Heat exchanger

Abstract

A heat exchanger is provided with: a plurality of first tubes (221) to which a refrigerant is distributed from a first tank (21); a first steering box (23) and a second steering box (24) into which the refrigerant flows from the first pipe (221); and a plurality of second pipes (251) to which the refrigerant is distributed from the second steering box (24). In an internal flow path from the plurality of first pipes (221) to the plurality of second pipes (251) through the first steering box (23) and the second steering box (24), a first region (Tc) and a second region (Tf, Tr), which have different pressure losses when a refrigerant having the same flow rate flows, are arranged side by side in the stacking direction (y).

Description

[0001] Cross-reference of related applications

[0002] This application is based on and claims priority to Japanese Patent Application No. 2023-041658, filed on March 16, 2023, the entire contents of which are incorporated herein by reference. Technical Field

[0003] This invention relates to heat exchangers. Background Technology

[0004] The heat exchanger described in Patent Document 1 includes: tubes, which are a plurality of tubes arranged in a first column and a second column, through which refrigerant circulates; and a first manifold box and a second manifold box, each containing a column of tubes. A longitudinal partition is provided within the first manifold box, dividing the box longitudinally into a refrigerant inlet compartment containing the first column of tubes and a refrigerant outlet compartment containing the second column of tubes.

[0005] Existing technical documents

[0006] Patent documents

[0007] Patent Document 1: Japanese Patent Publication No. 2014-518370

[0008] When a heat exchanger is used in the condenser of a refrigeration cycle, the superheated gaseous refrigerant flowing into the heat exchanger undergoes heat exchange, passes through a gas-liquid two-phase state, becomes subcooled refrigerant, and flows out. When the heat exchanger described in Patent Document 1 is used as a condenser, the superheated gaseous refrigerant flows into the refrigerant inlet compartment and undergoes heat exchange while passing through the first row of pipes, becoming a gas-liquid two-phase refrigerant. Then, the refrigerant undergoes further heat exchange while passing through the second row of pipes via the second manifold box, becoming subcooled refrigerant and reaching the refrigerant outlet compartment. The first and second rows of pipes are arranged upstream and downstream of the airflow, respectively. Therefore, for example, when the condenser is used in a heating device inside a vehicle, by overlapping the second row of pipes through which the low-temperature subcooled refrigerant passes and the first row of pipes through which the high-temperature superheated gaseous refrigerant passes in the airflow direction, the outlet temperature is adjusted to be uniform.

[0009] In the heat exchanger described in Patent Document 1, the superheated gaseous refrigerant flowing into the refrigerant inlet compartment is naturally distributed along the length of the refrigerant inlet compartment and flows into the first row of tubes. Therefore, as the length of the refrigerant inlet compartment increases, the pressure loss in the refrigerant inlet compartment increases, and the flow rate of the shortcut flow of superheated gaseous refrigerant into the vicinity of the inlet of the refrigerant inlet compartment increases. As a result, less superheated gaseous refrigerant flows to the side opposite to the inlet of the refrigerant inlet compartment, and a deterioration in the temperature distribution along the tube stacking direction is conceivable. Summary of the Invention

[0010] The purpose of this disclosure is to provide a heat exchanger that can effectively suppress the increase in refrigerant pressure loss while maintaining a good temperature distribution in the tube stack direction.

[0011] A heat exchanger based on one aspect of this disclosure includes: a first manifold, through which refrigerant, as a superheated gas, flows into the first manifold from an upstream flow path; a plurality of first pipes, through which refrigerant is distributed from the first manifold; a first diverting box, through which refrigerant flows from the first pipes; a second diverting box, through which refrigerant flows from the first diverting box; a plurality of second pipes, through which refrigerant is distributed from the second diverting box; and a second manifold, through which refrigerant, as a subcoolant, flows from the second pipes into the second manifold and out to a downstream flow path. In the internal flow path from the plurality of first pipes through the first and second diverting boxes to the plurality of second pipes, first regions and second regions, with different pressure losses when refrigerant of the same flow rate passes through, are arranged in the stacking direction of the plurality of first and second pipes. Attached Figure Description

[0012] Figure 1 This is a perspective view showing the overall structure of the heat exchanger in the first embodiment.

[0013] Figure 2 It is Figure 1 The heat exchanger shown is displayed in a three-dimensional view.

[0014] Figure 3 It is Figure 2 The heat exchanger shown is a top view presented by unfolding its planar structure.

[0015] Figure 4 (A) and (B) respectively represent Figure 3 Sectional views of IVA-IVA section and IVB-IVB section.

[0016] Figure 5 It is a pH graph that has been written into the refrigeration cycle.

[0017] Figure 6This is a top view showing a heat exchanger of the reference example unfolded in plan.

[0018] Figure 7 This is a top view showing a heat exchanger of the reference example unfolded in plan.

[0019] Figure 8 (A) and (B) are sectional views showing the cross-sectional structures of the first and second steering boxes in the reference example.

[0020] Figure 9 This is a top view showing the heat exchanger in a modified example of the first embodiment, unfolded in plan.

[0021] Figure 10 This is a top view showing the heat exchanger in the second embodiment unfolded in plan.

[0022] Figure 11 This is a top view showing the heat exchanger in the third embodiment unfolded in plan.

[0023] Figure 12 (A) and (B) respectively represent Figure 11 Sectional views of sections VIIIA-VIIIA and VIIIB-VIIIB.

[0024] Figure 13 This is a top view showing the heat exchanger in the fourth embodiment unfolded in plan.

[0025] Figure 14 (A) and (B) respectively represent Figure 13 Sectional views of sections XA-XA and XB-XB.

[0026] Figure 15 This is a cross-sectional view showing the cross-sectional structure of the second steering box of the heat exchanger in the fourth embodiment.

[0027] Figure 16 This is a top view showing the heat exchanger in the fifth embodiment unfolded in plan.

[0028] Figure 17 It means Figure 16 A diagram showing an example of the tubes used in a heat exchanger.

[0029] Figure 18 This is a top view showing the heat exchanger in the sixth embodiment unfolded in plan.

[0030] Figure 19 This is a perspective view showing the overall structure of the heat exchanger in the seventh embodiment.

[0031] Figure 20yes Figure 19 The diagram shows a three-dimensional cross-sectional view of the steering gearbox.

[0032] Figure 21 (A) and (B) respectively represent Figure 20 Sectional views of sections XVIA-XVIA and XVIB-XVIB.

[0033] Figure 22 It means Figure 21 A cross-sectional view of a modified example.

[0034] Figure 23 This is a graph showing the relationship between Nsc / Nall and the temperature difference ΔT between the left and right sides of the air blown out from the heat exchanger.

[0035] Figure 24 It is a graph showing the relationship between the total opening area AS of the connecting holes and the pressure loss PL of the refrigerant. Detailed Implementation

[0036] Hereinafter, this embodiment will be described with reference to the accompanying drawings. To facilitate understanding, the same symbols will be used as much as possible to refer to the same components in each drawing, and repeated descriptions will be omitted.

[0037] like Figure 1 As shown, the heat exchanger 2 includes a first manifold box 21, a first core 22, a first steering box 23, a second steering box 24, a second core 25, and a second manifold box 26. The heat exchanger 2 performs heat exchange between air, which is a first fluid, and a refrigerant, which is a second fluid. The heat exchanger 2 is used as a condenser for heating the interior of, for example, a car. The heat exchanger 2, as a condenser, is incorporated into a refrigeration cycle (not shown). The heat exchanger 2 incorporated into the refrigeration cycle is connected to an upstream flow path and a downstream flow path of the refrigeration cycle.

[0038] The first manifold 21 has an inlet 211. The inlet 211 is a portion through which refrigerant, as a second fluid, flows in from the upstream side of the refrigeration cycle. The refrigerant flowing into the inlet 211 flows into the first manifold 21. The refrigerant flowing into the first manifold 21 flows into the first core 22. The refrigerant flowing into the first core 22 flows into the first deflector 23 while exchanging heat with air, which is the first fluid.

[0039] The refrigerant flowing into the first diversion box 23 flows into the second diversion box 24. The refrigerant flowing into the second diversion box 24 flows into the second core 25. The refrigerant flowing into the second core 25 flows into the second manifold box 26 while exchanging heat with air, which is the first fluid.

[0040] The second manifold 26 has an outlet 261. The outlet 261 is a portion that allows refrigerant to flow out into the downstream flow path of the refrigeration cycle. The refrigerant flowing into the second manifold 26 flows out into the downstream flow path from the outlet 261.

[0041] exist Figure 1 In this design, the direction in which air flows through the first core 22 and the second core 25 is defined as the x-direction, and the x-axis is defined along this direction. Furthermore, the direction perpendicular to the x-direction and being the length direction of the first manifold box 21, the second manifold box 26, the first deflector box 23, and the second deflector box 24 is defined as the y-direction, and the y-axis is defined along this direction. Moreover, the direction perpendicular to both the x-direction and the y-direction... Figure 1 The direction from the lower side to the upper side, that is, from the first steering box 23 to the first manifold box 21 and from the second steering box 24 to the second manifold box 26, is defined as the z-direction, and the z-axis is defined along this direction. In the following explanation, the x-direction, y-direction, and z-direction as defined above will be used. Furthermore, the z-direction is... Figure 1 The direction from the bottom to the top. Figure 1 The vertical orientation does not necessarily have to be aligned with the vertical orientation. Therefore, when the heat exchanger 2 is actually installed in the vehicle, it can also be configured such that the first manifold box 21 and the second manifold box 26 are vertically downwards, and the first steering box 23 and the second steering box 24 are vertically upwards.

[0042] Figure 2 It is used to Figure 1 The heat exchanger 2 shown is unfolded to illustrate its internal structure in a three-dimensional view. It shows the internal structure from... Figure 1 The state shown indicates that the first manifold box 21, the first core 22, and the first steering box 23 are separated from the second manifold box 26, the second core 25, and the second steering box 24, and rotated 90° about the z-axis. The x, y, and z axes relative to the first manifold box 21, the first core 22, and the first steering box 23 are shown near the first manifold box 21, the first core 22, and the first steering box 23. The x, y, and z axes relative to the second manifold box 26, the second core 25, and the second steering box 24 are shown near the second manifold box 26, the second core 25, and the second steering box 24.

[0043] The first core portion 22 includes a first tube 221, a first fin 222, and a side plate 223. The first tube 221 is configured to allow refrigerant, which serves as a second fluid, to flow within it. One end of the first tube 221 communicates with the inside of a first manifold box 21, and the other end communicates with the inside of a first deflector box 23. Multiple first tubes 221 are provided, and the first tubes 221 and the first fins 222 are alternately stacked. A pair of side plates 223 are provided such that they clamp the stacked first tubes 221 and first fins 222 in the stacking direction.

[0044] The first fin 222 is bent into a wavy shape. An airflow path for air, which is a first fluid, is provided within the first fin 222. A refrigerant flow path for refrigerant, which is a second fluid, is provided within the first tube 221. The first fin 222 and the first tube 221 are in contact, configured to allow heat exchange. Therefore, the air flowing in the first fin 222 and the refrigerant flowing in the first tube 221 are configured to exchange heat.

[0045] The first steering box 23 has a partition wall 23w. The partition wall 23w is a wall that abuts against the second steering box 24. The partition wall 23w is provided with connecting holes 23f1, 23f2, 23c1, 23c2, 23c3, 23c4, 23r1, and 23r2. The connecting holes 23f1, 23f2, 23c1, 23c2, 23c3, 23c4, 23r1, and 23r2 are holes for allowing refrigerant to pass through.

[0046] The connecting holes 23f1, 23f2, 23c1, 23c2, 23c3, 23c4, 23r1, and 23r2 are all circular in shape. Furthermore, setting all the connecting holes 23f1, 23f2, 23c1, 23c2, 23c3, 23c4, 23r1, and 23r2 to be circular is for ease of explanation; the shape of the connecting holes is not particularly limited and can be various shapes, including, for example, semicircles and rectangles.

[0047] Connecting holes 23f1 and 23f2 are contained in the second region Tf. Connecting holes 23c1, 23c2, 23c3, and 23c4 are contained in the first region Tc. Connecting holes 23r1 and 23r2 are contained in the second region Tr. The number of connecting holes 23f1 and 23f2 formed in a second region Tf is less than the number of connecting holes 23c1, 23c2, 23c3, and 23c4 formed in the first region Tc. Similarly, the number of connecting holes 23r1 and 23r2 formed in a second region Tr is less than the number of connecting holes 23c1, 23c2, 23c3, and 23c4 formed in the first region Tc. In the ratio of the opening area of ​​the connecting holes 23f1, 23f2, 23c1, 23c2, 23c3, 23c4, 23r1, and 23r2 to the area of ​​the partition wall 23w, the opening ratio of the first region Tc is higher than that of the second region Tf, and the opening ratio of the first region Tc is higher than that of the second region Tr. The pressure loss of the second regions Tf and Tr is higher than that of the first region Tc, and a pair of second regions Tf and Tr are provided across the first region Tc.

[0048] The second steering box 24 has a partition wall 24w. The partition wall 24w is a wall that abuts against the first steering box 23. The partition wall 24w is provided with connecting holes 24f1, 24f2, 24c1, 24c2, 24c3, 24c4, 24r1, and 24r2. The connecting holes 24f1, 24f2, 24c1, 24c2, 24c3, 24c4, 24r1, and 24r2 are holes for allowing refrigerant to pass through. All connecting holes 24f1, 24f2, 24c1, 24c2, 24c3, 24c4, 24r1, and 24r2 are of the same circular shape.

[0049] Connecting holes 24f1 and 24f2 are contained in the second region Tf. Connecting holes 24c1, 24c2, 24c3, and 24c4 are contained in the first region Tc. Connecting holes 24r1 and 24r2 are contained in the second region Tr. The number of connecting holes 24f1 and 24f2 formed in a second region Tf is less than the number of connecting holes 24c1, 24c2, 24c3, and 24c4 formed in the first region Tc. Similarly, the number of connecting holes 24r1 and 24r2 formed in a second region Tr is less than the number of connecting holes 24c1, 24c2, 24c3, and 24c4 formed in the first region Tc. In the ratio of the opening area of ​​the connecting holes 24f1, 24f2, 24c1, 24c2, 24c3, 24c4, 24r1, and 24r2 to the area of ​​the partition wall 24w, the opening ratio of the first region Tc is higher than that of the second region Tf, and the opening ratio of the first region Tc is higher than that of the second region Tr. The pressure loss of the second regions Tf and Tr is higher than that of the first region Tc. A pair of second regions Tf and Tr are provided across the first region Tc.

[0050] With partition walls 23w and 24w in contact, the connecting holes 23f1 and 24f1 in the second region Tf are connected. Similarly, connecting holes 23f2 and 24f2 are connected. In the first region Tc, connecting holes 23c1 and 24c1 are connected. Similarly, connecting holes 23c2, 24c2, 23c3, and 24c4 are connected. In the second region Tr, connecting holes 23r1 and 24r1 are connected, and connecting holes 23r2 and 24r2 are connected.

[0051] In addition, the following, such as Figure 3As shown, the region in the second region Tf containing the connecting holes 23f1, 23f2, 24f1, and 24f2 is referred to as the "second outer region Tf1," and the region other than the outer region Tf1 is referred to as the "second inner region Tf2." Similarly, the region in the second region Tr containing the connecting holes 23r1, 23r2, 24r1, and 24r2 is referred to as the "second outer region Tr1," and the region other than the outer region Tr1 is referred to as the "second inner region Tr2." The second inner regions Tf2 and Tr2 are respectively positioned between the second outer regions Tf1 and Tr1 and the first region Tc. The first region Tc is sandwiched between the second region Tf and the second region Tr.

[0052] Figure 3 It is Figure 2 The top view shown is a planar unfolded view of the heat exchanger 2. Figure 2 Similarly, the x, y, and z axes relative to the first manifold 21, the first core 22, and the first steering box 23 are shown near the first manifold 21, the first core 22, and the first steering box 23. The x, y, and z axes relative to the second manifold 26, the second core 25, and the second steering box 24 are shown near the second manifold 26, the second core 25, and the second steering box 24.

[0053] Figure 4 (A) indicates along Figure 3 A sectional view of the cross-sectional structure of IVA-IVA. Figure 4 (B) indicates along Figure 3 A sectional view of the cross-sectional structure of IVB-IVB. (See attached image.) Figure 4 As shown in (B), the interior of the first steering box 23 is connected in the y-direction, which is its length direction. Figure 4 As shown in (A), the interior of the second steering box 24 is also connected in the y direction, which is its length direction.

[0054] While referring to Figure 5 The refrigeration cycle will be explained. Figure 5 The refrigeration cycle is plotted in a pH graph where enthalpy (h) is on the horizontal axis and pressure (p) is on the vertical axis. Figure 5 In the curve shown, the portion to the left of the critical point P10 is called the saturated liquid line M11, and the portion to the right of the critical point P10 is called the saturated vapor line M12. For example... Figure 5 As shown, the refrigeration cycle has a compression stroke, a condensation stroke, an expansion stroke, and an evaporation stroke.

[0055] The compression stroke is the process of compressing the refrigerant gas that evaporates in the evaporation stroke, forming a superheated refrigerant gas at high temperature and high pressure. The condensation stroke is the process of removing heat from the superheated refrigerant gas to form a subcooled refrigerant. The expansion stroke is the process of reducing the pressure of the high-pressure subcooled refrigerant. The evaporation stroke is the process of evaporating the liquid refrigerant by imparting heat to it.

[0056] For example, the evaporator is... Figure 5 The heat exchanger used in the evaporation process of the refrigeration cycle is shown. The refrigerant, in a gas-liquid two-phase state generated during the expansion stroke, flows into the evaporator. In the evaporator, the gas-liquid two-phase refrigerant exchanges heat with the air, thereby changing the state of the refrigerant as indicated by arrow L11. That is, the gas-liquid two-phase refrigerant changes into a low-temperature, low-pressure gaseous state by absorbing heat from the air. The intersection of arrow L11 and the saturated vapor line M12 indicates the point where the refrigerant changes from a gas-liquid two-phase state to a gaseous state. Thus, in the evaporator, essentially only two states exist as the refrigerant: the gas-liquid two-phase state and the gaseous state. Therefore, to homogenize the temperature distribution of the air blown out of the evaporator, it is generally sufficient to homogenize the refrigerant flow rate in the region of the gaseous refrigerant in the evaporator, the so-called superheated gas region.

[0057] In contrast, Figures 1-4The heat exchanger 2 shown in this embodiment functions as a condenser for the condensation process. Therefore, the refrigerant in a gaseous state, generated during the compression process, flows into the heat exchanger 2 at high temperature and high pressure. In the heat exchanger 2, the gaseous refrigerant exchanges heat with the air, thereby changing the state of the refrigerant as indicated by arrow L12. That is, the gaseous refrigerant releases heat to the air, and thus the state of the refrigerant changes sequentially to a gaseous state, a gas-liquid two-phase state, and a liquid state. The intersection of arrow L12 and the saturated vapor line M12 indicates the point where the state of the refrigerant changes from a gaseous state to a gas-liquid two-phase state. The intersection of arrow L12 and the saturated liquid line M11 indicates the point where the state of the refrigerant changes from a gas-liquid two-phase state to a liquid state. Thus, in the heat exchanger 2, the refrigerant exists in three states: gaseous state, gas-liquid two-phase state, and liquid state. Therefore, to achieve a uniform temperature distribution of the air blown out of the heat exchanger 2, it is necessary to uniformize not only the refrigerant flow rate in the region where the refrigerant exists in a gaseous state (the so-called superheated gas region) within the heat exchanger 2, but also the refrigerant flow rate in the region where the refrigerant exists in a liquid state (the so-called subcooled liquid region). In other words, the temperature distribution in the heat exchanger 2 that overlaps with the temperature distribution of the air in the superheated gas region and the air in the subcooled liquid region becomes the final temperature distribution of the air blown out of the heat exchanger 2. Therefore, adjusting the positional relationship between the superheated gas region and the subcooled liquid region within the heat exchanger 2 is crucial for achieving a uniform temperature distribution of the air blown out of the heat exchanger 2. Consequently, compared to an evaporator, the heat exchanger 2 in this embodiment, which functions as a condenser, has a practical limitation in achieving a uniform air temperature distribution.

[0058] Furthermore, in the heat exchanger 2, which functions as a condenser, for example in Figure 3 A superheated gas region is generated as shown by the dashed line SH. High-velocity gaseous refrigerant flows into this superheated gas region SH through inlet 211. Therefore, when adjusting the refrigerant flow rate in the superheated gas region by, for example, installing a throttling device in the first manifold 21, there is concern that the pressure loss of the gaseous refrigerant will increase. This inability to use a solution such as installing a throttling device in the first manifold 21 is a major reason why it is difficult to achieve uniform air temperature distribution in the heat exchanger 2.

[0059] Next, while discussing the structure of the heat exchanger 2 in this embodiment and Figures 6-8 The function and effect of the heat exchanger 2 in this embodiment will be explained by comparing its structure with that of the heat exchanger 200 in the reference example shown.

[0060] Figure 6 and Figure 7The heat exchanger 200 of the reference example shown has, except that the partition walls 23w of the first turning box 23 have equally formed connecting holes 231, and the partition walls 24w of the second turning box 24 have equally formed connecting holes 241, similar to... Figures 1-4 The heat exchanger 2 shown has the same construction. Furthermore, in Figure 6 and Figure 7 In the heat exchanger 200 shown, for the relationship with Figures 1-4 The same elements of the heat exchanger 2 shown are labeled with the same symbols, thus omitting repeated descriptions.

[0061] exist Figure 6 and Figure 7 In the heat exchanger 200 shown, the temperature distribution of the second core 25, located upstream in the x-direction which is the air flow direction, varies depending on the refrigerant flow rate.

[0062] Specifically, when the refrigerant flow rate is high, when Figure 6 As the first manifold 21 shown increases in length in the y-direction, the pressure loss of the refrigerant in the first manifold 21 increases. Therefore, more refrigerant flows in the first core 22 via a shortcut in the near-front region 224 near the inlet 211, resulting in a higher refrigerant flow rate in region 224. Conversely, the refrigerant flow rate in the opposite inner region 225 decreases. Consequently, in the second core 25, the refrigerant flow rate also increases in its near-front region 254, while the refrigerant flow rate in its inner region 255 decreases. Therefore, a supercoolant region SC10 is formed in the inner region 255 of the second core 25, resulting in a temperature distribution in the second core 25 that is significantly lower than the temperatures of the near-front region 254 and the intermediate region 256.

[0063] On the other hand, when the refrigerant flow rate is low, the pressure loss of the refrigerant in the first manifold box 21 is reduced. Therefore, in Figure 7In the first core 22 shown, less refrigerant flows through the near-front region 224 near the inlet 211, while more refrigerant flows inward due to inertia inside the first manifold 21. Therefore, in the first manifold 21, the flow rate of refrigerant flowing in the intermediate region 226 is less compared to the near-front region 224 and the inner region 225. Consequently, in the second core 25, the flow rate of refrigerant flowing in its near-front region 254 and the inner region 255 is also greater, while the flow rate of refrigerant flowing in its intermediate region 256 is reduced. Therefore, a supercoolant region SC20 is formed in the intermediate region 256 of the second core 25, resulting in a temperature distribution in the second core 25 that is significantly lower in the intermediate region 256 compared to the respective temperatures of the near-front region 254 and the inner region 255.

[0064] In this way, a different temperature distribution corresponding to the refrigerant flow rate is formed in the second core 25 of the heat exchanger 200.

[0065] In addition, Figure 6 and Figure 7 In the heat exchanger 200 of the reference example shown, in such a way... Figure 8 As shown in (A) and (B), when a partition wall 243 is formed inside the second steering box 24 in such a way as to divide each of the plurality of connecting holes 241, and a partition wall 233 is formed inside the first steering box 23 in such a way as to divide each of the plurality of connecting holes 231, the refrigerant in each steering box 23, 24 will not be pressure-equalized. Therefore, Figure 6 and Figure 7 The deviation in the refrigerant flow distribution shown is more likely to be more pronounced, and as a result, there is a possibility that the temperature distribution of the second core 25 will further deteriorate.

[0066] Regarding this point, in the heat exchanger 2 of this embodiment, as... Figure 3 As shown, the superheated refrigerant gas flowing into the first manifold 21 is distributed to multiple first pipes 221 and flows toward the first diverter 23. Due to this flow, a superheated gas region SH is formed on the first manifold 21 side. Figure 4 As shown in (A) and (B), the interiors of each of the diversion boxes 23 and 24 are connected in the y-direction, which is their length direction. Therefore, when the refrigerant flows into the first diversion box 23 from the plurality of first pipes 221, the refrigerant is easily pressure-equalized inside the first diversion box 23.

[0067] Furthermore, when the refrigerant, after being homogenized inside the first diversion box 23, flows into the second diversion box 24 through the connecting holes, the refrigerant flow rate is controlled based on the configuration of the connecting holes formed in each diversion box 23, 24. However, since a uniform pressure state is maintained when the refrigerant flow rate is controlled in the second diversion box 24, a change in the state of the refrigerant due to density variation occurs.

[0068] Specifically, in the heat exchanger 2 of this embodiment, as described above, the pressure loss ratio of the second region Tf to Tr is configured as follows: Figure 3 The pressure loss in the first region Tc shown is high.

[0069] Refrigerant flowing into the first diverting box 23 flows into the second diverting box 24 through connecting holes 23f1, 23f2, 23c1, 23c2, 23c3, 23c4, 23r1, 23r2 and connecting holes 24f1, 24f2, 24c1, 24c2, 24c3, 24c4, 24r1, 24r2. Since the pressure loss in the second region Tf, Tr is higher than that in the first region Tc, the flow rate of refrigerant flowing in the second region Tf, Tr is relatively reduced compared to the flow rate of refrigerant flowing in the first region Tc, forming a subcoolant region SC. The subcoolant regions SC form a pair, separated by the first region Tc.

[0070] More specifically, in the heat exchanger 2 of this embodiment, in the first region Tc corresponding to the connecting holes 23c1, 23c2, 23c3, 23c4, 24c1, 24c2, 24c3, 24c4, the second outer region Tf1 corresponding to the connecting holes 23f1, 23f2, 24f1, 24f2, and the second outer region Tr1 corresponding to the connecting holes 23r1, 23r2, 24r1, 24r2, the refrigerant pressure loss is smaller compared to the second inner regions Tf2 and Tr2 where no connecting holes are formed. Therefore, the refrigerant flow rate in the second inner regions Tf2 and Tr2 is less than the refrigerant flow rate in the first region Tc, the second outer region Tf1, and the second outer region Tr1. As a result, a supercoolant region SC is formed in the second core 25 corresponding to the second inner regions Tf2 and Tr2, respectively. Thus, in this embodiment, as... Figure 3 As shown, connecting holes are formed in each of the steering boxes 23 and 24 to control the refrigerant flow rate of the second core 25, thereby... Figure 3 The supercoolant region SC is intentionally formed in the second core 25 in the manner shown. According to this structure, even when the refrigerant flow rate is either high or low, the supercoolant region SC is easily formed in the second core 25 in the portion corresponding to the second inner regions Tf2 and Tr2. That is, it is difficult for the supercoolant region SC to occur due to differences in refrigerant flow rate. Figure 6 and Figure 7 This is a situation where the position of the coolant region is offset as shown. Furthermore, in the heat exchanger 2 of this embodiment, due to... Figure 6 and Figure 7 The deterioration of the local temperature distribution shown is suppressed, thus making it easier to homogenize the temperature distribution in the y direction of the second core 25. As a result, it is easier to homogenize the temperature of the air blown out from the heat exchanger 2.

[0071] On the other hand, in such a heat exchanger 2, the refrigeration cycle is controlled so that the temperature of the refrigerant flowing out from outlet 261 reaches the target temperature. When such control is performed, for example in... Figure 7 In the heat exchanger 200 of the reference example shown, the temperature distribution of the air blown out of the heat exchanger 200 is prone to deterioration. For example, in Figure 7 In the heat exchanger 200 of the reference example shown, the construction of each of the turning boxes 23 and 24 employs... Figure 8 In the configuration shown in (A) and (B), there is a possibility that the temperature of the intermediate region 256 may be too low compared to the temperatures of the front region 254 and the inner region 255. Furthermore, after the refrigerant flowing through the front region 254, the inner region 255, and the intermediate region 256 of the second core 25 is mixed in the second manifold 26, it flows out from the outlet 261. Therefore, the temperature of the refrigerant flowing out from the outlet 261 becomes the average temperature of the refrigerant after passing through the front region 254, the inner region 255, and the intermediate region 256 of the second core 25. Therefore, even if the target temperature of the refrigerant flowing out from the outlet 261 is controlled to be 40 degrees Celsius, for example, in... Figure 7 In the second core 25 of the heat exchanger 200 of the illustrated reference example, while the temperatures of the near-front region 254 and the inner region 255 are each approximately 50 degrees Celsius, the temperature of the middle region 256 sometimes shows approximately 30 degrees Celsius. In such a heat exchanger 200, when the temperature of the refrigerant flowing out of the outlet 261 is to be controlled to the target temperature, there is concern that the temperature difference between the high-temperature near-front region 254 and the inner region 255 and the low-temperature middle region 256 in the second core 25 may further widen. The temperature distribution of the second core 25 is reflected in the temperature distribution of the air blown out of the heat exchanger 200; therefore, as a result, the temperature distribution of the air in the heat exchanger 200 is prone to deterioration. Figure 6 The same problem may also occur in the heat exchanger 200 of the reference example shown.

[0072] In contrast, in the heat exchanger 2 of this embodiment, as described above, with Figure 6 and Figure 7Compared to the heat exchanger 200 of the reference example shown, it is easier to homogenize the temperature distribution in the second core 25. Therefore, even when the temperature of the refrigerant flowing out of the outlet 261 is controlled to the target temperature, it is difficult to generate regions with large temperature differences in the second core 25. For example, in the heat exchanger 2 of this embodiment, when the target temperature of the refrigerant flowing out of the outlet 261 is controlled to 40 degrees Celsius, Figure 3 The temperature of the supercoolant zone SC shown is approximately 38 degrees Celsius, while the temperature of the other zones is approximately 40 degrees Celsius. Thus, in the heat exchanger 2 of this embodiment, since it is easy to homogenize the temperature distribution of the second core 25, it is also easy to homogenize the temperature distribution of the air blown from the heat exchanger 200.

[0073] On the other hand, in such Figure 3 When the inlet 211 is formed at the center of the first manifold 21 as shown by the double-dotted line, the inlet 211 extends from the center of the first manifold 21 along the z-direction. Similarly, when the outlet 261 is formed at the center of the second manifold 26, the outlet 261 extends from the center of the second manifold 26 along the z-direction. With this configuration, it is necessary to connect the inlet 211 and the outlet 261 with piping in the z-direction, i.e., in the vertical direction, which may lead to a deterioration in the piping arrangement.

[0074] In contrast, in the heat exchanger 2 of this embodiment, such as Figure 3 As shown by the solid line, an inlet 211 is formed on the side of the first manifold 21, and an outlet 261 is formed on the side of the second manifold 26. With this structure, piping can be connected to the inlet 211 and outlet 261 in the y-direction, i.e., in the horizontal direction, thus simplifying the piping arrangement. Furthermore, by employing the structure of the heat exchanger 2 in this embodiment, the refrigerant can flow in a downstream manner.

[0075] Furthermore, the heat exchanger 2 in this embodiment has a single-pass structure with 1-1 turning, where the refrigerant flows in one direction in both the first core 22 and the second core 25. With such a single-pass structure, the flow path cross-sectional area can be increased compared to a heat exchanger where the refrigerant flows in multiple turns in the first core 22 and the second core 25, thus reducing refrigerant pressure loss. Alternatively, a method could be used to form a branch bypass during battery cooling without considering refrigerant pressure loss; however, this increases cost and is therefore difficult to implement.

[0076] exist Figure 9 A modified example of heat exchanger 2 is shown. Figure 9In the variant shown, only connecting holes 23f1 and 24f1 are formed in the second region Tf. In the first steering box 23V and the second steering box 24V, the number of connecting holes in the second region Tf is less than the number of connecting holes in the second region Tr. The number of connecting holes in the second region Tr is less than the number of connecting holes in the first region Tc.

[0077] Next, the heat exchanger 2A according to the second embodiment will be described. Figure 10 It is equivalent to Figure 3 The top view shows heat exchanger 2A. Heat exchanger 2A is a heat exchanger that changes the first steering box 23 and the second steering box 24 of heat exchanger 2 to a first steering box 23A and a second steering box 24A.

[0078] The first turning box 23A has a partition wall 23wA. The partition wall 23wA is a wall that abuts against the second turning box 24A. The partition wall 23wA is provided with connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23c1A, 23c2A, 23r1A, 23r2A, 23r3A, and 23r4A. These connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23c1A, 23c2A, 23r1A, 23r2A, 23r3A, and 23r4A are holes for allowing refrigerant to pass through.

[0079] All connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23r1A, 23r2A, 23r3A, and 23r4A are identical circular in shape. Connecting holes 23c1A and 23c2A are openings with an area larger than that of connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23r1A, 23r2A, 23r3A, and 23r4A, and are, for example, elliptical in shape. Furthermore, the identical circular shape of all connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23r1A, 23r2A, 23r3A, and 23r4A is for ease of explanation; the shape of the connecting holes is not particularly limited and can be various shapes, including, for example, semicircles and rectangles. In addition, the connecting holes 23c1A and 23c2A can be any openings with an area larger than that of the connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23r1A, 23r2A, 23r3A, and 23r4A. An elliptical shape is one example of a shape, and it can be set to various shapes including semi-elliptical shapes and rectangular shapes.

[0080] Connecting holes 23f1A, 23f2A, 23f3A, and 23f4A are contained in the second region Tf. Connecting holes 23c1A and 23c2A are contained in the first region Tc. Connecting holes 23r1A, 23r2A, 23r3A, and 23r4A are contained in the second region Tr. The total opening area of ​​the connecting holes 23f1A, 23f2A, 23f3A, and 23f4A formed in one second region Tf is less than the total opening area of ​​the connecting holes 23c1A and 23c2A formed in the first region Tc. Similarly, the total opening area of ​​the connecting holes 23r1A, 23r2A, 23r3A, and 23r4A formed in one second region Tr is less than the total opening area of ​​the connecting holes 23c1A and 23c2A formed in the first region Tc. Regarding the ratio of the opening area of ​​the connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23c1A, 23c2A, 23r1A, 23r2A, 23r3A, and 23r4A to the area of ​​the partition wall 23wA, the opening ratio of the first region Tc is higher than that of the second region Tf, and the opening ratio of the first region Tc is higher than that of the second region Tr. The pressure loss of the second regions Tf and Tr is higher than that of the first region Tc, and a pair of second regions Tf and Tr are provided across the first region Tc.

[0081] The second steering box 24A has a partition wall 24wA. The partition wall 24wA is a wall that abuts against the second steering box 24A. The partition wall 24wA is provided with connecting holes 24f1A, 24f2A, 24f3A, 24f4A, 24c1A, 24c2A, 24r1A, 24r2A, 24r3A, and 24r4A. The connecting holes 24f1A, 24f2A, 24f3A, 24f4A, 24c1A, 24c2A, 24r1A, 24r2A, 24r3A, and 24r4A are holes for allowing refrigerant to pass through. All connecting holes 24f1A, 24f2A, 24f3A, 24f4A, 24r1A, 24r2A, 24r3A, and 24r4A are of the same circular shape. The connecting holes 24c1A and 24c2A are openings with a larger area than the connecting holes 24f1A, 24f2A, 24f3A, 24f4A, 24r1A, 24r2A, 24r3A, and 24r4A, and are, for example, elliptical in shape.

[0082] Connecting holes 24f1A, 24f2A, 24f3A, and 24f4A are contained in the second region Tf. Connecting holes 24c1A and 24c2A are contained in the first region Tc. Connecting holes 24r1A, 24r2A, 24r3A, and 24r4A are contained in the second region Tr. The total opening area of ​​the connecting holes 24f1A, 24f2A, 24f3A, and 24f4A formed in one second region Tf is less than the total opening area of ​​the connecting holes 24c1A and 24c2A formed in the first region Tc. Similarly, the total opening area of ​​the connecting holes 24r1A, 24r2A, 24r3A, and 24r4A formed in one second region Tr is less than the total opening area of ​​the connecting holes 24c1A and 24c2A formed in the first region Tc. Regarding the ratio of the opening area of ​​the connecting holes 24f1A, 24f2A, 24f3A, 24f4A, 24c1A, 24c2A, 24r1A, 24r2A, 24r3A, and 24r4A to the area of ​​the partition wall 24wA, the opening ratio of the first region Tc is higher than that of the second region Tf, and the opening ratio of the first region Tc is higher than that of the second region Tr. The pressure loss of the second regions Tf and Tr is higher than that of the first region Tc, and a pair of second regions Tf and Tr are provided across the first region Tc.

[0083] With partition walls 23wA and 24wA in contact, the connecting holes 23f1A and 24f1A in the second region Tf are connected. Similarly, connecting holes 23f2A, 24f2A, 23f3A, and 24f3A are connected, as are connecting holes 23f4A and 24f4A. In the first region Tc, connecting holes 23c1A and 24c1A are connected. Similarly, connecting holes 23c2A and 24c2A are connected. In the second region Tr, connecting holes 23r1A, 24r1A, 23r2A, 24r2A, 23r3A, and 24r3A are connected, as are connecting holes 23r4A and 24r4A.

[0084] The superheated gas refrigerant flowing into the first manifold 21 is distributed to a plurality of first pipes 221 and flows toward the first diverter box 23A. Due to this flow, a superheated gas region SH is formed on the side of the first manifold 21.

[0085] Refrigerant flowing into the first diverting box 23A flows into the second diverting box 24A through connecting holes 23f1A, 23f2A, 23f3A, 23f4A, 23c1A, 23c2A, 23r1A, 23r2A, 23r3A, 23r4A and connecting holes 24f1A, 24f2A, 24f3A, 24f4A, 24c1A, 24c2A, 24r1A, 24r2A, 24r3A, 24r4A. Because the pressure loss in the second region Tf, Tr is higher than that in the first region Tc, the flow rate of refrigerant flowing in the second region Tf, Tr is relatively reduced compared to the flow rate of refrigerant flowing in the first region Tc, forming a subcoolant region SC. The subcoolant regions SC form a pair separated from the first region Tc.

[0086] Next, the heat exchanger 2B according to the third embodiment will be described. Figure 11 It is equivalent to Figure 3 The top view shows heat exchanger 2B. Heat exchanger 2B is a heat exchanger that changes the first steering box 23 and the second steering box 24 of heat exchanger 2 to a first steering box 23B and a second steering box 24B.

[0087] The first steering box 23B has a partition wall 23wB. The partition wall 23wB is a wall that abuts against the second steering box 24B. A connecting hole 231 is provided in the partition wall 23wB. For example, 14 connecting holes 231 are provided. The connecting holes 231 are holes for allowing refrigerant to pass through. All connecting holes 231 are of the same circular shape. The fact that all connecting holes 231 are of the same circular shape is for ease of explanation; the shape of the connecting holes is not particularly limited and can be of various shapes, including, for example, semicircular or rectangular shapes. Regarding the ratio of the opening area of ​​the connecting hole 231 to the area of ​​the partition wall 23wB, the opening ratio of the first region Tc is the same as the opening ratio of the second region Tf, and the opening ratio of the first region Tc is the same as the opening ratio of the second region Tr.

[0088] The first steering box 23B is provided with protrusions 232a and 232b. Protrusion 232a is located in the second region Tf. Protrusion 232b is located in the second region Tr.

[0089] The second steering box 24B has a partition wall 24wB. The partition wall 24wB is a wall that abuts against the second steering box 24B. A connecting hole 241 is provided in the partition wall 24wB. For example, 14 connecting holes 241 are provided. The connecting holes 241 are holes for allowing refrigerant to pass through. All connecting holes 241 are of the same circular shape. Regarding the ratio of the opening area of ​​the connecting hole 241 to the area of ​​the partition wall 24wB, the opening ratio of the first region Tc is the same as the opening ratio of the second region Tf, and the opening ratio of the first region Tc is the same as the opening ratio of the second region Tr.

[0090] The second steering box 24B is provided with protrusions 242a and 242b. Protrusion 242a is located in the second region Tf. Protrusion 242b is located in the second region Tr.

[0091] exist Figure 12 (A) shows Figure 11 Section VIIIA-VIIIA of the second steering box 24B. Figure 12 (B) shows Figure 11 Section VIIIB-VIIIB of the second steering box 24B in the middle. For example... Figure 12 (A) and Figure 12 As shown in (B), the protrusion 242a locally reduces the internal volume of the second steering box 24B. The pressure loss of the second region Tf and Tr is higher than that of the first region Tc, and a pair of second regions Tf and Tr are provided across the first region Tc.

[0092] Refer to again Figure 11 Continuing the explanation. With partition walls 23wB and 24wB in contact, connecting holes 231 and 241 are connected. The superheated gas refrigerant flowing into the first manifold box 21 is distributed to multiple first pipes 221 and flows toward the first diverter box 23B. Due to this flow, a superheated gas region SH is formed on the first manifold box 21 side.

[0093] Refrigerant flowing into the first diverter box 23B flows into the second diverter box 24B through connecting holes 231 and 241. Since the pressure loss in the second regions Tf and Tr, which are configured with protrusions 232a, 232b, 242a, and 242b, is higher than the pressure loss in the first region Tc, the flow rate of refrigerant flowing in the second regions Tf and Tr is relatively reduced compared to the flow rate of refrigerant flowing in the first region Tc, forming a subcoolant region SC. The subcoolant regions SC form a pair, separated by the first region Tc.

[0094] Next, the heat exchanger 2C according to the fourth embodiment will be described. Figure 13 It is equivalent to Figure 3The top view shows heat exchanger 2C. Heat exchanger 2C is a heat exchanger that changes the first steering box 23 and the second steering box 24 of heat exchanger 2 to a first steering box 23C and a second steering box 24C.

[0095] In the first steering box 23C, the edge reference is replaced. Figure 11 A throttling section 232C is provided on the protrusions 232a and 232b of the first steering box 23B as described above. In the second steering box 24C, a throttling section 232C is provided instead of the one described above. Figure 11 A throttling section 242C is provided on the protrusions 242a and 242b of the second steering box 24B as described above.

[0096] exist Figure 14 (A) shows Figure 13 The XA-XA section of the second steering box 24B. Figure 14 (B) shows Figure 13 The XB-XB section of the second steering box 24B in the middle. For example... Figure 14 As shown in (A), the throttling section 242C is a flat plate-shaped component running straight along the y-direction, with a through hole 242Ca in its central portion. Figure 14 (A) and Figure 14 As shown in (B), the throttling section 242C partially reduces the internal volume of the second steering box 24B.

[0097] Refer to again Figure 13 Continuing the explanation, the superheated gaseous refrigerant flowing into the first manifold 21 is distributed to multiple first pipes 221 and flows toward the first diverter 23C. Due to this flow, a superheated gas region SH is formed on the side of the first manifold 21.

[0098] Refrigerant flowing into the first diverter box 23C flows into the second diverter box 24C through connecting holes 231 and 241. Due to the presence of throttling sections 232C and 242C, the flow rate of refrigerant flowing in the second regions Tf and Tr is relatively reduced compared to the flow rate of refrigerant flowing in the first region Tc, forming a subcoolant region SC. The subcoolant regions SC form a pair, separated by the first region Tc.

[0099] Furthermore, in the second steering box 24C of the heat exchanger 2C in the fourth embodiment, it is also possible to adopt... Figure 15 The structure shown. As shown. Figure 15As shown, throttling sections 244C, 245C, 246C, and 247C are formed in the second steering box 24C. Throttling section 244C is formed between the second outer region Tf1 and the second inner region Tf2. Throttling section 245C is formed between the second inner region Tf2 and the first region Tc. Throttling section 246C is formed between the first region Tc and the second inner region Tr2. Throttling section 247C is formed between the second inner region Tr2 and the second outer region Tr1. According to this structure, due to the throttling sections 244C, 245C, 246C, and 247C, flow resistance is generated in the y-direction, which is the length direction, in the connected second steering box 24C, thereby reducing the refrigerant flow rate in the second steering box 24C. As a result, the effect of intentionally forming a low-flow-rate subcoolant region SC between the second outer region Tf1 and the first region Tc, and between the second outer region Tr1 and the first region Tc, can be further improved.

[0100] Next, the heat exchanger 2D according to the fifth embodiment will be described. Figure 16 It is equivalent to Figure 3 The top view shows heat exchanger 2D. Heat exchanger 2D is a heat exchanger in which the first turning box 23 and the second turning box 24 of heat exchanger 2 are changed to first turning box 23D and second turning box 24D. Heat exchanger 2D is a heat exchanger in which the first tube 221 of heat exchanger 2 is changed to first tubes 221Df, 221Dc, and 221Dr. Heat exchanger 2D is a heat exchanger in which the second tube 251 of heat exchanger 2 is changed to second tubes 251Df, 251Dc, and 251Dr.

[0101] The first steering box 23D is the edge reference. Figure 11 The first steering box 23B, as described above, has its protrusions 232a and 232b removed. The second steering box 24D is the steering box with the protrusions 232a and 232b removed. Figure 11 The steering box after removing the protrusions 242a and 242b of the second steering box 24B as described above.

[0102] The first tube 221Df and the second tube 251Df are located in the second region Tf. The first tube 221Dc and the second tube 251Dc are located in the first region Tc. The first tube 221Dr and the second tube 251Dr are located in the second region Tr.

[0103] The internal flow path of the first tube 221Df is narrower than that of the first tube 221Dc. The internal flow path of the first tube 221Dr is narrower than that of the first tube 221Dc. The internal flow path of the second tube 251Df is narrower than that of the second tube 251Dc. The internal flow path of the second tube 251Dr is narrower than that of the second tube 251Dc.

[0104] exist Figure 17The diagram illustrates the formation of the internal flow paths of four first tubes 221Df, 221Dc, 221Dr and second tubes 251Df, 251Dc, 251Dr. Examples 1 and 2 are examples of tubes formed by extrusion molding.

[0105] In Example 1, the internal flow paths of the first tube 221Dc and the second tube 251Dc are identical in shape. The internal flow paths of the first tube 221Df and the second tube 251Df are also identical in shape, but are narrower compared to the internal flow paths of the first tube 221Dc and the second tube 251Dc. The internal flow paths of the first tube 221Dr and the second tube 251Dr are also identical in shape, but are narrower compared to the internal flow paths of the first tube 221Dc and the second tube 251Dc.

[0106] In Example 2, the internal flow paths of the first tube 221Dc and the second tube 251Dc are identical in shape. In Example 2, the flow paths of the first tube 221Df and the second tube 251Df, which have the same shape as the internal flow paths of the first tube 221Dc and the second tube 251Dc, are arranged in the center, with narrower flow paths on either side of this central flow path. Similarly, the internal flow paths of the first tube 221Dr and the second tube 251Dr are arranged in the center, with the same shape as the internal flow paths of the first tube 221Dc and the second tube 251Dc, and narrower flow paths on either side of this central flow path.

[0107] Examples 3 and 4 are examples of tubes with internal fins. In Example 3, the spacing between the internal fins of the first tube 221Dc and the second tube 251Dc is equal. The spacing between the internal fins of the first tube 221Df and the second tube 251Df is also equal, but narrower compared to the spacing between the internal fins of the first tube 221Dc and the second tube 251Dc. Therefore, the internal flow paths of the first tube 221Df and the second tube 251Df are narrower compared to the internal flow paths of the first tube 221Dc and the second tube 251Dc. Similarly, the internal flow paths of the first tube 221Dr and the second tube 251Dr are narrower compared to the internal flow paths of the first tube 221Dc and the second tube 251Dc.

[0108] In Example 4, the spacing between the inner fins of the first tube 221Dc and the second tube 251Dc is also equal. In Example 2, among the inner fins of the first tube 221Df and the second tube 251Df, inner fins of the same shape as those of the first tube 221Dc and the second tube 251Dc are arranged in the center, while inner fins with a narrower spacing than those of the inner fins of the first tube 221Dc and the second tube 251Dc are arranged on both sides of this central inner fin. Therefore, the internal flow path of the first tube 221Df and the second tube 251Df is narrower compared to the internal flow path of the first tube 221Dc and the second tube 251Dc. The internal flow path of the first tube 221Dr and the second tube 251Dr is also narrower compared to the internal flow path of the first tube 221Dc and the second tube 251Dc.

[0109] The superheated gas refrigerant flowing into the first manifold 21 is distributed to multiple first pipes 221Df, 221Dc, and 221Dr and flows toward the first deflector box 23D. Due to this flow, a superheated gas region SH is formed on the side of the first manifold 21.

[0110] The refrigerant flowing into the first diverting box 23D flows into the second diverting box 24D through the connecting holes 231 and 241. The refrigerant flowing into the second diverting box 24D is distributed to the second pipes 251Df, 251Dc, and 251Dr and flows toward the second manifold box 26.

[0111] The internal flow paths of the first pipes 221Df and 221Dr are narrower than those of the first pipe 221Dc, and the internal flow paths of the second pipes 251Df and 251Dr are narrower than those of the second pipe 251Dc. Therefore, the flow rate of refrigerant flowing in the second regions Tf and Tr is relatively reduced compared to the flow rate of refrigerant flowing in the first region Tc, forming a subcoolant region SC. The subcoolant regions SC form a pair, separated by the first region Tc.

[0112] Next, the heat exchanger 2E according to the sixth embodiment will be described. Figure 18 It is equivalent to Figure 3 The top view shows heat exchanger 2E. Heat exchanger 2E is a heat exchanger that changes the first steering box 23 and the second steering box 24 of heat exchanger 2 to a first steering box 23D and a second steering box 24D. Regarding the first steering box 23D and the second steering box 24D, since it has already been referred to... Figure 16 The explanation has already been provided, so it will be omitted.

[0113] Heat exchanger 2E is a heat exchanger with a modified arrangement of the first tube 221 and the second tube 251 of heat exchanger 2. The arrangement of the first tube 221 and the second tube 251 in the first region Tc is narrowed compared to the arrangement of the first tube 221 and the second tube 251 in the second regions Tf and Tr. In other words, the arrangement of the first tube 221 and the second tube 251 in the second regions Tf and Tr is widened compared to the arrangement of the first tube 221 and the second tube 251 in the first region Tc.

[0114] The width of the first fin 222Ec and the second fin 252Ec in the y-axis direction of the first fin 222Ef, 222Er and the second fin 252Ef, 252Er ... second fins Tf, Tr is narrower than that of the first fin 222Ef, 222Er and the second fin 252Ef, 252Er in the y-axis direction of the second fins Tf, Tr.

[0115] The superheated gas refrigerant flowing into the first manifold 21 is distributed to a plurality of first pipes 221 and flows toward the first diverter box 23D. Due to this flow, a superheated gas region SH is formed on the side of the first manifold 21.

[0116] The refrigerant flowing into the first diverting box 23D flows into the second diverting box 24D through the connecting holes 231 and 241. The refrigerant flowing into the second diverting box 24D is distributed to the second pipe 251 and flows toward the second manifold box 26.

[0117] The spacing between the first pipes 221 in the second regions Tf and Tr is increased compared to the spacing between the first pipes 221 in the first region Tc, and the spacing between the second pipes 251 in the second regions Tf and Tr is increased compared to the spacing between the second pipes 251 in the first region Tc. Therefore, the flow rate of refrigerant flowing in the second regions Tf and Tr is relatively reduced compared to the flow rate of refrigerant flowing in the first region Tc, forming a subcoolant region SC. The subcoolant regions SC form a pair, separated by the first region Tc.

[0118] Next, the heat exchanger 2F according to the seventh embodiment will be described. Figure 19 It is equivalent to Figure 1 The diagram shows a three-dimensional representation of heat exchanger 2F. Heat exchanger 2F is a heat exchanger that replaces the first steering box 23 and the second steering box 24 of heat exchanger 2 with a single steering box 23F. Steering box 23F has a first steering box portion 23Ff and a second steering box portion 23Fs. The first steering box portion 23Ff corresponds to the first steering box 23, and the second steering box portion 23Fs corresponds to the second steering box 24. Steering box 23F is a steering box that integrates the first steering box portion 23Ff and the second steering box portion 23Fs.

[0119] The steering box 23F has a connecting portion that connects the first steering box portion 23Ff and the second steering box portion 23Fs and allows refrigerant to flow. Figure 20 It is a perspective view including the section where the connecting part 231F is not provided.

[0120] like Figure 20 As shown, the steering box 23F is formed by combining a first part 23Fa and a second part 23Fb. The first part 23Fa has a joint 23Fa1, a wall part 23Fa2, a wall part 23Fa3, a wall part 23Fa4, and a wall part 23Fa5.

[0121] The joint 23Fa1 and wall portions 23Fa2 and 23Fa3 are flat plates extending along the y-direction and are arranged to encompass the xy-plane. The wall portions 23Fa2 and 23Fa3 are arranged to sandwich the joint 23Fa1 in the x-direction. The wall portions 23Fa2 and 23Fa3 are separated from the joint 23Fa1 on the negative z-direction side.

[0122] Wall portions 23Fa4 and 23Fa5 are flat plates extending along the y-direction and are arranged to include the yz plane. Wall portion 23Fa4 is connected to wall portion 23Fa2 on the side opposite to the joint portion 23Fa1, relative to wall portion 23Fa2. Wall portion 23Fa5 is connected to wall portion 23Fa3 on the side opposite to the joint portion 23Fa1, relative to wall portion 23Fa3.

[0123] The second part 23Fb has a joint 23Fb1, a wall portion 23Fb2, a wall portion 23Fb3, a wall portion 23Fb4, and a wall portion 23Fb5.

[0124] The joint 23Fb1 and wall portions 23Fb2 and 23Fb3 are flat plates extending along the y-direction and are arranged to encompass the xy-plane. The wall portions 23Fb2 and 23Fb3 are positioned to clamp the joint 23Fb1 in the x-direction. The wall portions 23Fb2 and 23Fb3 are separated from the joint 23Fb1 on the positive side in the z-direction.

[0125] Wall portions 23Fb4 and 23Fb5 are flat plates extending along the y-direction and are arranged to include the yz plane. Wall portion 23Fb4 is connected to wall portion 23Fb2 on the side opposite to the joint portion 23Fb1, relative to wall portion 23Fb2. Wall portion 23Fb5 is connected to wall portion 23Fb3 on the side opposite to the joint portion 23Fb1, relative to wall portion 23Fb3.

[0126] When the first part 23Fa and the second part 23Fb are joined together by abutting the joint 23Fa1 and the joint 23Fb1, a steering box 23F is formed. The first steering box part 23Ff is mainly formed by wall parts 23Fa3, 23Fa5, 23Fb3, and 23Fb5. The second steering box part 23Fs is mainly formed by wall parts 23Fa2, 23Fa4, 23Fb2, and 23Fb4. A plurality of connecting parts 231F are provided to connect the first steering box part 23Ff and the second steering box part 23Fs.

[0127] exist Figure 21 (A) shows Figure 20 The XVIA-XVIA section is the connecting portion 231F. The XVIA-XVIA section is a sectional view through the zx plane of the XVIA-XVIA line. Figure 21 (B) shows Figure 20 The XVIB-XVIB section is the connecting portion 231F in the diagram. The XVIB-XVIB section is a cross-sectional view through the yz plane of the XVIB-XVIB line.

[0128] like Figure 21 (A) and Figure 21 As shown in (B), the connecting portion 231F has an outer contour portion 231Fa. The outer contour portion 231Fa is semi-cylindrical. A connecting hole 231Fb is formed between the outer contour portion 231Fa and the connecting portion 23Fa1. The connecting hole 231Fb is configured to connect the first steering box portion 23Ff and the second steering box portion 23Fs.

[0129] The configuration of the connecting hole 231Fb can be the same as the configuration of the connecting holes in the first to sixth embodiments described above. With the configuration of the connecting hole 231Fb, the first region Tc and the second regions Tf and Tr can be formed in the same way.

[0130] The connecting hole 231Fb can narrow the flow path cross-sectional area by partially filling the inner side of the outer contour 231Fa. (Refer to...) Figure 22 The method of reducing the cross-sectional area of ​​the flow path will be explained. Figure 22 In the example shown in (A), the outer contour 231Fa is flattened from above to form the outer contour 231FAa, thereby forming a narrowed connecting hole 231FAb. Figure 22 In the example shown in (B), the outer contour 231Fa is flattened from above and from the left and right to form the outer contour 231Fba, which is further narrowed to form the connecting hole 231FBb.

[0131] [Note] The following notes 1 to 12 can be combined arbitrarily as long as they are not technically contradictory.

[0132] [Postscript 1]

[0133] A heat exchanger 2, 2A, 2B, 2C, 2D, 2E, comprising:

[0134] The first manifold 21 is in which the refrigerant, which becomes superheated gas, flows into the first manifold from the upstream side flow path;

[0135] Multiple first pipes 221, 221Df, 221Dc, and 221Dr are provided, and refrigerant is distributed from the first manifold box 21 to these multiple first pipes;

[0136] The first diversion boxes 23, 23A, 23B, 23C, 23D, and 23F are connected by refrigerant flowing into them from multiple first pipes 221, 221Df, 221Dc, and 221Dr.

[0137] The second diversion boxes 24, 24A, 24B, 24C, 24D, and 23F are used to receive refrigerant flowing from the first diversion boxes 23, 23A, 23B, 23C, and 23D.

[0138] Multiple second pipes 251, 251Df, 251Dc, and 251Dr are provided with refrigerant, which is distributed from second diversion boxes 24, 24A, 24B, 24C, and 24D to these second pipes; and

[0139] The second manifold box 26 is inhabited by refrigerant that serves as the supercoolant, which flows into the second manifold box from multiple second pipes 251, 251Df, 251Dc, and 251Dr and flows out to the downstream flow path.

[0140] In the internal flow path from multiple first pipes 221, 221Df, 221Dc, 221Dr through first diversion boxes 23, 23A, 23B, 23C, 23D and second diversion boxes 24, 24A, 24B, 24C, 24D to multiple second pipes, the first region Tc and the second regions Tf, Tr, which have different pressure losses when the same flow rate of refrigerant flows through, are arranged in the stacking direction (y-axis direction) of the multiple first pipes 221, 221Df, 221Dc, 221Dr and the second pipes 251, 251Df, 251Dc, 251Dr.

[0141] According to Appendix 1, since a first region Tc and second regions Tf and Tr with different pressure losses when refrigerant of the same flow rate passes through are provided, the flow rate of the refrigerant flowing in the first region Tc and the flow rate of the refrigerant flowing in the second regions Tf and Tr can be adjusted. Since the first region Tc and the second regions Tf and Tr are arranged in the y-axis direction, which is the stacking direction of the multiple first pipes 221, 221Df, 221Dc, 221Dr and the second pipes 251, 251Df, 251Dc, 251Dr, the refrigerant flow rate can be adjusted in a direction intersecting the airflow direction. For example, the refrigerant flow rate can be suppressed to promote heat exchange, forming a supercooled region at the desired location, thus maintaining a good temperature distribution. For example, when heat exchangers 2, 2A, 2B, 2C, 2D, and 2E are used for heating in the vehicle interior, even when the airflow rates are different in the left and right directions along the y-axis, supercooled regions can be formed separately, maintaining a good left-right temperature distribution.

[0142] [Postscript 2]

[0143] As shown in Appendix 1, heat exchangers 2, 2A, 2B, 2C, 2D, and 2E, among which,

[0144] The pressure loss in the second region (Tf and Tr) is higher than the pressure loss in the first region (Tc).

[0145] A pair of second regions Tf and Tr are set apart from the first region Tc.

[0146] According to Appendix 2, the flow rate of refrigerant flowing in the second regions Tf and Tr is relatively reduced compared to the flow rate of refrigerant flowing in the first region Tc, forming a subcoolant region SC. Since the subcoolant regions SC are formed corresponding to the second regions Tf and Tr, they form a pair, separated by the first region Tc. For example, when the second region Tf is formed near the refrigerant inflow into the first manifold 21, even if the flow rate of refrigerant flowing into the first manifold 21 is low, it is possible to prevent the refrigerant from flowing excessively towards the second region Tf via a so-called shortcut. For example, when the second region Tr is formed on the side opposite to the refrigerant inflow into the first manifold 21, even if the flow rate of refrigerant flowing into the first manifold 21 is high, it is possible to prevent the refrigerant from flowing excessively towards the second region Tr.

[0147] When the refrigerant flowing in the first manifold 21 has a low flow velocity and low pressure loss, and the airflow is evenly distributed to the multiple first pipes 221, 221Df, 221Dc, 221Dr and second pipes 251, 251Df, 251Dc, 251Dr, the refrigerant distribution to each pipe becomes uniform. However, when there are pipes upstream of heat exchangers 2, 2A, 2B, 2C, 2D, 2E, and the pipes are rectangular, the airflow is better closer to the center. Therefore, the heat exchange capacity of the first region Tc is greater than that of the second regions Tf and Tr, resulting in a subcooled state. When the first region Tc becomes subcooled, a pressure drop ρgh is generated that lifts the heavier liquid. This pressure drop requires increasing the pressure drop of the second regions Tf and Tr to allow the refrigerant to flow in the first region Tc.

[0148] When the refrigerant flow velocity in the first manifold 21 is high and the pressure loss is high, the refrigerant flow rate to the second region Tr decreases. Therefore, it is necessary to increase the pressure loss in the first region Tc and the second region Tf, excluding the second region Tr. As a result, the pressure loss in the first region Tc is increased compared to the low flow rate, and since the flow rate is high, it is necessary to increase the pressure loss in the first region Tc and the second region Tf. To intentionally make the temperature distribution uniform in the left and right directions along the length of the first manifold 21, and similarly increase the pressure loss in the second regions Tf and Tr, excluding the first region Tc, a pair of subcooled regions are provided.

[0149] Furthermore, setting a pair of second regions Tf and Tr across the first region Tc is just one example. As long as they are arranged in the y-axis direction with the first region Tc, the second regions Tf and Tr can be set in any way.

[0150] [Postscript 3]

[0151] As described in Appendix 1 or 2, heat exchangers 2, 2A, 2B, wherein the first region Tc and the second regions Tf, Tr are disposed in the first steering boxes 23, 23A, 23B and / or the second steering boxes 24, 24A, 24B.

[0152] According to Appendix 3, since the first region Tc and the second region Tf, Tr are provided in the first steering box 23, 23A, 23B and / or the second steering box 24, 24A, 24B, it is possible to simply form the first region Tc and the second region Tf, Tr without setting the pipe as a special pipe.

[0153] [Postscript 4]

[0154] As described in Appendix 3, heat exchangers 2 and 2A are provided with partition walls 23w, 23wA, 24w, and 24wA between the first turning boxes 23 and 23A and the second turning boxes 24 and 24A. The first region Tc and the second regions Tf and Tr are located on the partition walls 23w, 23wA, 24w, and 24wA.

[0155] According to Appendix 4, since the first region Tc and the second region Tf and Tr are set in the partition walls 23w, 23wA, 24w, and 24wA, the first region Tc and the second region Tf and Tr can be easily set by processing the partition walls 23w, 23wA, 24w, and 23wA alone.

[0156] [Postscript 5]

[0157] As described in Appendix 4, the heat exchanger 2 has multiple connecting holes for refrigerant to pass through in the partition walls 23w and 24w. The number of connecting holes 23f1, 23f2, 24f1, and 24f2 formed in the second region Tf is less than the number of connecting holes 23c1, 23c2, 23c3, 23c4, 24c1, 24c2, 24c3, and 24c4 formed in the first region Tc. Similarly, the number of connecting holes 23r1, 23r2, 24r1, and 24r2 formed in the second region Tr is less than the number of connecting holes 23c1, 23c2, 23c3, 23c4, 24c1, 24c2, 24c3, and 24c4 formed in the first region Tc.

[0158] According to Appendix 5, by varying the number of connecting holes provided in the partition walls 23w and 24w between the first region Tc and the second regions Tf and Tr, the first region Tc and the second regions Tf and Tr can be easily formed. Furthermore, by adjusting the number of connecting holes provided in the partition walls 23w and 24w, the refrigerant flow difference can also be adjusted, thus making it easier to adjust the formation position and formation method of the second regions Tf and Tr relative to the first region Tc.

[0159] [Postscript 6]

[0160] As described in Appendix 5, heat exchanger 2, wherein...

[0161] Assuming that connecting holes are equally distributed in the first region Tc and the second regions Tf and Tr, the number of connecting holes in this case is Nall. Assuming that connecting holes are equally distributed in the unopened region from the connecting hole at the outer end of the first region Tc to the connecting hole at the inner end of the second region Tf or Tr, the hypothetical number of connecting holes that should be provided in this case is Nsc.

[0162] Nsc / Nall ≥ 0.12

[0163] The total opening area of ​​the connecting holes actually set in the first region Tc and the second regions Tf and Tr is 21.18 mm². 2 above.

[0164] In Appendix 6, the assumption that connecting holes are equally distributed in the first region Tc and the second regions Tf and Tr means, for example, with Figure 16 The state is the same as the formation state of the connecting hole 241 illustrated in the example. On the other hand, the state in which connecting holes are actually provided in the first region Tc and the second regions Tf and Tr and also satisfy the conditions of Appendix 5 refers to, for example, the state with Figure 3 The same state as illustrated in the example. In the same... Figure 16 In the same example, Nall is 14. In the case of... Figure 3 In the same cases illustrated, the connecting holes provided at the outer end of the first region Tc are connecting holes 23c1, 24c1 or connecting holes 23c4, 24c4. The connecting holes provided at the inner end of the second region Tf or the second region Tr are connecting holes 23f2, 24f2 or connecting holes 23r1, 24r1. If connecting holes are equally distributed from connecting hole 23c1 to connecting hole 23f2, the number is 2. Similarly, if connecting holes are equally distributed from connecting hole 23c4 to connecting hole 23r1, the number is 2. Similarly, if connecting holes are equally distributed from connecting hole 24c1 to connecting hole 24f2, the number is 2. Similarly, if connecting holes are equally distributed from connecting hole 24c4 to connecting hole 24r1, the number is 2. Therefore, in these examples, Nsc is 2. Therefore, Nsc / Nall = 2 / 14 = 0.14, which satisfies the condition Nsc / Nall ≥ 0.12.

[0165] Furthermore, the outer end of the first region Tc is, in other words, the end of the first region Tc on the side of the second region Tf or the end of the first region Tc on the side of the second region Tr. The inner end of the second region Tf is, in other words, the end of the second region Tf on the side of the first region Tc or the end of the second region Tr on the side of the first region Tc.

[0166] Figure 23 and Figure 24 These are graphs representing the results of experiments conducted by the inventors. Figure 23 The graph shown represents the relationship between Nsc / Nall on the horizontal axis and the temperature difference ΔT between the left and right sides of the air blown out from heat exchanger 2 on the vertical axis. When... Figure 3When the direction of the arrow y in the y-direction is defined as the right direction and its opposite as the left direction, the temperature difference ΔT between the left and right sides of the air blown out from heat exchanger 2 is the temperature difference between the air blown out from the left side of the central part in the y-direction of heat exchanger 2 after heat exchange, and the temperature difference between the air blown out from the right side of the central part in the y-direction of heat exchanger 2 after heat exchange. Figure 23 In the curve diagram shown, the solid line L20 represents the case where the height of cores 22 and 25 in the z-direction is small, and the dashed line L21 represents the case where the height of cores 22 and 25 in the z-direction is large. For example... Figure 23 As shown in the graph, when Nsc / Nall is above 0.12, the temperature difference ΔT between the left and right sides of heat exchanger 2 is below the threshold ΔTa. The threshold ΔTa represents the permissible difference in temperature between the air blown into the vehicle through heat exchanger 2 towards the driver's side and the air blown towards the passenger's side. Figure 23 As shown in the curve, when Nsc / Nall is above 0.12, the temperature difference ΔT between the left and right sides of heat exchanger 2 decreases sharply; in other words, the temperature difference ΔT between the left and right sides of heat exchanger 2 is improved.

[0167] Figure 24 The graph shown uses the total opening area AS of the connecting holes 241 actually installed in the first region Tc and the second regions Tf and Tr as the horizontal axis and the refrigerant pressure loss PL as the vertical axis to represent their relationship. Figure 24 As shown in the curve, if the total opening area AS of the connecting hole 241 is 21.18 mm... 2 The above ensures that the refrigerant pressure loss PL is less than the threshold PLa. The threshold PLa is, for example, the allowable value of refrigerant pressure loss that ensures cooling performance when cooling the battery of an electric vehicle using the refrigeration cycle of the heat exchanger 2 of this embodiment.

[0168] [Postscript 7]

[0169] As described in Appendix 4, the heat exchanger 2A has multiple connecting holes for refrigerant to pass through in the partition walls 23wA and 24wA. The total area of ​​the connecting holes 23f1A, 23f2A, 23f3A, and 23f4A formed in the second region Tf is smaller than the total area of ​​the connecting holes 23c1A and 23c2A formed in the first region Tc. Similarly, the total area of ​​the connecting holes 23r1A, 23r2A, 23r3A, and 23r4A formed in the second region Tr is smaller than the total area of ​​the connecting holes 23c1A and 23c2A formed in the first region Tc.

[0170] According to Appendix 7, by making the total area of ​​the connecting holes provided in the partition walls 23wA and 24wA different between the first region Tc and the second regions Tf and Tr, the first region Tc and the second region Tf and Tr can be easily formed. Furthermore, by adjusting the total area of ​​the connecting holes provided in the partition walls 23wA and 24wA, the refrigerant flow difference can also be adjusted, thus making it easier to adjust the formation position and formation method of the second regions Tf and Tr relative to the first region Tc. The total area of ​​the connecting holes refers to the sum of the opening areas of the connecting holes formed in that region.

[0171] [Postscript 8]

[0172] As described in Appendix 3, heat exchangers 2B and 2C are formed such that the cross-sectional area of ​​the interior of the first turning box 23B and 23C and / or the second turning box 24B and 24C varies along at least a portion of the stacking direction (y-axis direction) to form a first region Tc and a second region Tf and Tr.

[0173] According to Appendix 8, by varying the cross-sectional area of ​​the interior of the first steering boxes 23B, 23C and / or the second steering boxes 24B, 24C in the y-axis direction to create a difference in pressure loss, it is possible to easily form the first region Tc and the second regions Tf, Tr.

[0174] [Postscript 9]

[0175] As described in Appendix 8, the heat exchanger 2C has its internal cross-sectional area varied by providing throttling sections 232C and 242C inside the first turning box 23C and / or the second turning box 24C.

[0176] [Postscript 10]

[0177] As described in Appendix 8, the heat exchanger's internal cross-sectional area is varied by changing the shape of the inner walls within the first steering box 23B and / or the second steering box 24B. As an example, this is achieved by setting an edge reference... Figure 11 , Figure 12 The protrusions 232a and 242a, as described above, can change the shape of the inner wall.

[0178] [Postscript 11]

[0179] As described in Appendix 1 or 2, heat exchangers 2D and 2E, wherein a first region Tc and a second region Tf and Tr are disposed in a plurality of first tubes and / or a plurality of second tubes.

[0180] [Postscript 12]

[0181] As described in Appendix 11, the heat exchanger is configured such that the internal flow paths of the first tubes 221Df, 221Dr and / or the second tubes 251Df, 251Dr in the second regions Tf, Tr are narrower than the internal flow paths of the first tube 221Dc and / or the second tube 251Dc in the first region Tc.

[0182] According to Note 12, by creating a difference in pressure loss by making the internal flow paths of the pipe different, it is possible to form the first region Tc and the second region Tf, Tr by simply changing the pipe.

[0183] [Postscript 13]

[0184] As described in Appendix 11, the number of first tubes 221 and / or second tubes 251 disposed in the second regions Tf and Tr is less than the number of first tubes 221 and / or second tubes 251 disposed in the first region Tc.

[0185] According to Note 13, using ordinary pipes without making changes to the steering box, the first region Tc and the second region Tf, Tr can be formed by simply changing the number of pipes.

[0186] The present embodiment has been described above with reference to specific examples. However, this disclosure is not limited to these specific examples. Examples in which those skilled in the art have appropriately made design changes to these specific examples are also included within the scope of this disclosure, provided they possess the features of this disclosure. The elements, their configurations, conditions, shapes, etc., of each of the above-described specific examples are not limited to the illustrated content and can be appropriately modified. The elements of each of the above-described specific examples can be appropriately combined as long as they do not create technical contradictions.

Claims

1. A heat exchanger, characterized in that, have: The first manifold box (21) is filled with refrigerant that has become superheated gas, which flows into the first manifold box from the upstream side flow path; Multiple first tubes (221, 221Df, 221Dc, 221Dr) are provided with refrigerant, which is distributed from the first manifold box to these multiple first tubes. First diversion boxes (23, 23A, 23B, 23C, 23D, 23F), from which refrigerant flows into the first diversion box from the plurality of first pipes; The second diversion box (24, 24A, 24B, 24C, 24D, 23F) is where refrigerant flows from the first diversion box into the second diversion box; Multiple second tubes (251, 251Df, 251Dc, 251Dr) are provided with refrigerant, which is distributed from the second diversion box to these multiple second tubes. as well as The second manifold box (26) is where the refrigerant, which becomes the supercoolant, flows into the second manifold box from the plurality of second pipes and flows out to the downstream flow path. In the internal flow path from the plurality of first pipes through the first and second diversion boxes to the plurality of second pipes, first regions (Tc) and second regions (Tf, Tr) with different pressure losses when refrigerant of the same flow rate flows through are arranged in the stacking direction (y) of the plurality of first pipes and second pipes stacked together.

2. The heat exchanger according to claim 1, characterized in that, The pressure loss in the second region is higher than that in the first region. A pair of second regions are provided between the first region and the second region.

3. The heat exchanger according to claim 1, characterized in that, The first region and the second region are disposed in the first steering box and / or the second steering box.

4. The heat exchanger according to claim 3, characterized in that, A partition wall (23w, 23wA, 24w, 24wA) is provided between the first steering box and the second steering box. The first region and the second region are disposed on the partition wall.

5. The heat exchanger according to claim 4, characterized in that, The partition wall is provided with a plurality of connecting holes for refrigerant to pass through, and the number of connecting holes formed in the second region is less than the number of connecting holes formed in the first region.

6. The heat exchanger according to claim 5, characterized in that, Assuming that connecting holes are equally distributed in both the first and second regions, the number of connecting holes in this case is Nall. Assuming that connecting holes are equally distributed from the outer end of the first region Tc to the inner end of the second region Tf or Tr, the hypothetical number of connecting holes that should be distributed in this case is Nsc. Therefore, Nsc / Nall ≥ 0.

12. The total opening area of ​​the connecting holes actually provided in the first and second regions is 21.18 mm². 2 above.

7. The heat exchanger according to claim 4, characterized in that, The partition wall is provided with a plurality of connecting holes for refrigerant to pass through, and the total area of ​​the connecting holes formed in the second region is smaller than the total area of ​​the connecting holes formed in the first region.

8. The heat exchanger according to claim 3, characterized in that, The first region and the second region are formed in such a way that the cross-sectional area of ​​the interior of the first steering box and / or the second steering box varies along at least a portion of the stacking direction.

9. The heat exchanger according to claim 8, characterized in that, The internal cross-sectional area is changed by setting a throttling section inside the first steering box and / or the second steering box.

10. The heat exchanger according to claim 8, characterized in that, The internal cross-sectional area is changed by altering the shape of the inner wall within the first steering box and / or the second steering box.

11. The heat exchanger according to claim 1, characterized in that, The first region and the second region are disposed in the plurality of first tubes and / or the plurality of second tubes.

12. The heat exchanger according to claim 11, characterized in that, The internal flow path of the first tube and / or the second tube disposed in the second region is narrower than the internal flow path of the first tube and / or the second tube disposed in the first region.

13. The heat exchanger according to claim 11, characterized in that, The number of the first tube and / or the second tube disposed in the second region is less than the number of the first tube and / or the second tube disposed in the first region.

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