Heat exchanger

Abstract

To provide a heat exchanger which can make compatible both the securement of heat exchange performance and the reduction of ventilation resistance while employing a counterflow structure.SOLUTION: A heat exchanger 10 has an upper wall part 210 for partitioning an air flow passage W21 in which air flows, and a refrigerant flow passage W10 in which a refrigerant flows. Air progressing from the radially inner side toward the radially outer side flows to the air flow passage W21. The refrigerant progressing from the radially outer side toward the radially inner side flows to the refrigerant flow passage W10. A high flow velocity region A11 and a low flow velocity region A12 exist at an upper face 210a of the upper wall part 210. A heat exchange amount of outside outer fins 24b arranged in the low flow velocity region A12 is larger than a heat exchange amount of inside outer fins 24a arranged in the high flow velocity region A11.SELECTED DRAWING: Figure 5

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger. [Background technology]

[0002] Conventionally, there is a heat exchanger described in the following Patent Document 1. In this heat exchanger, heat is exchanged between a first medium flowing in a first direction and a second medium flowing in a second direction. The first direction and the second direction are perpendicular to each other. In this heat exchanger, a first fin is arranged in a portion where the first medium flows, and a second fin is arranged in a portion where the second medium flows. In this heat exchanger, the fin pitch of each fin is made small in a portion where the temperature difference between the first medium and the second medium is likely to be small, specifically, in a portion downstream of the first medium, thereby improving the heat exchange performance. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] China Utility Model No. 212431870 Summary of the Invention [Problem to be solved by the invention]

[0004] Heat exchangers that exchange heat between two fluids include not only cross-flow type in which the two fluids flow perpendicular to each other as described in Patent Document 1, but also counter-flow type in which the two fluids flow opposite each other. In such counter-flow type heat exchangers, it is difficult to generate a temperature difference between the two fluids, so it is difficult to improve the heat exchange performance even if the configuration of the heat exchanger described in Patent Document 1 is adopted. Rather, there is a concern that the ventilation resistance of each medium will increase in the area where the fin pitch of each fin is small.

[0005] The present disclosure has been made in consideration of these circumstances, and its purpose is to provide a heat exchanger that employs a counterflow structure while ensuring heat exchange performance and reducing ventilation resistance. [Means for solving the problem]

[0006] The heat exchanger that solves the above problem is a heat exchanger (10) that has a partition wall (210) that separates a first flow path (W21, W22) through which a first fluid flows and a second flow path (W10) through which a second fluid flows, and heat exchange between the first fluid and the second fluid occurs through the partition wall. The first fluid flows in a first direction in the first flow path. The second fluid flows in a second direction opposite to the first direction in the second flow path. In the wall surface of the partition wall facing the first flow path, there are a first region (A11) through which the first fluid passes and a second region (A12) through which the first fluid passes at a flow rate slower than that of the first region. In the first region of the wall surface of the partition wall, a first heat transfer section (24a) that increases the heat transfer area for the first fluid is formed. In the second region of the wall surface of the partition wall, a second heat transfer section (24b) that increases the heat transfer area for the first fluid is formed. The amount of heat exchange of the first fluid in the second heat transfer portion is greater than the amount of heat exchange of the first fluid in the first heat transfer portion.

[0007] According to this configuration, the first fluid and the second fluid flow in opposite directions. In addition, since the first heat transfer section having a relatively small heat exchange amount with respect to the first fluid is arranged in the first region where the first fluid flows at a relatively high flow rate, it is possible to reduce the ventilation resistance of the first fluid. Furthermore, since the second heat transfer section having a relatively large heat exchange amount with respect to the first fluid is arranged in the second region where the first fluid flows at a relatively low flow rate, the heat exchange amount of the second heat transfer section can make up for the shortage of the heat exchange amount in the first heat transfer section. Therefore, it is possible to ensure heat exchange performance.

[0008] The above means and the symbols in parentheses in the claims are merely examples showing the correspondence with specific means described in the embodiments described later. Effect of the Invention

[0009] According to the heat exchanger of the present disclosure, it is possible to ensure heat exchange performance and reduce ventilation resistance while adopting a counterflow structure. [Brief description of the drawings]

[0010] [Figure 1] FIG. 1 is a front view showing the front structure of a heat exchanger according to an embodiment. [Diagram 2] FIG. 2 is a plan view showing the planar structure of the heat exchanger of the embodiment. [Diagram 3] FIG. 3 is a plan view showing a planar structure of the plate member of the embodiment. [Figure 4] FIG. 4 is a cross-sectional view showing a cross-sectional structure of a plate member according to the embodiment. [Diagram 5] FIG. 5 is a cross-sectional view showing a cross-sectional structure taken along line VV in FIG. [Figure 6] 6(A) and (B) are cross-sectional views that typically show the flow channel structure of a reference example. [Figure 7] 7(A) to (C) are graphs respectively showing the relationship between the position in the flow path structure of the reference example and the heat transfer coefficient, the relationship between the position and the surface area of ​​the fins, and the relationship between the position and the ventilation resistance of the air. [Figure 8] FIG. 8 is a front view showing the front structure of a heat exchanger according to a first modified example of the embodiment. [Figure 9] FIG. 9 is a cross-sectional view showing a cross-sectional structure of a heat exchanger according to a first modified example of the embodiment. [Figure 10] FIG. 10 is a cross-sectional view showing a cross-sectional structure of a heat exchanger according to a second modified example of the embodiment. [Figure 11] FIG. 11 is a diagram illustrating a fin structure according to another embodiment. [Figure 12] FIG. 12 is a diagram illustrating a fin structure according to another embodiment. [Figure 13] FIG. 13 is a diagram illustrating a fin structure according to another embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0011] Hereinafter, an embodiment of a heat exchanger will be described with reference to the drawings. In order to facilitate understanding of the description, the same components in the drawings are denoted by the same reference numerals as much as possible, and duplicated descriptions will be omitted. <Embodiment> The heat exchanger 10 shown in Fig. 1 and Fig. 2 is a device for exchanging heat between, for example, air and a refrigerant. In this embodiment, the air corresponds to the first fluid, and the refrigerant corresponds to the second fluid. The second fluid is not limited to a refrigerant, and any fluid such as LLC (Long Life Coolant) can be used. Similarly, any fluid can be used as the first fluid.

[0012] The heat exchanger 10 includes a heat exchange core unit 20 and a centrifugal fan 30 . As shown in FIGS. 1 and 2, the heat exchange core portion 20 includes a plurality of plate members 21 to 23 and a plurality of outer fins 24 and 25. As shown in FIG.

[0013] The plate members 21 to 23 have the same shape. In the following, the shape of the plate member 21 will be described as a representative example. As shown in Fig. 3, the plate member 21 is formed in a ring shape centered on the axis m10. A notch 21a is formed in the plate member 21. In Fig. 3, reference numeral 215 is attached to one end in the circumferential direction of the plate member 21 that is disposed across the notch 21a, and reference numeral 216 is attached to the other end.

[0014] As shown in Fig. 4, a refrigerant flow path W10 through which a refrigerant flows is formed inside the plate member 21. As shown in Fig. 3, the refrigerant flow path W10 is formed to extend from one end 215 to the other end 216 of the plate member 21. As shown in Fig. 4, a plurality of inner fins 40 are arranged in the refrigerant flow path W10 of the plate member 21. The multiple inner fins 40 are arranged to extend radially around an axis m10.

[0015] When the wall portion 213 of the plate member 21 arranged radially outward around the axis m10 is defined as the "outer wall portion 213", a gap T11 is formed between the radially outer ends of the inner fins 40 and the outer wall portion 213. When the wall portion 214 of the plate member 21 arranged radially inward around the axis m10 is defined as the "inner wall portion 214", a gap T12 is formed between the radially inner ends of the inner fins 40 and the inner wall portion 214. Hereinafter, the former gap T11 will be referred to as the "distribution tank space T11", and the latter gap T12 will be referred to as the "collection tank space T12". In addition, the radially inner side around the axis m10 will be abbreviated as the "radially inner side", and the radially outer side around the axis m10 will be abbreviated as the "radially outer side".

[0016] As shown in Fig. 1 and Fig. 2, an inflow pipe 60 is provided at one end 215 of each of the plurality of plate members 21-23 so as to penetrate them in a direction parallel to the axis m10. The inflow pipe 60 is connected to the distribution tank space T11 of each of the plate members 21-23. An outflow pipe 70 is provided at the other end 216 of each of the plurality of plate members 21 so as to penetrate them in a direction parallel to the axis m10. An inflow piping for a refrigerant is connected to one end of the inflow pipe 60. An outflow piping for a refrigerant is connected to one end of the outflow pipe 70.

[0017] The refrigerant flows into the inlet pipe 60 through the inlet piping. The refrigerant that flows into the inlet pipe 60 flows from the inlet pipe 60 into the distribution tank space T11 of each of the plate members 21-23. The refrigerant that flows into the distribution tank space T11 flows through the gaps between the inner fins 40 toward the collecting tank space T12, that is, in the direction from the radially outer side to the radially inner side, as shown by the arrow D11 in FIG. 4. In the collecting tank space T12, the refrigerant that flows through the gaps between the inner fins 40 is collected. The refrigerant collected in the collecting tank space T12 of each of the plate members 21-23 flows to the outflow piping through the outflow pipe 70.

[0018] 1, the gap formed between the plate members 21 and 22 and the gap formed between the plate members 21 and 23 form air flow paths W21 and W22, respectively, through which air flows. Outer fins 24 and 25 are disposed in the air flow paths W21 and W22, respectively.

[0019] Each of the outer fins 24, 25 is a pin-shaped fin formed to extend in a direction parallel to the axis m10. The lower end of each outer fin 24 is joined and fixed to the outer surface 210a of the upper wall portion 210 of the plate member 21. The upper end of each outer fin 24 is joined and fixed to the outer surface 220a of the lower wall portion 220 of the plate member 22. The upper end of each outer fin 25 is joined and fixed to the outer surface 211a of the lower wall portion 211 of the plate member 21. The lower end of each outer fin 25 is joined and fixed to the outer surface 230a of the upper wall portion 230 of the plate member 23.

[0020] Hereinafter, the outer surfaces 210a, 230a of the upper wall portions 210, 230 of the plate members 21, 23 will be referred to as "upper surfaces 210a, 230a", and the outer surfaces 211a, 220a of the lower wall portions 211, 220 of the plate members 21, 22 will be referred to as "lower surfaces 211a, 220a". Since the outer fins 24, 25 have the same shape, the shape of the outer fin 24 will be described below as a representative example.

[0021] Fig. 5 shows a cross-sectional structure taken along line VV in Fig. 1. As shown in Fig. 5, the cross-sectional shape of each outer fin 24 perpendicular to the axis m10 is formed to be streamlined. In Fig. 5, the streamlined leading edge portion of the outer fin 24 is labeled with reference numeral 240, and the streamlined trailing edge portion of the outer fin 24 is labeled with reference numeral 241. Each outer fin 24 is disposed such that its leading edge portion 240 faces the axis m10.

[0022] As shown in FIG. 5, a plurality of outer fins 24 are sparsely arranged in a first region A11 on the radial inside of the upper surface 210a of the plate member 21. A plurality of outer fins 24 are densely arranged in a second region A12 on the radial outside of the upper surface 210a of the plate member 21. For example, when the interval between adjacent outer fins 24, 24 in the circumferential direction centered on the axis m10 is defined as a fin pitch, the fin pitch P12 of the outer fins 24 arranged in the second region A12 on the radial outside of the plate member 21 is narrower than the fin pitch P11 of the outer fins 24 arranged in the first region A11 on the radial inside of the plate member 21. Hereinafter, the plurality of outer fins 24 arranged in the first region A11 are referred to as "inner outer fins 24a", and the plurality of outer fins 24 arranged in the second region A12 are referred to as "outer outer fins 24b". In this embodiment, the plurality of inner outer fins 24a correspond to the first heat transfer section and the heat transfer member arranged in the first region A11. The outer fins 24b correspond to the first heat transfer portion and the heat transfer member disposed in the second area A12.

[0023] As shown in Fig. 2, the centrifugal fan 30 is disposed in the center of the plate members 21-23. The centrifugal fan 30 is driven based on the supply of power to circulate air through air flow paths W21, W22 formed between the plate members 21-23. The air flows in the direction indicated by the arrow D12 shown in Fig. 5, that is, from the radial inner side to the radial outer side.

[0024] Next, an example of the operation of the heat exchanger 10 of this embodiment will be described. In the heat exchanger 10 of this embodiment, heat exchange is performed between the refrigerant flowing through the refrigerant flow passage W10 of each plate member 21-23 and the air flowing through the air flow passages W21, W22 formed between each plate member 21-23. For example, the air flowing through one air flow passage W21 and the refrigerant flowing through the refrigerant flow passage W10 of the plate member 21 exchange heat through the upper wall portion 210 of the plate member 21. Also, the air flowing through the other air flow passage W22 and the refrigerant flowing through the refrigerant flow passage W10 of the plate member 21 exchange heat through the lower wall portion 211 of the plate member 21. At that time, in the air flow passages W21, W22, air flows in a direction from the radial inside to the radial outside. On the other hand, in the refrigerant flow passage W10 of the plate member 22, the refrigerant flows in a direction from the radial outside to the radial inside. Therefore, the heat exchanger 10 of this embodiment has a so-called counterflow structure in which two fluids that perform heat exchange flow in a manner to face each other.

[0025] In this embodiment, the direction from the radially outer side to the radially inner side corresponds to the first direction, and the direction from the radially inner side to the radially outer side corresponds to the second direction. The air flow paths W21 and W22 correspond to the first flow paths, and the refrigerant flow paths W10 of each of the plate members 21 to 23 correspond to the second flow paths. The upper wall portion 210 of the plate member 21 corresponds to a partition wall that separates one of the air flow paths W21 and the refrigerant flow path W10 of the plate member 21. The lower wall portion 211 of the plate member 21 corresponds to a partition wall that separates the other of the air flow paths W22 and the refrigerant flow path W10 of the plate member 21. The lower wall portion 220 of the plate member 22 and the upper wall portion 230 of the plate member 23 also correspond to partition walls.

[0026] The outer fins 24, 25 arranged in the air passages W21, W22 have the function of increasing the heat transfer area for the air. The inner fin 40 arranged in the refrigerant passage W10 has the function of increasing the heat transfer area for the refrigerant. Therefore, these fins 24, 25, 40 contribute to improving the heat exchange performance of the heat exchanger 10.

[0027] Since each of the plate members 21-23 is formed in a ring shape, the flow path cross-sectional area of ​​the air flow path W21 perpendicular to the air flow direction becomes larger from the radially inner side to the radially outer side, i.e., from the first area A11 to the second area A12 shown in Fig. 5. As a result, the air flow speed becomes slower from the radially inner side to the radially outer side. Hereinafter, the first area A11 will be referred to as the "high flow speed area A11" and the second area A12 will be referred to as the "low flow speed area A12".

[0028] In this embodiment, by sparsely arranging the inner outer fins 24a in the high flow velocity region A11 and densely arranging the outer outer fins 24b in the low flow velocity region A12, it is possible to reduce the ventilation resistance while ensuring the heat exchange performance. The reason is as follows.

[0029] The inventors experimentally measured and compared the heat transfer coefficient and ventilation resistance in the flow path structure 100A shown in Fig. 6(A) with the heat transfer coefficient and ventilation resistance in the flow path structure 100B shown in Fig. 6(B). Both of the flow path structures 100A and 100B are formed so that the flow path cross-sectional area gradually increases from the inlet 101 where the air flows in toward the outlet 102 where the air flows out. Therefore, a high flow velocity region 103 where the air flow velocity is relatively high is formed near the inlet 101 of each of the flow path structures 100A and 100B. In addition, a low flow velocity region 104 where the air flow velocity is relatively low is formed near the outlet 102 of each of the flow path structures 100A and 100B.

[0030] Fins 105 are arranged in each of the flow path structures 100A and 100B. In the flow path structure 100A, the fins 105 are arranged at uniform intervals in the entire region, including the high flow velocity region 103 and the low flow velocity region 104. In contrast, in the flow path structure 100B, the fins 105 are arranged sparsely in the high flow velocity region 103 and are arranged densely in the low flow velocity region 104.

[0031] 7(A) to (C) respectively show the relationship between the position of the flow path structures 100A and 100B and the heat transfer coefficient of the fin 105, the relationship between the position and the surface area of ​​the fin 105, and the relationship between the position and the ventilation resistance of the air. Note that the "position d" on the horizontal axis of FIG. 7 indicates the position in the air flow direction from the reference position (d=0) of the position of the inlet 101 as shown in FIGS. 6(A) and (B). Also, the surface area of ​​the fin 105 indicates the total area of ​​the fin 105 present at that position. Furthermore, in FIGS. 7(A) to (C), the heat transfer coefficient, surface area, and ventilation resistance of the flow path structure 100A are indicated by dashed lines, and the heat transfer coefficient, surface area, and ventilation resistance of the flow path structure 100B are indicated by solid lines.

[0032] In the flow path structure 100A, the fins 105 are arranged at uniform intervals, so that the heat transfer coefficient decreases from the inlet 101 toward the outlet 102, i.e., from the high flow velocity region 103 toward the low flow velocity region 104, as shown by the dashed line in Fig. 7(A). Also, as shown by the dashed line in Fig. 7(B), the surface area of ​​the fins 105 is constant in the flow path structure 100A. Furthermore, as shown by the dashed line in Fig. 7(C), in the flow path structure 100A, the ventilation resistance gradually increases from the inlet 101 toward the outlet 102.

[0033] In contrast, in flow path structure 100B, fins 105 are sparsely arranged in high flow velocity region 103. Therefore, as shown by the solid line in Fig. 7(B), the surface area of ​​fins 105 in high flow velocity region 103 of flow path structure 100B is smaller than that of flow path structure 100A. Also, in flow path structure 100B, fins 105 are densely arranged in low flow velocity region 104. Therefore, as shown by the solid line in Fig. 7(B), the surface area of ​​fins 105 in low flow velocity region 104 of flow path structure 100B increases sharply.

[0034] On the other hand, in the flow path structure 100B, the fins 105 are sparsely arranged in the high flow velocity region 103, so that the heat exchange efficiency and ventilation resistance are lower in the region 103 compared to the flow path structure 100A, as shown by the solid lines in Figures 7(A) and (C). In contrast, in the flow path structure 100B, the fins 105 are densely arranged in the low flow velocity region 104. Therefore, the heat exchange efficiency and ventilation resistance rise sharply in the region 104, as shown by the solid lines in Figures 7(A) and (C).

[0035] In the case of air, it is generally known that the flow velocity of air contributes to the resistance by about the square and to the heat transfer coefficient by about the first power. Considering this, in the flow path structure 100B, since the fins 105 are arranged sparsely in the high flow velocity region 103, the heat transfer coefficient decreases, but it is possible to effectively obtain the effect of reducing the ventilation resistance. In addition, in the flow path structure 100B, since the fins 105 are arranged densely in the low flow velocity region 104, it is possible to compensate for the decrease in the heat transfer coefficient in the high flow velocity region 103 with the increase in the heat transfer coefficient in the low flow velocity region 104. As a result, it is possible to ensure the heat exchange performance while reducing the ventilation resistance.

[0036] As described above, in the heat exchanger 10 of this embodiment shown in Fig. 1 to Fig. 5, the inner outer fins 24a are sparsely arranged in the high flow rate region A11 on the radial inner side of the plate member 21, and the outer outer fins 24b are densely arranged in the low flow rate region A12 on the radial outer side of the plate member 21. Therefore, the heat exchanger 10 of this embodiment has a structure similar to the flow path structure 100B shown in Fig. 6 (B). Therefore, like the flow path structure 100B, the heat exchanger 10 of this embodiment can ensure heat exchange performance while reducing ventilation resistance.

[0037] According to the heat exchanger 10 of the present embodiment described above, the following actions and effects (1) to (4) can be obtained. (1) In the refrigerant flow passage W10 of each plate member 21-23, the refrigerant flows in a direction from the radial outside to the radial inside. In the air flow passages W21, W22, the air flows in a direction from the radial inside to the radial outside, that is, in a direction opposite to the direction in which the refrigerant flows. In the high flow velocity region A11 of the upper surface 210a of the plate member 21, the inner outer fin 24a is arranged. In the low flow velocity region A12 of the upper surface 210a of the plate member 21, the outer outer fin 24b is arranged. The outer outer fin 24b is arranged more densely than the inner outer fin 24a. Therefore, the amount of heat exchange of air in the outer outer fin 24b is larger than the amount of heat exchange of air in the inner outer fin 24a. According to this configuration, the air and the refrigerant flow in a counter-flow manner. In addition, since the inner outer fins 24a are arranged more sparsely than the outer outer fins 24b in the high flow velocity region A11, it is possible to reduce the ventilation resistance of the air. Furthermore, the insufficient amount of heat exchange in the inner outer fins 24a can be compensated for by the amount of heat exchange in the outer outer fins 24b, so that the heat exchange performance can be ensured.

[0038] (2) The refrigerant flow path W10 and the air flow paths W21, W22 are formed in an arc shape, i.e., in a shape having a predetermined curvature. With this configuration, a flow velocity difference of the refrigerant can be easily generated in the refrigerant flow path W10, and a flow velocity difference of the air can also be easily generated in the air flow paths W21, W22.

[0039] (3) A centrifugal fan 30 that causes air to flow through the air flow paths W21, W22 is provided on the upstream side in the air flow direction of the upper surface 210a of the plate member 21. This configuration makes it possible to easily cause air to flow through the air flow paths W21, W22. (4) The inner outer fin 24a and the outer outer fin 24b are formed to protrude from the upper surface 210a of the plate member 21. The area of ​​the outer outer fins 24b in contact with the air is larger than the area of ​​the inner outer fins 24a in contact with the air. This configuration makes it easy to realize a structure in which the amount of heat exchanged between the outer outer fin 24b and the air is larger than the amount of heat exchanged between the inner outer fin 24a and the air.

[0040] (First Modification) Next, a first modification of the heat exchanger 10 of the embodiment will be described. The following mainly describes the differences from the heat exchanger 10 of the above embodiment. 8, the heat exchanger 10 of this modification has air flow paths W30 through which air flows and refrigerant flow paths W40 through which refrigerant flows, which are alternately arranged in the direction indicated by the arrow Z. Partition walls 50, 51 are provided between the air flow paths W30 and the refrigerant flow paths W40 to separate them. In this heat exchanger 10, heat exchange is performed between the air flowing through the air flow paths W30 and the refrigerant flowing through the refrigerant flow paths W40 via the partition walls 50, 51.

[0041] As shown in FIG. 9, the air flow path W30 is formed to extend in the direction indicated by the arrow X. At one end of the heat exchanger 10 in the direction indicated by the arrow X, an inlet 61 is formed to allow air to flow into the air flow path W30. At the other end of the heat exchanger 10 in the direction indicated by the arrow X, an outlet 62 is formed through which the air flowing through the air flow path W30 flows out. At the center of the air flow path W30 in the direction indicated by the arrow X, a throttle section 64 is formed in which the cross-sectional area of ​​the flow path is partially narrowed in the direction indicated by the arrow Y. Therefore, in the air flow path W30, the flow speed of the air is fast near the throttle section 64, and the flow speed of the air is slow near the inlet 61 and the outlet 62. As a result, for example, on the upper surface 500 of the partition wall 50, there are a high flow speed region A11 through which air passes at a high speed, and a low flow speed region A12 through which air passes at a flow speed slower than that of the high flow speed region A11.

[0042] 8, an outlet 72 of the refrigerant flow path W40 is further formed at one end of the heat exchanger 10. An inlet 71 of the refrigerant flow path W40 is further formed at the other end of the heat exchanger 10. Therefore, the flow direction of the air in the air flow path W30 and the flow direction of the refrigerant in the refrigerant flow path W40 are opposite to each other.

[0043] As shown in FIG. 9, the heat exchanger 10 further includes fins 81 disposed in the air flow path W30. The fin 81 is formed so as to extend in the direction indicated by the arrow Z. One end of the fin 81 is joined to the upper surface 500 of the partition wall 50 shown in FIG. 8. The other end of the fin 81 is joined to the lower surface 510 of the partition wall 51 shown in FIG. 8. As shown in FIG. 9, the fin 81 is formed in a streamlined shape similar to the outer fins 24, 25 of the above embodiment. A plurality of fins 81 are sparsely arranged in the high flow rate region A11 of the upper surface 500 of the partition wall 50. A plurality of fins 81 are densely arranged in the low flow rate region A12 of the upper surface 500 of the partition wall 50. In this modification, the fin 81 arranged in the high flow rate region A11 corresponds to the first heat transfer portion and heat transfer member arranged in the first region. Moreover, the fin 81 arranged in the low flow rate region A12 corresponds to the first heat transfer portion and heat transfer member arranged in the second region.

[0044] Even with the heat exchanger 10 having such a structure, it is possible to obtain the same or similar functions and effects as the heat exchanger 10 of the above embodiment. (Second Modification) Next, a second modification of the heat exchanger 10 of the embodiment will be described. The following description will focus on the differences from the heat exchanger 10 of the first modification.

[0045] As shown in FIG. 10, in the heat exchanger 10 of this modification, in the section from the inlet 61 to the central portion 63 in the air flow path W30, the flow path cross-sectional area becomes larger from the inlet 61 to the central portion 63. In the section from the central portion 63 to the outlet 62 in the air flow path W30, the flow path cross-sectional area is constant. As a result, on the upper surface 500 of the partition wall 50, there are a high flow velocity region A11 through which air passes at a high speed and a low flow velocity region A12 through which air passes at a flow velocity slower than that of the high flow velocity region A11. In the high flow velocity region A11, a plurality of fins 81 are sparsely arranged. In the low flow velocity region A12, a plurality of fins 81 are densely arranged. In addition, in the section from the central portion 63 to the outlet 62 in the air flow path W30, the flow velocity of the air is constant, so the density of the fins 81 in that section does not change. In this modification, the fins 81 arranged in the high flow velocity region A11 correspond to the first heat transfer section and the heat transfer member arranged in the first region. Moreover, the fins 81 arranged in the low flow velocity region A12 correspond to the first heat transfer portion and the heat transfer member arranged in the second region.

[0046] Even with the heat exchanger 10 having such a structure, it is possible to obtain the same or similar functions and effects as the heat exchanger 10 of the above embodiment. <Other embodiments> The above embodiment can also be implemented in the following manner.

[0047] In the first and second modified examples of the heat exchanger 10, a structure is adopted in which the cross-sectional area of ​​the air flow path W20 perpendicular to the air flow direction is changed in the direction indicated by the arrow Y. However, instead of this, a structure may be adopted in which the cross-sectional area of ​​the air flow path is changed in the direction indicated by the arrow Z.

[0048] In the heat exchanger 10 of the above embodiment, the first modification, and the second modification, in order to create a difference between the heat exchange amount of the fins arranged in the high flow rate region A11 and the heat exchange amount of the fins arranged in the low flow rate region A12, a configuration is adopted in which the density of the fins is changed without changing the shape of the fins in each region A11, A12, in other words, a configuration in which the surface area of ​​the fins is changed. Instead of this, for example, as shown in FIG. 11, the shapes of the fins 91, 92 arranged in the high flow rate region A11 and the low flow rate region A12, respectively, may be changed. Specifically, the first fin 91 arranged in the high flow rate region A11 is formed flatter than the second fin 92 arranged in the low flow rate region A12. As a result, the first fin 91 can reduce the number of collisions of air at its leading edge portion 910, and therefore the ventilation resistance of air can be reduced. In addition, the second fin 92 has a larger leading edge effect than the first fin 91, and therefore the heat transfer coefficient is improved. In this way, by using a structure that creates a difference between the heat transfer coefficient of the first fin 91 and the heat transfer coefficient of the second fin 92, it is possible to create a difference between the heat exchange amount of the fins arranged in the high flow rate region A11 and the heat exchange amount of the fins arranged in the low flow rate region A12.

[0049] The heat transfer member that exchanges heat with the air is not limited to pin-shaped fins, and any member can be used. For example, louvers 201, 202 as shown in Fig. 12 can be used as the heat transfer member. In this case, as shown in Fig. 12, a plurality of first louvers 201 are arranged at a predetermined pitch P11 in the high flow velocity region A11. Also, as shown in Fig. 12, a plurality of second louvers 202 are arranged at a pitch P12 shorter than the pitch P11 in the low flow velocity region A12.

[0050] In the heat exchanger 10 of the embodiment, a structure similar to the air flow paths W21 and W22 may be adopted for the refrigerant flow path W10. Specifically, as shown in FIG. 4, in the refrigerant flow path W10, a high flow velocity region A21 where the flow velocity of the refrigerant is relatively fast is formed near the collection tank space T12. Also, a low flow velocity region A22 where the flow velocity of the refrigerant is relatively slow is formed near the distribution tank space T11. Therefore, the high flow velocity region A21 and the low flow velocity region A22 exist on the inner surface 211b of the lower wall portion 211 of the plate member 21. In this case, the inner surface 211b of the plate member 21 corresponds to the second wall surface, the high flow velocity region A21 corresponds to the third region, and the low flow velocity region A22 corresponds to the fourth region. In such a structure, it is effective to make the heat exchange amount of the refrigerant in the low flow velocity region A22 of the inner fin 40 larger than the heat exchange amount of the refrigerant in the high flow velocity region A21 of the inner fin 40. 13 is used as the inner fin 40, an inner fin 40 having a relatively short offset pitch OP is arranged in the low flow velocity region A22, and an inner fin 40 having a relatively long offset pitch OP is arranged in the high flow velocity region A21. In this case, the inner fin 40 arranged in the high flow velocity region A21 corresponds to the second heat transfer section.

[0051] The present disclosure is not limited to the above specific examples. Any design modifications made by a person skilled in the art to the above specific examples are also included within the scope of the present disclosure as long as they have the features of the present disclosure. The elements of each of the above specific examples, as well as their arrangements, conditions, shapes, etc., are not limited to those exemplified and can be modified as appropriate. The elements of each of the above specific examples can be combined in different ways as appropriate, as long as no technical contradictions arise.

[0052] <Additional Notes> Next, the features of the present invention that can be understood from the above embodiment and its modifications will be described below. 4. The heat exchanger according to claim 1, wherein the heat transfer section is constituted by a plurality of heat transfer members (24) formed to protrude from the wall surface, and an area of ​​contact between the heat transfer section arranged in the second region and the first fluid is larger than an area of ​​contact between the heat transfer section arranged in the first region and the first fluid.

[0053] 4. The heat exchanger according to claim 1, wherein the heat transfer section is constituted by a plurality of heat transfer members (24) formed to protrude from the wall surface, and a heat transfer coefficient of the heat transfer section arranged in the second region to the first fluid is greater than a heat transfer coefficient of the heat transfer section arranged in the first region to the second fluid.

[0054] 6. The heat exchanger according to claim 1, wherein a wall surface of the partition wall facing the first flow path is defined as a first wall surface, a wall surface of the partition wall facing the second flow path is defined as a second wall surface, and the heat transfer section is defined as a first heat transfer section, the second wall surface of the partition wall has a third region (A21) through which the second fluid passes and a fourth region (A22) through which the second fluid passes at a flow velocity slower than that of the third region, the third region and the fourth region of the second wall surface of the partition wall are formed with a second heat transfer section (40) that transfers heat of the second fluid to the partition wall, and an amount of heat exchange of the second fluid in the fourth region of the second heat transfer section is greater than an amount of heat exchange of the second fluid in the third region of the second heat transfer section. [Explanation of symbols]

[0055] A11: High flow rate area (1st area) A12: Low flow rate area (second area) A21: High flow rate area (3rd area) A22: Low flow rate area (4th area) W10: Coolant flow path (second flow path) W21, W22: Air flow path (first flow path) 10: Heat exchanger 24a: Inner outer fin (first heat transfer part, heat transfer member) 24b: Outer fin (first heat transfer part, heat transfer member) 30: Centrifugal fan 40: Inner fin (second heat transfer section) 210: Upper wall (partition wall)

Claims

1. A heat exchanger (10) having a partition wall (210) separating a first flow path (W21, W22) through which a first fluid flows and a second flow path (W10) through which a second fluid flows, wherein heat exchange is performed between the first fluid and the second fluid via the partition wall, The first fluid flows in a first direction through the first flow path, The second fluid flows in a second direction opposite to the first direction in the second flow path, a first region (A11) through which the first fluid passes and a second region (A12) through which the first fluid passes at a flow velocity slower than that of the first region are present on a wall surface of the partition wall facing the first flow path, a heat transfer section (24) for increasing a heat transfer area for the first fluid is disposed in each of the first region and the second region of the partition wall; an amount of heat exchange of the first fluid in the heat transfer section (24b) arranged in the second region is greater than an amount of heat exchange of the first fluid in the heat transfer section (24a) arranged in the first region, The first flow path and the second flow path are formed in a shape having a predetermined curvature. heat exchanger.

2. A centrifugal fan (30) for causing the first fluid to flow through the first flow path is provided on an upstream portion of the wall surface of the partition wall in the flow direction of the first fluid.

2. The heat exchanger of claim 1.

3. The heat transfer section is composed of a plurality of heat transfer members (24) formed so as to protrude from the wall surface, An area where the heat transfer portion arranged in the second region comes into contact with the first fluid is larger than an area where the heat transfer portion arranged in the first region comes into contact with the first fluid.

2. The heat exchanger of claim 1.

4. The heat transfer section is composed of a plurality of heat transfer members (24) formed so as to protrude from the wall surface, The heat transfer coefficient of the heat transfer portion disposed in the second region with respect to the first fluid is greater than the heat transfer coefficient of the heat transfer portion disposed in the first region with respect to the first fluid.

2. The heat exchanger of claim 1.

5. A wall surface of the partition wall facing the first flow path is defined as a first wall surface, a wall surface of the partition wall facing the second flow path is defined as a second wall surface, and the heat transfer portion is defined as a first heat transfer portion. a third region (A21) through which the second fluid passes and a fourth region (A22) through which the second fluid passes at a flow velocity slower than that of the third region are present on the second wall surface of the partition wall, a second heat transfer section (40) that transfers heat of the second fluid to the partition wall is formed in the third region and the fourth region of the second wall surface of the partition wall, The amount of heat exchange of the second fluid in the fourth region of the second heat transfer portion is greater than the amount of heat exchange of the second fluid in the third region of the second heat transfer portion.

2. The heat exchanger of claim 1.

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