Heat exchanger

Abstract

A heat exchanger (10) is provided with a plurality of fins (30) that divide a heat medium flow path into a plurality of fine flow paths (W11) by being arranged with a prescribed interval. The fins are formed in a shape in which thick wall portions (301) and thin wall portions (302) are alternately arranged along a flow path length direction. A thick wall portion (301a) of one fin (30a) of two fins that are arranged adjacent to each other and a thin wall portion (302b) of the other fin (30b) are arranged opposite each other in a fin arrangement direction, and a thin wall portion (302a) of the one fin and a thick wall portion (301b) of the other fin are arranged opposite each other in the fin arrangement direction.

Description

[0001] Cross-reference of related applications

[0002] This application is based on and claims priority to Japanese Patent Application No. 2020-104893, filed on June 17, 2020, and Japanese Patent Application No. 2020-146344, filed on August 31, 2020, the entire contents of which are incorporated herein by reference. Technical Field

[0003] This invention relates to a heat exchanger. Background Technology

[0004] Conventionally, heat exchangers for dissipating heat from electronic components such as semiconductor devices have been described in Patent Document 1. The heat exchanger described in Patent Document 1 includes a flow path tube having a heat medium flow path through which a heat medium flows. Multiple inner fins are arranged inside the flow path tube, dividing the heat medium flow path into multiple narrow flow paths. The inner fins are formed by corrugated fins whose plate portion is bent into a wavy shape in the length direction when viewed from their arrangement direction. By using corrugated fins, the narrow flow paths between adjacent corrugated fins are formed in a meandering shape. Therefore, because the heat medium flow in the narrow flow paths easily becomes turbulent, the heat exchange performance of the heat exchanger can be improved.

[0005] Existing technical documents

[0006] Patent documents

[0007] Patent Document 1: Japanese Patent No. 5545260

[0008] In heat exchangers, one method to improve their heat exchange performance is to increase the thickness of the inner fins. Increasing the inner fin thickness improves fin efficiency, thus enhancing the heat exchanger's overall performance. Fin efficiency refers to the ratio of actual heat transfer from the fins to the ideal heat transfer from the fins. The ideal heat transfer is defined as the heat transfer assuming the fin surface temperature is equal to the root temperature of all fins.

[0009] In the heat exchanger described in Patent Document 1 above, if the plate thickness is increased to improve the fin efficiency of the corrugated fins, the gap between adjacent corrugated fins becomes narrower. That is, the flow path width of each narrow flow path becomes narrower. As a result, if the flow velocity of the hot medium flowing in each narrow flow path increases, it may lead to pressure loss in the hot medium flow path. Since there is a trade-off between fin efficiency and pressure loss in the hot medium flow path, it is difficult to balance them both in practice. Summary of the Invention

[0010] The purpose of this invention is to provide a heat exchanger that enables the meandering flow of the heat medium, avoids increasing the pressure loss of the heat medium flowing in the heat medium flow path, and improves fin efficiency.

[0011] One aspect of the present invention provides a heat exchanger that performs heat exchange between a heat medium flowing through a heat medium flow path and electronic components. The heat medium flow path is divided into multiple narrow flow paths by arranging the fins at predetermined intervals. The heat medium flow path extends along its length, intersecting the fin arrangement direction. The fins are formed by alternating thick-walled and thin-walled portions along the length of the flow path, with the thick-walled portions being the thicker parts and the thin-walled portions being the thinner parts. In two adjacent fins, the thick-walled portion of one fin and the thin-walled portion of the other fin are arranged opposite each other in the fin arrangement direction, and the thin-walled portion of one fin and the thick-walled portion of the other fin are arranged opposite each other in the fin arrangement direction.

[0012] If the thick-walled portions and thin-walled portions of adjacent fins are arranged opposite each other as in this structure, the flow path width of the narrow flow path will not be narrowed, and the narrow flow path between these fins will be formed in a meandering shape. Therefore, a meandering flow of the heat medium can be achieved, and the pressure loss of the heat medium flowing in the flow path is avoided. In addition, by forming both thin-walled and thick-walled portions in the fins, the fin thickness can be increased compared to the case of using thin-plate fins, thus improving fin efficiency. Attached Figure Description

[0013] Figure 1 This is a cross-sectional view showing the cross-sectional structure of the heat exchanger in the first embodiment.

[0014] Figure 2 It means along Figure 1 A sectional view of the cross-sectional structure along line II-II.

[0015] Figure 3 This is a diagram schematically illustrating the flow of the heat medium in the heat exchanger of the first embodiment.

[0016] Figure 4 This is a cross-sectional view showing the cross-sectional structure of a heat exchanger in a modified example of the first embodiment.

[0017] Figure 5 This is a cross-sectional view showing the cross-sectional structure of the fins in the second embodiment.

[0018] Figure 6 This is a perspective view showing the cross-sectional three-dimensional structure of the heat exchanger according to the second embodiment.

[0019] Figure 7 This is a cross-sectional view showing the cross-sectional structure of the heat exchanger in the first modified example of the second embodiment.

[0020] Figure 8 This is a cross-sectional view showing the cross-sectional structure of the fins in the second variation of the second embodiment.

[0021] Figure 9 This is a cross-sectional view showing the cross-sectional structure of the fins in the third variation of the second embodiment.

[0022] Figure 10 This is a cross-sectional view showing the cross-sectional structure of the fins in the fourth variation of the second embodiment.

[0023] Figure 11 This is a cross-sectional view showing the cross-sectional structure of the fins in the fourth variation of the second embodiment.

[0024] Figure 12 This is a cross-sectional view showing the cross-sectional structure of the heat exchanger according to the third embodiment.

[0025] Figure 13 This is a cross-sectional view showing the cross-sectional structure of the heat exchanger according to the third embodiment.

[0026] Figure 14 This is a cross-sectional view showing the cross-sectional structure of the heat exchanger according to the fourth embodiment.

[0027] Figure 15 This is a top view showing the top structure of the heat exchanger according to the fourth embodiment.

[0028] Figure 16 This is a top view showing the top structure of the heat exchanger of the modified example of the fourth embodiment.

[0029] Figure 17 This is a top view showing the top structure of the heat exchanger of the modified example of the fourth embodiment.

[0030] Figure 18 This is a cross-sectional view showing the cross-sectional structure of the fins in the fifth embodiment.

[0031] Figure 19 This is a graph showing the relationship between the clearance ratio α along the flow path length of the heat exchanger in the fifth embodiment and the heat transfer performance Pf.

[0032] Figure 20 This is a graph showing the relationship between the fin configuration direction occupancy β and the flow path length direction clearance ratio α of the heat exchanger in the fifth embodiment.

[0033] Figure 21 (A) and (B) are cross-sectional views showing the cross-sectional structure of the fins in a modified example of the fifth embodiment.

[0034] Figure 22 (A) and (B) are cross-sectional views showing the cross-sectional structure of the fins in a modified example of the fifth embodiment. Detailed Implementation

[0035] Hereinafter, embodiments of the heat exchanger will be described with reference to the accompanying drawings. To facilitate understanding, the same symbols will be used to label the same structural elements in each drawing as much as possible, and repeated descriptions will be omitted.

[0036] <First Implementation>

[0037] First of all, Figure 1 The heat exchanger 10 of the first embodiment shown will be described. A semiconductor element 40, such as an IGBT (Insulated Gate Bipolar Transistor), which is a structural element of an inverter device, is disposed on the outer surface of the heat exchanger. In this embodiment, the semiconductor element 40 corresponds to an electronic component. The heat exchanger 10 is a device for dissipating heat from the semiconductor element 40 by exchanging heat with a heat transfer medium such as water flowing inside it. The heat exchanger 10 includes a substrate 20 and a plurality of fins 30.

[0038] The substrate 20 is made of metals such as aluminum and copper and is formed into a hollow box shape. The substrate 20 has a first base 21 and a second base 22.

[0039] The first base 21 is formed in the shape of a flat plate. A semiconductor element 40 is disposed on one surface of the first base 21, namely the outer surface 210.

[0040] The cross-sectional shape of the second base 22, orthogonal to the direction indicated by arrow Y in the figure, is concave. A hollow box-shaped base 20 is formed by assembling the first base 21 onto the second base 22 in a manner that closes the opening of the second base 22. The internal space of the base 20 constitutes a heat medium flow path W10 for the flow of the heating medium. The heat medium flow path W10 is formed to extend along the direction indicated by arrow Y. Hereinafter, the direction indicated by arrow Y will also be referred to as the "flow path length direction".

[0041] Multiple fins 30, made of metals such as aluminum and copper, are disposed inside the base 20. The multiple fins 30 are integrally formed with the first base 21. The multiple fins 30 are arranged at predetermined intervals in the direction indicated by arrow X in the figure, which is orthogonal to the flow path length direction Y. The multiple fins 30 divide the internal heat medium flow path W10 of the base 20 into multiple narrow flow paths W11. Heat medium flows in each narrow flow path W11. One end 31 of the fin 30 is fixed to the other surface of the first base 21, i.e., the inner surface 211. The other end 32 of the fin 30 contacts the inner surface of the bottom wall portion 220 of the second base 22.

[0042] Furthermore, the direction indicated by arrow X will be referred to as the "fin configuration direction X" below. Additionally, the direction orthogonal to both the fin configuration direction X and the flow path length direction Y will be referred to as the "fin height direction Z".

[0043] Figure 2 Indicates along Figure 1 The cross-sectional structure of line II-II is shown. (See figure.) Figure 2 As shown, the fin 30 is formed by alternating thick-walled portions 301 and thin-walled portions 302 along the length direction Y of the flow path, resulting in an overall non-uniform thickness. The thick-walled portion 301 is relatively thicker than the average thickness of the fin 30. The thin-walled portion 302 is relatively thinner than the average thickness of the fin 30. The thick-walled portion 301 and the thin-walled portion 302 have the same length along the length direction Y. Furthermore, the length of the fin 30 in the fin height direction Z is shorter than the length of the fin in the length direction Y, but longer than the length of the first base 21 in the fin height direction Z. Hereinafter, the thickest portion of the thick-walled portion 301 will be referred to as the thickest wall portion 3010, and the thinnest portion of the thin-walled portion 302 will be referred to as the thinnest wall portion 3020.

[0044] In the fin 30, a plurality of thickest wall portions 3010 are formed at a predetermined spacing P along the flow path length direction Y, and a plurality of thinnest wall portions 3020 are formed at the same spacing P along the flow path length direction Y. The surfaces 303 and 304 of the fin 30 facing the narrow flow path W11 are formed by curved surfaces in a smooth and continuous manner with the thickest wall portions 3010 and the thinnest wall portions 3020, having a generally cycloidal curved surface continuous along the flow path length direction Y. When the lengths of the thickest wall portions 3010 and the thinnest wall portions 3020 in the fin arrangement direction X are each referred to as "widths," and the length of the narrow flow path W11 in the fin arrangement direction X is referred to as "flow path width," the width of the thickest wall portion 3010 is greater than the maximum flow path width of the narrow flow path W11. Furthermore, the width of the thinnest wall portion 3020 is less than the minimum flow path width of the narrow flow path W11.

[0045] Furthermore, hereinafter, two fins 30 arranged adjacent to each other in the fin configuration direction X will be referred to as "fins 30a and 30b". The symbols 301a and 301b will be used to represent the thick-walled portions of fins 30a and 30b, respectively, and the symbols 302a and 302b will be used to represent the thin-walled portions of fins 30a and 30b, respectively. The symbols 3010a and 3010b will be used to represent the thickest portions of fins 30a and 30b, respectively, and the symbols 3020a and 3020b will be used to represent the thinnest portions of fins 30a and 30b, respectively.

[0046] like Figure 2 As shown, the thick-walled portion 301a of one of the two adjacent fins 30a and 30b is positioned opposite to the thin-walled portion 302b of the other fin in the fin arrangement direction X. Furthermore, the thin-walled portion 302a of one fin 30a and the thick-walled portion 301b of the other fin 30b are positioned opposite to each other in the fin arrangement direction X. Moreover, the thickest wall portion 3010a of one fin 30a and the thickest wall portion 3010b of the other fin are offset by half a predetermined distance P "P / 2" in the flow path length direction Y. Similarly, the thinnest wall portion 3020a of one fin 30a and the thinnest wall portion 3020b of the other fin are offset by half a predetermined distance P "P / 2" in the flow path length direction Y. In addition, the cross-sectional shapes of the two adjacent fins 30a and 30b, which are orthogonal to the fin height direction Z, are the same except that they are staggered by “P / 2” in the flow path length direction Y.

[0047] According to the heat exchanger 10 of this embodiment described above, the following functions and effects (1) to (7) can be obtained.

[0048] (1) As Figure 2 As shown, if the thick-walled portions 301a and 301b of adjacent fins 30a and 30b are arranged opposite to the thin-walled portions 302a and 302b, the flow path width of the narrow flow path W11 will not be narrowed, and the narrow flow path W11 provided between these fins 30a and 30b is formed in a meandering shape. Therefore, a meandering flow of the heat medium can be achieved, and the pressure loss of the heat medium flowing in the heat medium flow path W10 is avoided. In addition, since not only thin-walled portions 302a and 302b are formed in the fins 30a and 30b, but also thick-walled portions 301a and 301b are formed, the plate thickness of the fins 30a and 30b can be ensured compared with the case of using thin plate-shaped fins, thus improving fin efficiency.

[0049] (2) In the heat exchanger 10 of this embodiment, such as Figure 3As shown by the middle arrow, the heat transfer medium flows in a meandering pattern inside the narrow flow path W11. By making the heat transfer medium flow in this way, the portion of the heat transfer medium that is easily impacted in fin 30a becomes the sidewall portion 308a of its thick-walled portion 301a. Similarly, the portion of the heat transfer medium that is easily impacted in fin 30b becomes the sidewall portion 308b of its thick-walled portion 301b. Because the heat transfer medium collides with the thick-walled portions 301a and 301b of each fin 30a and 30b in this way, heat from the heat transfer medium is easily transferred to the fins 30a and 30b, thus improving fin efficiency.

[0050] (3) The parts where the heat medium is easily peeled off from the surface of each fin 30a and 30b are: Figure 3 The thin-walled portions 302a and 302b are shown nearby. Therefore, since the thin-walled portions 302a and 302b are arranged in areas where heat exchange between each fin 30a and 30b and the heat medium is difficult, it is difficult for the thin-walled portions 302a and 302b to cause a deterioration in fin efficiency.

[0051] (4) The thickest wall portion 3010a of one fin 30a and the thickest wall portion 3010b of the other fin 30b are staggered by half a predetermined distance P "P / 2" in the flow path length direction Y. Similarly, the thinnest wall portion 3020a of one fin 30a and the thinnest wall portion 3020b of the other fin 30b are staggered by half a predetermined distance P "P / 2" in the flow path length direction Y. According to this structure, the narrow flow path W11 provided between adjacent fins 30a and 30b can easily be formed into a meandering shape, thus making it easier to achieve a meandering flow of the heat medium. As a result, the heat exchange performance of the heat exchanger 10 can be improved.

[0052] (5) When the heat medium flows in a meandering manner, it may flow in a way that detaches from the surface of the fins. If the heat medium flows in a way that detaches from the surface of the fins, it is easy for the heat medium to stagnate in that part. This is the main reason for the reduction in the heat exchange performance of the heat exchanger 10. In this regard, the surfaces 303 and 304 of the fins 30 facing the narrow flow path W11 are formed as curved surfaces. According to this structure, the heat medium flowing in the narrow flow path W11 is difficult to detach from the surfaces 303 and 304, thus avoiding a reduction in the heat exchange performance of the heat exchanger 10.

[0053] (6) The heat exchanger 10 includes a first base 21 on which a semiconductor element 40 is disposed on an outer surface 210. One end 31 of each of the plurality of fins 30 is fixed to the inner surface 211 of the first base 21. According to this structure, the semiconductor element 40 can be effectively heat-exchanged with the heat medium via the first base 21.

[0054] (7) One end 31 of the fin 30 is fixed to the other surface of the first base 21, namely the inner surface 211. The other end 32 of the fin 30 is in contact with the inner surface of the bottom wall portion 220 of the second base 22. According to this structure, each fine flow path W11 constitutes an independent flow path, thus facilitating the flow of the heat medium along each fin 30. Therefore, the heat exchange performance of the heat exchanger 10 can be improved.

[0055] (Modified Example)

[0056] Next, a modified example of the heat exchanger 10 of the first embodiment will be described.

[0057] like Figure 4 As shown, in the heat exchanger 10 of this modified example, a gap is formed between the other end 32 of the fin 30 and the inner surface of the bottom wall portion 220 of the second base 22. According to the structure of this modified example, even if there is a dimensional error in the length of the fin 30 in the fin height direction Z, the gap formed between the other end 32 of the fin 30 and the bottom wall portion 220 of the second base 22 can absorb the dimensional error, thereby mitigating the dimensional inaccuracy of the fin 30.

[0058] In addition, such as Figure 4 As shown, multiple fine flow paths W11 can be interconnected through a gap formed between the fin 30 and the bottom wall 220 of the second base 22. In other words, the multiple fine flow paths W11 do not need to be independent flow paths; they can be formed as flow paths interconnected at specified locations. Or, as... Figure 1 As shown, multiple fine flow paths W11 can also be formed as independent flow paths.

[0059] <Second Implementation>

[0060] Next, a second embodiment of the heat exchanger 10 will be described. Hereinafter, the description will focus on the differences between the heat exchanger 10 and the first embodiment.

[0061] like Figure 5 As shown, in the fin 30 of this embodiment, a connecting passage 305 is formed so as to penetrate each of its thin-walled portions 302 in the thickness direction. The connecting passage 305 connects a fine flow path W11 arranged along one surface 303 of the fin 30 and a fine flow path W11 arranged along the other surface 304 of the fin 30.

[0062] In addition, the portion of the fin 30 disposed between adjacent thinnest wall portions 3020, 3020 has a linearly symmetrical shape centered on an axis m10 passing through its center and parallel to the fin height direction Z.

[0063] In addition, such as Figure 6As shown, the connecting path 305 can also be formed only in a portion of the multiple fins 30. Furthermore, as... Figure 6 As shown, the connecting path 305 may also be provided in a portion of the region from one end to the other end in the fin height direction Z of the thin-walled portion 302. Alternatively, the connecting path 305 may be provided in the entire region from one end to the other end in the fin height direction Z of the thin-walled portion 302.

[0064] The heat exchanger 10 of this embodiment described above can further achieve the functions and effects shown in (8) and (9) below.

[0065] (8) Since the heat medium can flow between each narrow flow path W11 via the connecting passage 305, the heat unevenness of the heat medium flowing in each narrow flow path W11 can be reduced. Therefore, the unevenness of the heat exchange performance of the heat exchanger 10 can be improved. In addition, by forming the connecting passage 305 in the fin 30, the fin 30 can be easily formed using a mold, making the fin 30 easier to manufacture.

[0066] (9) A connecting passage 305 is provided in a portion of the thin-walled portion 302 of the fin 30, extending from one end to the other in the Z-direction of the fin height. According to this structure, the effect of improving the unevenness of heat exchange performance can be obtained by forming the connecting passage 305 in the fin 30. Furthermore, by not forming the connecting passage 305 in the portion of the thin-walled portion 302 of the fin 30, the heat transfer area of ​​the fin 30 can be ensured. As a result, both the effect of improving the unevenness of heat exchange performance and the effect of ensuring the heat transfer area of ​​the fin 30 can be achieved.

[0067] (First variation)

[0068] Next, a first variation of the heat exchanger 10 of the second embodiment will be described.

[0069] like Figure 7 As shown, the plurality of fins 30 in this modified example include fins 30c and fins 30d. In the fin height direction Z, fin 30c is positioned opposite to the semiconductor element 40, and fin 30d is positioned not opposite to the semiconductor element 40. In the heat exchanger 10 of this modified example, a connecting passage 305 is formed in fin 30d, but no connecting passage 305 is formed in fin 30c.

[0070] In such Figure 7In the heat exchanger 10 shown, the fin efficiency of the fin 30c, which is arranged opposite to the semiconductor element 40, tends to affect the heat dissipation of the semiconductor element 40 compared to the fin efficiency of the fin 30d, which is not arranged opposite to the semiconductor element 40. Therefore, if it is assumed that a connecting path 305 is formed in the fin 30c, the fin efficiency of the fin 30c deteriorates, and as a result, the heat dissipation of the semiconductor element 40 may decrease. In this respect, since no connecting path 305 is formed in the fin 30c in this modified heat exchanger 10, there is no concern about the deterioration of the fin efficiency in the fin 30c. Therefore, the heat dissipation of the semiconductor element 40 can be ensured more reliably.

[0071] (Second variation)

[0072] Next, a second variation of the heat exchanger 10 of the second embodiment will be described.

[0073] like Figure 8 As shown, in the fin 30 of this modified example, in the portion disposed between adjacent connecting passages 305, 305, a pin-shaped corner portion 306 is formed at one end in the fin arrangement direction X, and a pin-shaped corner portion 307 is also formed at the other end.

[0074] According to the structure of this modified example, the detachment of the heat medium near the corners 306 and 307 of the fins 30 can be reduced, thus increasing the heat transfer area of ​​the fins 30 to the heat medium. Therefore, the heat exchange performance of the heat exchanger 10 can be improved.

[0075] (Third variation)

[0076] Next, a third variation of the heat exchanger 10 of the second embodiment will be described.

[0077] like Figure 9 As shown, in this modified example, the portion of the fin 30 disposed between adjacent connecting passages 305, 305 has a non-linearly symmetrical shape centered on an axis m10 passing through its center and parallel to the fin height direction Z. More specifically, in the portion disposed between adjacent connecting passages 305, 305, on the downstream side of the flow path length direction Y, a pin-shaped corner portion 306 is formed at one end in the fin arrangement direction X, and an R-shaped corner portion 307 is formed at the other end.

[0078] According to the structure of this modified example, the flow velocity of the hot medium flowing along the narrow flow path W11 on one side of the pin-shaped corner 307 is faster than the flow velocity of the hot medium flowing along the narrow flow path W11 on the other side of the R-shaped corner. Therefore, the flow of hot medium from the narrow flow path W11 on one side of the pin-shaped corner 307 to the narrow flow path W11 on the other side of the R-shaped corner 307 via the connecting passage 305 is easily formed. As a result, it is difficult for hot medium to precipitate near the connecting passage 305, thus suppressing the reduction of the heat transfer performance of the hot medium.

[0079] (Fourth variation)

[0080] Next, a fourth variation of the heat exchanger 10 of the second embodiment will be described.

[0081] like Figure 10 As shown, in this modified example, the portion of the fin 30 disposed between the plurality of connecting paths 305 is referred to as the fin body 310. For example... Figure 10 As shown, in the case where there is a region A in the fin arrangement direction X where the fin bodies 310a and 310b of adjacent fins 30a and 30b do not overlap, the cross-sectional area of ​​the flow path of the heat medium locally increases sharply in region A. As a result, in region A, the heat medium becomes more prone to flow due to inertia. Therefore, downstream of the flow direction of the heat medium in the fin body 310, heat medium peeling and precipitation are likely to occur. This is the main reason for the reduced heat transfer performance of the fin 30.

[0082] Therefore, as Figure 11 As shown, the fin bodies 310a and 310b of adjacent fins 30a and 30b are preferably configured to overlap in the fin configuration direction X. With this structure, the localized rapid expansion of the flow path cross-sectional area of ​​the heat medium can be suppressed, thus reducing the likelihood of heat medium stripping and deposition in the fin body 310. Therefore, the heat transfer performance of the fin 30 can be improved.

[0083] <Third Implementation Method>

[0084] Next, a third embodiment of the heat exchanger 10 will be described. Hereinafter, the description will focus on the differences between the heat exchanger 10 and the one in the first embodiment.

[0085] like Figure 12 As shown, in the fin 30 of this embodiment, the sidewall portion of one end 31 fixed to the first base 21 is formed in an R shape. Alternatively, as... Figure 13 As shown, the sidewall portion of one end 31 of the fin 30 can also be formed into a conical shape to set the draft angle.

[0086] The heat exchanger 10 of this embodiment described above can further achieve the following functions and effects (9).

[0087] (9) Since heat can be easily transferred from the fins 30 to the first base 21, the fin efficiency of the fins 30 can be improved. Therefore, the heat exchange performance of the heat exchanger 10 can be improved.

[0088] <Fourth Implementation>

[0089] Next, a fourth embodiment of the heat exchanger 10 will be described. Hereinafter, the description will focus on the differences between the heat exchanger 10 and the one in the first embodiment.

[0090] like Figure 14 As shown, in the heat exchanger 10 of this embodiment, a concave insertion groove 212 is formed on the outer surface 210 of its first base 21. Specifically, as... Figure 15 As shown, on the outer surface 210 of the first base 21, two insertion slots 212 are formed and arranged in the flow path length direction Y. Two separately configured semiconductor elements 40 are inserted into the two insertion slots 212 respectively.

[0091] The heat exchanger 10 of this embodiment described above can further achieve the following functions and effects (10).

[0092] (10) If an insertion groove 212 for inserting a semiconductor element 40 is formed on the outer surface 210 of the first base 21 as in this embodiment, the placement of the semiconductor element 40 relative to the first base 21 becomes easier.

[0093] (Modified Example)

[0094] Next, a first variation of the heat exchanger 10 of the fourth embodiment will be described.

[0095] like Figure 16 As shown, in the heat exchanger 10, the fins 30 and the semiconductor element 40 may not be arranged opposite each other in the fin height direction Z.

[0096] In addition, in such Figure 16 In the structure shown, the heat transfer performance of the fins 30 to the semiconductor element 40 may be reduced. Therefore, as Figure 17 As shown, the heat exchanger 10 may also have a structure in which the fins 30 and the semiconductor element 40 are arranged opposite each other in the fin height direction Z.

[0097] <Fifth Implementation>

[0098] Next, the fifth embodiment of the heat exchanger 10 will be described. Hereinafter, the description will focus on the differences between the heat exchanger 10 and the one in the second embodiment.

[0099] Through experiments, the inventors have determined that, as in the heat exchanger 10 of the second embodiment, the heat exchanger 10 can improve performance when the fins 30 form a connecting path 305. The experiments conducted by the inventors will be described in detail below.

[0100] exist Figure 18 In the heat exchanger 10 of this embodiment shown, a plurality of fins 30 are arranged at a predetermined interval Df in the fin arrangement direction X. Hereinafter, the interval Df will be referred to as the "fin spacing". A plurality of connecting passages 305 are formed at predetermined intervals in the flow path length direction Y of the fins 300. The fins 30 have a plurality of fin bodies 310 disposed between the plurality of connecting passages 305. The cross-sectional shape of the fin body 310, which is orthogonal to the fin height direction Z, is an elliptical shape having a long side in the flow path length direction Y and a short side in the fin arrangement direction X. That is, the fin body 310 has a shape in which its length in the flow path length direction Y is longer than its length in the fin arrangement direction X. The fin bodies 310 are formed at predetermined intervals Lp in the flow path length direction Y.

[0101] When a fin adjacent to a specified fin 30g on one side of the fin arrangement direction X is designated as the first adjacent fin 30e, and a fin adjacent to a specified fin 30g on the other side of the fin arrangement direction X is designated as the second adjacent fin 30f, the fin bodies 310e and 310f of the first and second adjacent fins 30e and 30f, respectively, are staggered by "Lp / 2" relative to the fin body 310g of the specified fin 30g in the flow path length direction Y. The fin bodies 310e and 310f of the first and second adjacent fins 30e and 30f, respectively, are arranged opposite each other in the fin arrangement direction X, separated by the connecting path 305g of the specified fin 30g.

[0102] In such a heat exchanger 10, if a connecting passage 305 is formed in the fins 30, a flow of the heat medium occurs in the connecting passage 305 due to the static pressure difference generated by the velocity difference between adjacent narrow flow passages W11, W11. Because of the flow of the heat medium in the connecting passage 305, precipitation of the heat medium is eliminated, resulting in improved heat transfer performance of the heat exchanger 10. Based on this principle, it can be assumed that the larger the connecting passage 305, the higher the precipitation elimination effect, and therefore the improved heat transfer performance. However, in reality, the larger the connecting passage 305, the smaller the heat transfer area of ​​the fins 30, thus leading to a significant decrease in heat transfer performance. Therefore, there is a trade-off between the improved heat transfer performance associated with the precipitation elimination effect and the decreased heat transfer performance associated with the reduced heat transfer area of ​​the fins 305, regarding the size of the connecting passage 305. As a result, it is believed that there exists a size for the connecting passage 305 that represents the maximum heat transfer performance of the heat exchanger 10.

[0103] Based on the above-described concept, the heat transfer performance of the heat exchanger 10 was experimentally determined by varying the lengths d1, Lp, d2, and Wp shown in the figure, and then the results were obtained as follows: Figure 19 The graph shown is illustrated below. Additionally, "d1" represents the width of the fin body 310 in the Y-direction of the flow path. "Lp" is the distance between the centers of adjacent fin bodies 310, 310, separated by the connecting passage 305 in the Y-direction of the flow path. "d2" is the width of the fin body 310 in the X-direction of the fin arrangement. "Wp" is twice the length of the fin spacing Df in the X-direction of the fin arrangement. Figure 19 The graphs shown represent the gap ratio α (={(Lp-d1) / Lp}×100) along the flow path length on the horizontal axis and the heat transfer performance Pf of the heat exchanger 10 on the vertical axis, illustrating their relationship. Additionally, Figure 19 The solid lines m1 to m5 shown represent the heat transfer performance Pf relative to the clearance ratio α in the flow path length direction when the fin configuration direction occupancy β (=(d2 / Wp)×100) is “26%”, “30%”, “32%”, “39%” and “50%”, respectively.

[0104] Furthermore, the clearance ratio α in the flow path length direction is expressed as a percentage, representing the width of the connecting path 305 relative to the arrangement spacing Lp of the fins 310 in the flow path length direction Y. Therefore, a larger clearance ratio α in the flow path length direction means a larger width of the connecting path 305 in the flow path length direction Y. Additionally, in Figure 19 In the curve shown, the value of the gap ratio α when it is "0%" is equivalent to the value when the fin without the connecting path 305 is used.

[0105] like Figure 19As shown, as the clearance ratio α in the flow path length direction increases from "0%", the heat transfer performance Pf of the heat exchanger 10 gradually increases to a maximum value and then decreases. Therefore, there exists a region where the heat transfer performance Pf is higher than when the clearance ratio α in the flow path length direction is "0%", i.e., when no connecting path 305 is formed. For example, when the fin configuration direction occupancy β is "26%", when the heat transfer performance Pf when the clearance ratio α in the flow path length direction is "0%" is taken as the reference heat transfer performance Pf1b, the heat transfer performance Pf1b increases as the clearance ratio α in the flow path length direction increases from "0", and the clearance ratio α in the flow path length direction represents a maximum value Pf1max when it reaches a predetermined value α10. Then, when the clearance ratio α in the flow path length direction further increases from the predetermined value α10, the heat transfer performance Pf decreases, and when the clearance ratio α in the flow path length direction reaches a threshold α11, the heat transfer performance Pf represents the reference heat transfer performance Pf1b. As the clearance ratio α along the flow path length increases further, the heat transfer performance Pf decreases compared to the baseline heat transfer performance Pf1b. Therefore, if the clearance ratio α along the flow path length satisfies "α≤α11", it is possible to ensure heat transfer performance equal to or higher than the baseline heat transfer performance Pf1b.

[0106] The same applies when the fin configuration occupancy β is 30%, 32%, 39%, and 50%, respectively. Additionally, in... Figure 19 In these cases, the flow path length clearance ratio α of their maximum heat transfer performance Pf, Pf2max, Pf3max, Pf4max, and Pf5max, is represented by specified values ​​α20, α30, α40, and α50, respectively. Furthermore, for heat transfer performance Pf that ensures it is equivalent to the reference heat transfer performance Pf2b, Pf3b, Pf4b, and Pf5b, the flow path length clearance ratio α is represented by threshold values ​​α21, α31, α41, and α51, respectively.

[0107] exist Figure 20 middle, Figure 19 The relationships between the values ​​of the clearance ratio α in the flow path length direction (α11, α21, α31, α41, α51) and their corresponding fin configuration direction occupancy ratio β ("26%", "30%", "32%", "39%", "0%)) are represented by points γ11, γ21, γ31, γ41, γ51. Approximate formulas are derived using these points γ11, γ21, γ31, γ41, γ51, resulting in the following formula f1. Furthermore, in Figure 20 In the diagram, the solid line m11 represents the curve corresponding to the formula f1.

[0108] α = -0.306·β 2+0.4324·β+0.1298(f1)

[0109] consider Figure 19 The relationship between the flow path length direction clearance ratio α and the heat transfer performance Pf is shown. If the flow path length direction clearance ratio α and the fin configuration direction occupancy ratio β are set in the region that satisfies the following formula f2, heat transfer performance that is higher than the reference heat transfer performance can be obtained. In other words, heat transfer performance that is equal to or higher than that obtained without forming a connecting path 305 can be obtained.

[0110] α≤-0.306·β 2 +0.4324·β+0.1298(f2)

[0111] In conclusion, if Figure 18 If “d1”, “Lp”, “d2”, and “Wp” satisfy the following equation f3, then the heat transfer performance can be obtained with the same or higher performance without forming a connecting path 305.

[0112] (Lp-d1) / Lp≤-0.306(d2 / Wp) 2 +0.4324(d2 / Wp)+0.1298(f3)

[0113] In addition, Figure 20 middle, Figure 19 The relationships between the values ​​α10, α20, α30, α40, and α50 in the flow path length direction and the corresponding fin configuration direction occupancy values ​​β, "26%", "30%", "32%", "39%", and "50%", are represented by points γ10, γ20, γ30, γ40, and γ50. Approximate formulas are derived using these points γ10, γ20, γ30, γ40, and γ50, resulting in the following formula f4. Furthermore, in Figure 20 In the diagram, a single-dot dashed line m12 represents the curve corresponding to equation f4.

[0114] α = -0.0897·β 2 +0.1268·β+0.0381(f4)

[0115] Therefore, if Figure 18 If the given "d1", "Lp", "d2", and "Wp" satisfy the following equation f5, then the heat transfer performance of the heat exchanger 10 can be maximized.

[0116] (Lp-d1) / Lp=-0.0897(d2 / Wp) 2 +0.1268(d2 / Wp)+0.0381(f5)

[0117] In addition, in the use of Figure 20 The baseline heat transfer performance obtained by using the solid line m11 is set as "Pfb", and will be determined by using... Figure 20 When the maximum heat transfer performance obtained by the single-dot dashed line m12 is set as "Pfmax", if Figure 18 If the given values ​​“d1”, “Lp”, “d2”, and “Wp” satisfy the following equation f6, then the heat transfer performance of “(Pfmax-Pfb) / 2” can be obtained. Furthermore, in Figure 20 In the diagram, the double-dotted line m13 represents the relation f6.

[0118] (Lp-d1) / Lp≤-0.2097(d2 / Wp) 2 +0.2963(d2 / Wp)+0.089(f6)

[0119] The heat exchanger 10 of this embodiment described above can further achieve the functions and effects shown in (11) and (12) below.

[0120] (11) will Figure 18 The “d1”, “Lp”, “d2”, and “Wp” shown are set to satisfy the above equation f3. As a result, heat transfer performance equal to or higher than that in the case where the connecting path 305 is not formed can be obtained.

[0121] (12) will Figure 18 The values ​​“d1”, “Lp”, “d2”, and “Wp” shown are set to satisfy the above equation f5. As a result, the heat transfer performance of the heat exchanger 10 can be maximized.

[0122] (Modified Example)

[0123] Next, a modified example of the heat exchanger 10 of the fifth embodiment will be described.

[0124] Although the shape of the fin body 310 can be arbitrarily changed, it is effective for the fin body 310 to have a shape in which the length of its flow path direction Y is longer than the length of its fin arrangement direction X in order to facilitate the formation of a meandering flow of the heat medium. As an example, one can consider the following... Figure 21 As shown, the fin body 310 is formed into an elongated oval shape, or as... Figure 22 The shape shown is rhomboid. When the fin body 310 is formed into an oblong or rhomboid shape, the following effects and functions can be obtained.

[0125] Assuming Figure 21 As shown in (A), the cross-sectional shape of the fin body 310, which is orthogonal to the fin height direction Z, is formed as an elongated circle, and when the fin 30 does not form a connecting path 305, it is similar to the use of Figure 2Compared to the case of elliptical fins as shown, the heat medium is less likely to flow in a meandering pattern. Therefore, when the fin body 310 is formed as an elongated oval shape, as... Figure 21 As shown in (B), forming a connecting path 305 in the fin 30 becomes particularly effective. With this structure, the flow of the heat medium through the connecting path 305 facilitates a meandering flow, thus significantly improving fin efficiency. Therefore, when using the elongated oval fin body 310, the flow pattern of the heat medium with and without the connecting path 305 is significantly different; thus, a substantial improvement in fin efficiency can be expected by forming the connecting path 305.

[0126] In addition, such as Figure 22 As shown in (A), the cross-sectional shape of the fin body 310, which is orthogonal to the fin height direction Z, can also be rhomboid. For example... Figure 22 As shown in (A), when the fin body 310 is formed into a rhombus shape and the fin 30 does not form a connecting path 305, it is similar to the use of Figure 2 Compared to the elliptical fin body shown, the heat transfer medium is more easily detached from the fin body 310, resulting in heat transfer medium precipitation. This is the main reason for reducing the effective heat transfer area of ​​the fin 30. In contrast, as shown... Figure 22 As shown in (B), if a connecting passage 305 is formed in the fin 30, the flow of the heat medium through the connecting passage 305 makes it difficult for the heat medium to peel off from the fin body 310, thus preventing the precipitation of the heat medium. Therefore, the effective heat transfer area of ​​the fin 30 can be effectively increased, thereby improving the fin efficiency.

[0127] Furthermore, when the fin body 310 is formed as an elongated oval or a rhomboid shape, the relationship between the flow path length direction clearance ratio α and the fin configuration direction occupancy ratio β, which can achieve heat transfer performance equivalent to that obtained when the connecting passage 305 is formed, is considered to be, for example... Figure 20 The relationship is shown by the dashed line m14.

[0128] <Other Implementation Methods>

[0129] Alternatively, the above-described implementation method can also be carried out in the following ways.

[0130] exist Figure 5 As shown, in a heat exchanger 10 with fins 30 having a connecting path 305, it is also possible to use... Figure 4The structure shown forms a gap between the other end 32 of the fin 30 and the inner surface of the bottom wall portion 220 of the second base 22. According to this structure, the heat medium can flow between each narrow flow path W11 through the gap formed between the other end 32 of the fin 30 and the inner surface of the bottom wall portion 220 of the second base 22. The width of the connecting passage 305 formed in the plurality of fins 30 fluctuates, for example, due to the shape tolerances of the fins 30. This is the main reason for the fluctuation in pressure loss of each narrow flow path W11. In this respect, if the heat medium can flow between each narrow flow path W11 through the gap formed between the other end 32 of the fin 30 and the inner surface of the bottom wall portion 220 of the second base 22, then even if fluctuations in pressure loss occur in each narrow flow path W11, the fluctuations in pressure loss can be mitigated by allowing the heat medium to flow between each narrow flow path W11. Therefore, the robustness of pressure loss in each narrow flow path W11 can be improved.

[0131] The shape of the fin 30 in each embodiment can be arbitrarily changed as long as it is a shape in which thick-walled portions 301 and thin-walled portions 302 are alternately formed in the flow path length direction Y. In addition, the thick-walled portions 301 and thin-walled portions 302 can be formed in the entire flow path length direction Y of the fin 30, or formed in a part of the flow path length direction Y of the fin 30.

[0132] The flow path length direction Y is not limited to a direction orthogonal to the fin configuration direction X, as long as it is a direction that intersects with the fin configuration direction X.

[0133] In each embodiment, the fin 30 has a thick-walled portion 301 and a thin-walled portion 302 along the length direction Y of the flow path, and is constructed by a continuous structure of the curved outer surfaces of the thick-walled portion 301 and the thin-walled portion 302. Alternatively, the fin 30 may have an intermediate connecting portion between the thick-walled portion 301 and the thin-walled portion 302, which has a shape that directly connects the curved outer surfaces of the thick-walled portion 301 and the thin-walled portion 302.

[0134] The surfaces 303 and 304 of the fin 30 are not only curved surfaces, but can also be composed of only planes, or a combination of planes and curved surfaces. That is, the surfaces 303 and 304 of the fin 30 can be formed as non-curved surfaces, or they can be formed by a combination of curved and non-curved surfaces.

[0135] In the fins 30 of each embodiment, the portion with a relatively thicker plate thickness compared to the average plate thickness is defined as a thick-walled portion 301. However, the definition of thick-walled portion 301 is not limited to this; any portion with a relatively thicker plate thickness compared to other portions can also be defined as thick-walled portion 301. The same applies to thin-walled portion 302. In short, it is sufficient for the fins 30 to alternately have thick-walled portions 301 with a thicker plate thickness and thin-walled portions 302 with a thinner plate thickness along the flow path length direction Y.

[0136] In such Figure 18 In the fin body 310 of the fifth embodiment shown, for example, it is also possible to apply, for example Figure 12 The structure shown has one end of the sidewall shaped like an R. Figure 13 The structure shown is such that the sidewall portion at one end is formed into a conical shape. With these structures, the width of the fin body 310 varies along the fin height direction Z. In this case, the entire fin body 310 along the fin height direction Z may satisfy the above-described formula f3, or only a portion of the fin body 310 along the fin height direction Z may satisfy the above-described formula f3. In the former case, the entire fin body 310 can achieve the effects and benefits described in (11) above, while in the latter case, only a portion of the fin body 310 can achieve the effects and benefits described in (11) above. The same applies to formulas f5 and f6 above.

[0137] In the heat exchanger 10 of the fifth embodiment, fins satisfying formula f3 and fins not satisfying formula f3 can be mixed together. In this case, the effects and functions shown in (11) above can be obtained at the fins satisfying formula f3, thus improving fin efficiency compared to conventional heat exchangers. The same applies to formulas f5 and f6 above.

[0138] The heat exchanger 10 in each embodiment is not limited to heat exchange with semiconductor element 40, but can exchange heat with any electronic component.

[0139] This invention is not limited to the specific examples described above. Any technical solution derived by those skilled in the art through appropriate design modifications to the specific examples, as long as it possesses the features of this invention, is included within the scope of this invention. The elements, configurations, conditions, shapes, etc., of the various examples described above are not limited to the exemplified content and can be appropriately modified. The elements of the various examples described above can be appropriately combined and modified as long as they do not create technical contradictions.

Claims

1. A heat exchanger for exchanging heat between a heat medium flowing through a heat medium path and electronic components, characterized in that, The device has multiple fins disposed in the heat medium flow path. By arranging the multiple fins at intervals in a predetermined fin configuration direction, the heat medium flow path is divided into multiple narrow flow paths. The heat medium flow path is formed to extend along its length, which intersects the fin configuration direction. The fins are formed by alternating thick-walled and thin-walled portions along the length of the flow path, wherein the thick-walled portions are the parts with a thicker plate, and the thin-walled portions are the parts with a thinner plate. In two adjacent fins, the thick-walled portion of one fin and the thin-walled portion of the other fin are arranged opposite each other in the fin arrangement direction, and the thin-walled portion of one fin and the thick-walled portion of the other fin are arranged opposite each other in the fin arrangement direction. A connecting path is formed in the fin, which connects a narrow flow path arranged along one surface of the fin and a narrow flow path arranged along the other surface of the fin. In the fin, a plurality of connecting passages are formed at predetermined intervals along the length of the flow path. The fins have multiple fin bodies disposed between the multiple connecting paths. The fin body has a shape in which the length in the flow path direction is longer than the length in the fin arrangement direction. When the width of the fin body in the flow path length direction is set to "d1", the distance between the centers of adjacent fin bodies separated by the connecting path in the flow path length direction is set to "Lp", the width of the fin body in the fin arrangement direction is set to "d2", and twice the length of the fin spacing, which serves as the arrangement interval of multiple fins in the fin arrangement direction, is set to "Wp",... The fin body is formed to satisfy the following formula: (Lp-d1) / Lp≤-0.306(d2 / Wp) 2 +0.4324(d2 / Wp)+0.1298。 2. The heat exchanger according to claim 1, characterized in that, When the thickest part of the thick-walled section is taken as the thickest wall section, and the thinnest part of the thin-walled section is taken as the thinnest wall section, In the fin, a plurality of the thickest wall portions are formed at predetermined intervals along the flow path length direction, and a plurality of the thinnest wall portions are formed at the same predetermined intervals along the flow path length direction. The thickest wall portion of one fin and the thickest wall portion of the other fin are arranged to be offset by half the predetermined distance in the flow path length direction. The thinnest wall portion of one fin and the thinnest wall portion of the other fin are arranged offset from each other by half the predetermined distance in the flow path length direction.

3. The heat exchanger according to claim 1, characterized in that, The surface of the fin facing the narrow flow path is formed as a curved surface.

4. The heat exchanger according to claim 1, characterized in that, The surface of the fin facing the narrow flow path is formed as a non-curved surface.

5. The heat exchanger according to any one of claims 1 to 4, characterized in that, The fins arranged adjacent to each other in the fin configuration direction are configured to overlap in the fin configuration direction.

6. The heat exchanger according to any one of claims 1 to 4, characterized in that, When the direction orthogonal to both the flow path length direction and the fin configuration direction is taken as the fin height direction... The heat exchanger also includes a base, the electronic components are disposed on one surface of the base, and one end of each of the plurality of fins in the fin height direction is fixed to the other surface of the base.

7. The heat exchanger according to claim 6, characterized in that, A recessed insertion groove for inserting the electronic component is formed on one surface of the base.

8. The heat exchanger according to claim 6, characterized in that, The sidewall of one end of the fin, which is fixed to the other surface of the base, is formed in a conical shape.

9. The heat exchanger according to claim 6, characterized in that, The sidewall portion of one end of the fin, which is fixed to the other surface of the base, is formed in an R shape.

10. The heat exchanger according to any one of claims 1 to 4, characterized in that, When the direction orthogonal to both the flow path length direction and the fin configuration direction is taken as the fin height direction, and the thinnest part of the thin-walled section is taken as the thinnest wall section,... The portion of the fin disposed between adjacent thinnest wall portions has a shape symmetrical about an axis passing through the center of the portion and parallel to the height direction of the fin.

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