heat exchanger

Abstract

To provide a heat exchanger having excellent heat transfer performance, in the heat exchanger in which a casing 1 and a top plate 3 to which a core is connected, are detachably mounted in a separate structure.SOLUTION: A core mounted on a top plate 3 is composed of a corrugated fin 4 having planar surfaces 4d arranged in parallel and top portions 4a, 4b connecting the planar surfaces 4d into a waveform, one top plate 4a of the corrugated fin 4 and one surface 3a of the top plate 3 are joined, a clearance 15 is formed between the other top portion 4b of the corrugated fin 4 and a bottom portion 2a of a recessed portion 2 of the casing 1, at least one or more patterns 5 of at least one of recessed portion and projecting portion are formed on a ridge line 4c of the other top portion 4b, and an interval of the clearance 15 between the bottom portion 2a and the ridge line 4c of the other top portion 4b is defined to be changed in a main flow direction of a fluid 10.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a heat exchanger that transfers heat between a heat exchange object and a fluid, and in particular to a heat sink that cools an object to be cooled such as a semiconductor device. [Background technology]

[0002] FIG. 9 shows a heat exchanger for cooling a target object such as a semiconductor element. This heat exchanger has a casing 1 with a dish-shaped recess 2 and a flat top plate 3 that closes the opening of the recess 2. As shown in Fig. 9(A), a plurality of pin fins 24 that form a core are joined to one surface 3a of the top plate 3. A plurality of heat exchange objects 20, such as semiconductors, are joined to the other surface 3b of the top plate 3 (Fig. 9(B)). This core is housed in a recess 2 of a casing 1, and heat exchange is carried out between a fluid 10 such as a refrigerant introduced into the recess 2 and an object 20 to be heat exchanged via the core. In this heat exchanger, the casing 1 and the core attached to the top plate 3 are separate structures, and the top plate 3 and the casing 1 are attached detachably. Summary of the Invention [Problem to be solved by the invention]

[0003] As shown in Figure 9(B), a gap 15 is formed between the tip of each pin fin 24 and the bottom 2a of the recess 2, and a portion of the fluid 10 is short-circuited through this gap 15, resulting in a disadvantage of reduced heat transfer performance.

[0004] Therefore, the object of the present invention is to provide a heat exchanger with good heat transfer performance in which the casing 1 and the top plate 3 to which the core is connected are separate structures that can be attached and detached freely. [Means for solving the problem]

[0005] The present invention as set forth in claim 1 comprises a casing 1 having a dish-shaped recess 2 with a bottom 2a formed therein; a flat top plate 3 that closes the opening of the recess 2 of the casing 1; a core joined to one surface 3a of the top plate 3; Equipped with In a heat exchanger in which the core is housed in the recess 2 and heat exchange is performed between a fluid 10 introduced into the recess 2 and an object 20 to be heat exchanged through the core 4, The core is made up of corrugated fins 4 having parallel flat surfaces 4d and peaks 4a, 4b connecting the flat surfaces 4d in a wave shape, One top portion 4a of the corrugated fin 4 is joined to one surface 3a of the top plate 3, A gap 15 is formed between the other top 4b of the corrugated fin 4 and the bottom 2a. The other apex 4b has at least one or more patterns 5 of at least one of recesses and protrusions formed on its ridge 4c, This is a heat exchanger in which the width of the gap 15 between the bottom portion 2a and the ridge line 4c of the other top portion 4b changes in the main flow direction of the fluid 10.

[0006] The present invention according to claim 2 provides the heat exchanger according to claim 1, The other top portion 4b has at least one pattern 5 of at least one of recesses and protrusions formed on the back side thereof, This is a heat exchanger in which the distance between one surface 3a of the top plate 3 and the surface behind the ridge line 4c of the other top portion 4b changes in the main flow direction of the fluid 10.

[0007] The present invention according to claim 3 provides the heat exchanger according to claim 2, In this heat exchanger, an inclined pattern 6 of at least one of recesses and protrusions inclined with respect to the direction of fluid flow is formed on the plane 4d. [Effects of the Invention]

[0008] The invention described in claim 1 is a heat exchanger in which the core of the heat exchanger consists of a corrugated fin 4 having parallel flat surfaces 4d and peaks 4a, 4b connecting the flat surfaces 4d in a wave-like manner, one peak 4a of the corrugated fin 4 is joined to one surface 3a of the top plate 3, a gap 15 is formed between the other peak 4b of the corrugated fin 4 and the bottom 2a of the recess 2 of the casing 1, at least one or more patterns 5 of at least one of recesses or protrusions are formed on the ridge 4c of the other peak 4b, and the spacing of the gap 15 between the bottom 2a and the ridge 4c of the other peak 4b changes in the main flow direction of the fluid 10. With this configuration, the fluid 10 flowing through the gaps 15 formed between the casing 1 and the other crest 4b of the corrugated fin 4 is deflected against the main flow direction of the fluid 10 by the pattern 5 of at least one of the recesses and protrusions, increasing the fluid flow resistance in the gaps 15 and reducing short-circuiting of the fluid 10. As a result, the amount of fluid 10 flowing through the fluid flow paths of the corrugated fins 4 increases, improving the heat transfer performance of the heat exchanger.

[0009] The invention described in claim 2 is a heat exchanger in which, in the heat exchanger described in claim 1, at least one pattern 5 of at least one of a concave portion or a convex portion is formed on the back side of the other top 4b, and the distance between one surface 3a of the top plate 3 and the back surface of the ridge 4c portion of the other top 4b changes in the main flow direction of the fluid 10. With this configuration, in the fluid flow path surrounded by one surface 3a of the top plate 3 and the corrugated fins 4, the fluid 10 flowing near the back side of the other peak 4b is deflected from the mainstream flow of the fluid 10 by the pattern 5 of at least one of the concave and convex portions, increasing the flow resistance of the fluid 10 in the area of ​​the pattern 5 and reducing the flow rate of the fluid 10. Therefore, the flow rate of the fluid 10 on the top plate 3 side, where heat transfer efficiency is high, increases in the fluid flow path, improving the heat transfer performance of the heat exchanger.

[0010] The invention described in claim 3 is a heat exchanger described in claim 2, in which an inclined pattern 6 of at least one of recesses or protrusions inclined with respect to the direction of fluid flow is formed on the plane 4d. This configuration reduces the amount of heat flow near the top 4b, which is far from the top plate 3 and has poor heat transfer efficiency, and increases the amount of heat flow in the area where the inclined pattern 6, which has a high heat transfer coefficient, thereby improving the heat transfer performance of the heat exchanger. [Brief explanation of the drawings]

[0011] [Figure 1] 1A and 1B are perspective views showing the structure of a heat exchanger of the present invention, in which FIG. 1A is a perspective view of a corrugated fin 4 used in the core, and FIG. 1B is an exploded perspective view of the heat exchanger. [Figure 2] FIG. [Figure 3] 3A and 3B are cross-sectional views of the heat exchanger, where FIG. 3A is a cross-sectional view taken along the line III-III in FIG. 2, and FIG. 3B is an enlarged view of part B in FIG. 3A. [Figure 4] 4 is a cross-sectional view of a main part of the heat exchanger taken along the line IV-IV in FIG. 3(B). [Figure 5] 4 is a longitudinal cross-sectional view of a main portion illustrating the effect of a corrugated fin 4 used in a heat exchanger of the present invention. FIG. [Figure 6] 4 is a cross-sectional view illustrating the effect of a corrugated fin 4 used in the heat exchanger of the present invention. FIG. [Figure 7] FIG. 4 is a diagram showing a second embodiment of the corrugated fin 4 used in the heat exchanger of the present invention. [Figure 8] FIG. 10 is an explanatory diagram showing the effect of the second embodiment. [Figure 9] FIG. 1A is a perspective view showing the structure of a core of a conventional heat exchanger, and FIG. 1B is an explanatory diagram showing the problems of the conventional heat exchanger. DETAILED DESCRIPTION OF THE INVENTION

[0012] Next, an embodiment of the present invention will be described with reference to the drawings. Fig. 1 is a perspective view showing the structure of a heat exchanger of the present invention, Fig. 1(A) is a perspective view of a corrugated fin 4 used in the core, and Fig. 1(B) is an exploded perspective view of the heat exchanger. Fig. 2 is an assembled perspective view of the heat exchanger, and Fig. 3 is a cross-sectional view of the heat exchanger, Fig. 3(A) is a cross-sectional view taken along the arrows III-III in Fig. 2, and Fig. 3(B) is an enlarged view of part B in Fig. 3(A). Fig. 4 is a cross-sectional view of a main part of the heat exchanger, taken along the arrows IV-IV in Fig. 3(B).

[0013] This heat exchanger is composed of a casing 1, a top plate 3, and a core. As shown in Figure 1(B), the casing 1 has a rectangular housing with a dish-shaped recess 2 formed in the center of the top surface, recessed relative to a peripheral edge 1a, and a seal groove 1b formed on the periphery. A fastening hole 1c is provided on the outer periphery of the seal groove 1b. A seal ring 21 is disposed in the seal groove 1b. In this example, the recess 2 is rectangular, having a bottom 2a and a side 2b.

[0014] The top plate 3 is formed in a flat plate shape and has a size that closes the opening of the recess 2 of the casing 1. The top plate 3 has a core joined to one surface 3a thereof. On the other surface 3b of the top plate 3, as shown in FIG. 2, for example, a heat-exchanging object 20, such as a semiconductor element, is placed. The core is stored in the recess 2 of the casing 1, and the top plate 3 closes the opening of the recess 2 of the casing 1 so that the fastening holes 3c provided on the outer periphery of the top plate 3 are aligned with the fastening holes 1c formed on the peripheral portion 1a of the casing 1, and the top plate 3 is removably attached to the casing 1 by fasteners 23, as shown in Figure 2.

[0015] In this example, a pair of pipes 22 are provided on the outer periphery of the casing 1, one pipe 22 communicating with the inlet-side header section 11 of the recessed section 2, and the other pipe 22 communicating with the outlet-side header section 12 of the recessed section 2. A fluid 10 such as a refrigerant flows in through one pipe 22 and is guided into the inlet-side header section 11 of the recessed section 2. The core is disposed between the inlet header section 11 and the outlet header section 12 . Heat generated from a heat exchange object 20 such as a heat generating element is cooled by the fluid 10 flowing into the core, and heat exchange takes place between the heat exchange object 20 and the fluid 10 .

[0016] As shown in FIG. 1(A), the core of this heat exchanger is made up of corrugated fins 4 each having parallel flat surfaces 4d and a plurality of peaks 4a, 4b connecting the flat surfaces 4d in a wave-like manner. 3(A) and 3(B), each apex 4a on one side of the corrugated fin 4 is joined to one surface 3a of the top plate 3. The ridges 4c of each apex 4a, 4b of the corrugated fin 4 are arranged along the flow direction of the fluid 10. Here, one surface of the corrugated fin 4 that is joined to the top plate 3 is referred to as the back surface of the corrugated fin 4. The surface of the corrugated fin 4 opposite to the back surface is referred to as the front surface. As shown in FIG. 4, a first fluid flow path 13 is formed in the area surrounded by one surface 3a of the top plate 3 and the back surface of the corrugated fin 4. Adjacent to each first fluid flow path 13, a second fluid flow path 14 is formed in a region sandwiched between the front surfaces of the corrugated fins 4.

[0017] In order to avoid interference between the corrugated fins 4 and the casing 1 when the top plate 3 and the casing 1 are assembled, a gap 15 exists between the corrugated fins 4 and the bottom 2a of the recess 2 of the casing 1, as shown in Figures 3 and 4.

[0018] To solve the problem of short-circuiting of the fluid 10 through this gap 15, a pattern 5 is formed on each of the other apexes 4b of the corrugated fin 4 used in the present invention along the ridge line 4c of the apex 4b, as shown in Fig. 1(A). In this example, as shown in Fig. 3(B), a pattern 5 of multiple depressions is formed on the apex 4b along the ridge line 4c, with the ridge line 4c recessed toward the top plate 3. 3(B), the distance of the gap 15 between the bottom 2a of the recess 2 of the casing 1 and the front surface of the ridge 4c of the other top 4b of the corrugated fin 4 varies in the main flow direction of the fluid 10. In this example, the height T1 of the recessed portion is formed higher than the height T2 of the non-recessed portion.

[0019] FIG. 5 is a longitudinal cross-sectional view of a main part showing the effect of the corrugated fin 4 used in the heat exchanger of the present invention, and FIG. 6 is a cross-sectional view of a main part thereof. With the corrugated fin 4 having the above-described structure, the fluid 10 flowing through the gap 15 formed between the casing 1 and the other crest 4b of the corrugated fin 4 is deflected against the main flow direction of the fluid 10 by the pattern of recesses 5 that continuously appear along the ridge line 4c of the crest 4b, as shown in Fig. 5. As a result, the flow resistance of the fluid 10 increases throughout the entire gap 15 located directly below the core, forming a first flow resistance increased section 16, as shown in Fig. 6. This reduces the short-circuiting of the fluid 10 through the gap 15. 6, the fluid 10 is more easily guided into the second fluid flow passages 14 of the corrugated fin 4 than into the first increased flow resistance portions 16. As a result, short-circuiting of the fluid 10 into the gaps 15 is suppressed, and the amount of fluid 10 flowing through the second fluid flow passages 14 of the corrugated fin 4 increases, improving the heat transfer performance of the heat exchanger.

[0020] In this example, a pattern 5 of convex portions that protrude toward the top plate 3 and appear continuously along the ridge line 4c of the top 4b is formed on the back surface of the top 4b of the corrugated fin 4. The portions adjacent to the convex portions are recessed portions that are recessed relative to the convex portions. The distance between one surface 3a of the top plate 3 and the rear surface of the ridge line 4c of the other top portion 4b of the corrugated fin 4 varies in the main flow direction of the fluid 10. In this example, the height T3 of the convex portion is formed to be lower than the height T4 of the concave portion (FIG. 3(B)).

[0021] On the side of the first fluid flow path 13 surrounded by one surface 3a of the top plate 3 and the back surface of the corrugated fin 4, as shown in Fig. 5, the fluid 10 flowing near the back surface of the other peak 4b is deflected from the mainstream flow of the fluid 10 by the pattern 5 of the recesses, increasing the flow resistance of the fluid 10 in the area of ​​the pattern 5 and forming a second flow resistance increase area 17 (Fig. 6) there. Then, the flow rate of the fluid 10 decreases in the area near the pattern 5 on the back surface of the other peak 4b (Fig. 5). 6, the fluid 10 flowing through the first fluid flow path 13 is guided toward the top plate 3 side so as to avoid the second flow resistance increase section 17, and the amount of fluid 10 flowing on the top plate 3 side, where heat transfer efficiency is high, increases. As a result, the heat transfer performance of the heat exchanger can be improved.

[0022] FIG. 7 is a diagram showing a second embodiment of the corrugated fin 4 used in the heat exchanger of the present invention, and FIG. 8 is an explanatory diagram showing the effect of this embodiment. In this embodiment, as shown in Figures 7(A) and 7(B), in order to improve the heat transfer coefficient, an inclined pattern 6 consisting of a series of recesses and protrusions inclined relative to the direction of fluid flow is formed on the flat surface 4d of the first embodiment. The inclined pattern 6 is formed so as to connect the edge of one apex 4a to the edge of the other apex 4b. In this example, as shown in FIG. 7(C), the inclined patterns 6 are formed on each of a pair of flat surfaces 4d of the corrugated fin 4, and the inclination directions thereof are in the same direction.

[0023] In this case, a portion of the fluid 10 flowing inside the corrugated fin 4 (the area surrounded by the top plate 3 and the back surface of the corrugated fin 4) flows obliquely toward the back surface of the other top 4b along the inclined pattern 6 formed on the flat surface 4d of the corrugated fin 4, as shown in Figure 8, but is guided toward the top plate 3 so as to avoid the second increased flow resistance portion 17. As a result of this effect, the amount of air flowing near the top 4b, which is far from the top plate 3 and has poor heat transfer efficiency, decreases, while the amount of air flowing in the part where the inclined pattern 6, which has a high heat transfer coefficient, is formed increases, thereby improving the heat transfer performance of the heat exchanger.

[0024] The pattern 5 on the top 4b of the corrugated fin 4 is preferably formed of continuous recesses or protrusions as in the above-described embodiment, but the function can be achieved as long as one or more recesses or protrusions are formed. The direction of the concave-convex pattern 5 may be opposite to that of the present embodiment shown in the drawings. The means for forming the concave-convex pattern 5 is preferably to form it integrally with the corrugated fin 4 by roller molding, but the pattern 5 may also be formed by attaching a separate member. [Explanation of symbols]

[0025] 1 casing 1a Periphery 1b Seal groove 1c fastening hole 2 recesses 2a bottom 2b Side 3. Top plate 3a One side 3b The other side 3c Fastening hole

[0026] 4 Corrugated fins 4a Top 4b Top 4c Ridgeline 4d plane 5 Pattern 6 Slope Pattern

[0027] 10 fluid 11 Inlet header section 12 Outlet header section 13 First fluid flow path 14 Second fluid flow path 15 Gap 16 First flow resistance increase section 17 Second flow resistance increase section

[0028] 20 Heat exchange object 21 Seal ring 22 Pipe 23 Fasteners 24 Pinfin T1 Height of the recess T2 Height of undepressed part T3 Height of the convex part T4 Recess height

Claims

[Claim 1] a casing (1) having a dish-shaped recess (2) with a bottom (2a) formed therein; a flat top plate (3) that closes the opening of the recess (2) of the casing (1); a core joined to one surface (3a) of the top plate (3); Equipped with In a heat exchanger, the core is housed in a recess (2), and heat exchange is performed between a fluid (10) introduced into the recess (2) and an object (20) to be heat exchanged through the core, The core is made of a corrugated fin (4) having parallel flat surfaces (4d) and peaks (4a) and (4b) connecting the flat surfaces (4d) in a wave shape. One top portion (4a) of the corrugated fin (4) is joined to one surface (3a) of the top plate (3), A gap (15) is formed between the other top (4b) and the bottom (2a) of the corrugated fin (4), The other top portion (4b) has at least one or more patterns (5) of at least one of recesses and protrusions formed on its ridge line (4c), The gap (15) between the bottom (2a) and the ridge (4c) of the other top (4b) changes in the main flow direction of the fluid (10), The other top portion (4b) has at least one pattern (5) of at least one of recesses or protrusions formed on its back surface, The distance between one surface (3a) of the top plate (3) and the back surface of the ridge line (4c) of the other top portion (4b) changes in the main flow direction of the fluid (10), The plane (4d) has an inclined pattern (6) of at least one of recesses and protrusions inclined with respect to the direction of fluid flow, The inclined pattern (6) is formed on each of a pair of flat surfaces (4d) of the corrugated fin (4), and the inclination direction is the same and gradually approaches from one apex (4a) of the corrugated fin (4) to the other apex (4b) as it moves from the upstream side to the downstream side of the fluid flow.

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