CN215956923U - Radiator and heat exchange device - Google Patents

Abstract

The utility model provides a radiator and a heat exchange device. The heat sink has a plate-like base body and a fin group including a plurality of fins protruding from the base body. The base and the fin sets are respective different portions of a single component. At least a portion of the plurality of fins are arranged in a 1 st direction and a 2 nd direction intersecting the 1 st direction. The fin has a 1 st side. The 1 st side surface is a plane extending in the 1 st direction and faces a predetermined side of the upper surface of the base. The 1 st angle is a smaller angle between the 1 st direction of the 1 st side surface extension and the side when viewed from the normal direction of the upper surface of the base. The 1 st angle of each fin is the same.

Description

Radiator and heat exchange device

Technical Field

The present invention relates to a radiator and a heat exchanger.

Background

Conventionally, there is known a heat sink in which a plurality of rows of tongue-shaped fins are provided on an upper surface of a heat dissipation substrate. The tongue-shaped fins are provided in plurality at intervals in the front-rear direction. The rows of tongue-shaped fins are formed by cutting fin-forming portions of the heat sink material. (refer to Japanese laid-open patent publication No. 2001-102782.)

However, when the heat sink described above is used in a heat exchange device that cools a heat generating component by flowing a refrigerant through an internal flow path, the refrigerant flowing in the front-rear direction of the heat sink hits the tongue-shaped fins and is subjected to pressure loss. Therefore, the flow velocity of the refrigerant decreases, and the heat radiation efficiency from the fins to the refrigerant may decrease. Therefore, a technique for improving the heat radiation efficiency and further improving the cooling performance of the heat sink is required.

SUMMERY OF THE UTILITY MODEL

The utility model aims to improve the cooling performance of a radiator.

An exemplary heat sink of the present invention has a plate-like base body and fin groups. The fin group includes a plurality of fins protruding from the base. The base and the fin sets are each distinct portions of a component. At least a part of the plurality of fins are arranged in the 1 st direction and the 2 nd direction. The 1 st direction is parallel to the substrate. The 2 nd direction intersects the 1 st direction and is parallel to the base. The fin has a 1 st side. The 1 st side surface is a plane extending in the 1 st direction and faces a predetermined side of the upper surface of the base. The 1 st angle is a smaller angle between the 1 st direction of the 1 st side surface extension and the side when viewed from a normal direction of the upper surface of the base. The 1 st angle of each of the fins is the same.

In the above embodiment, the 1 st angle is 45 degrees.

In the above embodiment, the heat sink forms a part of a fluid flow path extending in a 1 st flow path direction, the 1 st flow path direction obliquely intersects the 1 st direction and is parallel to the base, the plurality of fin groups are arranged in the 1 st flow path direction, and an interval between the fin groups adjacent in the 1 st flow path direction is wider than an interval between the adjacent fins in each of the fin groups.

In the above embodiment, the interval between the adjacent fins in the fin group arranged on the discharge port side of the fluid flow path in the 1 st flow path direction is wider than the interval between the adjacent fins in the fin group arranged on the injection port side of the fluid flow path in the 1 st flow path direction.

In the above embodiment, the fin further includes a 2 nd side surface facing the 1 st channel direction, the 1 st side surface being a flat surface facing the 1 st channel direction, and the 2 nd side surface being one of a flat surface expanding in the 2 nd direction and forming an angle with the 1 st side surface and a curved surface protruding toward an inlet side of the fluid channel in the 1 st channel direction and continuing to the 1 st side surface.

In the above embodiment, the 2 nd side surface is a plane that extends in the 2 nd direction and forms the angle with the 1 st side surface, faces the side, and has a 2 nd angle that is smaller between the side intersecting the 1 st flow path direction and the 2 nd direction in which the 2 nd side surface extends when viewed from a normal direction of the upper surface of the base, and the 2 nd angle of each of the fins is the same as the 1 st angle.

In the above embodiment, the fin group includes a plurality of nearest neighboring fins, each nearest neighboring fin is the fin closest to a predetermined side of the upper surface of the base in at least one of the 1 st direction and the 2 nd direction, and intervals between each nearest neighboring fin and the side are the same.

In the above embodiment, the fin group includes a plurality of nearest fins, each nearest fin is the fin nearest to a predetermined side of the upper surface of the base in at least one of the 1 st direction and the 2 nd direction, intervals between each nearest fin and the side are the same, the 2 nd flow path direction is orthogonal to the 1 st flow path direction and parallel to the base, and the nearest fins are arranged in one of the 1 st flow path direction and the 2 nd flow path direction.

In the above embodiment, when viewed from the 1 st channel direction, the fins closest to each other in the 2 nd channel direction have a gap therebetween.

In the above embodiment, the nearest fins are arranged linearly.

In the above embodiment, the interval between the fins adjacent in the 1 st direction is wider than the width of the fins in the 1 st direction.

An exemplary heat exchange device of the present invention includes: the radiator described above; and a cover body. The cover and the radiator form a fluid flow path for fluid to flow. The fluid is a refrigerant, and flows between the fins of the radiator.

According to the exemplary heat sink and heat exchange device of the present invention, the cooling performance of the heat sink can be improved.

The above and other features, elements, steps, features and advantages of the present invention will be more clearly understood from the following detailed description of preferred embodiments of the present invention with reference to the accompanying drawings.

Drawings

Fig. 1 is an exploded perspective view showing an example of the heat exchanger.

Fig. 2 is a sectional view of the heat exchange device taken along line a-a of fig. 1.

Fig. 3 is a bottom view of the heat exchange device.

Fig. 4 is a partial top view of a heat sink.

Fig. 5 is a partial perspective view of the heat sink.

Fig. 6A is an embodiment of a fin.

Fig. 6B shows a modification of the fin.

Fig. 7 is a flowchart for explaining a method of manufacturing the heat exchange device.

Fig. 8A is a perspective view of the base before processing.

Fig. 8B is a perspective view of a base body formed with a plurality of mesa portions.

Fig. 8C is a partial perspective view of the base with a groove formed in the mesa.

Fig. 8D is a conceptual diagram of a crack raising step of the convex portion.

Fig. 8E is a partial perspective view of the base body in which fins are formed at the projections between the grooves.

Fig. 8F is a perspective view of a base formed with a plurality of fin groups.

Detailed Description

Hereinafter, exemplary embodiments will be described with reference to the drawings.

In the present specification, the term "parallel" in the positional relationship between any one of the orientation, line and plane and the other includes not only a state where both extend so as not to intersect each other at all, but also a state where both extend substantially parallel to each other. The terms "perpendicular" and "orthogonal" include not only a state where they intersect each other at 90 degrees, but also a substantially perpendicular state and a substantially orthogonal state, respectively. That is, "parallel", "perpendicular", and "orthogonal" include a state in which there is angular deviation in the positional relationship therebetween to the extent that does not depart from the gist of the present invention.

In the present specification, a direction from one of the base 1 and the lid 300 to the other is defined as a vertical direction, a direction from the base 1 to the lid 300 is defined as an upward direction, and a direction from the lid 300 to the base 1 is defined as a downward direction. In each component, a surface facing upward is an upper surface, and a surface facing downward is a lower surface. However, these are names used for illustration only, and are not intended to limit the actual positional relationship and direction.

Fig. 1 is an exploded perspective view showing an example of a heat exchanger 100. Fig. 2 is a sectional view of the heat exchange device 100 taken along line a-a of fig. 1. Fig. 3 is a bottom view of the heat exchange device 100.

As shown in fig. 1 and 2, the heat exchange device 100 has a radiator 200 and a cover 300. The cover 300 forms a fluid flow path Pf through which the fluid f flows together with the radiator 200. The heat sink 200 has a plurality of fins 2. In the present embodiment, the cover 300 covers the upper surface of the heat sink 200 on which the plurality of fins 2 are arranged. The lower end of the lid 300 is fixed to the heat sink 200 by means of, for example, screw fastening, welding, adhesion, or the like. The fluid flow path Pf is formed between the radiator 200 and the cover 300.

The heat generating component 400 is in contact with the lower surface of the heat sink 200. Specifically, in the present embodiment, as shown in fig. 3, the heat generating component 400 is arranged so as to be capable of heat transfer on the lower surface of the heat sink 200 via the heat conductive sheet 401. The thermally conductive sheet 401 has high thermal conductivity and high heat resistance. The heat conductive sheet 401 may be, for example, a graphite sheet, a composite resin sheet containing a heat conductive material, or the like. In addition, heat dissipating grease containing a heat conductive material may be used instead of the heat conductive sheet 401. Alternatively, the heat generating component 400 may be in direct contact with the lower surface of the heat sink 200. The heat generating component 400 is, for example, a CPU, a power device, or the like.

The cover 300 has an inlet 301 and an outlet 302. The inlet 301 is disposed on the side of the cover 300 in the 1 st flow path direction Df1 and is connected to the inlet side of the fluid flow path Pf. The discharge port 302 is disposed on the other side of the cover 300 in the 1 st flow path direction Df1, and is connected to the outlet side of the fluid flow path Pf. The inlet 301 and the outlet 302 are connected to a pump (not shown) for circulating the fluid f, a cooler (not shown) for cooling the fluid f, and the like. The fluid f circulates through the fluid flow path Pf, the cooler, and the pump by driving the pump.

The fluid f flows into the fluid flow path Pf from the inlet 301 of the cap 300. In the fluid flow path Pf, the fluid f flows between the fins 2 of the heat sink 200. The fluid f flows out of the fluid flow path Pf from the discharge port 302 of the cap 300. According to the present embodiment, the heat exchange device 100 that allows the fluid f to flow more smoothly through the fluid flow path Pf can be provided.

In the present embodiment, the fluid f is a refrigerant. The fluid f is, for example, an antifreeze such as ethylene glycol or propylene glycol, a liquid such as pure water, or a gas such as air. Accordingly, the heat exchange device 100 can be used as a cold plate to cool the heat generating component 400.

While the fluid f flows in the fluid flow path Pf, the heat transferred from the heat generating component 400 to the heat sink 200 is released to the fluid f, particularly, from the fins 2. The fluid f is cooled by the cooler and then returned to the fluid flow path Pf. By such a heat transfer cycle, the heat exchange device 100 can cool the heat generating component 400 in contact with the heat sink 200.

Next, the structure of the heat sink 200 will be described with reference to fig. 1 to 5. Fig. 4 is a partial top view of the heat sink 200. Fig. 5 is a partial perspective view of the heat sink 200. Fig. 4 is a view of a part of the fin group 210 as viewed from the normal direction of the upper surface of the base 1.

The radiator 200 forms a part of the fluid flow path Pf extending in the 1 st flow path direction Df 1. In the present embodiment, the heat sink 200 is formed using a metal material such as Al or Cu.

The heat sink 200 has a plate-like base 1. The substrate 1 is expanded in the 1 st flow path direction Df1 and the 2 nd flow path direction Df 2. As described above, the 1 st flow path direction Df1 obliquely intersects with the 1 st direction D1 described later and is parallel to the base 1. The 2 nd flow path direction Df2 is orthogonal to the 1 st flow path direction Df1 and parallel to the substrate 1. In the present embodiment, the 2 nd flow path direction Df2 obliquely intersects the 1 st direction D1. The substrate 1 is rectangular when viewed from the normal direction of the upper surface of the substrate 1.

In addition, the heat sink 200 also has fin groups 210. The fin group 210 includes a plurality of fins 2 protruding from the base 1, and the fin group 210 is disposed on the upper surface of the base 1. At least a part of the plurality of fins 2 are arranged in the 1 st direction D1 and the 2 nd direction D2. In addition, the 1 st direction D1 obliquely intersects the 1 st flow path direction Df1 and is parallel to the base 1. The 2 nd direction D2 obliquely intersects the 1 st flow path direction Df1 and intersects the 1 st direction D1 in parallel with the substrate 1. That is, the plurality of fins 2 are two-dimensionally arranged on the upper surface of the base 1. The structure and specific arrangement of the fins 2 will be described later.

A heat generating component 400 is disposed on the lower surface of the base 1 via a heat conductive sheet 401. As shown in fig. 3, the heat generating component 400 is preferably disposed inside the outer edge of the fin group 210 when viewed from the normal direction of the lower surface of the base 1. In this way, the heat transferred from the heat generating component 400 to the base 1 can be released to the fluid f by the fin group 210 directly above the heat generating component 400. That is, since heat can be transferred through a shorter path, the heat generating component 400 can be efficiently cooled.

The base 1 and the fin group 210 are respective different portions of one member. In this way, since the base 1 and the fins 2 can be integrally formed, the thermal resistance from the base 1 to the fins 2 can be greatly reduced. Therefore, the cooling performance of the heat generating component 400 by the heat sink 200 can be improved. In the present embodiment, the fin group 210 is formed by performing a shaving (skive) process on the base 1. The shaving process will be described later.

As shown in fig. 1 and 2, the fin group 210 is preferably provided in plural and arranged in the 1 st flow path direction Df 1. For example, in the present embodiment, the plurality of fin groups 210 includes the 1 st fin group 211, the 2 nd fin group 212, and the 3 rd fin group 213. That is, in the present embodiment, the number of fin groups 210 is 3. They are arranged from the inlet 301 side toward the outlet 302 side in the 1 st flow path direction Df 1. The plurality of fin groups 210 are arranged in the 1 st flow path direction Df1 at intervals Wg. Preferably, the interval Wg between the adjacent fin groups 210 in the 1 st flow path direction Df1 is wider than the interval between the adjacent fins 2 in each fin group 210. For example, the above-described interval Wg is wider in each fin group 210 than the interval Wi1 between the fins 2 adjacent in the 1 st direction D1 and the interval Wi2 between the fins 2 adjacent in the 2 nd direction D2 (see fig. 1, 4, and 5). By arranging the plurality of fin groups 210 in the 1 st flow path direction Df1 with the above-described interval Wg, the pressure loss of the fluid f flowing through the fluid flow path Pf in the 1 st flow path direction Df1 can be reduced as compared with the case where 1 fin group in which all the fins 2 are two-dimensionally arranged is disposed on the upper surface of the base 1. Therefore, the fluid f can be made to flow more smoothly in the fluid flow path Pf. Further, the number of fin groups 210 is not limited to the above example, and may be one or more than 3.

Further, it is preferable that the interval between the adjacent fins 2 in the fin group 210 disposed closer to the discharge port 302 of the fluid flow path Pf in the 1 st flow path direction Df1 is wider than the interval between the adjacent fins 2 in the fin group 210 disposed closer to the injection port 301 of the fluid flow path Pf in the 1 st flow path direction Df 1. More specifically, the interval between the adjacent fins 2 in the 2 nd fin group 212 is wider than the interval between the adjacent fins 2 in the 1 st fin group 211. For example, the interval Wi1 in the 2 nd fin group 212 is wider than the interval Wi1 in the 1 st fin group 211, and the interval Wi2 in the 2 nd fin group 212 is wider than the interval Wi2 in the 1 st fin group 211. In addition, the interval between the adjacent fins 2 in the 3 rd fin group 213 is wider than the interval between the adjacent fins 2 in the 2 nd fin group 212. For example, spacing Wi1 in group 3 of fins 213 is wider than spacing Wi1 in group 2 of fins 212, and spacing Wi2 in group 3 of fins 213 is wider than spacing Wi2 in group 2 of fins 212. That is, the fin group 210 disposed closer to the discharge port 302 side of the fluid flow path Pf in the 1 st flow path direction Df1 has a wider interval between the adjacent fins 2 in the arrangement direction of the fins 2. Therefore, the effect of making the fluid f flow more smoothly can be further improved. However, the above illustration does not exclude a configuration in which the interval between adjacent fins 2 in the fin group 210 arranged closer to the discharge port 302 of the fluid flow path Pf in the 1 st flow path direction Df1 is equal to or smaller than the interval between adjacent fins 2 in the fin group 210 arranged closer to the injection port 301 of the fluid flow path Pf in the 1 st flow path direction Df 1.

Next, the arrangement of the fins 2 in each fin group 210 will be described with reference to fig. 4 and 5. As described above, the plurality of fins 2 are two-dimensionally arranged in the 1 st direction D1 and the 2 nd direction D2. As shown in fig. 4 and 5, the interval Wi1 between adjacent fins 2 in the 1 st direction D1 is preferably wider than the width Wt1 of the fin 2 in the 1 st direction D1. By setting Wi1 > Wt1, the fluid f can smoothly pass between the fins 2 in the 1 st direction D1. That is, since the pressure loss of the fluid f can be reduced, the reduction in the flow velocity of the fluid f can be suppressed. Therefore, the heat dissipation efficiency of the heat sink 200 from the fins 2 to the fluid f can be improved, and thus the cooling performance of the heat sink 200 can be improved. However, the example is not limited to that shown in FIGS. 4 and 5, and Wi1 ≦ Wt1 may be used.

As shown in fig. 4 and 5, it is preferable that the interval Wi2 between the fins 2 adjacent to each other in the 2 nd direction D2 be wider than the width Wt2 of the fin 2 in the 2 nd direction D2. Since the pressure loss of the fluid f can be further reduced by setting Wi2 > Wt2, the reduction in the flow velocity of the fluid f can be further suppressed. Therefore, the cooling performance of the radiator 200 can be further improved. However, the example is not limited to that shown in FIGS. 4 and 5, and Wi2 ≦ Wt2 may be used.

As shown in fig. 4 and 5, the heat sink 200 preferably has a gap Ws between the fins 2 closest to each other in the 2 nd flow path direction Df2 when viewed in the 1 st flow path direction Df 1. In other words, the fins 2 closest to each other in the 2 nd flow path direction Df2 do not overlap each other when viewed from the 1 st flow path direction Df 1. For example, the fins 2 adjacent to each other in the 1 st direction D1 do not overlap each other when viewed from the 1 st flow path direction Df 1. Further, the fins 2 adjacent to each other in the 2 nd direction D2 do not overlap each other when viewed from the 1 st flow path direction Df 1. When the radiator 200 has the above-described gap Ws as viewed in the 1 st flow path direction Df1, the fluid f flowing in the 1 st flow path direction Df1 can flow more smoothly. Therefore, the cooling performance of the radiator 200 can be further improved.

Further preferably, the width of the gap Ws as viewed in the 1 st flow path direction Df1 is wider than at least one of the width Wt1 of the fin 2 in the 1 st direction D1 and the width Wt2 of the fin 2 in the 2 nd direction D2. By making the width of the gap Ws as viewed in the 1 st flow path direction Df1 wider than the width Wt1 and/or the width Wt2 of the fin 2, the fluid f flowing in the 1 st flow path direction Df1 can flow more smoothly. Therefore, the cooling performance of the radiator 200 can be further improved.

However, the present invention is not limited to the examples shown in fig. 4 and 5, and the gaps Ws may not be formed between the fins 2 closest to each other in the 2 nd flow path direction Df2 when viewed from the 1 st flow path direction Df 1. That is, the above illustration does not exclude the structure in which the fins 2 closest to each other in the 2 nd flow path direction Df2 overlap each other when viewed from the 1 st flow path direction Df 1. Alternatively, the width of the gap Ws viewed in the 1 st flow path direction Df1 may be equal to or less than at least one of the width Wt1 and the width Wt 2.

Next, the structure of the fin 2 will be described with reference to fig. 4 to 6B. Fig. 6A is an embodiment of the fin 2. Fig. 6B shows a modification of the fin 2.

The fins 2 have a prismatic shape and protrude from the upper surface of the base 1 in the normal direction. The fin 2 has a 1 st side 21. The 1 st side surface 21 is a plane facing the 1 st flow path direction Df1 and extends in the 1 st direction D1.

The 1 st side surface 21 of the fin 2 faces the predetermined side 10 of the upper surface of the base 1. For example, the side 10 is an edge extending in the 1 st channel direction Df1 or an edge extending in the 2 nd channel direction Df2 on the upper surface of the base 1. The 1 st side 21 forms a 1 st angle φ 1 with respect to the edge 10. The 1 st angle φ 1 is a smaller angle between the side 10 intersecting the 1 st channel direction Df1 and the 1 st direction D1 in which the 1 st side surface 21 spreads, when viewed from the normal direction of the upper surface of the substrate 1. The 1 st angle Φ 1 of each fin 2 is the same. Since the 1 st angle Φ 1 of each fin 2 is the same, the 1 st side 21 of each fin 2 is similarly inclined. Therefore, the flow of the fluid f between the fins 2 in the fin group 210 can be made more uniform. Since the fluid f can be made to flow more smoothly, the heat radiation efficiency from the fins 2 to the fluid f can be improved. Therefore, the cooling performance of the radiator 200 can be improved.

Preferably, the 1 st angle φ 1 is 45 degrees. If the 1 st angle Φ 1 is further decreased, the pressure loss when the fluid f flowing in the 1 st flow path direction Df1 toward the fins 2 hits the 1 st side surface 21 can be reduced, but the heat radiation efficiency at the 1 st side surface 21 is decreased. On the other hand, if the 1 st angle Φ 1 is further increased, the heat radiation efficiency at the 1 st side surface 21 can be improved, but the pressure loss when the fluid f hits the 1 st side surface 21 is increased. By setting the 1 st angle Φ 1 to 45 degrees, the reduction of the pressure loss and the improvement of the heat radiation efficiency at the 1 st side face 21 can be performed in a balanced manner. However, the 1 st angle Φ 1 is not limited to this example, and may be greater than 45 degrees or less than 45 degrees.

Next, the fin 2 further has the 2 nd side surface 22 facing the 1 st flow path direction Df 1. In the present embodiment, as shown in fig. 6A, the 2 nd side surface 22 of the fin 2 is a plane extending in the 2 nd direction D2, and forms an angle with the 1 st side surface 21. The 2 nd side 22 is opposite the edge 10. The smaller angle θ is preferably 90 degrees when viewed from the normal direction of the upper surface of the substrate 1. Here, if the angle θ is further reduced, the pressure loss when the fluid f flowing toward the fin 2 in the 1 st flow path direction Df1 hits the 1 st side surface 21 and the 2 nd side surface 22 can be reduced, but the heat radiation efficiency of the fin 2 is reduced. Conversely, if the angle θ is further increased, the heat radiation efficiency of the fin 2 can be improved, but the pressure loss when the fluid f hits the 1 st side surface 21 and the 2 nd side surface 22 of the fin 2 increases. By setting the angle θ to 90 degrees, the pressure loss of the fluid f and the heat dissipation efficiency of the fins 2 can be uniformly reduced.

It is further preferable that the width Wt1 of the fin 2 in the 1 st direction D1 is the same as the width Wt2 of the fin 2 in the 2 nd direction D2. By setting θ to 90 degrees and Wt1 to Wt2, the fin 2 can be formed in a prismatic shape having a square cross section. Thus, the fluid f contacting the fins 2 can easily flow equally to the 1 st side surface 21 and the 2 nd side surface 22, and thus the fluid f can smoothly flow.

The 2 nd side 22 forms a 2 nd angle φ 2 with respect to the edge 10. The 2 nd angle φ 2 is a smaller angle between the side 10 intersecting the 1 st channel direction Df1 and the 2 nd direction D2 in which the 2 nd side surface 22 spreads, as viewed from the normal direction of the upper surface of the substrate 1. Preferably, the 2 nd angle φ 2 of each fin 2 is the same as the 1 st angle φ 1. The flow of the fluid f toward the 1 st and 2 nd sides 21 and 22 of the fin 2 is easily equally divided in the 1 st and 2 nd directions D1 and D2. Therefore, variation in pressure loss of the fluid f flowing into the fin group 210 can be suppressed, and therefore the cooling performance of the fin group 210 can be improved.

However, the angle θ is not limited to these examples, and may be different from 90 degrees, and the width Wt1 of the fin 2 in the 1 st direction D1 may be different from the width Wt2 in the 2 nd direction D2. In addition, the 1 st angle φ 1 may be different from the 2 nd angle φ 2.

The 2 nd side surface 22 of the fin 2 is not limited to the example of fig. 6A. As shown in fig. 6B, the 2 nd side surface 22 may be a curved surface. The curved surface protrudes toward the inlet 301 side in the 1 st channel direction Df1 and is continuous with the 1 st side surface 21. Preferably, the curved surface is smoothly continuous with the 1 st side 21. That is, the curved surface does not form an angle with the 1 st side 21. Thus, the fluid f can smoothly flow in the portion where the 2 nd side surface 22 and the 1 st side surface 21 are connected.

As described above, the 2 nd side surface 22 of the fin 2 may be one of a flat surface which expands in the 2 nd direction D2 and forms an angle with the 1 st side surface 21 and a curved surface which protrudes toward the inlet 301 side in the 1 st flow path direction Df1 and is continuous with the 1 st side surface 21. When the angle formed by the 1 st side surface 21 and the 2 nd side surface 22 (see fig. 6A) or the curved surface protruding in the 1 st flow path direction Df1 (see fig. 6B) is arranged on the 2 nd side surface 22 of the fin 2 facing the 1 st flow path direction Df1, the flow of the fluid f in the 1 st flow path direction Df1 first hits the angle or the curved surface, and then is divided into one side and the other side in the 2 nd flow path direction Df2 to flow along the side surfaces of the fin 2. Therefore, for example, the fluid f can be made to flow more smoothly than in the case where the fluid f flows in the 1 st flow path direction Df1 and hits the side surface expanding in the 2 nd flow path direction Df2 of the fin 2.

The fins 2 closest to the predetermined side 10 on the upper surface of the base 1 are arranged at the outermost positions in the fin group 210. Hereinafter, such a fin 2 is referred to as a nearest fin 20. The fin group 210 contains a plurality of nearest neighbor fins 20. Each of the nearest fins 20 is the fin 2 nearest to the predetermined side 10 of the upper surface of the base 1 in at least one of the 1 st direction D1 and the 2 nd direction D2. In addition, the nearest fin 20 is disposed at a position away from the edge 10.

In the present embodiment, as shown in fig. 4 and 5, the intervals Wd between the respective nearest neighboring fins 20 and the sides 10 are the same. By the above-described spacing Wd being the same in each of the nearest neighboring fins 20, a plurality of the nearest neighboring fins 20 are arranged along the above-described side 10. Therefore, when manufacturing the heat sink 200, the shape of the base 1 as viewed from the normal direction of the upper surface of the base 1 can be formed into a shape corresponding to the outer shape of the fin group 210.

As shown in fig. 4 and 5, the nearest fins 20 are arranged linearly. Here, "linear" means one-dimensional arrangement. That is, "linear" includes not only an arrangement in which there is strictly no deviation in the direction perpendicular to the arrangement direction, but also an arrangement in which there is a deviation in the direction perpendicular to the arrangement direction to the extent that the gist of the present invention is not deviated. Thus, when manufacturing the heat sink 200, the side 10 along the arrangement of the nearest fins 20 can be formed in a straight line shape in one direction. Therefore, the shape of the heat sink 200 viewed from the normal direction of the upper surface of the base 1 can be further simplified.

The nearest fins 20 are arranged in one of the 1 st flow path direction Df1 and the 2 nd flow path direction Df 2. In other words, a part of the plurality of nearest neighboring fins 20 is aligned in the 1 st flow path direction Df1, and the remaining part of the plurality of nearest neighboring fins 20 is aligned in the 2 nd flow path direction Df 2. For example, the most adjacent fin 20 disposed closest to the inlet 301 side in the 1 st flow path direction Df1 in the 1 st fin group 211 is aligned in the 2 nd flow path direction Df 2. Further, the nearest fins 20 disposed on the most side in the 2 nd flow path direction Df2 in the 1 st fin group 211 to the 3 rd fin group 213 are aligned in the 1 st flow path direction Df 1. In the 3 rd fin group 213, the fins 2 disposed closest to the discharge port 302 in the 1 st flow path direction Df1 are aligned in the 2 nd flow path direction Df 2. Further, the nearest fins 20 disposed on the other side of the 2 nd flow path direction Df2 in the 1 st fin group 211 to the 3 rd fin group 213 are aligned in the 1 st flow path direction Df 1. Thus, when manufacturing the heat sink 200, the fin group 210 in which the fins 2 are two-dimensionally arranged on the base 1 can be formed in a rectangular shape, and the heat sink 200 can also be formed in a rectangular shape when viewed from the direction normal to the upper surface of the base 1. Therefore, the shape of the heat sink 200 can be further simplified.

Next, a method of manufacturing the heat exchange device 100 will be described with reference to fig. 7 to 8F. Fig. 7 is a flowchart for explaining a method of manufacturing the heat exchange device 100. In addition, fig. 8A to 8F are diagrams illustrating respective manufacturing processes of the heat sink 200. Fig. 8A is a perspective view of the base 1 before processing. Fig. 8B is a perspective view of the base 1 in which a plurality of table portions 11 described later are formed. Fig. 8C is a partial perspective view of the base 1 having the groove 12 formed in the table portion 11. Fig. 8D is a conceptual diagram of the crack raising step of the convex portion 13. Fig. 8E is a partial perspective view of the base 1 in which the fins 2 are formed by the projections 13 between the grooves 12. Fig. 8F is a perspective view of the base 1 in which a plurality of fin groups 210 are formed.

Steps S1 to S3 are a method of manufacturing the heat sink 200. The heat sink 200 manufactured by the manufacturing method of steps S1 to S3 has the fin group 210 including the plurality of fins 2 protruding from the plate-like base 1, and forms a part of the fluid flow path Pf extending in the 1 st flow path direction Df 1.

The manufacturing method of the heat sink 200 has a mesa forming step S1. In the step of forming a terrace portion S1, a terrace portion 11 is formed on the upper surface of the base 1 shown in fig. 8A. The number of the terrace portions 11 is the same as the number of the fin groups 210. In the present embodiment, as shown in fig. 8B, 3 table portions 11 are arranged in the 1 st flow path direction Df 1. In addition, the mesa forming step S1 may also be omitted.

The method of manufacturing the heat sink 200 has a groove forming step S2. In the groove forming step S2, 3 or more grooves 12 are formed in the upper surface of the base 1 extending in the 1 st flow path direction Df 1. More specifically, each table portion 11 has 3 or more grooves 12 formed therein. As shown in FIG. 8C, the respective slots 12 extend in the 1 st direction D1 and are aligned in the 2 nd direction D2.

The forming means in the mesa forming step S1 and the groove forming step S2 are not particularly limited. For example, a chemical processing means such as resist etching may be used, or a physical processing means such as cutting may be used.

The manufacturing method of the heat sink 200 has a fin forming step S3. In the fin forming step S3, the fin group 210 is formed. The fins 2 of each fin group 210 are formed by a so-called shaving process. Specifically, the fin forming step S3 has a cleavage raising step S31. As shown in fig. 8D, in the splitting and raising step S31, the protruding portions 13 formed between the grooves 12 are split and the protruding portions 13 are raised, so that the fins 2 protrude from the base 1. In the fin forming step S3, the splitting and raising step S31 is performed a plurality of times in the 1 st direction D1 at equal intervals.

The number of fins 2 that can be formed is formed on each projection 13. In each of the convex portions 13, the fin 2 formed at a position along the edge of the table portion 11 may not have a desired prismatic shape as shown in fig. 6A or 6B. Such fins 2 may be cut out by cutting or the like. When not all of the convex portions 13 in 1 table portion 11 have finished forming fins by the cleavage and tilting (no in step S32), the process of fig. 7 returns to the cleavage and tilting step S31.

As shown in fig. 8E, when all the convex portions 13 of the 1 table portion 11 have completed forming the fins 2 (yes in step S32), the fins 2 formed by the split lift are similarly formed in the other table portions 11. That is, when not all the table portions 11 have completed forming the fins 2 (no in step S33), the target of the dicing and raising step S31 is changed to the unfinished table portion 11 (step S34), and the dicing and raising step S31 is performed.

On the other hand, as shown in fig. 8F, when all the table portions 11 have completed forming the fins 2 (yes in step S33), the manufacturing process of the heat sink 200 is ended.

Next, the lid 300 is fixed to the heat sink 200 to cover the upper surface of the heat sink 200 (step S4). Then, the process of fig. 7 ends.

According to the process of fig. 7, a plurality of fins 2 two-dimensionally arranged in the 1 st direction D1 and the 2 nd direction D2 in the fin group 210 can be formed on the upper surface of the base 1. Since the pressure loss that the fluid f in the 1 st flow path direction Df1 obliquely crossing the 1 st direction D1 receives when flowing between the fins 2 can be reduced, the reduction in the heat radiation efficiency from the fins 2 to the fluid f can be suppressed. Further, the fins 2 can be formed on the heat sink 200 forming a part of the fluid flow path Pf by a so-called shaving process. Since the base body 1 and the fins 2 can be formed integrally, that is, the base body 1 and the fins 2 can be formed from a single plate material, the thermal resistance between the base body 1 and the fins 2 can be reduced. Therefore, the heat dissipation efficiency from the heat generating component 400 disposed on the lower surface of the base 1 to the fluid f via the heat sink 200 can be improved. Therefore, the heat sink 200 and the heat exchange device 100 having improved cooling performance can be manufactured.

In addition, the heat sink 200 can be formed at a lower cost than the case where the fins 2 are fixed to the base 1. Therefore, productivity of the radiator 200 and the heat exchange device 100 can be improved.

In the present embodiment, in the splitting and raising step S31, the protruding portion 13 is split and raised using the tool 500 having the flat blade 501. In this way, the fin 2 having a quadrangular prism shape as shown in fig. 6A can be formed.

Preferably, in the splitting and lifting step S31, the convex portion 13 is split and lifted so that the blade 501 of the tool 500 is perpendicular to the 1 st direction D1. In this way, the fin can be formed into a quadrangular prism shape. Further, by performing the multiple-slit lifting step S31 at equal intervals in the 1 st direction D1, the fins 2 can be aligned in the 2 nd direction D2 in which the 2 nd side surfaces 22 are spread.

However, the present embodiment is not limited to the example, and the protruding portion 13 may be cut and lifted by using a tool having a curved blade in the cut and lift step S31. The curved blade 501 protrudes toward the inlet 301 side of the fluid flow path Pf in the 1 st flow path direction Df 1. In this way, the prismatic fins 2 as shown in fig. 6B can be formed. That is, the 2 nd side surface 22 of the fin 2 is a curved surface and protrudes toward the inlet 301 side of the fluid flow path Pf in the 1 st flow path direction Df 1.

In addition, in the fin forming step S3, it is preferable that the interval Wi1 between the fins 2 adjacent in the 1 st direction D1 is wider than the width Wt1 of the fin 2 in the 1 st direction D1. For example, the interval Wi3 after the multiple cleavage and lift steps S31 are performed in the 1 st direction D1 is wider than 2 times the width Wt1 of the fin 2 in the 1 st direction D1. In addition, as shown in fig. 8D, the interval Wi3 is equal to the sum of the width Wt1 of the fin 2 in the 1 st direction D1 and the interval Wi1 between the adjacent fins 2 in the 1 st direction D1. Thus, the fluid f can smoothly pass through the fins 2 in the 1 st direction D1. That is, since the pressure loss of the fluid f can be reduced, the reduction in the flow velocity of the fluid f can be suppressed. Therefore, the heat sink 200 can improve the heat radiation efficiency from the fins 2 to the fluid f, and thus the cooling performance of the heat sink 200 can be improved.

In addition, it is preferable that in the groove forming step S2, the width of the groove 12 in the 2 nd direction D2 is wider than the width of the convex portion 13 in the 2 nd direction D2. According to the process of fig. 7, as shown in fig. 8C and 8E, the width of the convex portion 13 in the 2 nd direction D2 is the width Wt2 of the fin 2 in the 2 nd direction D2. The width of the groove 12 in the 2 nd direction D2 is the interval Wi2 between the fins 2 adjacent to each other in the 2 nd direction D2. Therefore, by making the width of the groove 12 wider than the width of the projection 13, the interval Wi2 between the fins 2 adjacent in the 2 nd direction D2 is wider than the width Wt1 of the fin 2 in the 1 st direction D1. By making the interval Wt2 between the fins 2 adjacent to each other in the 2 nd direction D2 wider, the pressure loss of the fluid f can be further reduced, and therefore the reduction in the flow velocity of the fluid f can be further suppressed. Therefore, the cooling performance of the radiator 200 can be further improved.

Further, it is preferable that the gaps Ws are provided between the fins 2 closest to each other in the 2 nd flow path direction Df2 as viewed in the 1 st flow path direction Df 1. Further, as described above, the 2 nd flow path direction Df2 is orthogonal to the 1 st flow path direction Df1 and parallel to the substrate 1. For example, the intervals Wi1, Wi2 and the widths Wt1, Wt2 of the fins 2 are determined so that the gap Ws can be formed. By providing the gaps Ws between the fins 2 closest to each other in the 2 nd flow path direction Df2 when viewed from the 1 st flow path direction Df1, the fluid f flowing in the 1 st flow path direction Df1 can flow smoothly. Therefore, the cooling performance of the radiator 200 can be further improved.

In the heat sink 200 manufactured by the manufacturing method described with reference to fig. 7, the plurality of fin groups 210 are arranged in the 1 st flow path direction Df 1. Preferably, the groove forming step S2 and the fin forming step S3 are performed a plurality of times in the 1 st flow path direction Df1 with an interval Wg. For example, in the table forming step S1, the table 11 is formed in plural at intervals Wg in the 1 st flow path direction Df 1. By arranging the plurality of fin groups 210 in the 1 st flow path direction Df1 with the interval Wg therebetween, the pressure loss of the fluid f flowing through the fluid flow path Pf in the 1 st flow path direction Df1 can be reduced as compared with the case where 1 fin group 210 is disposed on the upper surface of the substrate 1. Therefore, the fluid f can be made to flow more smoothly in the fluid flow path Pf.

More preferably, the interval between adjacent fins 2 in the fin group 210 disposed closer to the discharge port 302 of the fluid flow path Pf in the 1 st flow path direction Df1 is wider than the interval between adjacent fins 2 in the fin group 210 disposed closer to the injection port 301 of the fluid flow path Pf in the 1 st flow path direction Df 1. For example, the intervals Wi1 and Wi2 between the fins 2 adjacent to each other in the arrangement direction of the fins 2 are wider as the fin group 210 arranged closer to the discharge port 302 of the fluid flow path Pf in the 1 st flow path direction Df 1. Therefore, the effect of more smoothly flowing the fluid f can be improved.

In the heat sink 200 manufactured by the manufacturing method described in fig. 7, the fin group 210 includes a plurality of nearest fins 20. As described above, each of the nearest fins 20 is the fin 2 nearest to the predetermined side 10 of the upper surface of the base 1 in at least one of the 1 st direction D1 and the 2 nd direction D2. Preferably, in the fin forming step S3, the nearest fins 20 are arranged linearly and the intervals Wd between each nearest fin 20 and the side 10 are made the same. The plurality of nearest fins 20 arranged linearly in one direction are arranged along the predetermined side 10 of the upper surface of the base 1 by making the intervals Wd between the nearest fins 20 and the predetermined side 10 of the upper surface of the base 1 the same. Therefore, when manufacturing the heat sink 200, the side 10 along the arrangement of the nearest fins 20 can be formed linearly. Therefore, the shape of the heat sink 200 viewed from the normal direction of the upper surface of the base 1 can be further simplified.

The embodiments of the present invention have been described above. The scope of the present invention is not limited to the above-described embodiments. The present invention can be implemented by variously changing the above-described embodiments without departing from the gist of the present invention. The matters described in the above embodiments can be combined arbitrarily as appropriate within a range that does not contradict each other.

The present invention is useful, for example, for a heat sink having a plurality of fins, a method for manufacturing the same, and a heat exchange device having the heat sink.

Claims (12)

1. A heat sink, having:

a plate-like base body; and

a fin group including a plurality of fins protruding from the base,

the base and the fin sets are each distinct portions of a component,

at least a portion of the plurality of fins are arranged in a 1 st direction and a 2 nd direction,

the 1 st direction is parallel to the substrate,

the 2 nd direction intersects the 1 st direction and is parallel to the base,

it is characterized in that the preparation method is characterized in that,

the fin has a 1 st side surface,

the 1 st side surface is a plane extending in the 1 st direction and opposed to a predetermined side of the upper surface of the base,

the 1 st angle is a smaller angle between the 1 st direction of the 1 st side surface extension and the side when viewed from a normal direction of the upper surface of the base,

the 1 st angle of each of the fins is the same.

2. The heat sink of claim 1,

the 1 st angle is 45 degrees.

3. The heat sink of claim 1,

the heat sink forms a portion of a fluid flow path extending in a 1 st flow path direction,

the 1 st flow path direction intersects obliquely with the 1 st direction and is parallel to the substrate,

a plurality of the fin groups are arranged along the 1 st flow path direction,

the interval between the adjacent fin groups in the 1 st flow path direction is wider than the interval between the adjacent fins in each of the fin groups.

4. The heat sink of claim 3,

the interval between the adjacent fins in the fin group arranged on the discharge port side of the fluid flow path in the 1 st flow path direction is wider than the interval between the adjacent fins in the fin group arranged on the injection port side of the fluid flow path in the 1 st flow path direction.

5. The heat sink of claim 3,

the fin further has a 2 nd side surface facing the 1 st flow path direction,

the 1 st side surface is a plane facing the 1 st flow path direction,

the 2 nd side surface is one of a flat surface which extends in the 2 nd direction and forms an angle with the 1 st side surface and a curved surface which protrudes toward an inlet side of the fluid channel in the 1 st channel direction and is continuous with the 1 st side surface.

6. The heat sink of claim 5,

the 2 nd side is a plane extending in the 2 nd direction and forming the angle with the 1 st side, opposite to the edge,

a 2 nd angle is a smaller angle between the side intersecting the 1 st channel direction and the 2 nd direction in which the 2 nd side surface spreads when viewed from a normal direction of the upper surface of the base,

the 2 nd angle of each of the fins is the same as the 1 st angle.

7. The heat sink of claim 1,

the fin group includes a plurality of nearest neighbor fins,

each of the nearest fins is the fin nearest to a predetermined side of the upper surface of the base in at least one of the 1 st direction and the 2 nd direction,

the spacing between each of said nearest adjacent fins and said edge is the same.

8. The heat sink of claim 3,

the fin group includes a plurality of nearest neighbor fins,

each of the nearest fins is the fin nearest to a predetermined side of the upper surface of the base in at least one of the 1 st direction and the 2 nd direction,

the spacing between each of said nearest adjacent fins and said edge is the same,

a 2 nd channel direction orthogonal to the 1 st channel direction and parallel to the substrate,

the nearest neighboring fins are arranged in one of the 1 st flow path direction and the 2 nd flow path direction.

9. The heat sink of claim 8,

when viewed from the 1 st flow path direction, gaps are formed between the fins closest to each other in the 2 nd flow path direction.

10. The heat sink of claim 7,

the nearest fins are arranged linearly.

11. The heat sink of claim 1,

the interval between the fins adjacent in the 1 st direction is wider than the width of the fins in the 1 st direction.

12. A heat exchange device is characterized in that,

the heat exchange device comprises:

the heat sink of any one of claims 1 to 11; and

a cover body forming a fluid flow path for fluid flow together with the heat sink,

the fluid is a refrigerant, and flows between the fins of the radiator.

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