Heat exchanger and refrigeration cycle device

Abstract

A heat exchanger is provided with: a downwind-side heat exchange unit disposed on the downstream side in the direction of air flow; an upwind-side heat exchange unit disposed on the upstream side of the downwind-side heat exchange unit in the air flow direction; the downwind-side heat exchange unit is provided with: a downwind-side heat transfer tube row having heat transfer tubes arranged at intervals in a direction intersecting the air flow direction; and a first header connected to the lower end of the leeward heat transfer tube row, the windward heat exchange unit being provided with: a windward heat transfer tube row having heat transfer tubes arranged at intervals in a direction intersecting the air flow direction; and a second header connected to the lower end of the upwind-side heat transfer tube row, and a common header connected to the upper end of the downwind-side heat transfer tube row and the upper end of the upwind-side heat transfer tube row, and connecting the downwind-side heat transfer tube row and the upwind-side heat transfer tube row. The downwind-side heat exchange unit and the upwind-side heat exchange unit are provided with: a first region in which the refrigerant flowing into the first header flows in the direction facing the air flow direction and flows into the second header; a second region through which the refrigerant flowing into the second header through the first region flows in parallel with respect to the air flow direction and flows into the first header; and a third region through which the refrigerant flowing into the first header through the second region flows in the direction facing the air flow direction and flows into the second header.

Description

Technical Field

[0001] The present disclosure relates to a heat exchanger and a refrigeration cycle device for performing heat exchange of a refrigerant. Background Art

[0002] There is a heat exchanger in which an upwind heat exchange portion and a downwind heat exchange portion are connected in series in the air flow direction. In such a heat exchanger, in order to improve the performance of the heat exchanger, when the heat exchanger functions as a condenser, the refrigerant is caused to flow in a direction opposite to the direction of the air flow direction flowing into the heat exchanger in the area where the supercooled liquid flows on the downstream side of the heat exchanger (for example, refer to Patent Document 1).

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: Japanese Patent Application Laid-Open No. 7-98162 Summary of the invention

[0006] Problem that the invention aims to solve

[0007] Such a heat exchanger has a problem in that when the heat exchanger functions as a condenser, the refrigerant flows in parallel with the air flow direction in the superheated gas region, and the heat exchange performance is degraded.

[0008] The present disclosure is made in view of the above-mentioned actual situation, and its object is to provide a heat exchanger and a refrigeration cycle device with improved heat exchange performance.

[0009] Means used to solve problems

[0010] The heat exchanger disclosed in the present invention comprises: a leeward heat exchange section, which is arranged on the downstream side in the direction of air flow; an upwind heat exchange section, which is arranged on the upstream side in the direction of air flow compared to the leeward heat exchange section; and a common header, wherein the leeward heat exchange section comprises: a leeward heat transfer tube row, which has heat transfer tubes arranged at intervals in a direction intersecting the air flow direction; and a first header connected to the lower end of the leeward heat transfer tube row, and the upwind heat exchange section comprises: an upwind heat transfer tube row, which has heat transfer tubes arranged at intervals in a direction intersecting the air flow direction; and a second header connected to the lower end of the upwind heat transfer tube row, and the common header is connected to the upper end of the leeward heat transfer tube row and the upwind heat transfer tube row The upper end of the leeward heat transfer tube row and the upwind heat transfer tube row are connected, and when the leeward heat exchange section and the upwind heat exchange section function as a condenser, the leeward heat exchange section and the upwind heat exchange section have: a first area, in which the refrigerant flowing into the first header flows in opposite directions relative to the air flow direction and flows into the second header; a second area, in which the refrigerant flowing into the second header through the first area flows in parallel with the air flow direction and flows into the first header; and a third area, in which the refrigerant flowing into the first header through the second area flows in opposite directions relative to the air flow direction and flows into the second header.

[0011] Effects of the Invention

[0012] According to the present disclosure, when the heat exchanger functions as a condenser, the heat exchanger has a first region, a second region, and a third region. In the first region, the refrigerant flows in opposite directions relative to the air flow direction. In the second region, the refrigerant that has passed through the first region flows in parallel with the air flow direction. In the third region, the refrigerant that has passed through the second region flows in opposite directions relative to the air flow direction.

[0013] Therefore, when the heat exchanger functions as a condenser, unlike in the past, the refrigerant flows in the opposite direction to the air flow direction not only in the third region that becomes the supercooled liquid region but also in the first region that becomes the superheated gas region. Therefore, the heat exchange performance of the heat exchanger is improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 This is a schematic diagram showing a refrigerant circuit of the air-conditioning apparatus according to Embodiment 1.

[0015] Figure 2 It is a perspective view showing the heat exchanger according to Embodiment 1.

[0016] Figure 3This is a diagram showing the state of the flow of the refrigerant in the heat exchanger according to Embodiment 1.

[0017] Figure 4 This is a diagram showing the state of the refrigerant flowing through the heat exchanger according to Embodiment 1.

[0018] Figure 5 It is a diagram showing the state of the flow of the refrigerant in the heat exchanger of the air-conditioning apparatus according to Embodiment 2.

[0019] Figure 6 It is a diagram showing the arrangement of a first header and a second header of a heat exchanger in an air-conditioning apparatus according to Embodiment 2.

[0020] Figure 7 This is a diagram showing a state in which two first heat exchangers and a second heat exchanger according to Embodiment 2 are arranged on four sides in the outdoor unit housing so as to surround a fan.

[0021] Figure 8 This is a diagram showing a state in which a heat exchanger according to Embodiment 3 is arranged in an outdoor unit housing. DETAILED DESCRIPTION

[0022] Hereinafter, the heat exchanger of the air conditioning device of the embodiment is described with reference to the accompanying drawings. In addition, in the accompanying drawings, the same constituent elements are described by attaching the same figure marks, and the description is repeated only when necessary. The present disclosure may include any combination of the structures that can be combined in the structures described in the following embodiments. In addition, in the accompanying drawings, the relationship between the sizes of the various structural components is sometimes different from the actual. Moreover, the manner of the constituent elements shown in the entire specification is merely illustrative and is not limited to the manner described in the specification. In particular, the combination of constituent elements is not limited to the combination in each embodiment, and the constituent elements described in other embodiments can also be applied to other embodiments.

[0023] Implementation method 1.

[0024] Figure 1 1 is a schematic diagram showing the refrigerant circuit 110 of the air-conditioning apparatus 300 according to Embodiment 1.

[0025] The refrigerant circuit 110 includes a compressor 6 , a condenser 100 a , an expansion valve 8 , and an evaporator 100 b .

[0026] In the air conditioning device 300, the outdoor heat exchanger functions as the condenser 100a and the indoor heat exchanger functions as the evaporator 100b during cooling operation. The outdoor heat exchanger functions as the evaporator 100b and the indoor heat exchanger functions as the condenser 100a during heating operation.

[0027] The compressor 6 compresses the sucked refrigerant and discharges it. Although not particularly limited here, the compressor 6 can arbitrarily change the operating frequency by, for example, an inverter circuit, thereby changing the capacity of the compressor 6. The capacity of the compressor 6 indicates the amount of refrigerant delivered per unit time.

[0028] The condenser 100a performs heat exchange between the refrigerant discharged from the compressor 6 and the air. The condenser 100a condenses and liquefies the refrigerant.

[0029] The expansion valve 8 decompresses the refrigerant and expands the refrigerant. For example, when the expansion valve 8 is constituted by an electronic expansion valve, the expansion valve 8 adjusts the opening degree based on an instruction of a control device (not shown) or the like.

[0030] The evaporator 100b performs heat exchange between air and refrigerant. The evaporator 100b evaporates and gasifies the refrigerant.

[0031] The gaseous single-phase refrigerant discharged from the compressor 6 is condensed into a liquid single-phase in the condenser 100a. The refrigerant condensed into a liquid single-phase in the condenser 100a passes through the expansion valve 8 to become a gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant passing through the expansion valve 8 evaporates through the evaporator 100b and becomes a gas single-phase again. The gaseous single-phase refrigerant passing through the evaporator 100b flows into the compressor 6.

[0032] Figure 2 It is a perspective view showing the heat exchanger 100 according to the first embodiment. Figure 2 The heat exchanger 100 shown is suitable for use with a condenser 100a. Figure 2 In the figure, the direction of the air flow into the heat exchanger 100 is set as the direction from the left to the right of the paper as shown by the hollow arrow. In addition, the dotted arrow shows the flow direction of the refrigerant when the heat exchanger 100 functions as the condenser 100a.

[0033] like Figure 2 As shown, the heat exchanger 100 includes a leeward heat exchange portion 100_1 and an upwind heat exchange portion 100_2. The leeward heat exchange portion 100_1 is disposed on the downstream side of the air flow direction. The upwind heat exchange portion 100_2 is disposed on the upstream side of the air flow direction compared to the leeward heat exchange portion 100_1.

[0034] The leeward heat exchange unit 100_1 includes: a leeward heat transfer tube row 1_1 having heat transfer tubes 1 arranged at intervals in a direction intersecting the air flow direction; and a first header 21 connected to the lower end of the leeward heat transfer tube row 1_1. The first header 21 distributes the refrigerant to the leeward heat transfer tube row 1_1 or merges the refrigerant flowing from the leeward heat transfer tube row 1_1. The heat transfer tubes 1 of the leeward heat transfer tube row 1_1 allow the refrigerant to flow up and down.

[0035] The upwind heat exchange unit 100_2 includes: an upwind heat transfer tube row 1_2 having heat transfer tubes 1 arranged at intervals in a direction intersecting the air flow direction; and a second header 22 connected to the lower end of the upwind heat transfer tube row 1_2. The second header 22 distributes the refrigerant to the upwind heat transfer tube row 1_2 or merges the refrigerant flowing from the upwind heat transfer tube row 1_2. The heat transfer tubes 1 of the upwind heat transfer tube row 1_2 allow the refrigerant to flow up and down.

[0036] The leeward heat exchanger 100_1 and the upwind heat exchanger 100_2 are provided with a common header 23, which is connected to the upper end of the leeward heat transfer tube row 1_1 and the upper end of the upwind heat transfer tube row 1_2, and connects the leeward heat transfer tube row 1_2 and the upwind heat transfer tube row 1_2. The common header 23 allows the refrigerant to flow in the row direction between the leeward heat transfer tube row 1_1 and the upwind heat transfer tube row 1_2.

[0037] Here, the air flow direction and the refrigerant flow direction are defined as follows. The air flow direction is set to the direction from left to right on the paper. The refrigerant in the first header 21 flows into the common header 23 through the downwind heat transfer tube row 1_1. The refrigerant flowing into the common header 23 moves in the row direction of the heat exchanger 100 and flows into the upwind heat transfer tube row 1_2. The refrigerant flowing into the upwind heat transfer tube row 1_2 flows into the second header 22. In this case, the flow of the refrigerant flows from the right side to the left side of the paper, and flows in the opposite direction to the air flow direction. At this time, the flow of the refrigerant is defined as flowing in the opposite direction relative to the air flow direction.

[0038] When the air flow direction is also from left to right on the paper, the refrigerant in the second header 22 flows into the upwind heat transfer tube row 1_2. The refrigerant flowing into the upwind heat transfer tube row 1_2 moves in the row direction in the common header 23, and flows into the first header 21 through the downwind heat transfer tube row 1_1. In this case, the refrigerant flows from the left side to the right side facing the paper, and flows in the same direction relative to the air flow direction. At this time, it is defined that the refrigerant flows in parallel with the air flow direction.

[0039] Figure 31 is a diagram showing the state of the flow of the refrigerant in the heat exchanger 100 of Embodiment 1. Figure 3 , the state of the flow of the refrigerant when the refrigerant flowing into the first header 21 flows out from the second header 22 is shown. Figure 3 In the figure, the arrows indicate the flow of refrigerant and the hollow arrows indicate the direction of air flow.

[0040] When the heat exchanger 100 of Embodiment 1 functions as a condenser, the leeward heat transfer tube row 1_1 and the upwind heat transfer tube row 1_2 have a first region R1, a second region R2, and a third region R3.

[0041] The first region R1 is a region where the refrigerant flowing into the first header 21 flows in opposite directions with respect to the air flow direction and flows into the second header 22. The second region R2 is a region where the refrigerant flowing into the second header 22 through the first region R1 flows in parallel with respect to the air flow direction and flows into the first header 21. The third region R3 is a region where the refrigerant flowing into the first header 21 through the second region R2 flows in opposite directions with respect to the air flow direction and flows into the second header 22.

[0042] like Figure 3 As shown, the first header 21 includes a first header 21_1 of the first region R1, a first header 21_2 of the second region R2, and a first header 21_3 of the third region R3. The second header 22 includes a second header 22_1 of the first region R1, a second header 22_2 of the second region R2, and a second header 22_3 of the third region R3. The common header 23 includes a common header 23_1 of the first region R1, a common header 23_2 of the second region R2, and a common header 23_3 of the third region R3.

[0043] exist Figure 3 , the first header 21, the second header 22, and the common header 23 are divided into three, but they may not be divided into three. For example, the interior of one header may be divided into a plurality of areas by a partition plate provided inside the header.

[0044] exist Figure 3 In the embodiment, the first region R1, the second region R2 and the third region R3 are connected in series via the connecting pipe 4. Specifically, the second header 22_1 is connected in series with the second header 22_2 via the connecting pipe 4. The first header 21_2 is connected in series with the first header 21_3 via the connecting pipe 4.

[0045] In addition, the first region R1 , the second region R2 , and the third region R3 may be divided by partition plates in the first header 21 , the second header 22 , and the common header 23 .

[0046] exist Figure 3, the length of the downwind side heat exchanger 100_1 in the length direction of the first header 21_1 in the first region R1 and the length of the upwind side heat exchanger 100_2 in the length direction of the second header 22_1 in the first region R1 are set to L1. The length of the downwind side heat exchanger 100_1 in the length direction of the first header 21_2 in the second region R2 and the length of the upwind side heat exchanger 100_2 in the length direction of the second header 22_2 in the second region R2 are set to L2. The length of the downwind side heat exchanger 100_1 in the length direction of the first header 21_3 in the third region R3 and the length of the upwind side heat exchanger 100_2 in the length direction of the second header 22_3 in the third region R3 are set to L3.

[0047] exist Figure 3 In the figure, points A, B, and C correspond to the following Figure 4 Point A, point B and point C in the diagram.

[0048] Figure 4 : is a diagram showing the state of the refrigerant flowing in the heat exchanger 100 of Embodiment 1. Figure 4 In , the vertical axis represents temperature T and the horizontal axis represents entropy S. In addition, Figure 4 In FIG. 1 , arrows indicate the direction of change of the refrigerant when the heat exchanger 100 functions as a condenser.

[0049] Generally, when the heat exchanger 100 functions as a condenser, the refrigerant first flows into the heat exchanger 100 in a state of superheated gas, passes through a gas-liquid two-phase state, becomes a state of supercooled liquid, and flows out. At this time, the area where the refrigerant is a superheated gas is set as area X, the area where the refrigerant is a gas-liquid two-phase state is set as area Y, and the area where the refrigerant is a state of supercooled liquid is set as area Z.

[0050] In embodiment 1, Figure 3 L1, L2 and L3 are shown in Figure 4 The state of the refrigerant at points A, B and C is shown in Figure 3 The method of implementing the points A, B and C shown is determined. Here, point A represents the temperature T and entropy S of the refrigerant just before it flows into region X. Point B represents the temperature T and entropy S of the refrigerant just before it leaves region Y and flows into the third region R3. Point C represents the temperature T and entropy S of the refrigerant just after it flows out of region Z.

[0051] L1 is preferably determined in such a manner that the refrigerant flowing in the region X as superheated gas flows in the first header 21_1 and the second header 22_1. L3 is preferably determined in such a manner that the refrigerant flowing in the region Z as supercooled liquid flows in the first header 21_3 and the second header 22_3. The heat exchanger 100 of Embodiment 1 is configured such that L1, L2, and L3 are counter-currents with respect to the air flow direction in the region X and the region Y where the refrigerant temperature changes.

[0052] Region X and region Z are sensible heat regions. The sensible heat region is a region where the temperature of the refrigerant changes due to heat exchange using the heat exchanger 100. Region Y is a latent heat region where the temperature of the refrigerant does not change even if heat exchange is performed using the heat exchanger 100. When the same amount of heat exchange is performed, a larger temperature difference is required in the sensible heat region than in the latent heat region. Therefore, in the heat exchanger 100, in the first region R1 and the third region R3 as the latent heat region, the refrigerant flows in opposite directions relative to the air flow direction. This improves the heat exchange performance.

[0053] The refrigerant flowing in the first region R1 includes superheated gas, the refrigerant flowing in the second region R2 is a refrigerant in a gas-liquid two-phase state, and the refrigerant flowing in the third region R3 includes a supercooled liquid.

[0054] When a mixed refrigerant is used, even when the heat exchanger 100 functions as an evaporator, a temperature change occurs in the second region R2 where the gas-liquid two-phase refrigerant flows. Usually, when the heat exchanger 100 functions as an evaporator, a gas-liquid two-phase refrigerant flows in and becomes a gas single phase through the evaporator. The heat exchanger 100 may also be configured such that, when it functions as an evaporator using a variable path or the like, the refrigerant becomes a counterflow, a parallel flow, or a counterflow relative to the air flow direction, as in the case of a condenser. Thus, the evaporation performance of the heat exchanger 100 can also be improved.

[0055] According to the first embodiment, a heat exchanger 100 can be provided, in which, when the heat exchanger 100 functions as a condenser, unlike the past, the refrigerant and the air flow directions are opposite to each other not only in the third region R3 as the supercooled liquid region but also in the first region R1 as the superheated gas region. In addition, in the second region R2 as the latent heat region where sufficient heat exchange can be performed even with a small temperature difference, the refrigerant in the gas-liquid two-phase state is made to flow in parallel with respect to the air flow direction. In this way, in the supercooled liquid state and the superheated gas state as the sensible heat region requiring a large temperature difference, the refrigerant flows opposite to the air flow direction. Thus, the heat exchange performance of the heat exchanger 100 is improved.

[0056] Implementation method 2.

[0057] Figure 5 1 is a diagram showing the state of the flow of the refrigerant in the heat exchanger 100 of the air-conditioning apparatus 300 according to Embodiment 2. Figure 5 , the state of the flow of the refrigerant when the refrigerant flowing into the first header 21 flows out from the second header 22 is shown. Figure 5 In the figure, the arrows indicate the flow of refrigerant and the hollow arrows indicate the direction of air flow.

[0058] Figure 6 FIG. 2 is a diagram showing the arrangement of the first header 21 and the second header 22 of the heat exchanger 100 in the air conditioning apparatus 300 according to Embodiment 2. Figure 6 In, yes Figure 5 The common header 23 and the heat transfer tube 1 are omitted and not shown. Figure 6 In the figure, the arrows indicate the flow of refrigerant and the hollow arrows indicate the direction of air flow.

[0059] As an example of a heat exchanger 100 having three zones, Embodiment 2 shows a heat exchanger 100 having two heat exchangers, namely, a first heat exchanger 11 and a second heat exchanger 12. The first header 21_1, the second header 22_1, the common header 23_1, the first header 21_2, the second header 22_2, the common header 23_2, and the heat transfer tubes 1 connected thereto are set as the first heat exchanger 11. In addition, the first header 21_3, the second header 22_3, the common header 23_3, and the heat transfer tubes 1 connected thereto are set as the second heat exchanger 12.

[0060] like Figure 6 As shown, the outdoor unit housing 7 accommodates the fan 5 , the compressor 6 , the first heat exchanger 11 , and the second heat exchanger 12 .

[0061] The outdoor unit housing 7 is a side-flow housing having a rectangular planar shape. The compressor 6 compresses the refrigerant and discharges the high-pressure gas refrigerant. The fan 5 sends air for heat exchange to the first heat exchanger 11 and the second heat exchanger 12.

[0062] The first heat exchanger 11 and the second heat exchanger 12 are arranged in an L shape so as to surround the fan 5 .

[0063] like Figure 6 As shown, the first heat exchanger 11 has a first region R1 and a second region R2, and the second heat exchanger 12 has a third region R3.

[0064] The first heat exchanger 11 includes a first header 21_1 in the first region R1 and a first header 21_2 in the second region R2. A partition plate 3 is provided between the first header 21_1 and the first header 21_2 to partition the first region R1 from the second region R2.

[0065] In addition, if Figure 5 As shown, the first heat exchanger 11 has a common header 23_1 for the first region R1 and a common header 23_2 for the second region R2. A partition plate 3 is provided between the common header 23_1 and the common header 23_2 to partition the first region R1 from the second region R2.

[0066] The second heat exchanger 12 has a third region R3. The second heat exchanger 12 has a first header 21_3 in the third region R3, a second header 22_3 in the third region R3, and a common header 23_3 in the third region R3.

[0067] The third region R3 is a region where the supercooled liquid flows. When the length L3 of the heat exchange portion in the longitudinal direction of the third region R3 is set too large, the refrigerant of the superheated gas may flow into the second region R2. In this case, since the flow direction of the refrigerant in the first region R1 is made to flow in the opposite direction to the air flow direction, the effect of improving the heat exchange performance is reduced. In addition, compared with the refrigerant in the supercooled liquid state, the region where the superheated gas and the refrigerant in the gas-liquid two-phase state flow into which the pressure loss is large becomes smaller, so the pressure loss increases, which leads to a decrease in the heat exchange performance.

[0068] In Embodiment 2, when the length of the first region R1 in the longitudinal direction is set to L1, the length of the second region R2 in the longitudinal direction is set to L2, and the length of the third region R3 in the longitudinal direction is set to L3, (L1+L2) / 2>L3. The sum of the length L1 of the heat exchange portion in the longitudinal direction of the first region R1 of the first heat exchanger 11 and the length L2 of the heat exchange portion in the longitudinal direction of the second region R2 is longer than the length L3 of the heat exchange portion in the longitudinal direction of the third region R3 of the second heat exchanger 12. In addition, in Embodiment 2, L2>L1.

[0069] The first header 21_1 has a refrigerant inlet 21_1_A through which the refrigerant flows in. The first header 21_2 has a refrigerant outlet 21_2_B through which the refrigerant flowing in from the refrigerant inlet 21_1_A flows out.

[0070] The first header 21_3 has a refrigerant inlet 21_3_A into which the refrigerant flowing out from the refrigerant outlet 21_2_B flows in. The second header 22_3 has a refrigerant outlet 22_3_B from which the refrigerant flows out.

[0071] The refrigerant outflow port 21_2_B and the refrigerant inflow port 22_3_A are connected by a connecting pipe 4. The refrigerant inflow port 21_3_A is provided at an end portion of the first header 21_3 in the third region R3 on a side away from the refrigerant outflow port 21_2_B.

[0072] The refrigerant flowing into the first heat exchanger 11 from the refrigerant inlet 21_1_A of the first header 21_1 first flows in the first region R1 in a direction opposite to the air flow direction. The refrigerant flowing through the first region R1 flows into the second header 22 of the first region R1 and flows in the second region R2 in parallel with the air flow direction.

[0073] The refrigerant flowing through the second region R2 flows into the first header 21_2 and flows out from the refrigerant outlet 21_2_B. The refrigerant flowing out from the refrigerant outlet 21_2_B then flows into the refrigerant inlet 21_3_A of the first header 21_3 of the third region R3 of the second heat exchanger 12 through the connecting pipe 4.

[0074] The refrigerant having flowed into the refrigerant inlet 21_3_A flows in the third region R3 in a direction opposite to the air flow direction, and flows out of the second heat exchanger 12 .

[0075] In addition, the heat exchanger 100 of embodiment 2 is also applicable to situations other than the side flow frame. For example, a plurality of heat exchangers 100 may be arranged on all four sides of the top flow outdoor unit frame 7 in a manner surrounding the fan 5, and the top flow outdoor unit frame 7 blows out the air sucked from the side of the frame from the upper part of the frame.

[0076] Figure 7 1 is a diagram showing a state in which two heat exchangers 100_A and 100_B are arranged on four sides in the outdoor unit housing 7 so as to surround the fan 5 according to the second embodiment. Figure 7 In, yes Figure 5 The common header 23 and the heat transfer tube 1 are omitted and not shown. Figure 7 In the figure, the arrows indicate the flow of refrigerant and the hollow arrows indicate the direction of air flow.

[0077] like Figure 7 As shown, there are two heat exchangers 100_A and 100_B, and the two heat exchangers 100_A and 100_B have a first heat exchanger 11 and a second heat exchanger 12. The heat exchanger 100_A and the heat exchanger 100_B are arranged to surround the fan 5.

[0078] and Figure 6 Similarly, the first heat exchanger 11 and the second heat exchanger 12 of the heat exchanger 100_A are arranged in an L shape to surround the fan 5. The first heat exchanger 11 and the second heat exchanger 12 of the heat exchanger 100_B are arranged in an L shape to surround the fan 5.

[0079] <Effect>

[0080] According to the heat exchanger 100 of the second embodiment, since the first region R1 and the second region R2 are included in one first heat exchanger 11, it is possible to save space and increase the heat transfer area.

[0081] In addition, according to the heat exchanger 100 of Embodiment 2, the first heat exchanger 11 includes the first region R1 and the second region R2. That is, as an example of a method of switching the flow direction of the refrigerant relative to the air flowing into the heat exchanger 100 from opposite to parallel, a method of providing a partition plate 3 that divides the internal space of the first header 21 is adopted. Therefore, the influence on the structure of the heat exchanger 100 can be minimized, the refrigerant flow can be switched, and the manufacturing cost can be suppressed.

[0082] When the ends of the adjacent headers of the first heat exchanger 11 and the second heat exchanger 12 are connected to each other through the connecting pipe 4, they are easily affected by structural limitations such as pressure loss and bending angle. When the adjacent headers of the first heat exchanger 11 and the second heat exchanger 12 are to be connected, if the connecting pipe 4 is bent at a steeper angle for connection, the pressure loss is large. In addition, a bending radius greater than a certain value is required depending on the diameter of the connecting pipe 4, or a component for connecting the connecting pipe 4 is installed at the end of the header, so the distance between the first heat exchanger 11 and the second heat exchanger 12 becomes longer. As a result, the frame of the heat exchanger 100 equipped with the first heat exchanger 11 and the second heat exchanger 12 is enlarged.

[0083] Furthermore, when the heat exchanger 100 including the first heat exchanger 11 and the second heat exchanger 12 is to be mounted without changing the size of the housing, the heat transfer area of ​​the heat exchanger 100 has to be reduced due to structural restrictions such as piping. As a result, the installation area of ​​the heat exchanger 100 is reduced, and the heat exchange performance is reduced.

[0084] In the heat exchanger 100 of Embodiment 2, the refrigerant outflow port 21_2_B and the refrigerant inflow port 21_3_A are connected by the connecting pipe 4. The refrigerant inflow port 21_3_A is provided at the end of the first header 21_3 in the third region R3 away from the refrigerant outflow port 21_2_B.

[0085] Therefore, the heat transfer area between the first heat exchanger 11 and the second heat exchanger 12 can be maximized, and the installation area of ​​the heat exchanger 100 can be increased, so it is expected that the heat exchange performance will be improved. As a result, by installing the heat exchanger 100 of the second embodiment, the performance of the heat exchanger 100 can be maximized.

[0086] Implementation method 3.

[0087] Figure 81 is a diagram showing a state where the heat exchanger 100 of Embodiment 3 is arranged in the outdoor unit housing 7. The outdoor unit housing 7 is a top-flow type housing. Figure 8 In, yes Figure 5 The common header 23 shown is omitted and not shown. Figure 8 In the figure, the arrows indicate the flow of refrigerant and the hollow arrows indicate the direction of air flow.

[0088] like Figure 8 As shown, the heat exchanger 100 of the third embodiment includes a first heat exchanger 11, a second heat exchanger 12, and a third heat exchanger 13. The first heat exchanger 11, the second heat exchanger 12, and the third heat exchanger 13 are arranged in a U-shape so as to surround the fan 5.

[0089] The first heat exchanger 11 has a first region R1, and the refrigerant forms a counterflow relative to the air flow direction. The second heat exchanger 12 has a second region R2, and the refrigerant forms a parallel flow relative to the air flow direction. The third heat exchanger 13 has a third region R3, and the refrigerant forms a counterflow relative to the air flow direction.

[0090] The second header 22_1 of the first region R1 on the upwind side of the first heat exchanger 11 is connected to the second header 22_2 of the second region R2 on the upwind side of the second heat exchanger 12 via the connecting pipe 4. The first header 21_2 of the second region R2 on the leeward side of the second heat exchanger 12 is connected to the first header 21_3 of the third region R3 on the leeward side of the third heat exchanger 13 via the connecting pipe 4.

[0091] The connection between the first heat exchanger 11 and the second heat exchanger 12 is achieved by connecting the outer second header 22_1 to the outer second header 22_2 by the connecting pipe 4. The connection between the second heat exchanger 12 and the third heat exchanger 13 is achieved by connecting the inner first header 21_2 to the inner first header 21_3 by the connecting pipe 4.

[0092] That is, when the first heat exchanger 11 in which the refrigerant flows as countercurrent flow and the second heat exchanger 12 in which the refrigerant flows as parallel flow are connected by the connecting pipe 4, the outer second header 22_1 and the outer second header 22_2 of the second region R2 are connected.

[0093] When the second heat exchanger 12 through which the refrigerant flows as a parallel flow and the third heat exchanger 13 through which the refrigerant flows as a counterflow are connected by the connecting pipe 4, the inner first header 21_2 and the inner first header 21_3 are connected.

[0094] When connecting the header inside the frame, if you bend the pipes in the same way as when connecting the header outside, a certain amount of space will be required. Figure 8 As shown, the refrigerant inlet 21_3_A is provided at the end of the first header 21_3 in the third region R3 away from the refrigerant outlet 21_2_B. Therefore, according to the heat exchanger 100 of Embodiment 3, the heat exchanger 100 can be space-saving, and the improvement of heat exchange performance and the maximization of the installation area can be expected.

[0095] The embodiments are presented as examples and are not intended to limit the scope of the claims. The embodiments can be implemented in various other ways, and various omissions, substitutions, and changes can be made without departing from the scope of the embodiment. These embodiments and their variations are included in the scope and purpose of the embodiment.

[0096] Description of Reference Numerals

[0097] 1 heat transfer tube; 1_1 downwind heat transfer tube row; 1_2 upwind heat transfer tube row; 3 partition plate; 4 connecting pipe; 5 fan; 6 compressor; 7 outdoor unit frame; 8 expansion valve; 11 first heat exchanger; 12 second heat exchanger; 13 third heat exchanger; 21 first header; 21_1 first header of the first area; 21_1_A refrigerant inlet; 21_2 first header of the second area; 21_2_B refrigerant outlet; 21_3 first header of the third area; 21_3_A refrigerant inlet; 22 second header; 22_1 second header of the first area; 22_2 second header of the second area; 22_3 second header of the third area; 22_3 _B refrigerant outflow port; 23 common header; 23_1 common header for the first area; 23_2 common header for the second area; 23_3 common header for the third area; 100, 100_A, 100_B heat exchangers; 100_1 heat exchange section on the leeward side; 100_2 heat exchange section on the upwind side; 100a condenser; 100b evaporator; 110 refrigerant circuit; 300 air conditioning device; R1 first area; R2 second area; R3 third area; L1 length of the heat exchange section in the length direction of the first area; L2 length of the heat exchange section in the length direction of the second area; L3 length of the heat exchange section in the length direction of the third area; T temperature; S entropy.

Claims

1. A heat exchanger, wherein: have: The downwind heat exchange part is arranged on the downstream side of the air flow direction; an upwind heat exchange portion, arranged on an upstream side in the air flow direction compared to the downwind heat exchange portion; and common header, The downwind side heat exchange unit comprises: a leeward heat transfer tube array having heat transfer tubes arranged at intervals in a direction intersecting the air flow direction; and A first header is connected to the lower end of the leeward heat transfer tube array, The upwind side heat exchange unit comprises: an upwind heat transfer tube array having heat transfer tubes arranged at intervals in a direction intersecting the air flow direction; and The second header is connected to the lower end of the upwind heat transfer tube array, The common header is connected to the upper end of the leeward heat transfer tube row and the upper end of the upwind heat transfer tube row, and connects the leeward heat transfer tube row and the upwind heat transfer tube row. When the leeward heat exchanger and the upwind heat exchanger function as condensers, the leeward heat exchanger and the upwind heat exchanger include: a first region in which the refrigerant flowing into the first header flows in a direction opposite to the air flow direction and flows into the second header; a second region in which the refrigerant flowing into the second header through the first region flows in parallel with respect to the air flow direction and flows into the first header; as well as A third region in which the refrigerant having flowed into the first header through the second region flows in the opposite direction with respect to the air flow direction and flows into the second header.

2. The heat exchanger according to claim 1, wherein: The length of the downwind heat exchange portion in the length direction of the first header in the first region and the length of the upwind heat exchange portion in the length direction of the second header in the first region are denoted as L1. The length of the downwind heat exchange portion in the length direction of the first header in the second region and the length of the upwind heat exchange portion in the length direction of the second header in the second region are set to L2, and When the length of the downwind heat exchange portion in the length direction of the first header in the third region and the length of the upwind heat exchange portion in the length direction of the second header in the third region are defined as L3, (L1+L2) / 2>L3.

3. The heat exchanger according to claim 2, wherein: L2>L1.

4. The heat exchanger according to any one of claims 1 to 3, wherein: The common header and the first header each include a partition plate that partitions the first region and the second region.

5. The heat exchanger according to any one of claims 1 to 4, wherein: The downwind heat exchange part and the upwind heat exchange part are divided into: a first heat exchanger having the first region and the second region; as well as a second heat exchanger having the third region, The first header of the first heat exchanger has a refrigerant outflow port through which the refrigerant flows out. The first header of the second heat exchanger has a refrigerant inlet into which the refrigerant flowing out of the refrigerant outlet flows. The heat exchanger includes a connecting pipe connecting the refrigerant outflow port and the refrigerant inflow port. The first heat exchanger and the second heat exchanger are arranged in an L shape in a plan view. The refrigerant inlet is provided at an end portion of the first header on a side away from the refrigerant outlet.

6. The heat exchanger according to any one of claims 1 to 5, wherein: The refrigerant flowing through the first region includes superheated gas, and the refrigerant flowing through the third region includes supercooled liquid.

7. A heat exchanger, wherein: A side-flow type frame for accommodating the heat exchanger according to any one of claims 1 to 6 is provided.

8. A heat exchanger, wherein: A top-flow frame is provided for accommodating the heat exchanger according to any one of claims 1 to 6.

9. A refrigeration cycle device, wherein: A heat exchanger according to any one of claims 1 to 8.

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