Header flow divider and heat exchanger

Abstract

To provide a header flow divider which is easy to suppress lowering of heat exchange efficiency even when a circulation amount of a refrigerant is low, and to provide a heat exchanger.SOLUTION: A header flow divider is provided at a heat exchanger which includes a plurality of flat tubes arranged vertically, and includes a header pipe connected to one end part of the plurality of flat tubes. Inside the header pipe, a hollow intermediate chamber, inflow chambers which are provided being arranged vertically by sandwiching the intermediate chamber and in which a refrigerant inflow port is formed, and outflow chambers which are provided being arranged vertically by sandwiching the intermediate chamber and partitioned from the inflow chamber and which are connected to the flat tubes are formed. In the intermediate chamber, an intermediate inflow port opening upward and downward and communicating each inflow chamber with the intermediate chamber, and an intermediate outflow port opening upward and downward and communicating each outflow chamber and the intermediate chamber are formed.SELECTED DRAWING: Figure 3

Description

[Technical Field]

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

[0002] Patent Document 1 discloses a heat exchanger that uses 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 the dividing space formed on the side connected to the flat tubes and the introduction space to increase the refrigerant velocity and improve the inertial force. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 6458432 Summary of the Invention [Problem to be solved by the invention]

[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 amount of refrigerant circulating is low. [Means for solving the problem]

[0005] The header diverter of the present disclosure is a header diverter that is provided 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, and inside the header pipe are formed: a hollow intermediate chamber; inlet chambers arranged vertically on either side of the intermediate chamber, each having a refrigerant inlet; and outlet chambers arranged vertically on either side of the intermediate chamber, separated from the inlet chamber and connected to the flat tubes.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.

[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. [Effects of the Invention]

[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. [Brief explanation of the drawings]

[0008] [Figure 1] Schematic diagram of a heat exchanger according to embodiment 1 [Figure 2] Perspective view of header flow divider [Figure 3] Cross-sectional view of header flow divider [Figure 4] IV-IV cross section in Figure 3 [Figure 5] Side view of the insertion hole from the right [Figure 6] 10 is a cross-sectional view of a header flow divider according to a second embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0009] (Findings that formed the basis of this disclosure) At the time the inventors came up with the idea for this disclosure, there was a technology in the technical field of heat exchangers that utilized the inertial force generated by the flow velocity of the refrigerant to divert liquid refrigerant, which tends to accumulate at the bottom, into multiple flat tubes arranged above and below. However, the inventors discovered a problem in that when the amount of refrigerant circulating in the refrigeration cycle is small, the flow velocity of the refrigerant is small, so the inertial force tends to be less than gravity, and liquid refrigerant tends to accumulate at the bottom of the heat exchanger, reducing the efficiency of heat exchange.In order to solve this problem, the inventors came up with the subject matter of the present disclosure. Therefore, 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.

[0010] Hereinafter, embodiments will be described in detail with reference to the drawings. However, unnecessary detailed description may be omitted. For example, detailed description of well-known matters or redundant description of substantially the same configuration may be omitted. This is to avoid unnecessary redundancy in the following description and to facilitate understanding by those skilled in the art. 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] (Embodiment 1) Hereinafter, the first embodiment will be described with reference to the drawings.

[0012] [1-1.Configuration] [1-1-1. Overall configuration of heat exchanger] 1 is a schematic diagram of a heat exchanger 1 according to embodiment 1. In the following drawings, 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 equipment that uses 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-to-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 the 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 is equipped with 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 two-layer gas-liquid refrigerant. The header diverter 10 is a device that mainly divertes the two-layer gas-liquid 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 header shunt] FIG. 2 is a perspective view of the header flow distributor 10. FIG. 3 is a cross-sectional view of the header flow distributor 10, showing a cross section of the header flow distributor 10 cut along a plane perpendicular to the front-to-rear direction. The header flow distributor 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 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 the lower part 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 tubes 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 the header pipe 20. In this embodiment, the intermediate chamber 51 is provided in the center of the header pipe 20 in the up-down direction. Also, in this embodiment, the 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 the 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 the 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 inflow chamber 56 is formed below the intermediate chamber 51, adjacent to the intermediate chamber 51 and the lower inflow pipe connecting chamber 55. The lower inflow chamber 56 communicates with the lower inflow pipe connecting chamber 55 via an open lower inflow port 63. The lower inflow chamber 56 communicates with the intermediate chamber 51 via a lower intermediate inflow port 64 that opens downward in the intermediate chamber 51. The upper inflow chamber 53 and the lower inflow chamber 56 in this embodiment each correspond to the "inflow chamber" in this disclosure. The upper inflow port 61 and the lower inflow port 63 in this embodiment correspond to the "refrigerant inflow port" in this disclosure. The upper intermediate inflow port 62 and the lower intermediate inflow port 64 in this embodiment correspond to the "intermediate inflow port" 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 is formed to the right of the upper inlet chamber 53, adjacent to the intermediate chamber 51 and 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 this 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 this 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 this 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 this 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 this embodiment correspond to the "outlet chambers" in this 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 in the intermediate chamber 51 flows into the outlet chambers 54, 57 through the intermediate outlet ports 65, 67. The refrigerant in 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 in the outlet chambers 54, 57 is returned to the inlet chambers 53, 56 through 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 this embodiment, the chambers 51 to 57 are separated by the partition members 41 to 45. The partition members 41 to 45 are plate-shaped members. The intermediate chamber 51 is formed by dividing the interior space of the header pipe 20 with the upper partition member 41 and the 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 this 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 inflow pipe connecting chamber 52 is formed by partitioning the internal space of the header pipe 20 with the upper connecting chamber partition member 43. The above-mentioned upper inflow port 61 is formed in the upper connecting chamber partition member 43. The lower inflow pipe connecting chamber 55 is formed by partitioning the internal space of the header pipe 20 with the lower connecting chamber partition member 44. The above-mentioned lower inflow 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 via the communication hole 69 as a single chamber that straddles the vertical partition member 45 on the left and right.

[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, the upper intermediate inlet 62 does not overlap with the lower intermediate inlet 64 in a plan view. In this embodiment, the upper intermediate inlet 62 is located to the right of the lower intermediate inlet 64 in a plan view. 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 in Fig. 5, the microchannels 4 of the flat tubes 3 are shown by imaginary lines. As shown in Figs. 3 to 5, a depth-regulating member 46 is provided inside the header pipe 20. In this embodiment, the depth-regulating 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-regulating member 46 in this embodiment corresponds to the "depth-regulating portion" in the present disclosure.

[0039] 5, the depth-regulating member 46 blocks the portions of the insertion holes 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 portions of the insertion holes 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 surface 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 surface 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. Condenser action] 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. When the heat exchanger 1 functions as a condenser in this way, 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. Evaporator function] 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 pipe flows into the inlet pipes 31, 33 provided in the header shunt 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 the intermediate inlets 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 both 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. For this reason, 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, since 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, and therefore the flow rates of the refrigerant passing through the intermediate outlets 65, 67 tend to be different. 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 has passed 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 this 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 pipe connecting chamber 52 through the upper inlet 61 and into the upper inlet chamber 53 is unlikely to flow directly to the upper return port 66 and is likely to flow to 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 to the lower return port 68 and is likely to flow to 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 makes it easy for the refrigerant and air to exchange heat efficiently 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, and inside the header pipe 20 are formed 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, and the intermediate chamber 51 is formed with intermediate inlet ports 62, 64 that open upward and downward and connect each inlet chamber 53, 56 to the intermediate chamber 51, and intermediate outlet ports 65, 67 that open upward and downward and connect each outlet chamber 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.

[0058] As in this embodiment, the inflow chambers 53, 56 and the outflow chambers 54, 57 may be configured to communicate with each other through open return ports 66, 68, respectively. This facilitates natural circulation within the header pipe, where the refrigerant flows in order 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 amount of refrigerant circulating is low.

[0059] As in this embodiment, in the intermediate chamber 51, the upper intermediate inlet 62 that opens upward and the lower intermediate inlet 64 that opens downward may be configured to have portions that do not overlap with each other in a planar view. This prevents the refrigerant from one of the inlet chambers 53, 56 from flowing directly into the other chamber via 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 prevent a decrease in the efficiency of heat exchange in the heat exchanger 1.

[0060] As in this embodiment, in the intermediate chamber 51, the upper intermediate inlet 62 that opens upward and the lower intermediate inlet 64 that opens downward 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, making it easy 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 1.

[0061] As in this embodiment, in the intermediate chamber 51, the upper intermediate outlet 65 that opens upward and the lower intermediate outlet 67 that opens downward may be configured so that their centers C1, C2 do not overlap with each other in a planar 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 prevent a decrease in the heat exchange efficiency in the heat exchanger 1.

[0062] As in this embodiment, in the intermediate chamber 51, the upper intermediate outlet 65 that opens upward and the lower intermediate outlet 67 that opens downward 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 of the outflow chambers 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 prevent a decrease in the heat exchange efficiency of the heat exchanger 1.

[0063] As in this embodiment, the upper return port 66 located on the upper side of the intermediate chamber 51 may be located higher than the upper inlet 61 located on the upper side of the intermediate chamber 51, and the lower return port 68 located on the lower side of the intermediate chamber 51 may be located lower than the lower inlet 63 located on the lower side of the intermediate chamber 51. This prevents the refrigerant that has flowed into the inlet chambers 53, 56 from the inlet ports 61, 63 from flowing directly into the outlet chambers 54, 57 through the return ports 66, 68, making it easier to divert the refrigerant through natural circulation. 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 1.

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

[0065] As in this 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 to the specified depth into the inflow chambers 53, 56, making it easier to ensure flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easier to suppress a decrease in the efficiency of heat exchange 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 and 56 arranged vertically on either side of the intermediate chamber 51 and having inlets 61 and 63 formed therein, and outlet chambers 54 and 57 arranged vertically on either side of the intermediate chamber 51 and separated from the inlet chambers 53 and 56 and connected to the flat tubes 3. The intermediate chamber 51 is formed with intermediate inlet ports 62 and 64 that open upward and downward and connect each of the inlet chambers 53 and 56 to the intermediate chamber 51, and intermediate outlet ports 65 and 67 that open upward and downward and connect each of the outlet chambers 54 and 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] (Embodiment 2) The following describes the second embodiment, with only the differences from the first embodiment being explained.

[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 an inclination downward to the right, and the lower partition member 142 is disposed with an inclination upward 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] 6, in this embodiment, the cross-sectional area of ​​the upper inlet pipe 131 and the cross-sectional area of ​​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 and the opening area of ​​the lower inlet 163 are different from each other. 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] In addition, 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 operation of the heat exchanger 1 of the second embodiment when it functions as an evaporator will be described below. In the second embodiment, the cross-sectional areas of the inlet pipes 131, 133 and the opening areas of the inlets 161, 163 are different from each other, so the flow rate and flow velocity of the refrigerant flowing into the inlet chambers 53, 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, as in the first embodiment, the refrigerant flows from the intermediate chamber 151 into the outlet chambers 54, 57 via the intermediate outlet ports 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 outlet chamber 54 is smaller than the number of flat tubes 3 connected to the lower outlet chamber 57, and therefore, it is easy to divide the flow against gravity in the upper outlet 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 easy to increase the number of flat tubes 3 connected to the lower outflow chamber 57, which facilitates flow division, and ensures good flow division performance. Therefore, even when the refrigerant circulation rate is low, it is easy to prevent 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 and 57 may be configured to have a smaller vertical dimension than the portion of the intermediate chamber 151 between the inflow chambers 53 and 56 . This makes it easy to arrange the intermediate chamber 151 at a height between the vertically adjacent flat tubes 3 on the outflow chambers 54, 57 side, and makes it easy to configure the flat tubes 3 so that they are not directly connected to the intermediate chambers 151, 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.

[0075] As in this embodiment, the opening area of ​​the upper inlet 61 may be different from the opening area of ​​the lower inlet 63 . This makes it possible to adjust the ratio of the flow rates and flow velocities of the refrigerant flowing into each inlet chamber 53, 56, 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 efficiency of heat exchange in the heat exchanger.

[0076] As in this embodiment, the inflow chambers 53, 56 may communicate with the inflow pipes 131, 133 via the inflow ports 161, 163, respectively, and the inflow pipes 131, 133 may have different cross-sectional areas. This makes it possible to adjust the ratio of the flow rates and flow velocities of the refrigerant flowing into each inlet chamber 53, 56, 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 efficiency of heat exchange in heat exchanger 1.

[0077] (Other embodiments) As described above, the first and second embodiments have been described as examples of the technology disclosed in the present application. However, the technology in the present 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 the first and second embodiments to create new embodiments. Therefore, other embodiments will be exemplified below.

[0078] In the above embodiment, it has been described that 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 partial non-overlapping portion.

[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 be two or more. The relationship in size and position of the opening areas between the intermediate inlets 62, 64 or between the intermediate outlets 65, 67 described in the above embodiment is merely an example 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] (Addendum) The above description of the embodiments discloses the following techniques. (Technology 1) A header diverter is provided in a heat exchanger having a plurality of flat tubes arranged vertically, and has a header pipe connected to one end of a plurality of the 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) The header flow divider according to Technology 1, wherein the inlet chamber and the outlet chamber are communicated with each other 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, before returning to the inlet chamber via the return port, making it easier to separate the refrigerant through natural circulation.As a result, even when the refrigerant circulation rate is low, it is easy to prevent a decrease in heat exchange efficiency in the heat exchanger.

[0084] (Technology 3) A header flow divider according to Technology 1 or 2, 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. This prevents the refrigerant in one inlet chamber from flowing directly into the other inlet chamber via the intermediate chamber, ensuring good flow separation performance, and therefore preventing a decrease in heat exchange efficiency in the heat exchanger even when the refrigerant circulation rate is low.

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

[0086] (Technology 5) A header flow divider according to any one of Technologies 1 to 4, wherein in the intermediate chamber, the centers of the intermediate outlet that opens upward and the intermediate outlet that opens downward do not overlap with each other in a planar view. This allows the 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 separation performance, and therefore easy to prevent a decrease in heat exchange efficiency in the heat exchanger even when the refrigerant circulation rate is low.

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

[0088] (Technology 7) A header distributor described in 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 increases the number of flat tubes connected to the outlet chamber below the intermediate chamber, which facilitates flow separation, and therefore makes it easier to ensure flow separation performance.As a result, even when the refrigerant circulation rate is low, it is easier to prevent a decrease in heat exchange efficiency in the heat exchanger.

[0089] (Technology 8) A header divider according to any one of Technologies 2 to 7, 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. This prevents the refrigerant that has flowed into the inlet chamber from flowing directly into the outlet chamber through the return port, facilitating natural circulation of the refrigerant, thereby preventing a decrease in the heat exchange efficiency of the heat exchanger even when the refrigerant circulation rate is low.

[0090] (Technology 9) A 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 adjacent flat tubes, and because each flat tube is easily configured so as not to be directly connected to the intermediate chamber, it is easy to ensure flow separation performance, and therefore it is easy to suppress a decrease in heat exchange efficiency in the heat exchanger even when the refrigerant circulation rate is low.

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

[0092] (Technology 11) A 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 allows the ratio of the refrigerant flowing into each inlet chamber to be adjusted, making it easier to ensure flow separation performance and therefore easier to prevent a decrease in heat exchange efficiency in the heat exchanger even when the refrigerant circulation rate is low.

[0093] (Technology 12) A 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 each of the refrigerant inlet pipes has a different cross-sectional area. This allows the ratio of the refrigerant flowing into each inlet chamber to be adjusted, making it easier to ensure flow separation performance and therefore easier to prevent a decrease in heat exchange efficiency in the heat exchanger even when the refrigerant circulation rate is low.

[0094] (Technology 13) A header flow divider according to any one of Technologies 1 to 13, 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. This makes it easier to insert each flat tube into the inlet chamber to the specified depth, ensuring good flow separation performance and preventing a decrease in heat exchange efficiency in the heat exchanger even when the refrigerant circulation rate is low.

[0095] (Technology 14) A heat exchanger comprising: 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 is formed with a hollow intermediate chamber inside, 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. 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. [Industrial Applicability]

[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. [Explanation of symbols]

[0097] 1 heat exchanger 3 flat tube 4 Microchannel 5 Gas side header pipe 7 Fin 10 Header Divider 20 Header pipe 21 First side member 22 Insertion hole 23 Second side member 25 Upper surface member 27 Bottom member 31 Upper inflow pipe (refrigerant inflow pipe) 33 Lower inflow pipe (refrigerant inflow 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 regulation member (depth regulation part) 51 Intermediate Room 52 Upper inlet pipe connection chamber 53 Upper inflow chamber (inflow chamber) 54 Upper outflow chamber (outflow chamber) 55 Lower inflow pipe connection room 56 Lower inflow chamber (inflow chamber) 57 Lower outflow chamber (outflow chamber) 60 aperture 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 Divider 131 Upper inflow pipe (refrigerant inflow pipe) 133 Lower inflow pipe (refrigerant inflow pipe) 141 Upper partition member 142 Lower partition member 151 Intermediate Room 161 Upper inlet (refrigerant inlet) 163 Lower inlet (refrigerant inlet)

Claims

1. A header diverter provided in a heat exchanger having a plurality of flat tubes arranged vertically, the header diverter having a header pipe connected to one end of the plurality of flat tubes, Inside the header pipe, a hollow intermediate chamber; inlet chambers, each of which has a refrigerant inlet port, and which are arranged vertically with the intermediate chamber interposed therebetween; An outflow chamber is provided above and below the intermediate chamber, separated from the inflow chamber and connected to the flat tube, The intermediate chamber includes: intermediate inflow ports that open upward and downward and communicate each of the inflow chambers with the intermediate chamber; intermediate outlets that open upward and downward and communicate each of the outflow chambers with the intermediate chamber are formed; Header shunt.

2. The inlet chamber and the outlet chamber are connected by an open return port.

2. The header flow divider of claim 1.

3. 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.

2. The header flow divider of claim 1.

4. In the intermediate chamber, the intermediate inlet opening upward and the intermediate inlet opening downward have different opening areas.

2. The header flow divider of claim 1.

5. In the intermediate chamber, the centers of the intermediate outlet opening upward and the intermediate outlet opening downward do not overlap with each other in a plan view.

2. The header flow divider of claim 1.

6. In the intermediate chamber, the intermediate outlet opening upward and the intermediate outlet opening downward have different opening areas.

2. The header flow divider of claim 1.

7. The number of the flat tubes connected to the outflow chamber located above the intermediate chamber is: The number of the flat tubes connected to the outflow chamber located below the intermediate chamber is equal to or less than the number of the flat tubes connected to the outflow chamber located below the intermediate chamber.

2. The header flow divider of claim 1.

8. 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, 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.

3. The header flow divider of claim 2.

9. The vertical dimension of the intermediate chamber is equal to or less than the vertical spacing between the flat tubes.

2. The header flow divider of claim 1.

10. a portion of the intermediate chamber between the outflow chambers has a smaller dimension in the up-down direction than a portion of the intermediate chamber between the inflow chambers; 2. The header flow divider of claim 1.

11. an opening area of ​​the refrigerant inlet located on the upper side of the intermediate chamber is different from an opening area of ​​the refrigerant inlet located on the lower side of the intermediate chamber; 2. The header flow divider of claim 1.

12. Each of the inlet chambers communicates with a refrigerant inlet pipe via the refrigerant inlet port, Each of the refrigerant inlet pipes has a different cross-sectional area.

2. The header flow divider of claim 1.

13. The header pipe is provided with a depth determining portion that determines an insertion depth of the plurality of flat tubes into the outflow chamber.

2. The header flow divider of claim 1.

14. A plurality of flat tubes arranged vertically; a header divider having a header pipe connected to one end of the plurality of flat tubes, Inside the header pipe, a hollow intermediate chamber; inlet chambers, each of which has a refrigerant inlet port, and which are arranged vertically with the intermediate chamber interposed therebetween; An outflow chamber is provided above and below the intermediate chamber, separated from the inflow chamber and connected to the flat tube, The intermediate chamber includes: intermediate inflow ports that open upward and downward and communicate each of the inflow chambers with the intermediate chamber; intermediate outlets that open upward and downward and communicate each of the outflow chambers with the intermediate chamber are formed; heat exchanger.

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