CN112992814A - Cooling device - Google Patents
Cooling device Download PDFInfo
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- CN112992814A CN112992814A CN202011013369.8A CN202011013369A CN112992814A CN 112992814 A CN112992814 A CN 112992814A CN 202011013369 A CN202011013369 A CN 202011013369A CN 112992814 A CN112992814 A CN 112992814A
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- fins
- fin
- end portion
- tip
- heat sink
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
- H01L23/00—Details of semiconductor or other solid state devices
- H01L23/34—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
- H01L23/46—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids
- H01L23/473—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids by flowing liquids
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
- H01L23/00—Details of semiconductor or other solid state devices
- H01L23/34—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
- H01L23/36—Selection of materials, or shaping, to facilitate cooling or heating, e.g. heatsinks
- H01L23/367—Cooling facilitated by shape of device
- H01L23/3672—Foil-like cooling fins or heat sinks
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- Condensed Matter Physics & Semiconductors (AREA)
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- Computer Hardware Design (AREA)
- Microelectronics & Electronic Packaging (AREA)
- Power Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Materials Engineering (AREA)
- Cooling Or The Like Of Electrical Apparatus (AREA)
- Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
Abstract
The present invention relates to a cooling device. Provided is a cooling device capable of increasing the number of fins by reducing the distance between the fins, thereby improving the cooling performance. The cooling device is provided with a plurality of fins (11), wherein the plurality of fins (11) are plate-shaped and are arranged in the direction orthogonal to the plate surface, and a plurality of recesses (111) arranged in the short-side direction are formed at the end of each fin (11), which is the end in the long-side direction parallel to the plate surface and is the end on the inlet side of the cooling liquid.
Description
Technical Field
The present invention relates to a cooling device.
Background
In recent years, as a liquid-cooled cooling device for cooling power devices (semiconductor elements) such as IGBTs (Insulated Gate Bipolar transistors) used in power control devices mounted on electric vehicles, hybrid vehicles, electric vehicles, and the like, a cooling device having a plurality of fins has been proposed. In such a cooling device, if the fins are clogged with foreign matter, the flow rate of the refrigerant decreases, and the cooling efficiency decreases, so a technique for suppressing the decrease in cooling efficiency has been proposed.
For example, the cooler described in patent document 1 is configured as follows. The cooling device is provided with a 1 st fin group and a 2 nd fin group, wherein the 1 st fin group is arranged on the upstream side of the flow passage, is arranged in the longitudinal direction of the cross section of the flow passage, and extends in the flowing direction of the refrigerant. The 2 nd fin group is arranged on the downstream side of the 1 st fin group, is arranged in the longitudinal direction, extends in the flow direction of the refrigerant, and is in contact with each of the fins on the inner surface of the flow path facing in the short side direction of the flow path cross section. The pitch of the 2 nd fin group is larger than that of the 1 st fin group.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2017-45857
Disclosure of Invention
Problems to be solved by the invention
In order to improve the cooling performance, it is conceivable to reduce the distance between adjacent fins and increase the number of fins. When the distance between the fins is reduced, foreign matter is likely to clog, and the refrigerant is likely to be difficult to flow. If the refrigerant becomes difficult to flow, the cooling performance may deteriorate even if the number of fins is increased.
The invention aims to provide a cooling device which can increase the number of fins by reducing the distance between the fins and improve the cooling performance.
Means for solving the problems
The present invention has been made in view of the above-described object, and has a plurality of fins which are plate-shaped and arranged in a direction orthogonal to a plate surface, and in which a plurality of recesses are formed in an end portion of the fins which is an end portion in a longitudinal direction parallel to the plate surface and which is an end portion on an inlet side of a coolant.
Here, the size of the recess in the short side direction may be larger than the distance between the fins of the plurality of fins.
Further, when a total area of the plurality of recesses is S, a distance between the fins of the plurality of fins is w, and a size of the fins in the short side direction is h, S/2> w × h may be used.
Further, the size of the plurality of concave portions in the longitudinal direction may be increased as being distant from the heat generating element disposed on one end portion side in the short direction.
Further, the fin formed by the adjacent recess of the plurality of recesses may have a tip end portion bent with respect to the plate surface.
In addition, the direction of bending of one of the plurality of tip portions of the fin may be opposite to the direction of bending of the other tip portion different from the one tip portion with respect to the plate surface.
Effects of the invention
According to the present invention, it is possible to provide a cooling device capable of improving cooling performance by reducing the distance between fins.
Drawings
Fig. 1 is a perspective view of a liquid-cooled cooling device according to embodiment 1.
Fig. 2 is a sectional view of a portion II-II of fig. 1.
Fig. 3 is a sectional view of the section III-III of fig. 2.
Fig. 4 (a) is a perspective view showing an example of an inlet-joint-side end portion of the heat sink. (b) Is a view when the radiator is viewed in the IVb direction of (a).
Fig. 5 is a perspective view showing an example of a state in which foreign matter is blocked at an end portion of the radiator on the inlet joint side.
Fig. 6 (a) is a perspective view showing an example of an inlet-joint-side end portion of the heat sink according to embodiment 2. (b) This is a view when the heat sink is viewed in the VIb direction of (a).
Fig. 7 (a) is a perspective view showing an example of an inlet-joint-side end portion of the heat sink according to embodiment 3. (b) This is a view when the heat sink is viewed in the VIIb direction of (a).
Fig. 8 (a) and (b) are perspective views showing an example of a modification of the inlet-joint-side end portion of the heat sink according to embodiment 3.
Fig. 9 (a), (b), and (c) are perspective views showing an example of a modification of the inlet-joint-side end portion of the heat sink.
Description of the reference symbols
1 … liquid-cooled cooling device, 10, 50, 70 … radiator, 11, 60, 71 … fin, 20 … casing, 30 … inlet joint, 40 … outlet joint, 111, 61, 62, 63, 64, 65, 66, 711 … recess, 112, 712 … front end, P … heating element, I … insulating member.
Detailed Description
Hereinafter, embodiments will be described in detail with reference to the drawings.
< embodiment 1 >
Fig. 1 is a perspective view of a liquid-cooled cooling device 1 according to embodiment 1.
Fig. 2 is a sectional view of a portion II-II of fig. 1.
Fig. 3 is a sectional view of the section III-III of fig. 2.
The liquid-cooled cooling device 1 of the embodiment includes: a heat sink 10 having a plurality of fins 11 of a rectangular shape, and a case 20 housing the heat sink 10. The liquid-cooled cooling device 1 further includes: an inlet joint 30 for allowing the coolant to flow into the housing 20 from the outside thereof, and an outlet joint 40 for allowing the coolant to flow out of the housing 20 from the inside thereof to the outside thereof. Hereinafter, the longitudinal direction of the rectangular fins 11 is sometimes referred to as the left-right direction, the short-side direction of the fins 11 is sometimes referred to as the up-down direction, and the arrangement direction of the plurality of fins 11 is sometimes referred to as the front-back direction.
The liquid-cooled cooling device 1 is a device that cools a heating element P attached to an outer surface (upper surface in the present embodiment) of a case 20 via a flat plate-shaped insulating member I, using a cooling liquid that flows inside the case 20 and a radiator 10. The heating element P may be exemplified by a power semiconductor device such as an insulated Gate Bipolar transistor (igbt). The heating element P can be exemplified by an IGBT module in which an IGBT and a control circuit for controlling the IGBT are packaged, and an intelligent power module in which the IGBT module and a self-protection function are packaged.
(case 20)
The housing 20 includes: a case body 21 to which the heating element P is attached via an insulating member I, and a cover 22 covering an opening of the case body 21.
The case main body 21 has a flat plate-shaped top portion 21a, side portions 21b projecting downward from respective ends of the top portion 21a in a direction orthogonal to the top portion 21a, and flange portions 21c projecting outward from respective ends of the side portions 21b in a direction orthogonal to the side portions 21 b. The heating element P is attached to the center portion of the surface (upper surface) of the top portion 21a on the side opposite to the side on which the side portion 21b is provided, via the insulating member I. Further, an inlet through hole 21d and an outlet through hole 21e that penetrate the inside of the case 20 so as to communicate with the outside are formed on the respective outer sides in the left-right direction of the top portion 21a than the portions where the insulating member I and the heating element P are arranged.
The cover 22 is flat and rectangular, and is larger than the flange portion 21c of the case main body 21. Through holes 221 through which bolts and the like for attaching the liquid-cooled cooling device 1 to other members are inserted are formed in 4 corners of the cover 22.
The case 20 is formed in a box shape so that the radiator 10 can be housed therein by brazing the flange portion 21c of the case main body 21 and the cover 22. The case body 21 and the cover 22 can be formed by using an aluminum brazing sheet as an example. At this time, the brazing material layers are located at least on the sides facing each other.
Further, the case main body 21 and the cover 22 are brazed to form an inflow side space 23 below the inlet through hole 21d in the case 20 and an outflow side space 24 below the outlet through hole 21e in the case 20.
(Inlet fitting 30)
The inlet joint 30 has a cylindrical portion 31 and a rectangular parallelepiped portion 32, and is formed with a cavity therein so as to allow the coolant to flow therethrough. One end (right end) of the cylindrical portion 31 is open, and the other end is connected to the rectangular parallelepiped portion 32. A through hole 33 for communicating the inside and the outside of the inlet joint 30 is formed in one surface (lower surface) of the rectangular parallelepiped portion 32. The inlet joint 30 is brazed to the case body 21 in a state where a surface on which the through-hole 33 is formed is placed on a surface (upper surface) on which the heating element P is mounted in the top portion 21a of the case body 21. At this time, the inside of the inlet joint 30 and the inside of the housing main body 21 communicate with each other through the through hole 33 of the inlet joint 30 and the inlet through hole 21d of the housing main body 21.
(Outlet connection 40)
The outlet joint 40 has a cylindrical portion 41 and a rectangular parallelepiped portion 42, and is formed with a cavity therein so as to allow the coolant to flow therethrough. One end (left end) of the cylindrical portion 41 is open, and the other end is connected to the rectangular parallelepiped portion 42. A through hole 43 that communicates the inside and the outside of the outlet joint 40 is formed in one surface (lower surface) of the rectangular parallelepiped portion 42. The outlet joint 40 is brazed to the case body 21 in a state where a surface on which the through hole 43 is formed is placed on a surface (upper surface) on which the heating element P is mounted in the top portion 21a of the case body 21. At this time, the interior of the outlet joint 40 and the interior of the housing main body 21 communicate with each other through the through hole 43 of the outlet joint 40 and the outlet through hole 21e of the housing main body 21.
(heating radiator 10)
The heat sink 10 has a plurality of fins 11, and the plurality of fins 11 are plate-shaped and arranged in a direction orthogonal to the plate surface. The area in which the plurality of fins 11 are arranged is larger than the insulating member I when viewed in the vertical direction.
The fins 11 are rectangular in shape, and are arranged such that the short side direction of the fins 11 is the vertical direction shown in fig. 1, and the long side direction of the fins 11 is the horizontal direction shown in fig. 1. The plurality of fins 11 are arranged in a direction perpendicular to the surfaces of the fins 11 in a state where the distance between adjacent fins (in other words, the gap between the fins 11 and the fins 11) is a predetermined interval w (hereinafter, may be referred to as "predetermined interval w"). The plurality of fins 11 are arranged so that the arrangement direction is the front-rear direction shown in fig. 1.
The heat sink 10 is fixed in the case 20 by brazing the upper ends of the plurality of fins 11 to the surface (lower surface) of the top portion 21a of the case main body 21 on the side opposite to the surface on which the heating element P is mounted, and brazing the lower ends of the plurality of fins 11 to the upper surface of the cover 22. At the time of brazing, there can be exemplified: after the lower ends of the plurality of fins 11 are joined to the cover 22, the case main body 21 and the cover 22 are brazed, and the upper ends of the plurality of fins 11 and the case main body 21 are brazed at the same time. The joining of the lower ends of the plurality of fins 11 to the cover 22 can be performed by welding such as pressure welding, adhesion, and brazing. Further, brazing of the lower ends of the plurality of fins 11 and the cover 22, brazing of the upper ends of the plurality of fins 11 and the case main body 21, and brazing of the case main body 21 and the cover 22 may be performed all at the same time.
Fig. 4 (a) is a perspective view showing an example of an end portion of the radiator 10 on the inlet joint 30 side.
Fig. 4 (b) is a view of the heat sink 10 viewed in the IVb direction of fig. 4 (a). In other words, fig. 4 (b) is a view of the fin 11 when one example of the end portion on the inlet joint 30 side is viewed in the front-rear direction.
As shown in fig. 4 (a) and 4 (b), a plurality of recesses 111 are formed at equal intervals in the short-side direction at the end of the fin 11, which is the end in the long-side direction and on the inlet joint 30 side. The concave portions 111 may be exemplified as rectangular parallelepiped. That is, the shape of each concave portion 111 when viewed in the front-rear direction is rectangular. The width a, which is the size in the short-side direction of the concave portion 111, is larger than the predetermined interval w, which is the distance between the adjacent fins 11. That is, the width a > the predetermined interval w.
The size of each portion is set so that the flow path area (1/2) of the bypass path flowing through the recess 111 formed in the adjacent fin 11 to the flow path formed between the adjacent fins 11 is larger than the flow path area of the inter-fin flow path 14, which will be described later, formed between the adjacent fins 11. That is, when the number of the recesses 111 formed in each fin 11 is N and the size of the recesses 111 in the longitudinal direction is depth b, the total area S of the plurality of recesses 111 in each fin 11 becomes "width a × depth b × N". When the dimension of the fin 11 in the short side direction is defined as the height h, the dimensions of the respective portions are set so that "the total area S/2> the predetermined interval w × the height h". The reason why the flow path area of the bypass path (1/2) is taken as a reference is that the coolant can flow into the inter-fin flow paths 14 formed on both sides of the fin 11 in which the recess 111 is formed, via the recess 111.
The material of the fin 11 may be aluminum, aluminum alloy, or other aluminum material. The fin 11 may be made of a composite material of copper, aluminum, or an aluminum alloy and carbon.
The fins 11 can be formed by pressing a plate material made of, for example, an aluminum material. The thickness of the fin 11 (plate thickness of the plate material) can be 0.3 to 1.2 mm. The thickness of the fins 11 is appropriately changed depending on the size of the entire liquid-cooled cooling device 1, the type of the cooling liquid flowing through the casing 20, and the heat conductivity of the fins 11.
In the liquid-cooled cooling device 1 configured as described above, the coolant flows into the inflow side space 23 in the casing 20 through the inlet through hole 21d and the interior of the inlet joint 30. Then, the flow flows in the left direction in the inter-fin flow path 14 (see fig. 3) formed by the gap between the fins 11 adjacent to each other among the plurality of fins 11 in the heat sink 10, and reaches the outflow space 24. The air flows leftward through the front side flow paths 15 (see fig. 3) formed between the foremost fins 11 of the heat sink 10 and the side portions 21b of the case body 21 and the rear side flow paths 16 (see fig. 3) formed by the gaps between the rearmost fins 11 of the heat sink 10 and the side portions 21b of the case body 21, and reaches the outflow side space 24. The coolant that has reached the outflow space 24 flows through the outlet through hole 21e and the inside of the outlet joint 40, and flows out of the housing 20.
The heat generated from the heating element P is radiated to the coolant flowing through the inter-fin flow path 14, the front side flow path 15, and the rear side flow path 16 via the insulating member I, the top portion 21a of the case main body 21, and the fins 11 of the heat sink 10. Thereby, the heating element P is cooled.
Fig. 5 is a perspective view showing an example of a state in which foreign matter is blocked at an end portion of the radiator 10 on the inlet joint 30 side.
In the liquid-cooled cooling device 1 of the present embodiment, since the plurality of recesses 111 are formed in the end portions of the fins 11 of the radiator 10 on the inlet joint 30 side, foreign matter mixed into the coolant is easily captured. That is, since the convex tip portion 112 is provided between the adjacent concave portions 111 and easily comes into contact with a foreign object not in a line but in a point manner, for example, a thread-like foreign object is easily caught by the tip of the convex tip portion 112. Therefore, the foreign matter can be suppressed from being clogged at a portion on the downstream side in the flow path of the coolant such as the inter-fin flow path 14. The "foreign matter" can be exemplified by dust mixed in the coolant or an object peeled off from the inner wall of a flow path through which the coolant flows upstream of the liquid-cooled cooling device 1 in a cooling flow path of the same system such as a motor case, a radiator, and a water pump.
In the fins 11 of the heat sink 10, since the width a of the recessed portion 111 is larger than the predetermined interval w, which is the distance between the adjacent fins 11, even if foreign matter is clogged at the end portion of the heat sink 10 on the inlet joint 30 side, the coolant easily passes through the recessed portion 111, as compared with the case where the width a is not larger than the predetermined interval w. Therefore, even in a portion where foreign matter is clogged, clogging of the flow path of the coolant can be suppressed. The size of each region is set so that "total area S/2> predetermined interval w × height h". This makes it possible to reduce the resistance of the coolant when passing through the recess 111 compared to the resistance when passing through the fins 11. As described above, in the radiator 10 of the present embodiment, the flow of the coolant can be bypassed as shown by the arrows in fig. 5 while capturing foreign matter, and the flow path of the coolant is less likely to be blocked.
As described above, according to the liquid-cooled cooling device 1 having the radiator 10, even if the distance (predetermined interval w) between the fins 11 is reduced, it is possible to suppress clogging of foreign matter at a portion on the downstream side in the flow path of the cooling liquid and to suppress resistance when the cooling liquid flows, and therefore it is possible to increase the number of fins 11 and improve cooling performance.
Further, the fins 11 of the heat sink 10 are formed by press working a plate material made of, for example, an aluminum material, but the recesses 111 may be formed simultaneously with the outer shape of the fins 11. Therefore, the manufacturing cost of the fin 11 is not easily increased by forming the recess 111 in the fin 11.
In the above-described embodiment, the shape of the recess 111 of the fin 11 of the heat sink 10 is illustrated as "width a > predetermined interval w" and "total area S/2> predetermined interval w × height h", but the present invention is not particularly limited to this form. The shape may satisfy one of "width a > predetermined interval w" and "total area S/2> predetermined interval w × height h".
< embodiment 2>
Fig. 6 (a) is a perspective view showing an example of an end portion on the inlet joint 30 side in the radiator 50 according to embodiment 2.
Fig. 6 (b) is a view of the heat sink 50 viewed in the VIb direction of fig. 6 (a).
The heat sink 50 according to embodiment 2 is different from the heat sink 10 according to embodiment 1 in the fins 60 corresponding to the fins 11. The following description deals with differences from the heat sink 10. Elements having the same function in embodiment 2 and embodiment 1 are denoted by the same reference numerals, and detailed description thereof is omitted.
The fin 60 is formed with a recess 61, a recess 62, a recess 63, a recess 64, a recess 65, and a recess 66, which are different in size in the longitudinal direction, that is, different in depth, in order from the case main body 21 side to the cover 22, to which the heating element P is attached via the insulating member I. When the depths of the concave portions 61, 62, 63, 64, 65, and 66 are b1, b2, b3, b4, b5, and b6, respectively, as shown in fig. 6, the depth is formed to become deeper as the distance from the case body 21 increases, as b1< b2< b3< b4< b5< b6 increases. In other words, as shown by the two-dot chain line in fig. 6, in the region where the insulating member I does not exist above, the heat generated from the heating element P is transmitted radially from the end portion of the insulating member I to the fin 60, and therefore, the depth is formed to be smaller so as to increase the contact area with the coolant as the distance from the top portion 21a of the case main body 21 becomes closer.
According to the fin 60 of embodiment 2, for example, the resistance when the coolant flows through the bypass passage can be reduced as compared with the case where the depth is fixed to b 1. As described above, according to the fin 60, the flow path of the coolant can be made less likely to be blocked while capturing foreign matter.
As a result, according to the heat sink 50 of embodiment 2, the distance between the fins 60 can be reduced, and the number of fins 60 can be increased, thereby improving the cooling performance.
< embodiment 3 >
Fig. 7 (a) is a perspective view showing an example of an end portion on the inlet joint 30 side in the radiator 70 according to embodiment 3.
Fig. 7 (b) is a view of the heat sink 70 as viewed in the VIIb direction in fig. 7 (a). In other words, fig. 7 (b) is a view of an example of the end portion of the fin 71 on the inlet joint 30 side as viewed from the inlet joint 30 side to the outlet joint 40 side.
The heat sink 70 according to embodiment 3 is different from the heat sink 10 according to embodiment 1 in the shape of the fins 71 corresponding to the fins 11. The following description deals with differences from the heat sink 10. Elements having the same function as those in embodiment 3 and embodiment 1 are denoted by the same reference numerals, and detailed description thereof is omitted.
In the end portion of the fin 71 of embodiment 3, a plurality of recesses 711 are formed at equal intervals in the short-side direction, and the tip end portion 712 of the fin 71 formed by the adjacent recesses 711 out of the plurality of recesses 711, which is the end portion in the long-side direction of the fin 71 and is the end portion on the inlet joint 30 side, is bent with respect to the plate surface. As shown in fig. 7 (b), the tip portion 712 is formed such that, when viewed in the longitudinal direction of the fin 71, the tip of the tip portion 712 of the fin 71 is positioned so as to overlap the inter-fin flow channel 14 formed between adjacent fins 71. The bending direction of one tip portion 713 of the plurality of tip portions 712 and the bending direction of the other tip portion 714 adjacent to the one tip portion 713 are opposite to the plate surface of the fin 71. In the example shown in fig. 7 (a) and 7 (b), one tip end 713 and the other tip end 714 are formed so as to alternate in the short-side direction.
In the heat sink 70 according to embodiment 3, when the fin 71 is viewed in the longitudinal direction, the tip portion 712 of the fin 71 is located at a position overlapping the inter-fin flow channel 14. In other words, the tip portion 712 is present so as to close a part of the flow path of the coolant flowing from the inlet joint 30 to the outlet joint 40, that is, a part of the inlet of the inter-fin flow path 14. Therefore, according to the heat sink 70, foreign matter slightly smaller than the predetermined interval w is easily captured also at the distal end portion 712, and therefore clogging of foreign matter at a portion on the downstream side in the flow path of the coolant such as the inter-fin flow path 14 can be suppressed.
Further, in the heat sink 70 according to embodiment 3, one tip end portion 713 and the other tip end portions 714 are formed so as to alternate in the short-side direction. Therefore, as shown in fig. 7 (b), the opening area of the inlet of the inter-fin flow path 14 formed by the one fin 71a and the other fin 71b is narrowed by the one tip 713 of the one fin 71a and the other tip 714 of the other fin 71b adjacent to the one fin 71a among the plurality of fins 71. Therefore, according to the heat sink 70, foreign matter mixed into the coolant is easily captured, and therefore, clogging of foreign matter at a portion on the downstream side in the flow path of the coolant such as the inter-fin flow path 14 can be suppressed.
In the heat sink 70 according to embodiment 3, as in the heat sink 10, the width a, which is the size in the short-side direction of the recesses 711 of the fins 71, is larger than the predetermined interval w, which is the size between adjacent fins 71. The size of each region is set so that "total area S/2> predetermined interval w × height h". Therefore, even if foreign matter is clogged at the end portion of the radiator 70 on the inlet joint 30 side, the coolant easily passes through the recessed portion 711, as compared with the case where the width a is equal to or smaller than the predetermined interval w. Therefore, the clogging of the flow path can be suppressed even at the portion where the foreign matter is clogged. Further, since "total area S/2> predetermined interval w × height h", the resistance when the coolant passes through the recess 111 can be made smaller than the resistance when the coolant passes through the fins 71. As described above, in the radiator 70 according to embodiment 3, the flow of the coolant can be bypassed while capturing foreign matters, and the flow path is less likely to be blocked.
As a result, according to the heat sink 70 of embodiment 3, the cooling performance can be improved by reducing the distance between the fins 60 and increasing the number of fins 60.
When the fin 71 is formed by pressing a plate material made of, for example, an aluminum material, the recess 711 and the tip portion 712 can be processed while forming the outer shape of the fin 71. Therefore, the manufacturing cost of the fin 71 is not easily increased by forming the recess 711 and the distal end 712 in the fin 71.
(modification example)
Fig. 8 (a) and 8 (b) are perspective views showing an example of a modification of the end portion of the heat sink 70 on the inlet joint 30 side in embodiment 3.
In the fin 71 illustrated in fig. 7 (a) and 7 (b), the one tip end 713 and the other tip end 714 having different bending directions are formed so as to alternate in the short-side direction, but the present invention is not particularly limited to this configuration. The bending direction of the distal end 712 may be the direction shown in fig. 8 (a) and 8 (b).
For example, as illustrated in fig. 8 (a), the tip end portions 712 may be bent in the same direction with respect to all the plate surfaces of the fins 71, and when viewed in the longitudinal direction of the fins 71, all the tip end portions 712 may be located at positions overlapping the inter-fin flow channels 14. Even if the tip portion 712 has such a shape, foreign matter slightly smaller than the predetermined interval w is easily captured at the tip portion 712, and therefore clogging of foreign matter at a portion on the downstream side in the flow path of the coolant such as the inter-fin flow path 14 can be suppressed.
As illustrated in fig. 8 (b), the tip portion 712 may have one tip portion 715 and another tip portion 716 bent in different directions with respect to the plate surface of the fin 71, and parallel tip portions 717 not bent with respect to the plate surface of the fin 71, and the one tip portion 715 and the other tip portions 716 may be alternately provided with the parallel tip portions 717 interposed therebetween. Further, when viewed in the longitudinal direction of the fin 71, the one tip 715 and the other tip 716 are positioned so as to overlap the inter-fin flow path 14, and foreign matter slightly smaller than the predetermined interval w is easily captured also at the tip 712, so that clogging of foreign matter at a portion on the downstream side in the flow path of the coolant such as the inter-fin flow path 14 can be suppressed.
Fig. 9 (a), 9 (b), and 9 (c) are perspective views showing an example of a modification of the end portion of the heat sink 70 on the inlet joint 30 side.
As shown in fig. 9 (a), 9 (b), and 9 (c), in the heat sink 70 of embodiment 3 illustrated in fig. 7 (a) and 7 (b), and the heat sink 70 of the modification illustrated in fig. 8 (a) and 8 (b), the depth of the concave portion 711 may be formed to be deeper as being farther from the top portion 21a of the case main body 21, as in the heat sink 50 of embodiment 2. Thus, the resistance of the coolant flowing through the bypass passage can be reduced as compared with the case where the depth is fixed, and the flow passage of the coolant can be made less likely to be blocked while capturing foreign matter. As a result, according to the heat sink 50 of embodiment 2, the distance between the fins 60 can be reduced, and the number of fins 60 can be increased, thereby improving the cooling performance.
Claims (9)
1. A cooling device comprises a plurality of fins which are plate-shaped and arranged in a direction orthogonal to a plate surface,
a plurality of recesses are formed in the fin at the end portion thereof, which is the end portion in the longitudinal direction parallel to the plate surface and is the end portion on the inlet side of the coolant, and which are aligned in the short-side direction.
2. The cooling apparatus as set forth in claim 1,
the size of the recess in the short side direction is larger than the distance between the fins of the plurality of fins.
3. The cooling apparatus according to claim 1 or 2,
when the total area of the plurality of recesses is S, the distance between the fins of the plurality of fins is w, and the size of the fins in the short side direction is h,
S/2>w×h。
4. the cooling device according to any one of claims 1 to 3,
the size of the plurality of concave portions in the longitudinal direction increases as the distance from the heating element disposed on one end portion side in the short-side direction increases.
5. The cooling device according to any one of claims 1 to 4,
the fin formed by the adjacent recess of the plurality of recesses has a tip end bent with respect to the plate surface.
6. The cooling apparatus as set forth in claim 5,
the direction of bending of one of the plurality of tip portions of the fin is opposite to the direction of bending of the other tip portion different from the one tip portion with respect to the plate surface.
7. The cooling apparatus as set forth in claim 5,
the plurality of tip portions of the fin are all bent in the same direction with respect to the plate surface.
8. The cooling apparatus as set forth in claim 6,
the one tip end portion and the other tip end portion are alternately arranged in the short side direction.
9. The cooling apparatus as set forth in claim 6,
the one tip end portion and the other tip end portion are alternately arranged in the short side direction with the tip end portion that is not bent with respect to the plate surface interposed therebetween.
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| JP2019227396A JP7363446B2 (en) | 2019-12-17 | 2019-12-17 | Cooling system |
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| JP5608787B2 (en) * | 2013-05-17 | 2014-10-15 | 株式会社豊田自動織機 | Liquid cooling system |
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