more heat transfer tubes having a refrigerant flow path through which a refrigerant flows; a header connected to at least one end of the plurality of heat transfer tubes, The header may include: a first plate member to which a refrigerant inlet pipe having an inlet port for introducing the refrigerant is connected; One or more intermediate plates having spatial flow paths through which the coolant is introduced; A second plate member to which the heat transfer tube is connected, The spatial flow path is an introduction space into which the refrigerant is introduced from the introduction port; a first space formed adjacent to one side of the introduction space, into which the refrigerant flows from the introduction space; a second space formed adjacent to the other side of the introduction space and into which the refrigerant flows from the introduction space, The intermediate plate member is formed with a first wall portion that increases the flow resistance of the refrigerant from the introduction space to the first space, and a second wall portion that increases the flow resistance of the refrigerant from the introduction space to the second space. heat exchanger.

2. The spatial flow path is an introduction chamber having the introduction space, the first space, and the second space; a first compartment into which the refrigerant is introduced from the introduction chamber; a second compartment into which the refrigerant is introduced from the introduction chamber, The plurality of heat transfer tubes include a first heat transfer tube through which the refrigerant flows out of the first space; a second heat transfer tube that guides the refrigerant from the second space, 2. The heat exchanger of claim 1.

3. the first wall portion and the second wall portion are adjacent to an outer surface of the refrigerant inlet pipe and restrict tilting of the refrigerant inlet pipe.

2. The heat exchanger of claim 1.

4. A narrow wall portion is formed in the intermediate plate material so as to face at least one of the first wall portion and the second wall portion and be spaced apart from each other.

2. The heat exchanger of claim 1.

5. One of the first space and the second space is located on the downwind side of the other space in a direction of outside air flow, A third wall portion is formed on the intermediate plate material, The third wall portion increases a flow resistance of the refrigerant from a windward partial space located upstream in a flow direction of the outside air to a leeward partial space located downstream in the leeward space of the first space or the second space.

2. The heat exchanger of claim 1.

6. One of the first space and the second space is a low space located lower than the other space, the first wall portion or the second wall portion increases a flow resistance of the refrigerant from the introduction space to the low-level space; 2. The heat exchanger of claim 1.

7. The height of the first wall portion and the second wall portion corresponds to the entire height range of the inlet.

2. The heat exchanger of claim 1.

8. A refrigeration cycle device comprising the heat exchanger according to any one of claims 1 to 7.

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