Patent Application
20200149829
The present invention relates to a heatsink used for radiating heat.
Priority is claimed on Japanese patent Application No. 2017-149843, filed Aug. 2, 2017, the content of which is incorporated herein by reference.
In electronic devices generating heat such as power modules or the like on which semiconductor elements such as power elements, a heatsink is provided for radiating the heat from heat-generating elements (the power elements) in order to work the electronic devices normally. The heatsinks broadly employed are formed from aluminum or copper having high thermal conductivity and have a structure in which a lot of fins of a plate shape, a pin shape and the like stand on one surface of a flat base board. The heatsink cools the cooled body by closely attaching the base board to a cooled body such as the power module and arranging the fins in a coolant path.
For example, in a heatsink described in Patent Document 1, plate shape fins connected by lateral ribs at a medium position in a height direction are formed on a base board by extrusion molding.
In a heatsink described in Patent Document 2, fins made of three-dimensional mesh material are bonded on a base board by brazing or the like in order to increase specific surface area. As the three-dimensional mesh material, foam metal having connected pores formed by foaming metal such as copper, nickel, stainless, aluminum and the like are exemplified.
Patent Document 3 discloses a structure in which a porous body having communicated pores is filled between fins of pin-shape or plate-shape standing on a base board. In this structure, heat is moved from the base board to the porous body by the fins of a non-porous body (a dense solid ingot) having no pores with a large area; and the heat is conducted from the porous body to the air by the porous bod: so that it is described that heat exchange performance can be improved.
Patent Document 1: Japanese Unexamined Patent Application, First Publication No. H06-244327
The heatsink described in Patent Document 1 cannot be expected to have high thermal exchange performance because the specific surface area is small since the fin is non-porous body. The heatsink described in Patent Document 2 is feared that the brazing material bonding the fins and the base board reacts to base materials and thermal resistance increases at a bonding interface. Moreover, it is feared that the brazing material impregnates into the porous body (three-dimensional mesh material) and the specific surface area decreases: and there is a tendency for a cost to increase by the brazing material and flux which are necessary for bonding.
In the structure described in Patent Document 3, foamed aluminum (a metal porous body) having an open-cell structure is used as a porous body. The foamed metal is manufactured generally by mixing eutectic elements with metal powder and liquid phase sintering: so that the thermal conductivity decreases by the eutectic elements disperse in the foamed metal.
The inventors of the present application suggests a thermal exchanging member in Patent Document 4 that has fins formed by bonding a porous body formed by sintering and integrating aluminum fibers on a surface of a base board (a non-porous body). Thereby sintered strength of the porous body is improved and thermal conductivity is improved, so that heat can be efficiently exchanged though: further improvement of the heat exchange performance is required.
The present invention has an object to improve the heat exchange performance of the heatsink.
A heatsink according to the present invention is provided with: a base board formed of non-porous material (solid material) of aluminum; a plurality of plate like fins, formed of non-porous material of aluminum, standing integrally on a surface of the base board, and arranged with an interval mutually in parallel to form grooves; and a porous-body part including at least one porous body, formed from a sintered body of aluminum fibers having a three-dimensional mesh structure, filled in the grooves between the fins, and joined to the fins and the base board with sintered-joint portions therebetween.
In this heatsink, the porous body is filled between the fins of non-porous material, so that heat transfer is carried out in a broad area including the fins and the base board, and the porous body. Since the porous body is joined to the fins and the base board with the sintered-joint portions therebetween, heat resistance at an joint interface of the porous body to the fins and the base board is small, so that the smooth heat transfer is promoted between the porous body and the base board and the fins. The heat medium flows through vacancy in the porous body, so that the heat exchange is carried out between the surfaces of the porous body, the fins and the base board and the heat medium.
Since the heatsink has a large surface area by the porous body, the heat received at the porous body can move efficiently, and an excellent heat exchange performance can be obtained. Moreover, the porous body (the aluminum fibers) obstructs the flow of the heat medium, the flow can be disturbed (a disturbance effect), so that the effect of promoting the thermal exchange is larger in addition to the largeness of the specific surface area comparing with the heatsink formed only from non-porous material.
The porous body formed from the sintered body of the aluminum fibers has higher heat transfer coefficient than foamed metal because eutectic elements are not dispersed as in the foamed metal and skeleton is solid. The porous body can be freely controlled of the pore percentage, a size of opening diameter of the pores opening inside and the like only by changing a thickness of the aluminum fibers, a filling method and the like: flexibility of product design is high, and a desired external form can be easily made by using a molding die formed to have the desired shape.
The porous body is joined to the fins and the base board by the sintered-joint portions without brazing material, so that the pore percentage of the porous body is not decreased owing to percolation of the brazing material.
In a preferred embodiment of the heatsink of the present invention, in the porous body, in a transverse section parallel to an arrangement direction of the fins, a proportion of a number of cross sections in which an aspect ratio of a major axis diameter and a minor axis diameter is not less than 1.2 to a total number of observed cross sections of the aluminum fibers is not less than 40% and not less than 70%.
Since the proportion of the number of the cross sections of the aluminum fibers having the aspect ratio of the major axis diameter and the minor axis diameter not less than 1.2 in the transverse cross section of the porous body is not less than 40%, it is possible to increase surfaces opposing the flowing direction of the heat medium (a longitudinal direction of the fins), i.e., surfaces disturbing the flow of the heat medium. Thereby the disturbance effect disturbing the flow of the heat medium can be generated in the porous medium, the heat exchange between the porous body and the heat medium can be furthermore promoted. Moreover, it is more preferable that the proportion of the numbers of the cross sections of the aluminum fibers having the aspect ratio of the major axis diameter and the minor axis diameter not less than 1.2 be not less than 50% and not more than 60%: furthermore preferably, not less than 52% and not more than 58%.
If the proportion of the numbers of the cross section of the aluminum fibers having the aspect ratio of the major axis diameter and the minor axis diameter not less than 1.2 is less than 40% in the transverse cross section of the porous body, there are few aluminum fibers contributing to the disturbance effect so it is difficult to promote the effect disturbing the heat medium, accordingly, the heat exchange performance may be deteriorated. In contrast with that, if the proportion of the number of the cross sections of the aluminum fibers having the aspect ratio of the major axis diameter and the minor axis diameter is not less than 1.2 is more than 70%, a flow resistance of the heat medium increases and the pressure loss is too large.
In the heatsink of the present invention, as described above, since the sintered body of the aluminum fibers is used as the porous body, it is easy to make a direction of the aluminum fibers even or uneven intendedly: accordingly, it is possible to easily control the proportion of the number of the cross section of the aluminum fibers having the aspect ratio of the major axis diameter and the minor axis diameter in the transverse cross section is not less than 1.2.
Moreover, since it is possible to easily control the direction of the aluminum fibers, by arranging many aluminum fibers perpendicular to the longitudinal direction of the fins, there are few interfaces between the aluminum fibers which are the thermal resistance in a heat transfer path along a thickness direction of the porous body (an arranging direction of the fins) so that the heat transfer between the fins and the heat medium can be promoted; in contrast with that, by arranging many aluminum fibers parallel to the longitudinal direction of the fins, it is possible to reduce the pressure loss when the heat medium passes through inside the porous body.
For example, since a direction of a skeleton of the foam metal is isotropic in general, foamed metal cannot be promote the disturbance effect or reduce the pressure loss by changing the skeleton of the porous body intendedly as in the present invention.
In a preferred embodiment of the heatsink of the present invention, a vacant proportion that is a percentage of a vacant volume excluding metal portions of the fins and the porous-body part to a total volume obtained by a product of a height of the fins and a plane area of regions through which heat medium flows on the surface of the base board be not less than 40% and not more than 70%. The vacant proportion is more preferably not less than 45% and not more than 65%; furthermore preferably, not less than 50% and not more than 60%.
If the vacant proportion is less than 40%, the pressure loss to the flow of the heat medium is large. Meanwhile, if the vacant proportion is more than 70%, the heat exchange performance (the heat transfer coefficient) is low. Accordingly, since the vacant proportion is not less than 40% and not more than 70%, it is possible to improve the heat exchange performance and reduce the pressure loss.
In a preferred embodiment of the heatsink of the present invention, a specific surface area per a unit volume in a whole of the fins and the porous-body part be not less than 1.0×103 [m2/m3] and not more than 10.0×103 [m2/m3]. More preferably, the specific surface area be not less than 2×103 [m2/m3] and not more than 9×103 [m2/m3]: furthermore preferably, not less than 4×103 [m2/m3] and not more than 7×103 [m2/m3].
If the specific surface area of the whole of the fins and the porous body (the total surface area of the fins+the total surface area of the porous body)/(the volume of the fins+a bulk of the porous body) is less than 1.0×103 [m2/m3], the heat exchange area to the heat medium is small, the heat transfer coefficient of the heatsink is deteriorated, and the heat exchange performance may be deteriorated. In contrast with that, the specific surface area exceeds 10.0×103 [m2/m3], the pressure loss is large. Accordingly, since the specific surface area of the whole of the fins and the porous body is not less than 1.0×103 [m2/m3] and not more than 10.0×103 [m2/m3], it is possible to improve the heat exchange performance and reduce the pressure loss low.
In a preferred embodiment of the heatsink of the present invention, it is preferable that a longitudinal-section fiber density D1 [%] which is a percentage of a cross-sectional area of the aluminum fibers to an area of the grooves in a longitudinal cross section parallel to the surface of the base board be not less than 10% and not more than 40%; and a transverse-section fiber density D2 [%] which is a percentage of a cross-sectional area of the aluminum fibers to an area of the grooves in a transverse cross section parallel to an arrangement direction of the fins perpendicular to the longitudinal cross section be not less than 10% and not more than 40%. The longitudinal-section fiber density and the transverse-section fiber density are more preferably not less than 15% and not more than 35%; furthermore preferably, not less than 20% and not more than 30%.
If the longitudinal-section fiber density D1 and the transverse-section fiber density D2 are less than 10%, the heat exchange area to the heat medium is small, the heat transfer coefficient is deteriorated, and the heat exchange performance may be deteriorated. Meanwhile, if the longitudinal-section fiber density D1 and the transverse-section fiber density D2 exceed 40%, the pressure loss is large. Accordingly, since both the longitudinal-section fiber density D1 and the transverse-section fiber density D2 are not less than 10% and not more than 40%, it is possible to improve the heat exchange performance and reduce the pressure loss low.
In a preferred embodiment of the heatsink of the present invention, it is preferable that outer fins that are arranged at outermost side in the arrangement direction among the fins be arranged inside side edges of the base board; and the porous body be joined on outer side surfaces of the outer fins and the surface of the base board at outer part than the outer fins.
Not only filling the porous body in the grooves between the fins, but also joining the porous body to the outer side surfaces of the outer fins that are arranged at the outermost side in the arrangement direction among the fins arranged mutually in parallel and the surfaces of the base board at the outer part than the outer fins, it is possible to form the heatsink from the porous body having larger surface area comparing to a case in which the outer fins are arranged on both side edges of the base board. Accordingly, the heat received at the porous body can be transferred to the heat medium efficiently, and the heat exchange performance can be further improved.
According to the present invention, it is possible to promote the disturbance effect of disturbing the flow of the heat medium, so that the heat exchange performance of the heatsink can be improved.
Below, embodiments of the present invention will be explained. A heatsink 101 showing one embodiment of the present invention is provided with: a base board 11 having a flat board shape; a plurality (seven in this embodiment) of plate-like fins 12 standing on a surface (one surface) of the base board 11 and arranged with an interval mutually in parallel; and a porous-body part 200 formed from one or more porous bodies 20 having a three-dimensional mesh structure and filled in grooves 13 formed between the fins 12, as shown in
The base board 11 and the fins 12 are formed as an aluminum-formed body 10 integrally from non-porous material (solid material) of aluminum (including aluminum alloy). The porous bodies 20 are, as shown in
For example, as shown in
Here, the “longitudinal direction” in the heatsink 101 or the base board 11 means a direction along a longitudinal dimension S1 of the base board shown in
The porous bodies 20 are filled in the grooves 13 between the fins 12. The porous bodies 20 are formed along the length direction of the fins 12 so as to fill gaps between the fins 12, and as shown in
The porous bodies 20 are formed from a sintered body of an aggregate of a plurality (e.g., 20 to 4000 per 1 cm3) of the aluminum fibers 21. The aluminum fibers 21 can be used having a thickness (an outer diameter, a fiber diameter) “d” 20 μm to 3000 μm inclusive and a length 0.2 mm to 50 mm inclusive.
The porous bodies 20 shown in
In the porous body 20, as shown in
As described above, by forming the oval fiber proportion in the transverse cross section of the porous body 20 to be not less than 40%, it is possible to increase surfaces against a flow of heat medium, i.e., surfaces disturbing the flow of the heat medium. Thereby a disturbance effect of disturbing the flow of the heat medium in the porous body 20 can be easily generated.
If the oval fiber proportion in the transverse cross section of the porous body 20 is less than 40%, since the less aluminum fibers 21 are difficult to promote the disturbance effect, so that the heat exchange performance is deteriorated. In contrast, if the oval fiber proportion is more than 70%, flow resistance the heat medium is disturbed by the porous body 20 and increased, and pressure loss is excessively large. The oval fiber proportion is more preferably 45% to 65% inclusive, furthermore preferably 50% to 60% inclusive.
The aspect ratio of the major axis diameter and the minor axis diameter of the aluminum fibers 21 in the transverse cross section of the porous body 20 can be easily modified by changing a thickness (the fiber diameter “d”) of the aluminum fibers 21 or a method of filling into a mold. Specifically, because it is easy to make a direction of the aluminum fiber 21 even or uneven intendedly, the oval fiber proportion in the transverse cross section of the porous body 20 can be easily controlled. It is possible to control a magnitude of a pore proportion (a volume proportion of vacant portions, excluding solid parts of the aluminum fibers 21, in inner spaces of the grooves 13 in which the porous bodies 20 are filled) of the porous bodies 20 and a dimension of an open diameter of pores opening inside the porous bodies 20. It is also easy and possible to form the porous bodies 20 into a desired outer shape by using a forming mold having a desired shape.
Since it is easy to control the direction of the aluminum fibers 21 when manufacturing the porous bodies 20 as described above, it is also possible to arrange more aluminum fibers 21 vertical to the length direction of the fins 12 (i.e., parallel to the thickness direction of the fins 12). In this case, interfaces between the aluminum fibers 21 being the thermal resistance in a heat transfer path along the thickness direction of the porous bodies 20 (the thickness direction of the fins 12) are small, so it is possible to promote the heat transfer between the fins 12 and the heat medium. Moreover, the pressure loss while the heat medium passing through the inside of the porous bodies 20 can be reduced by arranging more aluminum fibers 21 in parallel to the length direction of the fins 12. In addition, foamed metal cannot promote the disturbance effect or reduce the pressure loss by changing a skeleton intendedly as in the porous bodies 20, since a direction of a skeleton is isotropic in general.
In the heatsink 101, a ratio of a vacant volume Vp in a total volume V is 40% to 70% inclusive (hereinafter it is denoted as a vacant proportion Vp/V); where the total volume V is obtained by a product of a plane area including the porous bodies 20 and the fins 12 and the height h1 of the fins 12, and the space volume Vp is obtained by subtracting aluminum portions (the solid portion) of the fins 12 and the porous bodies 20 from the total volume V. The vacant proportion Vp/V is more preferably 45% to 65% inclusive, furthermore preferably 50% to 60% inclusive.
The total volume V for calculating the vacant proportion Vp/V can be obtained by a product of the plane area (S1×S2) of the entire base board 11 and the height h1 of the fins 12.
In a case in which “n” numbers of the fins 12 with the thickness t1 [mm]×the height h1 [mm] are provided on the base board 11 with the longitudinal dimension S1 [mm]×the lateral dimension S2 along an entire length thereof, the total volume V [mm3] is V=S1×S2×h1. However, a relation S2=t1×n+c1×(n−1)+c3×2 is satisfied. In addition, the respective inner porous bodies 20 have the width c1 [mm], and outsides of the respective outer fins 12A have a width c3 [mm].
The pore proportion X of the porous bodies 20 is a volume proportion of vacancy portions in the space in the grooves 13 stuffed with the porous bodies 20, excluding the portions of the aluminum fibers 21 (the solid portions). The vacant volume Vp [mm3] is:
Vp=[V−t1+{2×c3+(n−1)×c1}×(1−X/100)]×S1×h1
when the heatsink 101 is formed by joining the porous bodies 20 with the pore proportion X % in the grooves 13 with the width c1 [mm] and a depth h1 [mm] and to the outside of the outer fins 12A (the width c3 [mm]). The vacant proportion is obtained as Vp/V.
In the heatsink 101, a specific surface area of a whole of the fins 12 and the porous bodies 20 per volume (a total surface area of the fins 12+the total surface area of the porous bodies 20)/(a volume of the fins 12+a bulk of the porous bodies 20) is set to not less than 1.0×103 [m2/m3] and not more than 10.0×103 [m2/m3]. The specific surface area is more preferably not less than 2.0×103 [m2/m3] and not more than 9.0×103 [m2/m3], and furthermore preferably not less than 3.0×103 [m2/m3] and not more than 8.0×103 [m2/m3].
The porous bodies 20 has a longitudinal-section fiber density D1 is 10% to 40% inclusive and a transverse-section fiber density D2 is 10% to 40% inclusive; where the longitudinal-section fiber density D1 [%] is a proportion of a sectional area of the aluminum fibers 21 in an area of the grooves 13 (an area between the fins 12) in a longitudinal section parallel to the surface of the base board 11 (a cross section along the line A-A in
It is more preferable that the longitudinal-section fiber density and the transverse-section fiber density be 15[%] to 35 [%] inclusive; and furthermore preferably, 20 [%] to 30 [%] inclusive.
The fiber densities are area proportion of the aluminum fibers 21 in the respective cross sections as described above. Specifically, the transverse-section fiber density D2 is obtained by calculating a proportion of a sectional area of the aluminum fibers 21 in a whole area in the transverse cross section of the porous bodies 20 shown in
Although the illustration is omitted, the longitudinal-section fiber density D1 is obtained by calculating a proportion of a section area of the aluminum fibers 21 in a whole area obtained by a product (S1×c1) of the length of the fins 12 (the longitudinal dimension S1 of the base board 11) and the interval c1 between the fins 12, in the longitudinal cross section of the porous bodies 20 (a cross section taken along the line A-A shown in
The higher the fiber densities are, the more the flow resistance of the heat medium, so that the pressure loss is tend to increase though; meanwhile, the disturbance effect is easy to occur and the heat transfer performance is easy to be improved. If the longitudinal-section fiber density D1 and the transverse-section fiber density D2 are less than 10%, a heat exchange area to the heat medium is decreased since the pore proportion of the porous bodies 20 is increased. Accordingly, the thermal conductivity is deteriorated, and there is a fear that the heat transfer coefficient of the heatsink 101 may be deteriorated. If the longitudinal-section fiber density D1 and the transverse-section fiber density D2 is more than 40%, the flow resistance of the heat medium is increased and the pressure loss is increased.
From this point of view, it is desirable that the longitudinal-section fiber density D1 and the transverse-section fiber density D2 be 15% to 35% inclusive. The pore proportion X of the porous bodies 20 is a vacant volume which excludes the aluminum fibers 21 (the solid portions) in the whole volume obtained by a product of the plane area (the longitudinal dimension S1×the interval c1) of a region through which the heat medium flows in the grooves 13 and the height h1 of the fins 12.
In a case of manufacturing the heatsink 101 structured as above, the aluminum-formed body 10 of non-porous material is formed to have the base board 11 and the fins 12 integrally by extrusion molding of aluminum for example, and the porous bodies 20 are joined in the grooves 13 between the fins 12 by using a mold 51 shown in
The mold 51 is made of material such as carbon and the like, which does not easily react with aluminum of the aluminum-formed body 10 and the porous bodies 20, and as shown in
Aggregates 23 of the aluminum fibers 21 are arranged beforehand in the grooves 13 between the fins 12 forming the spaces 53, then the aluminum-formed body 10 and the mold 51 are piled, so that the spaces 53 are stuffed with the aggregates 23 of the aluminum fibers 21. Then, by heating them in inert atmosphere with temperature of 600° C. to 660° C. for 0.5 minutes to 60 minutes for example, the porous bodies 20 in which the aluminum fibers 21 are sintered at the contact points 21a to each other are formed, and the aluminum fibers 21 and the aluminum-formed body 10 (the fins 12 and the base board 11) are sintered so that the sintered-joint portions 22 are formed. Thereby obtained is the heatsink 101 in which the porous bodies 20 and the aluminum-formed body 10 are integrally joined with the sintered-joint portions 22.
In the heatsink 101 structured as above, the porous bodies 20 are respectively filled in the grooves 13 between the fins 12 of the aluminum-formed body 10, so that the heat transfers through a broad area of the fins 12 and the base board 11 (the aluminum-formed body 10). Moreover, since the porous bodies 20 are joined on the fins 12 and the base board 11 with the sintered-joint portions 22, the heat resistance is small at the joint interfaces of the porous bodies 20 and the fins 12 and the base board 11, so that the heat can be smoothly transferred between the base board 11 and the fins 12 and the porous bodies 20.
The heat medium flows through the vacant spaces in the porous bodies 20, so that the heat transmission is carried out between the heat medium and the respective surfaces of the porous bodies 20, the fins 12 and the base board 11. In this case, since the large surface area is formed in the heatsink 101 by the porous bodies 20, the heat received by the porous bodies 20 moves efficiently to the heat medium, so that an excellent heat transmission performance can be obtained. Moreover, the porous bodies 20 obstruct the flows of the heat medium, so that the flows of the heat medium can be disturbed. Accordingly, in comparison with a heatsink which is made only from non-porous material, there is an effect of promoting the heat transmission in addition to an effect of the large specific surface area.
As described above, since the porous bodies 20 are formed from the sintered bodies of the aluminum fibers 21, less eutectic elements which deteriorate the thermal conductivity are dispersed unlike in foamed metal, so that the higher thermal conductivity can be obtained than the foamed metal. Moreover, the porous bodies 20 has high flexibility of product design because magnitude of the pore percentage, opening size of the pores opening inside and the like can be freely modified only by changing thickness or the filling method of the aluminum fibers 21. Furthermore, the porous bodies can be easily formed into a desired outer shape by using a forming die formed to have the desired shape.
The porous bodies 20 are joined to the fins 12 and the base board 11 by the sintered-joint portions 22 and brazing material is not used, the pore proportion of the porous bodies 20 is not decreased by permeation of the brazing material.
In the heatsink 101 of the present embodiment, the oval fiber proportion at the transverse cross section of the porous bodies 20 is 40% to 70% inclusive, so increased are the surfaces against the direction of the flow of the heat medium (the length direction of the fins 12), in other words, the surfaces disturbing the flow of the heat medium. Thereby the disturbance effect of disturbing the flow of the heat medium is easily obtained in the porous bodies 20, and the heat exchange with respect to the heat medium is further promoted.
Moreover, as described above, in the aluminum fibers 21 structuring the pore bodies 20, it is easy to make the direction of the fibers even or uneven intendedly, so that the oval fiber proportion in the transverse cross section of the porous bodies 20 can be easily controlled.
Moreover, in the heatsink 101 of the present embodiment, since the vacant proportion is set to 40% to 70% inclusive as described above, it is possible to improve the heat exchange performance with reducing the increase of the pressure loss. If the vacant proportion is less than 40%, the pressure loss is large with respect to the flow of the heat medium: if the vacant proportion is more than 70%, the heat exchange performance is deteriorated.
The specific surface area of the fins 12 and the porous bodies 20 in total is set to not less than 1.0×103 [m2/m3] and not more than 10.0×103 [m2/m3], so that there are effects of improving the heat exchange performance and the reduction of the pressure loss. If the specific surface area is less than 1.0×103 [m2/m3], the heat exchange performance is deteriorated resulting from reduction of a heat exchange area: if it is more than 10×103 [m2/m3], an increase of the pressure loss is incurred.
Moreover, as described above, since both the longitudinal-section fiber density D1 and the transverse-section fiber density D2 are 10% to 40%, the heat exchange performance can be improved and the pressure loss can be reduced low. If the longitudinal-section fiber density D1 and the transverse-section fiber density D2 are less than 10%, the heat exchange area with the heat medium is reduced, so that the heat transfer coefficient is reduced and the heat exchange performance may be deteriorated. If the longitudinal-section fiber density D1 and the transverse-section fiber density D2 are more than 40%, the pressure loss is increased.
As examples of the present invention, the heatsinks 101 (Sample Nos. 1 to 8) having the plate like fins 12 were made as in the above-mentioned embodiment shown in
As a Comparative Example (Sample No. 9), a heatsink 201 in which a porous body was not provided but made only of the aluminum-formed body 10 having the base board 11 and the plate like fins 12 was made as shown in
As a Comparative Example (Sample No. 10), a pin-fin type heatsink 202 having pin like fins 15 was made as shown in
The aluminum formed bodies 10 and 16 and the porous body 20 were made by using A1050 (pure aluminum of 99.50% or more of Al component) as material. The porous body 20 was made with various factors (a fiber diameter, a pore proportion, a fiber density and the like) shown in Table 1 and Table 2.
The pore proportion X of the porous body 20 was calculated from a calculation formula of: the pore proportion X={c1×h1×S1−(m/p)}/(c1×h1×S1), where fiber weight is “m” [g] and specific fiber gravity is “ρ” [g/cm3] of aluminum fibers 21 in the porous body 20 filled in one of the grooves 13.
Vacant proportions of the respective heatsinks were calculated based on the pore proportion X of the porous body 20, where the heat exchange was performed between the heat medium and a whole surface of the base board 11 and 14 on which the fins 12 and 15 were stand (the total volume V=S1×S2×h1 or V=S1×S2×h2).
The longitudinal-section fiber density D1 and the transverse-section fiber density D2 of the porous body 20 were calculated as follows. Colorless and transparent resin (specifically, epoxy resin) was filled in the grooves 13 in which the porous bodies 20 are fixed, i.e., between the fins 12 (the space in the porous bodies 20): longitudinal sectional surfaces of the porous bodies 20 cut in a longitudinal direction at a position of 4 mm from a tip of the fins 12 were polished; and transverse sectional surfaces of the porous bodies 20 cut in the transverse direction at three positions divided into four in the longitudinal direction were polished: and images of the sectional surfaces were taken by a microscope. With respect to the images, by binarizing the aluminum fibers 21 and the space in the porous bodies 20 using an image analysis software (WinROOF made by Mitani Corporation), fiber density [%] was measured.
A total number of cross sections of the aluminum fibers 21 was counted observed in the images of the transverse section on the three positions of the porous bodies 20; and a major axis diameter and a minor axis diameter of the cross sections of the aluminum fibers 21 were measured by a scale. An aspect ratio of the major axis diameter and the minor axis diameter of the aluminum fibers 21 was calculated, a number of the relatively oval cross sections of the aluminum fibers 21 with the aspect ratio of not less than 1.2 was counted; and the ratio (an oval fiber proportion) was obtained.
With respect to the aluminum fibers 21 in which the aspect ratio of the major axis diameter and the minor axis diameter is less than 1.05, a mean value of the major axis diameter of the aluminum fibers 21 was obtained to be the fiber diameter “d” (a thickness) of the aluminum fibers 21 structuring the porous bodies 20.
The specific surface area of the whole of the fins 12 and the porous bodies 20 of the heatsink 101, the specific surface area of the fins 12 of the heatsink 201, and the specific surface area of the fins 15 of the heatsink 202 were respectively calculated from the following formulas.
The surface area of the fins 12
A1=S1×{(12×h1)+(5×c1)+(2×c3)}
The surface area of the fins 15
A2=S1×S2−π×(2.3×10−3)2×N+π×(2.3×10−3)h2×N
(here, “N” is a number of pins)
The surface area of the porous bodies 20
A3=4×[{(5×c1)+(2×c3)}×h1×S1×{1−(X/100)}]/d
The heatsink 101 (Sample Nos. 1 to 8)
Volume V1=S1×S2×h1
Specific surface area of the whole of the fins 12 and the porous bodies 20 (A1+A3)/V1
The heatsink 201 (Sample No. 9)
Volume V1=S1×S2×h1
Specific surface area of the fins 12 A1/V1
The heatsink 202 (Sample No. 10)
Volume V2=S1×S2×h2
Specific surface area of the fins 15 A2/V2
The pressure loss was measured as follows using a coolability measuring device in which the heat medium (water) flows one direction. The heatsinks 101, 201 and 202 were fitted to the measuring device, the heat medium of 30° C. was flown to the fins 12 and 15 at a volume flow rate of 4 L/min (constant), and differential pressure before and after the heatsinks 101, 201 and 202 was measured as the pressure loss. The heat medium was flown in the longitudinal direction of the base boards 11 and 14 (a longitudinal direction of the fins 12 in a case of the plate-fin type heatsinks 101 and 201).
The heat transfer coefficients (the heat exchange performance) H of the heatsinks were measured as follows, using the coolability measuring device used in measuring the pressure loss. At center parts on the base boards 11 and 14 of the heatsinks 101, 201 and 202 (on opposite surfaces to the fins 12 and 15), soft heat radiation grease, cooled members (heat-generating elements) and heat insulation member were piled in order; the cooled members were press-joined at 50 cm·N by a pressing tool.
In a laboratory controlled at a constant temperature (30° C.), the heat medium (water) of 30° C. was flown at 4 L/min (constant) to the fins 12 and 15 for 5 minutes: after confirming that the temperature of the cooled members (temperature before heat generation) was steady, the cooled members generated heat for 15 minutes at electric power of 450 W, and temperature Tb1 at an interface of the cooled members joined on the center parts of the base boards 11 and 14 and the base boards 11 and 14 and water temperature Tw were measured. Then, using the temperature Tb1, temperature Tb2 at an interface of the heat medium (water) and the base boards 11 and 14 was calculated by a formula of Tb2=[Tb1−{450×h0/(A×k)}]. Here, “h0” is a thickness of the base boards 11 and 14; “A” is a mounting area of the cooled member to the base boards 11 and 14; and “k” is a heat transfer coefficient of A1050 (aluminum).
From a formula H=[450/{A×(Tb2−Tw)}], using the calculated temperature Tb2, the heat transfer coefficients H of the respective heatsinks were calculated and evaluated as parameters of the heat exchange performance of the heatsinks 101, 201 and 202. That is to say, larger the heat transfer coefficient H, it can be evaluated as a heatsink having an excellent heat exchange performance.
Results of them are shown in Tables 1 to 3. Since Sample Nos. 9 and 10 are the heatsinks 201 and 202 that are formed only from the aluminum formed bodies 10 and 16 with which the porous bodies are not provided, items regarding the porous bodies in Tables 1 to 3 were denoted by “-”
As recognized from these results, Sample Nos. 1 to 8 of Examples of the present invention having the porous bodies 20 could obtain higher heat transfer coefficient in comparison with Sample Nos 9 and 10 which were not provided with the porous body. In Sample Nos. 1 to 8 of Examples of the present invention, the vacant proportion was 40% to 70% inclusive, the specific surface area per unit volume in the whole of the fins 12 and the porous bodies 20 was 1.0×103 m2/m3 to 10.0×103 m2/m3 inclusive, and the fiber densities D1 and D2 were 10% to 40% inclusive: the heat transfer coefficient was maintained high and the pressure loss was reduced low.
Among Examples 1 to 8 of the present invention, in Sample Nos 1, 3 and 5 to 8 in which the oval fiber proportion in the transverse section of the porous bodies 20 was 40% to 70% inclusive, a balance of the heat transfer coefficient and the pressure loss was especially good, so that the increase of the pressure loss was restrained, and the the high heat transfer coefficient could be maintained efficiently.
The present invention is not limited to the above-described embodiments and various modifications may be made without departing from the scope of the present invention.
For example, the porous bodies are formed in the grooves between the fins in the above embodiment though, it may be provided so as to cover also on tips of the fins. In that case, a height of fins includes a thickness of porous bodies at the tips of the fins. In the above embodiment, it was explained that the fins, the base board and the porous bodies were structured by A1050 though: it is not limited to this, other aluminum or aluminum alloys may structure them. Moreover, the fins, the base board and the porous bodies may be structured from aluminum (aluminum alloys) with different purity respectively.
The heat exchange performance of the heatsink can be improved.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2017-149843 | Aug 2017 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2018/028835 | 8/1/2018 | WO | 00 |
