Header distributor and heat exchanger

Abstract

Provided are: a header distributor capable of easily suppressing deterioration in heat exchange efficiency even when the circulation amount of a refrigerant is low; and a heat exchanger.　A header distributor according to the present disclosure is provided to a heat exchanger equipped with a plurality of flat tubes arranged vertically, and has a header pipe connected to one ends of the plurality of flat tubes. The header pipe has formed thereinside: a hollow intermediate chamber; inflow chambers which are provided in a state of being arranged vertically and having the intermediate chamber therebetween, and which have formed therein refrigerant inflow ports; and outflow chambers which are provided in a state of being arranged vertically and having the intermediate chamber therebetween, and which are partitioned from the inflow chambers and are connected to the flat tubes. The intermediate chamber has formed therein: intermediate inflow ports that open upward and downward and connect the inflow chambers to the intermediate chamber; and intermediate outflow ports that open upward and downward and connect the outflow chambers to the intermediate chamber.

Description

Header divider and heat exchanger

[0001] The present disclosure relates to a header flow divider and a heat exchanger.

[0002] Patent Document 1 discloses a heat exchanger that utilizes the inertial force generated by the refrigerant flow velocity to divide the refrigerant into multiple flat tubes arranged vertically. The header manifold of this heat exchanger has a narrow inlet opening between a dividing space formed on the side connected to the flat tubes and an inlet space to increase the refrigerant velocity and improve the inertial force.

[0003] Patent No. 6458432

[0004] The present disclosure provides a header shunt and a heat exchanger that can easily suppress a decrease in heat exchange efficiency even when the refrigerant circulation rate is low.

[0005] This specification includes the entire contents of Japanese Patent Application No. 2024-031089, filed on March 1, 2024. The header diverter in the present disclosure is provided in a heat exchanger including a plurality of flat tubes arranged vertically, and has a header pipe connected to one end of the plurality of flat tubes, wherein the header pipe is formed with a hollow intermediate chamber inside, an inlet chamber arranged vertically across the intermediate chamber, and a refrigerant inlet formed therein, and an outlet chamber arranged vertically across the intermediate chamber, separated from the inlet chamber and connected to the flat tube, and the intermediate chamber has intermediate inlet ports that open upward and downward and connect each of the inlet chambers to the intermediate chamber, and intermediate outlet ports that open upward and downward and connect each of the outlet chambers to the intermediate chamber.

[0006] The heat exchanger of the present disclosure comprises a plurality of flat tubes arranged vertically, and a header distributor having a header pipe connected to one end of the plurality of flat tubes, and inside the header pipe are formed a hollow intermediate chamber, inlet chambers arranged vertically on either side of the intermediate chamber and having a refrigerant inlet formed therein, and outlet chambers arranged vertically on either side of the intermediate chamber, separated from the inlet chamber and connected to the flat tubes, and the intermediate chamber is formed with intermediate inlet ports that open upward and downward and connect each of the inlet chambers to the intermediate chamber, and intermediate outlet ports that open upward and downward and connect each of the outlet chambers to the intermediate chamber.

[0007] The header flow divider and heat exchanger according to the present disclosure can easily ensure flow division performance for the multiple flat tubes arranged vertically, even when the refrigerant circulation rate is low, and therefore can easily suppress a decrease in heat exchange efficiency even when the refrigerant circulation rate is low.

[0008] FIG. 1 is a schematic diagram of a heat exchanger according to a first embodiment; FIG. 2 is a perspective view of a header flow divider; FIG. 3 is a cross-sectional view of the header flow divider; FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 3; FIG. 5 is a side view of an insertion hole as viewed from the right; and FIG. 6 is a cross-sectional view of a header flow divider according to a second embodiment.

[0009] (Knowledge and other information that forms the basis of the present disclosure) At the time the inventors conceived the present disclosure, there was a technology in the technical field of heat exchangers that uses inertial force generated by the refrigerant flow rate to divert liquid refrigerant, which tends to accumulate at the bottom, into multiple flat tubes arranged vertically. However, the inventors discovered a problem: when the refrigerant circulation rate in the refrigeration cycle is low, the refrigerant flow rate is low, so the inertial force tends to be greater than gravity, and liquid refrigerant tends to accumulate at the bottom of the heat exchanger, resulting in a decrease in heat exchange efficiency. The present disclosure therefore provides a header diverter and a heat exchanger that can easily suppress a decrease in heat exchange efficiency even when the refrigerant circulation rate is low.

[0010] Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed description than necessary may be omitted. For example, detailed description of already well-known matters or redundant description of substantially identical configurations may be omitted. This is to avoid unnecessary redundancy in the following description and to facilitate understanding by those skilled in the art. Note that the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter described in the claims.

[0011] (First Embodiment) Hereinafter, a first embodiment will be described with reference to the drawings.

[0012] [1-1. Configuration] [1-1-1. Overall configuration of heat exchanger] Fig. 1 is a schematic diagram of a heat exchanger 1 according to embodiment 1. In the following figures, the left direction of the heat exchanger 1 is indicated by the symbol X, the front direction by the symbol Y, and the upward direction by the symbol Z.

[0013] The heat exchanger 1 is provided in an apparatus using a refrigeration cycle, such as an air conditioner, etc. The heat exchanger 1 is a fin-tube type heat exchanger that exchanges heat between a refrigerant in the refrigeration cycle and air.

[0014] The heat exchanger 1 has a plurality of flat tubes 3 arranged vertically. Each flat tube 3 extends in the left-right direction. The flat tubes 3 are arranged at equal intervals in the up-down direction. The flat tubes 3 are perforated tubes made of a metal such as aluminum, and have a plurality of microchannels 4 formed therein through which a refrigerant flows. In a cross section perpendicular to the left-right direction, the flat tubes 3 have a flat shape in which the dimension in the up-down direction is smaller than the dimension in the front-rear direction.

[0015] The heat exchanger 1 has a gas-side header pipe 5 connected to the right end of each flat tube 3. The gas-side header pipe 5 is a hollow member extending in the vertical direction. The interior of the gas-side header pipe 5 is in communication with the microchannels 4 of each flat tube 3. The gas-side header pipe 5 is also connected to a gas pipe (not shown) through which a gas refrigerant flows in a refrigeration cycle.

[0016] The heat exchanger 1 has metal fins 7 provided between adjacent flat tubes 3 in the vertical direction. The fins 7 are, for example, corrugated fins, and are configured to allow ventilation in the front-rear direction.

[0017] The heat exchanger 1 includes a header diverter 10 connected to the left end of each flat tube 3. The header diverter 10 is connected to a liquid pipe (not shown) through which liquid refrigerant flows in the refrigeration cycle. An expansion valve (not shown) is provided in the liquid pipe. The expansion valve converts the liquid refrigerant flowing through the liquid pipe into a gas-liquid two-layer refrigerant. The header diverter 10 is a device that primarily divertes the gas-liquid two-layer refrigerant that flows in from the liquid pipe when the heat exchanger 1 functions as an evaporator to each of the flat tubes 3 arranged above and below while suppressing variations in dryness fraction.

[0018] [1-1-2. Detailed Configuration of the Header Flow Divider] FIG. 2 is a perspective view of the header flow divider 10. FIG. 3 is a cross-sectional view of the header flow divider 10, showing a cross section of the header flow divider 10 cut along a plane perpendicular to the front-to-rear direction. The header flow divider 10 has a hollow header pipe 20 extending in the vertical direction. In this embodiment, the header pipe 20 has a substantially rectangular parallelepiped shape and includes a first side member 21, a second side member 23, an upper surface member 25, and a lower surface member 27. The first side member 21 is a member that forms the front, rear, and right side of the header pipe 20. The second side member 23 is a plate-like member that forms the left side of the header pipe 20. The upper surface member 25 is a member that forms the upper surface of the header pipe 20. The lower surface member 27 is a member that forms the lower surface of the header pipe 20. The members 21, 23, 25, and 27 that form the outer surfaces of the header pipe 20 are fixed in place with the notches formed in each member fitting together.

[0019] The header pipe 20 has a plurality of insertion holes 22 arranged vertically. The insertion holes 22 are holes for inserting the left ends of the flat tubes 3, and are formed on the right side surface of the header pipe 20. The insertion holes 22 have the same shape as the cross-sectional shape of the flat tubes 3 in a cross section perpendicular to the left-right direction.

[0020] The header flow divider 10 has an upper inlet pipe 31 and a lower inlet pipe 33. The upper inlet pipe 31 is connected to the upper part of the header pipe 20. The upper inlet pipe 31 is a pipe that connects the liquid pipe and the header pipe 20, and extends from the left side surface of the header pipe 20 toward the left side.

[0021] The lower inlet pipe 33 is connected to a lower portion of the header pipe 20. The lower inlet pipe 33 is a pipe that connects the liquid pipe and the header pipe 20, and extends leftward from the left side surface of the header pipe 20. That is, each inlet pipe 31, 33 is connected to the header pipe 20 on the opposite side of the flat tube 3. The upper inlet pipe 31 and the lower inlet pipe 33 in this embodiment each correspond to the "refrigerant inlet pipe" in the present disclosure.

[0022] As shown in FIG. 3, seven hollow chambers 51 to 57 are formed inside the header pipe 20 of this embodiment.

[0023] An intermediate chamber 51 is formed at a height near the middle of the interior of header pipe 20. In this embodiment, intermediate chamber 51 is provided in the center of header pipe 20 in the up-down direction. Also, in this embodiment, intermediate chamber 51 is provided across the entire header pipe 20 in the left-right direction.

[0024] An upper inlet pipe connecting chamber 52 is formed above the intermediate chamber 51. The upper inlet pipe connecting chamber 52 is a chamber that includes the connection portion between the header pipe 20 and the upper inlet pipe 31, and is located at the left end and upper end inside the header pipe 20. A lower inlet pipe connecting chamber 55 is formed below the intermediate chamber 51. The lower inlet pipe connecting chamber 55 is a chamber that includes the connection portion between the header pipe 20 and the lower inlet pipe 33, and is located at the left end and lower end inside the header pipe 20. The inlet pipe connecting chambers 52, 55 are chambers into which refrigerant flows from the inlet pipes 31, 33 when the heat exchanger 1 functions as an evaporator.

[0025] An upper inlet chamber 53 is formed above the intermediate chamber 51 and adjacent to the intermediate chamber 51 and the upper inlet pipe connecting chamber 52. The upper inlet chamber 53 communicates with the upper inlet pipe connecting chamber 52 via an open upper inlet 61. The upper inlet chamber 53 communicates with the intermediate chamber 51 via an upper intermediate inlet 62 that opens upward in the intermediate chamber 51.

[0026] A lower inlet chamber 56 is formed below the intermediate chamber 51, adjacent to the intermediate chamber 51 and the lower inlet pipe connecting chamber 55. The lower inlet chamber 56 communicates with the lower inlet pipe connecting chamber 55 via an open lower inlet 63. The lower inlet chamber 56 communicates with the intermediate chamber 51 via a lower intermediate inlet 64 that opens downward in the intermediate chamber 51. The upper inlet chamber 53 and the lower inlet chamber 56 in this embodiment each correspond to the "inlet chamber" in this disclosure. The upper inlet 61 and the lower inlet 63 in this embodiment correspond to the "refrigerant inlet" in this disclosure. The upper intermediate inlet 62 and the lower intermediate inlet 64 in this embodiment correspond to the "intermediate inlet" in this disclosure.

[0027] The inlet chambers 53, 56 are arranged vertically with the intermediate chamber 51 in between. When the heat exchanger 1 functions as an evaporator, the refrigerant from the inlet pipe connecting chambers 52, 55 flows into the inlet chambers 53, 56 via the inlet ports 61, 63. The refrigerant from the inlet chambers 53, 56 also flows into the intermediate chamber 51 via the intermediate inlet ports 62, 64.

[0028] An upper outlet chamber 54 adjacent to the intermediate chamber 51 and the upper inlet chamber 53 is formed to the right of the upper inlet chamber 53. The upper outlet chamber 54 is a chamber that includes a connection portion between the header pipe 20 and the flat tubes 3. In the present embodiment, the upper outlet chamber 54 is connected to five flat tubes 3. The upper outlet chamber 54 communicates with the intermediate chamber 51 via an upper intermediate outlet port 65 that opens upward in the intermediate chamber 51. In the present embodiment, the upper outlet chamber 54 also communicates with the upper inlet chamber 53 via an open upper return port 66. The upper return port 66 is provided above the upper inlet port 61.

[0029] A lower outlet chamber 57 is formed to the right of the lower inlet chamber 56, adjacent to the intermediate chamber 51 and the lower inlet chamber 56. The lower outlet chamber 57 is a chamber including a connection portion between the header pipe 20 and the flat tubes 3. In the present embodiment, the lower outlet chamber 57 is connected to five flat tubes 3. In other words, the number of flat tubes 3 connected to the lower outlet chamber 57 is the same as the number of flat tubes 3 connected to the upper outlet chamber 54. The lower outlet chamber 57 communicates with the intermediate chamber 51 via a lower intermediate outlet port 67 that opens downward in the intermediate chamber 51. In the present embodiment, the lower outlet chamber 57 communicates with the lower inlet chamber 56 via an open lower return port 68. The lower return port 68 is provided below the lower inlet port 63. The upper outlet chamber 55 and the lower outlet chamber 57 in the present embodiment correspond to the "outlet chambers" in the present disclosure. The upper intermediate outlet 65 and the lower intermediate outlet 67 in this embodiment correspond to the “intermediate outlet” in this disclosure. The upper return port 66 and the lower return port 68 in this embodiment correspond to the “return port” in this disclosure.

[0030] The outlet chambers 54, 57 are arranged vertically with the intermediate chamber 51 in between. When the heat exchanger 1 functions as an evaporator, the refrigerant from the intermediate chamber 51 flows into the outlet chambers 54, 57 via the intermediate outlet ports 65, 67. The refrigerant from the outlet chambers 54, 57 flows into the flat tubes 3 connected to the header pipe 20. In this embodiment, a portion of the refrigerant from the outlet chambers 54, 57 is returned to the inlet chambers 53, 56 via the return ports 66, 68.

[0031] In this embodiment, there is one each of the inlets 61, 63, the intermediate inlets 62, 64, the intermediate outlets 65, 67, and the return ports 66, 68. Furthermore, each of the inlets 61, 63, the intermediate inlets 62, 64, the intermediate outlets 65, 67, and the return ports 66, 68 has a rectangular opening shape.

[0032] In the present embodiment, the chambers 51 to 57 are separated by partition members 41 to 45. Each of the partition members 41 to 45 is a plate-shaped member. The intermediate chamber 51 is formed by partitioning the interior space of the header pipe 20 with an upper partition member 41 and a lower partition member 42. The upper partition member 41 and the lower partition member 42 are each substantially horizontal plate-shaped members that separate the interior of the header pipe 20 into upper and lower sections. The lower partition member 42 is provided at a position spaced downward from the upper partition member 41. In the present embodiment, the distance between the upper partition member 41 and the lower partition member 42, i.e., the vertical dimension of the intermediate chamber 51, is smaller than the vertical distance between the insertion holes 22, i.e., the distance between the flat tubes 3. The upper intermediate inlet 62 and the upper intermediate outlet 65 are formed in the upper partition member 41. The lower intermediate inlet 64 and the lower intermediate outlet 67 are formed in the lower partition member 42 .

[0033] The upper inlet pipe connecting chamber 52 is formed by dividing the internal space of the header pipe 20 with the upper connecting chamber partition member 43. The above-mentioned upper inlet port 61 is formed in the upper connecting chamber partition member 43. The lower inlet pipe connecting chamber 55 is formed by dividing the internal space of the header pipe 20 with the lower connecting chamber partition member 44. The above-mentioned lower inlet port 63 is formed in the lower connecting chamber partition member 44.

[0034] The upper inflow chamber 53 is formed by partitioning the internal space of the header pipe 20 with the upper partition member 41, the upper connecting chamber partition member 43, and the vertical partition member 45. The upper outflow chamber 54 is formed by partitioning the internal space of the header pipe 20 with the upper partition member 41 and the vertical partition member 45. The lower inflow chamber 56 is formed by partitioning the internal space of the header pipe 20 with the lower partition member 42, the lower connecting chamber partition member 44, and the vertical partition member 45. The lower outflow chamber 57 is formed by partitioning the internal space of the header pipe 20 with the lower partition member 42 and the vertical partition member 45.

[0035] The vertical partition member 45 is a member that divides the interior of the header pipe 20 into left and right sections, above the upper partition member 41 and below the lower partition member 42. The return ports 66, 68 described above are formed in the vertical partition member 45. The vertical partition member 45 also has an open communication hole 69 formed at a height between the upper partition member 41 and the lower partition member 42. The intermediate chamber 51, which spans the entire left-right direction of the header pipe 20, communicates with the vertical partition member 45 as a single chamber that straddles the left and right sides via the communication hole 69.

[0036] 4 is a cross-sectional view taken along line IV-IV in FIG. 3, showing the intermediate chamber 51 as viewed from above. As shown in FIG. 4, in plan view, the upper intermediate inlet 62 does not overlap with the lower intermediate inlet 64. In this embodiment, the upper intermediate inlet 62 is located to the right of the lower intermediate inlet 64 as viewed from above. In addition, in this embodiment, the opening area of ​​the upper intermediate inlet 62 is configured to be larger than the opening area of ​​the lower intermediate inlet 64.

[0037] As shown in FIG. 4 , the upper intermediate outlet 65 does not overlap with the lower intermediate outlet 67 in a plan view. In this embodiment, the upper intermediate outlet 65 is located to the left of the lower intermediate outlet 67 in a plan view. That is, in a plan view, the center C1 of the upper intermediate outlet 65 is located to the left of the center C2 of the lower intermediate outlet 67. The centers C1 and C2 are the geometric centers of the intermediate outlets 65 and 67, respectively. In addition, in this embodiment, the opening area of ​​the upper intermediate outlet 65 is configured to be larger than the opening area of ​​the lower intermediate outlet 67.

[0038] Fig. 5 is a side view of the insertion hole 22 as viewed from the right. Note that Fig. 5 shows the microchannels 4 of the flat tubes 3 with imaginary lines. As shown in Figs. 3 to 5 , a depth defining member 46 is provided inside the header pipe 20. In this embodiment, the depth defining member 46 is a plate-shaped member provided inside the header pipe 20 along the right side surface of the header pipe 20. The depth defining member 46 in this embodiment corresponds to the "depth defining portion" in the present disclosure.

[0039] 5 , the depth regulating member 46 closes the portion of the insertion hole 22 where the microchannels 4 of the flat tubes 3 are not arranged, from the inside of the header pipe 20. In detail, the depth regulating member 46 has the same number of openings 60 as the number of insertion holes 22 formed therein, and when viewed in the insertion direction of the flat tubes 3, the openings 60 overlap the portion of the insertion hole 22 where the microchannels 4 of the flat tubes 3 are arranged.

[0040] Therefore, when the flat tubes 3 are inserted into the insertion holes 22, the end faces of the flat tubes 3 come into contact with the depth regulating member 46, thereby positioning the flat tubes 3 relative to the header pipe 20. In other words, the depth regulating member 46 regulates the insertion depth of the flat tubes 3 relative to the header pipe 20. In the present embodiment, the depth regulating member 46 is disposed in close contact with the inner surface of the right side surface of the first side member 21 that constitutes the header pipe 20, and therefore the insertion depth of each flat tube 3 is unified to a depth at which the end faces of the flat tubes 3 are flush with the inner surface of the right side surface of the first side member 21.

[0041] [1-2. Operation] The operation and function of the heat exchanger 1 configured as above will be described below.

[0042] [1-2-1. Function as a Condenser] For example, when the heat exchanger 1 is used as a heat source-side heat exchanger provided in an outdoor unit of an air conditioner, the heat exchanger 1 functions as a condenser when the air conditioner is in heating operation. In this way, when the heat exchanger 1 functions as a condenser, high-temperature, high-pressure gas refrigerant discharged from the compressor flows from the gas pipe 91 into the gas side header pipe 5 of the heat exchanger 1. Because the density of the gas refrigerant that has flowed into the gas side header pipe 5 is low, it spreads vertically inside the gas side header pipe 5 and tends to flow approximately evenly into each of the flat tubes 3.

[0043] The gas refrigerant flowing through each flat tube 3 dissipates heat to the air flowing back and forth through the gaps between the fins 7 and becomes liquid refrigerant. As described above, when the heat exchanger 1 functions as a condenser, the refrigerant flows into each flat tube 3 approximately evenly, facilitating efficient heat exchange between the refrigerant and the air in the heat exchanger 1. The refrigerant that has flowed through each flat tube 3 flows into the liquid pipe via the header pipe 20 and each inlet pipe 31, 33 of the header flow divider 10.

[0044] [1-2-2. Function as an Evaporator] For example, when the heat exchanger 1 is used as a heat source-side heat exchanger provided in an outdoor unit of an air conditioner, the heat exchanger 1 functions as an evaporator when the air conditioner is in cooling operation. When the heat exchanger 1 functions as an evaporator in this way, the refrigerant that has flowed through the liquid pipes flows into the inlet pipes 31, 33 provided in the header flow divider 10 in a state where it has been converted into a gas-liquid two-layer refrigerant by an expansion valve.

[0045] The refrigerant that has passed through each inlet pipe 31, 33 flows into each inlet pipe connecting chamber 52, 55. The refrigerant that has flowed into each inlet pipe connecting chamber 52, 55 flows into each inlet chamber 53, 56 through each inlet 61, 63. The refrigerant then flows into the intermediate chamber 51 through each intermediate inlet 62, 64.

[0046] As described above, the opening area of ​​the upper intermediate inlet 62 and the opening area of ​​the lower intermediate inlet 64 are different from each other. Therefore, the flow speeds of the refrigerant passing through each intermediate inlet 62, 64 tend to be different. In the present embodiment, the opening area of ​​the lower intermediate inlet 64 is smaller than the opening area of ​​the upper intermediate inlet 62. Therefore, the flow speed of the refrigerant passing through the lower intermediate inlet 64 tends to be higher than the flow speed of the refrigerant passing through the upper intermediate inlet 62. Furthermore, since the intermediate inlets 62, 64 are positioned so as not to overlap in a plan view, the refrigerant that flows into the intermediate chamber 51 through one of the intermediate inlets 62, 64 is unlikely to flow out from the other of the intermediate inlets 62, 64.

[0047] The refrigerant that flows into the intermediate chamber 51 through the intermediate inlets 62, 64 flows to the right while being mixed, and passes through the communication hole 69. The refrigerant that passes through the communication hole 69 toward the right flows into the outlet chambers 54, 57 through the intermediate outlets 65, 67.

[0048] At this time, the refrigerant in the intermediate chamber 51 contains a liquid component of the refrigerant that has flowed into the intermediate chamber 51 from the upper inlet chamber 53 and a gas component of the refrigerant that has flowed into the intermediate chamber 51 from the lower inlet chamber 56. As described above, in this embodiment, the flow velocity of the refrigerant flowing into the intermediate chamber 51 from the lower inlet chamber 56 tends to be higher than the flow velocity of the refrigerant flowing into the intermediate chamber 51 from the upper inlet chamber 53. Therefore, the flow of the liquid component of the refrigerant is subjected to dynamic pressure due to the rising of the gas component, which has a low specific gravity, and the liquid component tends to pass upward through the upper intermediate outlet 65 with force.

[0049] Furthermore, because the centers C1, C2 of the intermediate outlets 65, 67 are located at positions that do not overlap with each other in a plan view, the flow rates of the refrigerant passing through the intermediate outlets 65, 67 tend to be different. In the present embodiment, the center C1 of the upper intermediate outlet 65 is located to the left of the center C2 of the lower intermediate outlet 67. As described above, the refrigerant flows from left to right within the intermediate chamber 51. In other words, the center C1 of the upper intermediate outlet 65 is located upstream of the center C2 of the lower intermediate outlet 67 in the intermediate chamber 51. For this reason, the flow rate of the refrigerant passing through the upper intermediate outlet 65 tends to be greater than the flow rate of the refrigerant passing through the lower intermediate outlet 67.

[0050] Furthermore, in the present embodiment, the opening areas of the intermediate outlets 65, 67 are different from each other, and therefore the flow rates of the refrigerant passing through the intermediate outlets 65, 67 tend to be different from each other. In the present embodiment, the opening area of ​​the upper intermediate outlet 65 is larger than the opening area of ​​the lower intermediate outlet 67. Therefore, the flow rate of the refrigerant passing through the upper intermediate outlet 65 tends to be larger than the flow rate of the refrigerant passing through the lower intermediate outlet 67.

[0051] The refrigerant that passes through the upper intermediate outlet 65 flows upward within the upper outlet chamber 54 and flows into each of the flat tubes 3 lined up above and below. At this time, refrigerant with a large flow rate tends to pass through the upper intermediate outlet 65 with force, and the liquid component of the refrigerant resists the action of gravity due to inertia and tends to reach the upper flat tubes 3. For this reason, the refrigerant tends to flow into each of the flat tubes 3 connected to the upper outlet chamber 54 with a uniform dryness.

[0052] The refrigerant that passes through the lower intermediate outlet 67 flows downward within the lower outlet chamber 57 and flows into each of the flat tubes 3 lined up above and below. At this time, the liquid component of the refrigerant tends to reach the lower flat tubes 3 due to the action of gravity. Therefore, the refrigerant tends to flow into each of the flat tubes 3 connected to the lower outlet chamber 57 with a uniform dryness.

[0053] Furthermore, in the present embodiment, the vertical partition member 45 is formed with return ports 66, 68. This facilitates natural circulation, in which a portion of the refrigerant that has flowed through the upper inlet chamber 53, the intermediate chamber 51, and the upper outlet chamber 54 in that order returns to the upper inlet chamber 53. Similarly, this facilitates natural circulation, in which a portion of the refrigerant that has flowed through the lower inlet chamber 56, the intermediate chamber 51, and the lower outlet chamber 57 in that order returns to the lower inlet chamber 56. This natural circulation makes it easier for liquid refrigerant, which tends to accumulate at the bottom of the outlet chambers 54, 57, etc., to flow evenly through the flat tubes 3.

[0054] In particular, in this embodiment, the upper return port 66 is located above the upper inlet 61, and the lower return port 68 is located below the lower inlet 63. Therefore, the refrigerant that flows downward from the upper inlet 61 from the upper inlet pipe connecting chamber 52 and into the upper inlet chamber 53 is unlikely to flow directly into the upper return port 66 and is likely to flow into the upper intermediate inlet 62. Similarly, the refrigerant that flows upward from the lower inlet pipe connecting chamber 55 through the lower inlet 63 and into the lower inlet chamber 56 is unlikely to flow directly into the lower return port 68 and is likely to flow into the lower intermediate inlet 64. This makes it easy to generate natural circulation of the refrigerant and make it easy to flow liquid refrigerant evenly through the flat tubes 3.

[0055] In this way, in this embodiment, it is possible to easily distribute refrigerant of equal dryness to each flat tube 3, not only depending on the flow associated with the circulation of refrigerant in the refrigeration cycle, but also when the amount of refrigerant circulating in the refrigeration cycle is small.

[0056] The refrigerant that flows into each flat tube 3 absorbs heat from the air flowing back and forth through the gaps between the fins 7 as it passes through each flat tube 3, and becomes gas refrigerant. As described above, even when the heat exchanger 1 functions as an evaporator, the refrigerant tends to flow evenly into each flat tube 3. This facilitates efficient heat exchange between the refrigerant and the air in the heat exchanger 1. The refrigerant that has flowed through each flat tube 3 flows into the gas pipe of the refrigeration cycle via the gas-side header pipe 5.

[0057] [1-3. Effects, etc.] As described above, in this embodiment, the header diverter 10 is provided in a heat exchanger 1 having a plurality of flat tubes 3 arranged vertically, and is a header diverter 10 having a header pipe 20 connected to one end of the plurality of flat tubes 3. Inside the header pipe 20, a hollow intermediate chamber 51, inlet chambers 53, 56 arranged vertically on either side of the intermediate chamber 51, and in which each inlet 61, 63 is formed, and outlet chambers 54, 57 arranged vertically on either side of the intermediate chamber 51, separated from the inlet chambers 53, 56 and connected to the flat tubes 3 are formed. In the intermediate chamber 51, intermediate inlet ports 62, 64 that open upward and downward and connect the inlet chambers 53, 56 to the intermediate chamber 51, and intermediate outlet ports 65, 67 that open upward and downward and connect the outlet chambers 54, 57 to the intermediate chamber 51 are formed. As a result, the dynamic pressure of the refrigerant that has flowed from the lower inlet chamber 56 into the intermediate chamber 51 tends to increase the inertial force of the refrigerant flowing out from the intermediate chamber 51 toward the upper outlet chamber 54, making it easy to ensure the flow division performance for the multiple flat tubes 3 arranged vertically even when the refrigerant circulation rate is low. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the efficiency of heat exchange in the heat exchanger 1.

[0058] As in the present embodiment, the inlet chambers 53, 56 and the outlet chambers 54, 57 may be configured to communicate with each other through the open return ports 66, 68. This facilitates natural circulation within the header pipe, in which the refrigerant flows sequentially through the inlet chambers 53, 56, the intermediate chamber 51, and the outlet chambers 54, 57, and then returns to the inlet chambers 53, 56 via the return ports 66, 68, making it easier to separate the refrigerant through natural circulation. This makes it easier to prevent a decrease in the efficiency of heat exchange in the heat exchanger 1, even when the refrigerant circulation rate is low.

[0059] As in the present embodiment, the upper intermediate inlet 62, which opens upward, and the lower intermediate inlet 64, which opens downward, may be configured to have portions that do not overlap with each other in a plan view in the intermediate chamber 51. This prevents refrigerant from one of the inlet chambers 53, 56 from flowing directly into the other through the intermediate chamber 51, making it easier to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easier to prevent a decrease in the heat exchange efficiency in the heat exchanger 1.

[0060] As in the present embodiment, the upper intermediate inlet 62, which opens upward, and the lower intermediate inlet 64, which opens downward, in the intermediate chamber 51 may be configured to have different opening areas. This makes it easy to adjust the flow rate of the refrigerant flowing from each inlet chamber 53, 56 into the intermediate chamber 51 according to the specifications of the entire heat exchanger 1 or the refrigeration cycle in which the heat exchanger 1 is installed, thereby making it easy to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the heat exchange efficiency in the heat exchanger 1.

[0061] As in the present embodiment, the centers C1, C2 of the upper intermediate outlet 65, which opens upward, and the lower intermediate outlet 67, which opens downward, in the intermediate chamber 51 may be configured not to overlap with each other in a plan view. This allows the refrigerant in the intermediate chamber 51 to flow preferentially through one of the intermediate outlets 65, 67 depending on the specifications of the heat exchanger 1 or the refrigeration cycle in which the heat exchanger 1 is installed, making it easy to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the heat exchange efficiency in the heat exchanger 1.

[0062] As in the present embodiment, the upper intermediate outlet 65, which opens upward, and the lower intermediate outlet 67, which opens downward, in the intermediate chamber 51 may be configured to have different opening areas. This makes it easy to adjust the flow rate of the refrigerant flowing from the intermediate chamber 51 into each outlet chamber 54, 57 according to the specifications of the entire heat exchanger 1 or the refrigeration cycle in which the heat exchanger 1 is installed, making it easy to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the heat exchange efficiency in the heat exchanger 1.

[0063] As in the present embodiment, the upper return port 66 located above the intermediate chamber 51 may be located above the upper inlet 61 located above the intermediate chamber 51, and the lower return port 68 located below the intermediate chamber 51 may be located below the lower inlet 63 located below the intermediate chamber 51. This prevents the refrigerant that flows into the inlet chambers 53, 56 from the inlets 61, 63 from flowing directly into the outlet chambers 54, 57 via the return ports 66, 68, making it easier to separate the refrigerant by natural circulation. Therefore, even when the refrigerant circulation rate is low, it is easy to prevent a decrease in the heat exchange efficiency in the heat exchanger 1.

[0064] As in the present embodiment, the vertical dimension of the intermediate chamber 51 may be configured to be equal to or less than the vertical spacing between the flat tubes 3. This makes it easy to arrange the intermediate chamber 51 at a height between vertically adjacent flat tubes 3, and makes it easy to configure the flat tubes 3 so that they are not directly connected to the intermediate chamber 51, making it easy to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the efficiency of heat exchange in the heat exchanger 1.

[0065] As in the present embodiment, the header pipe 20 may be provided with a depth regulating member 46 that regulates the insertion depth of the flat tubes 3 into the outflow chambers 54, 57. This makes it easier to insert each flat tube 3 into the inflow chambers 53, 56 at the specified depth, making it easier to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the heat exchange efficiency in the heat exchanger 1.

[0066] In this embodiment, the heat exchanger 1 comprises a plurality of flat tubes 3 arranged vertically, and a header distributor 10 having a header pipe 20 connected to one end of the plurality of flat tubes 3. Inside the header pipe 20, there are formed a hollow intermediate chamber 51, inlet chambers 53, 56 arranged vertically on either side of the intermediate chamber 51 and having inlets 61, 63 formed therein, and outlet chambers 54, 57 arranged vertically on either side of the intermediate chamber 51, separated from the inlet chambers 53, 56 and connected to the flat tubes 3. The intermediate chamber 51 is formed with intermediate inlet ports 62, 64 that open upward and downward and connect each of the inlet chambers 53, 56 to the intermediate chamber 51, and intermediate outlet ports 65, 67 that open upward and downward and connect each of the outlet chambers 54, 57 to the intermediate chamber 51. As a result, the dynamic pressure of the refrigerant that has flowed from the lower inlet chamber 56 into the intermediate chamber 51 tends to increase the inertial force of the refrigerant flowing out from the intermediate chamber 51 toward the upper outlet chamber 54, making it easy to ensure the flow division performance for the multiple flat tubes 3 arranged vertically even when the refrigerant circulation rate is low. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the efficiency of heat exchange in the heat exchanger 1.

[0067] Second Embodiment Hereinafter, a second embodiment will be described, focusing only on the differences from the first embodiment.

[0068] [2-1. Configuration] FIG. 6 is a cross-sectional view of a header flow distributor 110 according to the second embodiment, showing a cross section corresponding to FIG. 3 . As shown in FIG. 6 , the intermediate chamber 151 according to the second embodiment differs from the intermediate chamber 51 according to the first embodiment in that the vertical dimension on the left side is larger and the vertical dimension on the right side is smaller. That is, the portion of the intermediate chamber 151 between the upper outlet chamber 54 and the lower outlet chamber 57 has a smaller vertical dimension than the portion between the upper inlet chamber 53 and the lower inlet chamber 56. In this embodiment, the upper partition member 141 is disposed with a downward slope to the right, and the lower partition member 142 is disposed with an upward slope to the right. Furthermore, the vertical dimension of the right end of the intermediate chamber 151, i.e., the end on the flat tube 3 side, is smaller than the spacing between the flat tubes 3.

[0069] As shown in FIG. 6 , in this embodiment, the cross-sectional areas of the upper inlet pipe 131 and the lower inlet pipe 133 are different from each other. Specifically, the cross-sectional area of ​​the lower inlet pipe 133 is configured to be smaller than the cross-sectional area of ​​the upper inlet pipe 131. In this embodiment, the opening area of ​​the upper inlet 161 is different from the opening area of ​​the lower inlet 163. Specifically, the opening area of ​​the lower inlet 163 is configured to be smaller than the opening area of ​​the upper inlet 161. The upper inlet pipe 131 and the lower inlet pipe 133 in this embodiment correspond to the "refrigerant inlet pipe" in this disclosure. The upper inlet 161 and the lower inlet 163 in this embodiment correspond to the "refrigerant inlet" in this disclosure.

[0070] Furthermore, in this embodiment, the number of flat tubes 3 connected to the upper outflow chamber 54 is smaller than the number of flat tubes 3 connected to the lower outflow chamber 57 .

[0071] [2-2. Operation] The following describes the operation of the heat exchanger 1 of the second embodiment when it functions as an evaporator. In the second embodiment, the cross-sectional areas of the inlet pipes 131 and 133 and the opening areas of the inlets 161 and 163 are different from each other, so the flow rate and flow velocity of the refrigerant flowing into the inlet chambers 53 and 56 tend to be different from each other. In the present embodiment, the cross-sectional areas and opening areas of the lower inlet pipe 133 and the lower inlet 163 are small, so the flow velocity of the refrigerant flowing into the lower inlet chamber 56 tends to be high. Therefore, the inertial force of the refrigerant flowing from the lower inlet pipe connecting chamber 55 into the lower inlet chamber 56 tends to be high, and the liquid component of the refrigerant tends to flow into the intermediate chamber 151 without stagnating in the lower inlet chamber 56.

[0072] Thereafter, similar to the first embodiment, the refrigerant flows from the intermediate chamber 151 into the outflow chambers 54, 57 via the intermediate outlets 65, 67, and is divided and flows into the flat tubes 3. In the present embodiment, the number of flat tubes 3 connected to the upper outflow chamber 54 is smaller than the number of flat tubes 3 connected to the lower outflow chamber 57, and therefore, it is easy to divide the flow against gravity in the upper outflow chamber 54. Therefore, it is easy to divide refrigerant with a uniform degree of heating into the flat tubes 3.

[0073] [2-3. Effects, etc.] As described above, in this embodiment, the number of flat tubes 3 connected to the upper outflow chamber 54 may be equal to or less than the number of flat tubes 3 connected to the lower outflow chamber 57. This makes it easier to increase the number of flat tubes 3 connected to the lower outflow chamber 57, where flow division is easy, and makes it easier to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the efficiency of heat exchange in the heat exchanger 1.

[0074] The portion of the intermediate chamber 151 between the outflow chambers 54, 57 may be configured to have a smaller vertical dimension than the portion of the intermediate chamber 151 between the inflow chambers 53, 56. This makes it easier to arrange the intermediate chamber 151 at the height between the vertically adjacent flat tubes 3 on the outflow chamber 54, 57 side, and makes it easier to configure the flat tubes 3 so that they are not directly connected to the intermediate chamber 151, making it easier to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in the efficiency of heat exchange in the heat exchanger 1.

[0075] As in the present embodiment, the opening area of ​​the upper inlet 61 may be configured to be different from the opening area of ​​the lower inlet 63. This allows the ratio and flow velocity of the refrigerant flowing into each inlet chamber 53, 56 to be adjusted, making it easier to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easy to prevent a decrease in the heat exchange efficiency in the heat exchanger.

[0076] As in this embodiment, the inlet chambers 53, 56 may communicate with the inlet pipes 131, 133 via the inlets 161, 163, respectively, and the inlet pipes 131, 133 may have different cross-sectional areas. This allows the ratio and flow velocity of the refrigerant flowing into the inlet chambers 53, 56 to be adjusted, making it easier to ensure flow separation performance. Therefore, even when the refrigerant circulation rate is low, it is easy to prevent a decrease in the heat exchange efficiency of the heat exchanger 1.

[0077] (Other Embodiments) As described above, Embodiments 1 and 2 have been described as examples of the technology disclosed in this application. However, the technology in this disclosure is not limited to these and can be applied to embodiments in which modifications, substitutions, additions, omissions, etc. are made. Furthermore, it is also possible to combine the components described in Embodiments 1 and 2 above to create new embodiments. Therefore, other embodiments will be described below as examples.

[0078] In the above embodiment, the upper intermediate inlet 62 does not overlap with the lower intermediate inlet 64 in a plan view, but the present disclosure is not limited to this. Each intermediate inlet 62, 64 only needs to be able to prevent the refrigerant that has flowed into the intermediate chamber 51 from one of the intermediate inlets 62, 64 from directly flowing out of the intermediate chamber 51 from the other of the intermediate inlets 62, 64. Therefore, it is sufficient that the upper intermediate inlet 62 and the lower intermediate inlet 64 have at least a portion that does not overlap with each other.

[0079] In the above embodiment, the number of upper intermediate inlets 62 and the number of lower intermediate inlets 64 are each described as being one, but this is merely an example. The number of upper intermediate inlets 62 and the number of lower intermediate inlets 64 may each be two or more. The size relationship and positional relationship of the opening areas between the intermediate inlets 62, 64 or between the intermediate outlets 65, 67 described in the above embodiment are merely examples and may be changed depending on the configuration of the refrigeration cycle in which the heat exchanger 1 is installed.

[0080] Furthermore, the depth-regulating member 46 is not limited to that described in the above embodiment. For example, two or more depth-regulating members 46 may be provided in the header pipe 20. Furthermore, the depth-regulating members 46 may be configured to regulate the insertion depth of each flat tube 3 to a different insertion depth. Furthermore, the depth-regulating members 46 do not need to be separate members, but may be integrated with each part of the header pipe 20.

[0081] It should be noted that the above-described embodiments are intended to illustrate the technology of the present disclosure, and various modifications, substitutions, additions, omissions, etc. may be made within the scope of the claims or their equivalents.

[0082] (Additional Notes) The above embodiments disclose the following technologies: (Technology 1) A header flow divider that is provided in a heat exchanger including a plurality of flat tubes arranged vertically, and that has a header pipe connected to one end of the plurality of flat tubes, wherein the header pipe is formed with a hollow intermediate chamber inside, inlet chambers arranged vertically across the intermediate chamber and each having a refrigerant inlet, and outlet chambers arranged vertically across the intermediate chamber, separated from the inlet chamber and connected to the flat tubes, and the intermediate chamber is formed with intermediate inlet ports that open upward and downward and connect each of the inlet chambers to the intermediate chamber, and intermediate outlet ports that open upward and downward and connect each of the outlet chambers to the intermediate chamber. This makes it easier for the dynamic pressure of the refrigerant flowing into the intermediate chamber from the inlet chamber below the intermediate chamber to increase the inertial force of the refrigerant flowing out from the intermediate chamber to the outlet chamber above, making it easier to ensure flow separation performance for the multiple flat tubes arranged vertically even when the refrigerant circulation rate is low, and therefore easier to suppress a decrease in heat exchange efficiency in the heat exchanger even when the refrigerant circulation rate is low.

[0083] (Technology 2) In the header diverter according to Technology 1, the inlet chamber and the outlet chamber are connected by an open return port. This facilitates natural circulation within the header pipe, where the refrigerant flows sequentially through the outlet chamber, intermediate chamber, and outlet chamber, and then returns to the inlet chamber via the return port. This facilitates diverting the refrigerant through natural circulation. This makes it easier to prevent a decrease in heat exchange efficiency in the heat exchanger, even when the refrigerant circulation rate is low.

[0084] (Technology 3) In the header divider according to Technology 1 or 2, the intermediate inlet opening upward and the intermediate inlet opening downward in the intermediate chamber have portions that do not overlap with each other in a plan view. This prevents refrigerant from one inlet chamber from flowing directly into the other inlet chamber via the intermediate chamber, making it easier to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easier to prevent a decrease in heat exchange efficiency in the heat exchanger.

[0085] (Technology 4) The header flow divider according to any one of Technologies 1 to 3, wherein the intermediate inlet opening upward and the intermediate inlet opening downward in the intermediate chamber have different opening areas. This makes it easy to adjust the flow rate of the refrigerant flowing from each inlet chamber into the intermediate chamber according to the specifications of the entire heat exchanger or the refrigeration cycle in which the heat exchanger is installed, thereby ensuring good flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0086] (Technology 5) The header flow divider according to any one of Technologies 1 to 4, wherein the centers of the intermediate outlets that open upward and the intermediate outlets that open downward in the intermediate chamber do not overlap each other in a plan view. This allows refrigerant in the intermediate chamber to flow preferentially through one of the intermediate outlets depending on the specifications of the entire heat exchanger or the refrigeration cycle in which the heat exchanger is installed, making it easy to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0087] (Technology 6) The header flow divider according to any one of Technologies 1 to 6, wherein the intermediate outlet opening upward and the intermediate outlet opening downward in the intermediate chamber have different opening areas. This makes it easy to adjust the flow rate of refrigerant flowing from the intermediate chamber into each outlet chamber according to the specifications of the entire heat exchanger or the refrigeration cycle in which the heat exchanger is installed, thereby making it easy to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0088] (Technology 7) A header diverter according to any one of Technologies 1 to 6, wherein the number of flat tubes connected to the outlet chamber located above the intermediate chamber is equal to or less than the number of flat tubes connected to the outlet chamber located below the intermediate chamber. This makes it easier to increase the number of flat tubes connected to the outlet chamber below the intermediate chamber, where diverting is easier, and makes it easier to ensure diverting performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0089] (Technology 8) The header diverter according to any one of Technologies 2 to 7, wherein the return port located on the upper side of the intermediate chamber is located above the refrigerant inlet located on the upper side of the intermediate chamber, and the return port located on the lower side of the intermediate chamber is located below the refrigerant inlet located on the lower side of the intermediate chamber. This prevents the refrigerant that flows into the inlet chamber from the refrigerant inlet from directly flowing out into the outlet chamber through the return port, making it easier to divert the refrigerant by natural circulation. Therefore, even when the refrigerant circulation rate is low, it is easy to prevent a decrease in heat exchange efficiency in the heat exchanger.

[0090] (Technology 9) The header flow divider according to any one of Technologies 1 to 8, wherein the vertical dimension of the intermediate chamber is equal to or less than the vertical spacing between the flat tubes. This makes it easy to arrange the intermediate chamber at the height between vertically adjacent flat tubes, and it is easy to configure the flat tubes so that they are not directly connected to the intermediate chamber, making it easy to ensure flow dividing performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0091] (Technology 10) A header diverter according to any one of Technologies 1 to 9, wherein the portions of the intermediate chamber between the outflow chambers have a vertical dimension smaller than the portions of the intermediate chamber between the inflow chambers. This makes it easy to arrange the intermediate chambers at a height between vertically adjacent flat tubes on the outflow chamber side, and makes it easy to configure the flat tubes so that they are not directly connected to the intermediate chambers, making it easy to ensure flow diverting performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0092] (Technology 11) The header flow divider according to any one of Technologies 1 to 10, wherein the opening area of ​​the refrigerant inlet located on the upper side of the intermediate chamber is different from the opening area of ​​the refrigerant inlet located on the lower side of the intermediate chamber. This makes it possible to adjust the ratio of the flow rates of the refrigerant flowing into each inlet chamber, thereby making it easier to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0093] (Technology 12) The header divider according to any one of Technologies 1 to 11, wherein each of the inlet chambers communicates with a refrigerant inlet pipe via the refrigerant inlet port, and the refrigerant inlet pipes have different cross-sectional areas. This allows the ratio of the flow rates of the refrigerant flowing into each inlet chamber to be adjusted, making it easier to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easier to prevent a decrease in heat exchange efficiency in the heat exchanger.

[0094] (Technology 13) The header diverter according to any one of Technologies 1 to 13, wherein the header pipe is provided with a depth defining portion that defines the insertion depth of the flat tubes into the outlet chamber. This makes it easier to insert each flat tube into the inlet chamber at the defined depth, thereby ensuring flow diverting performance. Therefore, even when the refrigerant circulation rate is low, it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger.

[0095] (Technology 14) A heat exchanger including a plurality of flat tubes arranged vertically and a header divider having a header pipe connected to one end of the plurality of flat tubes, wherein the header pipe has formed therein a hollow intermediate chamber, inlet chambers arranged vertically on either side of the intermediate chamber and each having a refrigerant inlet, and outlet chambers arranged vertically on either side of the intermediate chamber and separated from the inlet chamber and connected to the flat tubes, wherein the intermediate chambers have intermediate inlet ports that open upward and downward and communicate each of the inlet chambers with the intermediate chamber, and intermediate outlet ports that open upward and downward and communicate each of the outlet chambers with the intermediate chamber. This makes it easy to ensure flow division performance for the plurality of flat tubes arranged vertically, even when the refrigerant circulation rate is low. Therefore, even when the amount of refrigerant circulating is low, it is easy to prevent a decrease in the efficiency of heat exchange in the heat exchanger.

[0096] The present disclosure is applicable to header flow dividers and heat exchangers, specifically to header flow dividers provided in heat exchangers used in refrigeration cycles of air conditioners, refrigeration devices, refrigerated showcases, etc., or to the heat exchangers themselves.

[0097] REFERENCE SIGNS LIST 1 Heat exchanger 3 Flat tube 4 Microchannel 5 Gas side header pipe 7 Fin 10 Header flow divider 20 Header pipe 21 First side member 22 Insertion hole 23 Second side member 25 Upper surface member 27 Lower surface member 31 Upper inlet pipe (refrigerant inlet pipe) 33 Lower inlet pipe (refrigerant inlet pipe) 41 Upper partition member 42 Lower partition member 43 Upper connecting chamber partition member 44 Lower connecting chamber partition member 45 Vertical partition member 46 Depth setting member (depth setting portion) 51 Intermediate chamber 52 Upper inlet pipe connecting chamber 53 Upper inlet chamber (inlet chamber) 54 Upper outlet chamber (outlet chamber) 55 Lower inlet pipe connecting chamber 56 Lower inlet chamber (inlet chamber) 57 Lower outlet chamber (outlet chamber) 60 Opening 61 Upper inlet (refrigerant inlet) 62 Upper intermediate inlet (intermediate inlet) 63 Lower inlet (refrigerant inlet) 64 Lower intermediate inlet (intermediate inlet) 65 Upper intermediate outlet (intermediate outlet) 66 Upper return port (return port) 67 Lower intermediate outlet (intermediate outlet) 68 Lower return port (return port) 69 Communication hole 110 Header flow divider 131 Upper inlet pipe (refrigerant inlet pipe) 133 Lower inlet pipe (refrigerant inlet pipe) 141 Upper partition member 142 Lower partition member 151 Intermediate chamber 161 Upper inlet (refrigerant inlet) 163 Lower inlet (refrigerant inlet)

Claims

1. A header flow divider that is installed in a heat exchanger having a plurality of flat tubes arranged vertically, and has a header pipe connected to one end of the plurality of flat tubes, wherein the header pipe is formed with the following inside: a hollow intermediate chamber; inlet chambers arranged vertically with the intermediate chamber between them, each having a refrigerant inlet; and outlet chambers arranged vertically with the intermediate chamber between them, separated from the inlet chamber and connected to the flat tubes, and the intermediate chamber is formed with intermediate inlet ports that open upward and downward and connect each of the inlet chambers to the intermediate chamber, and intermediate outlet ports that open upward and downward and connect each of the outlet chambers to the intermediate chamber.

2. A header flow divider as claimed in claim 1, wherein the inlet chamber and the outlet chamber are connected by an open return port.

3. A header flow divider according to claim 1, wherein in the intermediate chamber, the intermediate inlet opening upward and the intermediate inlet opening downward have portions that do not overlap with each other in a plan view.

4. The header flow divider according to claim 1, wherein in the intermediate chamber, the intermediate inlet opening upward and the intermediate inlet opening downward have mutually different opening areas.

5. A header flow distributor according to claim 1, wherein in the intermediate chamber, the centers of the intermediate outlets that open upward and the intermediate outlets that open downward do not overlap with each other in a plan view.

6. The header flow divider according to claim 1, wherein the intermediate outlet opening upward and the intermediate outlet opening downward in the intermediate chamber have mutually different opening areas.

7. A header flow distributor as described in claim 1, wherein the number of flat tubes connected to the outlet chamber located above the intermediate chamber is equal to or less than the number of flat tubes connected to the outlet chamber located below the intermediate chamber.

8. A header flow divider as described in claim 2, wherein the return port located on the upper side of the intermediate chamber is located higher than the refrigerant inlet located on the upper side of the intermediate chamber, and the return port located on the lower side of the intermediate chamber is located lower than the refrigerant inlet located on the lower side of the intermediate chamber.

9. A header flow divider according to claim 1, wherein the vertical dimension of the intermediate chamber is equal to or less than the vertical spacing between the flat tubes.

10. A header flow divider according to claim 1, wherein the portions of the intermediate chamber between the outlet chambers have a smaller vertical dimension than the portions of the intermediate chamber between the inlet chambers.

11. The header flow divider according to claim 1, wherein the opening area of ​​the refrigerant inlet located on the upper side of the intermediate chamber is different from the opening area of ​​the refrigerant inlet located on the lower side of the intermediate chamber.

12. A header flow divider according to claim 1, wherein each of the inlet chambers communicates with a refrigerant inlet pipe via the refrigerant inlet port, and each of the refrigerant inlet pipes has a different cross-sectional area from each other.

13. The header flow divider according to claim 1, wherein the header pipe is provided with a depth determining portion that determines the insertion depth of the plurality of flat tubes into the outflow chamber.

14. A heat exchanger comprising: a plurality of flat tubes arranged vertically; and a header flow divider having a header pipe connected to one ends of the plurality of flat tubes, wherein the header pipe is formed with: a hollow intermediate chamber; inlet chambers arranged vertically with the intermediate chamber in between, and each having a refrigerant inlet; and outlet chambers arranged vertically with the intermediate chamber in between, separated from the inlet chamber and connected to the flat tubes; and the intermediate chamber is formed with intermediate inlet ports that open upward and downward and connect each of the inlet chambers to the intermediate chamber, and intermediate outlet ports that open upward and downward and connect each of the outlet chambers to the intermediate chamber.

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