Heat Exchanger

Abstract

The heat exchanger of the present invention includes: a plurality of heat transfer flat tubes and a hollow header, the header having: an inflow plate, which divides the interior of the header into an inflow portion for allowing refrigerant to flow in, and a circulation portion located above the inflow portion; and a first partition component, which divides the circulation portion into an ascending circuit located on the inner side connected to the ends of the plurality of heat transfer flat tubes, and a descending circuit located on the outer side, and forms an upper connecting path and a lower connecting path, the upper connecting path connects the ascending circuit and the descending circuit on the upper side of the circulation portion, and the lower connecting path connects the ascending circuit and the descending circuit on the lower side of the circulation portion, and the inflow plate has a first ejection hole on the ascending circuit side and the leeward side for ejecting the refrigerant from the inflow portion to the ascending circuit.

Description

Technical Field

[0001] The technology disclosed in the present invention relates to a heat exchanger Background Art

[0002] A heat exchanger used in an air conditioner generally has the following structure: both ends of a heat transfer flat tube having a plurality of flow paths are connected to a header on one side and another side, respectively, and the refrigerant is divided from the header on one side to each heat transfer flat tube. For example, the following technology has been proposed: the refrigerant is circulated inside the header so that the refrigerant is distributed uniformly to a plurality of heat transfer flat tubes connected to the header (see Patent Document 1).

[0003] Patent Document 1: Japanese Patent Application Publication No. 2015-127618 Summary of the invention

[0004] However, the heat exchange amount varies between the flow paths on the windward side and the leeward side in each heat transfer flat tube, which causes the state of the refrigerant to become uneven between the multiple flow paths in each heat transfer flat tube, thereby reducing the heat exchange capacity.

[0005] The technology disclosed in the present invention is completed in view of the above problems, and its purpose is to provide a heat exchanger capable of dividing the refrigerant in each heat transfer flat tube in consideration of the difference in heat exchange amount between the flow paths on the windward side and the leeward side.

[0006] According to one embodiment of the heat exchanger disclosed in the present invention, it includes: a plurality of heat transfer flat tubes stacked at intervals; and a hollow header connected to the ends of the plurality of heat transfer flat tubes, the header having: an inflow plate dividing the interior of the header into an inflow portion for allowing refrigerant to flow in, and a circulation portion located on the upper side of the inflow portion and connected to the ends of the plurality of heat transfer flat tubes; and a first partition member dividing the circulation portion into an ascending circuit located on the side connected to the ends of the plurality of heat transfer flat tubes, i.e., the inner side, and a descending circuit located on the opposite side of the inner side, i.e., the outer side, and forming an upper connecting path and a lower connecting path, the upper connecting path connecting the ascending circuit and the descending circuit on the upper side of the circulation portion, and the lower connecting path connecting the ascending circuit and the descending circuit on the lower side of the circulation portion, and the inflow plate having at least one first ejection hole on the ascending circuit side and the leeward side for ejecting refrigerant from the inflow portion to the ascending circuit.

[0007] The heat exchanger disclosed in the present invention can split the refrigerant in each heat transfer flat tube in consideration of the difference in heat exchange amount between the flow paths on the windward side and the leeward side. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 It is a diagram for explaining the structure of an air conditioner to which the heat exchanger according to Embodiment 1 is applied.

[0009] Figure 2AA top view of the heat exchanger.

[0010] Figure 2B This is the front view of the heat exchanger.

[0011] Figure 3 It is a perspective view of a header of the heat exchanger according to Embodiment 1.

[0012] Figure 4 An example diagram of an inflow plate with two ejection holes.

[0013] Figure 5 A cross-sectional view showing a portion of the header and a plurality of heat transfer flat tubes as viewed from the windward side.

[0014] Figure 6 A cross-sectional view showing a header viewed from the side of a plurality of heat transfer flat tubes.

[0015] Figure 7 It is a perspective view of a header of a heat exchanger according to the second embodiment.

[0016] Figure 8 This is a cross-sectional view of the header of the heat exchanger according to Embodiment 2 as viewed from the windward direction.

[0017] Fig. 9A for Figure 8 Cross-sectional view along aa.

[0018] Fig. 9B for Figure 8 Cross-sectional view along aa.

[0019] Fig.10 A cross-sectional view showing a header viewed from the side of a plurality of heat transfer flat tubes.

[0020] Fig.11 For illustration Fig.10 A diagram of a comparative example of a header is shown. DETAILED DESCRIPTION

[0021] Hereinafter, the embodiment will be described in detail with reference to the drawings. In the description of the entire embodiment, the same reference numerals are given to the same structures.

[0022] Implementation Method 1

[0023] Air conditioner

[0024] Figure 1 1 is a diagram for explaining the structure of the air conditioner 1 to which the heat exchangers 4 and 5 according to the first embodiment are applied. Figure 1 As shown, the air conditioner 1 includes an indoor unit 2 and an outdoor unit 3. The indoor unit 2 includes an indoor heat exchanger 4, and the outdoor unit 3 includes an outdoor heat exchanger 5, a compressor 6, an expansion valve 7, and a four-way valve 8.

[0025] During heating operation, the high-temperature and high-pressure gas refrigerant discharged from the compressor 6 of the outdoor unit 3 flows into the heat exchanger 4 serving as a condenser via the four-way valve 8. Figure 1 The refrigerant flows in the direction indicated by the black arrow shown. In the heat exchanger 4, the refrigerant exchanges heat with the outside air and is liquefied. The liquefied high-pressure refrigerant passes through the expansion valve 7 and is decompressed, and flows into the heat exchanger 5 used as an evaporator as a low-temperature and low-pressure gas-liquid two-phase refrigerant. In the heat exchanger 5, the refrigerant exchanges heat with the outside air and is vaporized. The vaporized low-pressure refrigerant is sucked into the compressor 6 through the four-way valve 8.

[0026] During cooling operation, the high-temperature and high-pressure gas refrigerant discharged from the compressor 6 of the outdoor unit 3 flows into the heat exchanger 5 serving as a condenser via the four-way valve 8. Figure 1 The refrigerant flows in the direction indicated by the white arrow shown in FIG. 5. In the heat exchanger 5, the refrigerant exchanges heat with the outside air and is liquefied. The liquefied high-pressure refrigerant passes through the expansion valve 7 and is decompressed, and flows into the heat exchanger 4 used as an evaporator as a low-temperature and low-pressure gas-liquid two-phase refrigerant. In the heat exchanger 4, the refrigerant exchanges heat with the outside air and is vaporized. The vaporized low-pressure refrigerant is sucked into the compressor 6 through the four-way valve 8.

[0027] Heat Exchanger

[0028] The heat exchanger according to Embodiment 1 can be applied to any of the heat exchanger 4 and the heat exchanger 5. Hereinafter, for the sake of specific description, a case where the heat exchanger according to Embodiment 1 is applied to the heat exchanger 5 used as an evaporator during heating operation will be described.

[0029] Figure 2A is a top view of the heat exchanger 5, Figure 2B It is a front view of the heat exchanger 5. The heat exchanger 5 includes a plurality of heat transfer flat tubes 11, a header 12, a header 13, and fins 14.

[0030] The low-temperature and low-pressure gas-liquid two-phase refrigerant that has been decompressed by the expansion valve 7 is supplied to the header 12 through the pipe 15, and then is divided into each heat transfer flat tube 11. When the gas-liquid two-phase refrigerant flows in the heat transfer flat tube 11, it exchanges heat with the air through the heat sink 14 and is gasified, and then flows out of the header 13. The refrigerant that has merged in the header 13 is sucked into the compressor 6 through the pipe 16 and the four-way valve 8. The specific structure of the plurality of heat transfer flat tubes 11, the header 12, the header 13, and the heat sink 14 is described below.

[0031] The plurality of heat transfer flat tubes 11 are conductive tubes each having a flat cross section and a plurality of flow paths for allowing the refrigerant to flow therein along the direction in which the heat transfer flat tubes extend. The plurality of heat transfer flat tubes 11 are stacked at intervals in the vertical direction of the headers 12 and 13 so that the plurality of heat transfer flat tubes 11 face each other in the width direction. One end of each of the plurality of heat transfer flat tubes 11 is connected to the header 12, and the other end of each of the plurality of heat transfer flat tubes 11 is connected to the header 13.

[0032] The refrigerant branched from the header 12 to each of the heat transfer flat tubes 11 flows in the flow path inside each of the heat transfer flat tubes 11, and flows out to the header 13. The refrigerant flowing in the flow path inside each of the heat transfer flat tubes 11 exchanges heat with the outside air passing through the space between the plurality of heat transfer flat tubes 11. In the following description, the upstream side of the flow of the outside air is referred to as the windward side, and the downstream side is referred to as the leeward side.

[0033] In addition, Figure 2B In the examples, the number of the heat transfer flat tubes 11 is 9. However, this is an example, and the number of the heat transfer flat tubes 11 is not limited to 9.

[0034] The header 12 is a refrigerant flow path having a tubular shape (e.g., a cylindrical shape). The interior of the header 12 is formed to be hollow so that the refrigerant is distributed to the plurality of heat transfer flat tubes 11. The header 12 is connected to the pipe 15 and the respective ends of the plurality of heat transfer flat tubes 11. The refrigerant flowing into the header 12 through the pipe 15 is distributed to the respective heat transfer flat tubes 11 in the header 12.

[0035] Figure 3 FIG. 1 is a perspective view of the header 12 of the heat exchanger 5 according to Embodiment 1. Figure 3 As shown in FIG. 1 , the header 12 includes an inflow plate 120 and a first partition member 121. In the following description, the side of the header 12 connected to the ends of the plurality of heat transfer flat tubes 11 is referred to as the inner side, and the opposite side of the inner side, that is, the side not connected to the ends of the plurality of heat transfer flat tubes 11 is referred to as the outer side. Figure 3 In the figure, arrows indicate the flow direction of the external air, and the heat sink 14 is omitted.

[0036] The inflow plate 120 divides the interior of the header 12 into an inflow portion 12F and a circulation portion 12S located above the inflow portion 12F. The inflow portion 12F is connected to the pipe 15. The circulation portion 12S is connected to the ends of the plurality of heat transfer flat tubes 11.

[0037] The first partition member 121 is disposed inside the header 12 along the longitudinal direction of the tubular header 12 (i.e., the stacking direction of the heat transfer flat tubes 11). The first partition member 121 divides the circulation section 12S into an inner ascending circuit 12Su and an outer descending circuit 12Sd.

[0038] In addition, the cross-sectional areas of the ascending circuit 12Su and the descending circuit 12Sd can be designed in advance according to the state and type of the flowing refrigerant. These items can be appropriately set according to the performance required of the heat exchanger 5.

[0039] In addition, the first partition member 121 is provided at a distance from the upper surface and the bottom surface of the header 12. The first partition member 121 forms an upper communication path 12St that connects the ascending circuit 12Su and the descending circuit 12Sd at the upper side inside the circulation section 12S. In addition, the first partition member 121 forms a lower communication path 12Sb that connects the ascending circuit 12Su and the descending circuit 12Sd at the lower side inside the circulation section 12S.

[0040] Here, the upper end of the first partition member 121 is located above the uppermost heat transfer flat tube 11 among the plurality of heat transfer flat tubes 11 , and the lower end of the first partition member 121 is located below the lowermost heat transfer flat tube 11 among the plurality of heat transfer flat tubes 11 .

[0041] The inflow plate 120 has at least one first ejection hole (orifice) 121H1 on the leeward side of the ascending circuit 12Su for ejecting the refrigerant from the inflow portion 12F to the ascending circuit 12Su. In addition, the first ejection hole 121H1 is located between the first partition member 121 and the ends of the plurality of heat transfer flat tubes 11 when viewed from above. In this way, the first ejection hole 121H1 is arranged at a position that does not overlap with the ends of the plurality of heat transfer flat tubes 11, thereby preventing the refrigerant ejected from the first ejection hole 121H1 to the circulation portion 12S from being decelerated by the plurality of heat transfer flat tubes 11.

[0042] In addition, Figure 3 , a case where one first ejection hole 121H1 is formed in the inflow plate 120 is illustrated. In contrast, a plurality of first ejection holes 121H1 may be formed in the inflow plate 120. In addition, the number or size (cross-sectional area) of the first ejection holes 121H1 may be pre-designed according to the state or type of the flowing refrigerant. These items may be appropriately set according to the performance required of the heat exchanger 5.

[0043] In addition, the inflow plate 120 may have at least one second ejection hole for ejecting the refrigerant from the inflow portion 12F to the ascending circuit 12Su on the side of the ascending circuit 12Su and on the windward side relative to the first ejection hole 121H1. The second ejection hole is formed to be smaller than the first ejection hole 121H1. In other words, the first ejection hole 121H1 is formed to be larger than the second ejection hole.

[0044] Figure 4 FIG. 1 is a diagram for explaining an inflow plate 120 having a second ejection hole 121H2. Figure 4As shown, the first ejection holes 121H1 on the leeward side are formed to be larger than the second ejection holes 121H2 on the windward side.

[0045] like Figure 2A , Figure 2B , Figure 3 As shown, the header 13 forms a pair with the header 12 and is a refrigerant flow path having a tubular shape (e.g., a cylindrical shape). The header 13 has substantially the same structure as the header 12. The header 13 is connected to the pipe 16 and the other ends of the plurality of heat transfer flat tubes 11. Since the header 13 is connected to the other ends of the plurality of heat transfer flat tubes 11, the refrigerants flowing out of the respective heat transfer flat tubes 11 merge in the header 13.

[0046] The fins 14 extend in a direction perpendicular to the plurality of heat transfer flat tubes 11 and are connected to the plurality of heat transfer flat tubes 11. The fins 14 are arranged at a predetermined interval along the length direction of the plurality of heat transfer flat tubes 11 to separate spaces for air to pass through.

[0047] Refrigerant circulation in the header

[0048] Next, the circulation of the refrigerant in the header will be described. In addition, the header 12 is taken as an example for the purpose of specific description below.

[0049] Figure 5 , Figure 6 It is a diagram for explaining the circulation of the refrigerant in the header 12 . Figure 5 A cross-sectional view showing a portion of the header 12 and the plurality of heat transfer flat tubes 11 as viewed from the windward side is shown. Figure 6 1 is a cross-sectional view of the header 12 viewed from the side of the plurality of heat transfer flat tubes 11. Figure 6 In FIG. 1 , the dotted area of ​​the circulation section 12S schematically represents the distribution of the liquid refrigerant, and the white area of ​​the circulation section 12S schematically represents the distribution of the gas refrigerant. Figure 5 , Figure 6 The heat sink 14 is omitted in the figure.

[0050] like Figure 5 As shown, the refrigerant (gas-liquid two-phase refrigerant) supplied from the pipe 15 to the inflow portion 12F is ejected to the circulation portion 12S via the first ejection hole 121H1 of the inflow plate 120. The first ejection hole 121H1 is formed on the rising circuit 12Su side and the leeward side of the inflow portion 12F. Figure 6 As shown by arrow A1, the refrigerant discharged from the first discharge hole 121H1 to the circulation unit 12S rises on the leeward side of the rising circuit 12Su.

[0051] That is, the refrigerant ejected from the first ejection hole 121H1 to the ascending circuit 12Su of the circulation unit 12S is a gas-liquid two-phase refrigerant of liquid refrigerant and gas refrigerant, but the flow rate of the gas refrigerant is faster than that of the liquid refrigerant. Therefore, when the refrigerant is ejected from the first ejection hole 121H1 to the leeward side of the ascending circuit 12Su and ascends, Figure 6 As shown by arrow A1, most of the gas refrigerant flows strongly from the first discharge port 121H1 toward the upper part of the leeward side of the rising circuit 12Su.

[0052] On the other hand, Figure 6 As shown by arrow A2, the liquid refrigerant with a slow flow rate is pushed from the leeward side to the windward side by the gas refrigerant flow ejected from the first ejection hole 121H1. Figure 6 As shown, the gas refrigerant with a fast flow rate blown up is distributed more on the leeward side of the ascending circuit 12Su, and the liquid refrigerant with a lower flow rate than the gas refrigerant is distributed more on the windward side of the ascending circuit 12Su.

[0053] In the ascending circuit 12Su, the following is constructed: Figure 6 The refrigerant of the phase distribution shown is divided into a plurality of heat transfer flat tubes 11. When the refrigerant divided into the plurality of heat transfer flat tubes 11 flows in each heat transfer flat tube 11, the refrigerant exchanges heat with the air through the heat sink 14 and is vaporized, and then flows out to the header 13.

[0054] In addition, the refrigerant that is not divided into the plurality of heat transfer flat tubes 11 has its up-and-down flow direction reversed in the upper communication path 12St and flows into the descending circuit 12Sd of the circulation section 12S. The refrigerant that has flowed into the descending circuit 12Sd descends in the descending circuit 12Sd of the circulation section 12S, and its up-and-down flow direction is reversed in the lower communication path 12Sb, and then flows into the ascending circuit 12Su again.

[0055] The refrigerant that has flowed into the rising circuit 12Su in the above-described manner merges with the refrigerant newly discharged from the first discharge port 121H1 to the circulation unit 12S, and the same cycle is repeated again.

[0056] As described above, by providing the first ejection hole 121H1 on the leeward side of the ascending circuit 12Su of the inflow plate 120, the gas refrigerant can be ejected strongly to the top of the ascending circuit 12Su. Figure 6As shown in the figure, the upward flow of the gas refrigerant on the leeward side can change the flow ratio between the gas refrigerant and the liquid refrigerant in the width direction of each of the plurality of heat transfer flat tubes 11. Specifically, with respect to each heat transfer flat tube 11, more liquid refrigerant in the gas-liquid two-phase refrigerant can be diverted to the windward side with a larger heat exchange capacity, and more gas refrigerant can be diverted to the leeward side with a smaller heat exchange capacity than the windward side. In addition, in the present embodiment, such an effect of making the flow ratio between the gas refrigerant and the liquid refrigerant in the width direction of the plurality of heat transfer flat tubes 11 different is called a deviation effect of the refrigerant phase distribution.

[0057] In addition, since the gas refrigerant is strongly ejected from the first ejection hole 121H1 to the top of the ascending circuit 12Su, the aforementioned deviation effect of the refrigerant phase distribution also acts on the heat transfer flat tubes 11 at the top of the header 12. Furthermore, the liquid refrigerant is strongly ejected from the first ejection hole 121H1 together with the gas refrigerant to the top of the ascending circuit 12Su, thereby preventing the liquid refrigerant from flowing into the heat transfer flat tubes 11 at the bottom layer.

[0058] In addition, it is conceivable that the inflow plate 120 is provided with the second ejection hole 121H2 on the windward side and the first ejection hole 121H1 on the leeward side (see Figure 4 ). By providing the second ejection hole 121H2, the liquid refrigerant that tends to accumulate on the windward side of the upper surface of the inflow plate 120 can be pushed up by the gas refrigerant ejected from the second ejection hole 121H2, thereby suppressing the deviation in the amount of refrigerant flowing into the plurality of heat transfer flat tubes 11. In this case, the first ejection hole 121H1 on the leeward side is formed to be larger than the second ejection hole 121H2 on the windward side. Usually, the amount of refrigerant flowing into the circulation part 12S from the first ejection hole 121H1 on the leeward side and the second ejection hole 121H2 on the windward side is proportional to their respective opening areas. Therefore, the amount of refrigerant ejected from the first ejection hole 121H1 on the leeward side can be made larger than the amount of refrigerant ejected from the second ejection hole 121H2 on the windward side. Therefore, even if the inlet plate 120 has the second ejection hole 121H2 on the windward side and the first ejection hole 121H1 on the leeward side, the liquid refrigerant in the gas-liquid two-phase refrigerant can be diverted more to the windward side with a larger heat exchange capacity, and the gas refrigerant can be diverted more to the leeward side with a smaller heat exchange capacity than the windward side.

[0059] As described above, according to the heat exchanger 5 according to the first embodiment, the refrigerant can be divided into each heat transfer flat tube 11 in consideration of the difference in heat exchange amount between the flow paths on the windward side and the leeward side.

[0060] Implementation Method 2

[0061] Next, a heat exchanger according to Embodiment 2 will be described.

[0062] Figure 7 It is a perspective view of the header 12 of the heat exchanger 5 according to the second embodiment. Figure 8 1 is a cross-sectional view of the header 12 of the heat exchanger 5 according to Embodiment 2 as viewed from the windward direction. Figure 7 , Figure 8 As shown, the heat exchanger 5 according to the second embodiment further includes a second partition member in the circulation section 12S in the header 12 in addition to the structure of the heat exchanger 5 according to the first embodiment.

[0063] The second partition member 123 divides the circulation section 12S in the header 12 into an upper circulation section 12S1 located at the upper side and a lower circulation section 12S2 located at the lower side. Figure 7 , Figure 8 In the longitudinal direction of the header 12 in the middle, it is arranged at the center of the circulation part 12S or at an upper side compared to the center.

[0064] In addition, Figure 7 , Figure 8 In the embodiment, the number of the heat transfer flat tubes 11 connected to the upper circulation part 12S1 is set to 4, and the number of the heat transfer flat tubes 11 connected to the lower circulation part 12S2 is set to 5. However, these are only examples, and the number of the heat transfer flat tubes 11 connected to the upper circulation part 12S1 and the lower circulation part 12S2 is not limited thereto.

[0065] Fig. 9A , Fig. 9B for Figure 8 , and corresponds to the front view of the second partition member 123. Fig. 9A As shown, the second partition member 123 has an opening 123H1 on the leeward side of the ascending circuit 12Su. The opening 123H1 ejects the refrigerant from the lower circulation section 12S2 to the upper circulation section 12S1. In addition, the second partition member 123 has at least one opening 123H2 on the descending circuit 12Sd side for ejecting the refrigerant from the upper circulation section 12S1 to the lower circulation section 12S2.

[0066] In addition, the shape of the opening 123H1 may be a hole shape or a notch shape. Fig. 9B As shown, when viewed from above, the opening 123H1 has a positional relationship of overlapping with at least one first ejection hole 121H1. For example, the opening 123H1 is located above (for example, directly above) the first ejection hole 121H1 of the inflow plate 120. In addition, for example, the size (opening area) of the opening 123H1 is larger than the total opening area of ​​the at least one first ejection hole 121H1.

[0067] The opening 123H1 and the first ejection hole 121H1 are provided with the above-mentioned positional relationship and size relationship for the following reason: That is, in order to prevent the portion other than the opening 123H1 of the second partition member 123 (i.e., the plate-shaped portion) from becoming a flow resistance for the refrigerant ejected from the first ejection hole 121H1.

[0068] The specific number and size of the openings 123H1 may be designed in advance according to the state and type of the refrigerant flowing. These items may be appropriately set according to the performance required of the heat exchanger 5 .

[0069] Refrigerant circulation in the header

[0070] Next, refer to Figure 8 , Fig.10 The circulation of the refrigerant in the header will be described.

[0071] Fig.10 1 is a cross-sectional view of the header 12 viewed from the side of the plurality of heat transfer flat tubes 11. Figure 6 Same, in Fig.10 In FIG. 1 , the dotted area of ​​the circulation section 12S schematically represents the distribution of the liquid refrigerant, and the white area of ​​the circulation section 12S schematically represents the distribution of the gas refrigerant. Fig.10 The heat sink 14 is omitted in the figure.

[0072] like Fig.10 As shown, the refrigerant (gas-liquid two-phase refrigerant) supplied from the pipe 15 to the inflow portion 12F is ejected to the rising circuit 12Su of the lower circulation portion 12S2 via the first ejection hole 121H1 of the inflow plate 120. The first ejection hole 121H1 is formed on the rising circuit 12Su side and the leeward side of the inflow portion 12F. Fig.10 As shown by arrow A3, the refrigerant ejected from the first ejection hole 121H1 to the ascending circuit 12Su of the lower circulation unit 12S2 rises strongly on the leeward side. Fig.10 As shown by arrow A5, the liquid refrigerant with a slow flow rate is pushed from the leeward side to the windward side by the gas refrigerant flow ejected from the first ejection hole 121H1. This structure can achieve the above-mentioned deviation effect of the refrigerant phase distribution in the lower circulation part 12S2.

[0073] In the ascending circuit 12Su of the lower circulation part 12S2, the refrigerant with more gas refrigerant distributed on the leeward side and more liquid refrigerant distributed on the windward side is divided into a plurality of heat transfer flat tubes 11 connected to the lower circulation part 12S2. When the refrigerant divided into the plurality of heat transfer flat tubes 11 connected to the lower circulation part 12S2 flows through each heat transfer flat tube 11, the refrigerant is vaporized after exchanging heat with the air through the heat sink 14, and then flows out to the header 13.

[0074] In addition, the refrigerant that is not divided into the plurality of heat transfer flat tubes 11 is ejected from the opening 123H1 of the second partition member 123 to the ascending circuit 12Su of the upper circulation unit 12S1. Fig.10 As shown by arrow A4, most of the gas refrigerant is accelerated again through the opening 123H1 of the second partition member 123 and rises strongly toward the upper circulation unit 12S1. Fig.10 As shown by arrow A5, the gas refrigerant gas flow is accelerated by the opening 123H1 and the liquid refrigerant with a slow flow rate is pushed from the leeward side to the windward side. As a result, the above-mentioned refrigerant phase distribution deviation effect can be achieved in the upper circulation unit 12S1.

[0075] In the ascending circuit 12Su of the upper circulation unit 12S1, the refrigerant, which is more distributed as gas refrigerant on the leeward side and more distributed as liquid refrigerant on the windward side, is divided into a plurality of heat transfer flat tubes 11 connected to the upper circulation unit 12S1. When the refrigerant divided into the plurality of heat transfer flat tubes 11 connected to the upper circulation unit 12S1 flows through each heat transfer flat tube 11, the refrigerant is vaporized after exchanging heat with the air through the heat sink 14, and then flows out to the header 13.

[0076] In addition, the refrigerant that is not diverted to the plurality of heat transfer flat tubes 11 connected to the upper circulation section 12S1 has its up-and-down flow direction reversed in the upper communication passage 12St and flows into the descending circuit 12Sd of the circulation section 12S. The refrigerant that has flowed into the descending circuit 12Sd descends in the descending circuit 12Sd of the circulation section 12S, and then has its up-and-down flow direction reversed in the lower communication passage 12Sb and flows again into the ascending circuit 12Su of the lower circulation section 12S2.

[0077] The refrigerant that has flowed into the ascending circuit 12Su of the lower circulation section 12S2 as described above merges with the new refrigerant ejected from the first ejection hole 121H1 to the lower circulation section 12S2, and the same cycle is repeated again.

[0078] As described above, by providing the first ejection hole 121H1 on the leeward side and the ascending circuit 12Su of the inflow plate 120, most of the gas refrigerant flowing from the lower circulation section 12S2 to the upper circulation section 12S1 is accelerated again by the opening 123H1 of the second partition member 123. As a result, in the upper part of the circulation section 12S, the flow ratio between the gas refrigerant and the liquid refrigerant in the width direction of the plurality of heat transfer flat tubes 11 can be further made different compared to the case where the second partition member 123 having the opening 123H1 does not exist. In other words, in the upper circulation section 12S1, the efficiency is not reduced compared to the lower circulation section 12S2, and the effect of the deviation of the refrigerant phase distribution can be achieved. As a result, the refrigerant flow can be more effectively divided for each heat transfer flat tube 11 in consideration of the difference in heat exchange between the flow paths on the windward side and the leeward side.

[0079] Fig.11 To illustrate as Fig.10 FIG. 1 is a diagram for explaining a comparative example of the header shown in FIG. 1 , that is, a diagram for explaining a case where a refrigerant with a low circulation amount (low flow rate) flows into the header of Embodiment 1. Fig.11 The headers shown and Fig.10 The header shown, Fig.11 The illustrated header does not have the second partition member 123 having the opening 123H1. Fig.11 In FIG. 1 , the oblique line area of ​​the ascending circuit 12Su of the circulation unit 12S schematically represents the distribution of the gas-liquid two-phase refrigerant, the dotted area of ​​the circulation unit 12S schematically represents the distribution of the liquid refrigerant, and the white area of ​​the circulation unit 12S schematically represents the distribution of the gas refrigerant. Fig.11 In the figure, the heat sink 14 is omitted.

[0080] exist Fig.11 The comparative example shown involves a header, such as Fig.11 As shown by the arrow A6, the refrigerant ejected from the first ejection hole 121H1 to the ascending circuit 12Su of the circulation unit 12S slows down as it ascends because of its low circulation volume. Therefore, the flow velocity difference between the windward side and the leeward side of the ascending circuit 12Su of the circulation unit 12S gradually decreases toward the upper part of the circulation unit 12S. Fig.11 As shown by arrow A7, in the area of ​​the first ejection hole 121H1 of the ascending circuit 12Su adjacent to the circulation unit 12S, the gas refrigerant with a fast ascending speed can push the liquid refrigerant with a slow flow rate from the leeward side to the windward side. On the other hand, if the gas refrigerant is decelerated, the gas refrigerant cannot push the liquid refrigerant from the leeward side to the windward side. Therefore, Fig.11 As shown by arrow A8, the flow of the gas-liquid two-phase refrigerant increases as it moves toward the upper part of the ascending circuit 12Su of the circulation unit 12S, and it can be considered that the phase distribution between the liquid refrigerant and the gas refrigerant changes in the direction of no deviation.

[0081] In contrast, in the heat exchanger according to the present embodiment, since the gas refrigerant is accelerated again through the opening 123H1 and is forcefully ejected to the upper portion of the upper circulation portion 12S1, the deviation effect of the refrigerant phase distribution further acts effectively on the heat transfer flat tubes 11 at the upper portion of the upper circulation portion 12S1. Furthermore, since the gas refrigerant is forcefully ejected from the first ejection hole 121H1 to the upper portion of the upper circulation portion 12S1, it is possible to suppress the liquid refrigerant from flowing into the heat transfer flat tubes 11 at the lowest layer.

[0082] As described above, according to the heat exchanger 5 according to the first embodiment, the refrigerant flow can be divided in each of the heat transfer flat tubes 11 in consideration of the difference in heat exchange amount between the flow paths on the windward side and the leeward side.

[0083] Although the embodiments have been described above, the disclosed technology is not limited to the above contents and may include various embodiments not described here.

[0084] Explanation of symbols

[0085] 1 Air conditioner

[0086] 2 Indoor units

[0087] 3 Outdoor unit

[0088] 4.5 Heat exchanger

[0089] 6 Compressor

[0090] 7 Expansion valve

[0091] 8 Four-way valve

[0092] 11 Heat transfer flat tube

[0093] 12, 13 header

[0094] 14 Heat sink

[0095] 15, 16 Pipeline

[0096] 12F Inflow

[0097] 12S Circulation Department

[0098] 12S1 upper circulation unit

[0099] 12S2 Lower circulation unit

[0100] 12Su Ascending loop

[0101] 12Sd descent circuit

[0102] 12St upper connecting road

[0103] 12Sb Lower connecting path

[0104] 120 Inflow plate

[0105] 121 first partition member

[0106] 121H1 First outlet

[0107] 121H2 Second ejection hole

[0108] 123 Second partition member

[0109] 123H1 Opening.

Claims

1. A heat exchanger, comprising: A plurality of heat transfer flat tubes are stacked at intervals; as well as A hollow header connected to the ends of the plurality of heat transfer flat tubes, The header has: an inflow plate that divides the interior of the header into an inflow portion for allowing the refrigerant to flow in, and a circulation portion that is located above the inflow portion and connected to the ends of the plurality of heat transfer flat tubes; a first partition member, which divides the circulation section into an ascending circuit located on a side connected to the ends of the plurality of heat transfer flat tubes, that is, an inner side, and a descending circuit located on an opposite side of the inner side, that is, an outer side, and forms an upper connecting path and a lower connecting path, wherein the upper connecting path connects the ascending circuit and the descending circuit at an upper side inside the circulation section, and the lower connecting path connects the ascending circuit and the descending circuit at a lower side inside the circulation section; and a second partition member, which divides the circulation part into an upper circulation part located on the upper side and a lower circulation part located on the lower side, The inflow plate has at least one first discharge hole for discharging the refrigerant from the inflow portion to the ascending circuit on the leeward side of the ascending circuit. The second partition member has an opening portion for discharging the refrigerant from the lower circulation portion to the upper circulation portion on the ascending circuit side and the leeward side.

2. The heat exchanger according to claim 1, The inlet plate has at least one second ejection hole for ejecting the refrigerant from the inlet portion to the ascending circuit on the ascending circuit side and on the windward side of the at least one first ejection hole. At least one of the second ejection holes is formed to be smaller than at least one of the first ejection holes.

3. The heat exchanger according to claim 1, The second partition member is disposed at the center of the circulation portion or above the center in the stacking direction of the plurality of heat transfer flat tubes.

4. The heat exchanger according to claim 1, The opening portion overlaps with at least one of the first ejection holes in a plan view.

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