heat sink

Abstract

The present application provides a heat sink. The heat sink comprises a substrate (1) and fins, wherein a plurality of fins are arranged at intervals on the substrate (1), and each fin is provided with a flow hole, wherein the fin forms a preset angle with the direction of the airflow, and along the direction of the airflow, the fin comprises a head end fin (2) that first contacts the airflow and a terminal fin (3) that last contacts the airflow, the flow hole located on the head end fin (2) is the head end flow hole (4), the flow hole located on the terminal fin (3) is the terminal flow hole (5), the flow hole between the head end flow hole (4) and the terminal flow hole (5) is the middle flow hole (6), and the middle flow holes (6) are all located on the center line connecting the head end flow hole (4) and the terminal flow hole (5). According to the heat sink of the present application, the laminar flow state on the fin surface of the heat sink can be broken, the air flow field between the fins and around the fins can be improved, and the heat dissipation efficiency of the heat generating components can be enhanced.

Description

Technical Field

[0001] The present application relates to the field of heat dissipation technology, and in particular to a heat sink. Background Art

[0002] At present, due to the popularity of intelligence and integration, many electronic components generate high heat, but are compactly placed on the same circuit board. In order to ensure the long-term reliability of components and the normal operation of equipment, adding heat dissipation devices is an effective method.

[0003] The current heat dissipation methods include: using heat sink fins to dissipate heat from heat generating components, or using a combination of fans and fins to dissipate heat. However, due to the placement of the fins and heat generating components and the influence of the wind field between the fins, the heat dissipation efficiency of the radiator is low, the fin surface is in a laminar state, the air flow rate is low, the heat exchange is insufficient, and the temperature of the heat generating module continues to run at a high temperature, which has a great impact on the use of the equipment and also has a great impact on the reliability of the components. Summary of the invention

[0004] Therefore, the technical problem to be solved by the present application is to provide a heat sink that can break the laminar flow state on the fin surface of the heat sink, improve the air flow field between and around the fins, and enhance the heat dissipation efficiency of the heat-generating components.

[0005] In order to solve the above problems, the present application provides a heat sink, including a substrate and fins, a plurality of fins are arranged at intervals on the substrate, and each fin is provided with a flow hole, the fin and the direction of the airflow form a preset angle, along the direction of the airflow, the fin includes a head fin that first contacts the airflow and an end fin that last contacts the airflow, the flow hole located on the head fin is the head flow hole, the flow hole located on the end fin is the end flow hole, the flow hole between the head flow hole and the end flow hole is the intermediate flow hole, and the intermediate flow holes are all located on the center line connecting the head flow hole and the end flow hole.

[0006] Preferably, the angle between the center line and the first plane is θ1,

[0007]

[0008] The first plane is a plane perpendicular to both the windward surface of the fin and the surface of the base plate, Z1 is the distance between the center of the head end flow hole and the second plane, the second plane is a plane parallel to the first plane, passes through the heat source area and has the largest distance to the center of the head end flow hole, Z2 is the distance between the center of the head end flow hole and the third plane, the third plane is a plane parallel to the first plane, passes through the heat source area and has the smallest distance to the center of the head end flow hole, t is the value angle of θ1, L is the distance between the windward side of the head end fin and the heat source area, and D is the effective diameter of the flow hole.

[0009] Preferably, the projections of all the flow holes in the direction along the center line have overlapping figures, the minimum distance between the overlapping figures and the center line is D1, and the maximum distance is D2, wherein D∈[D1, D2].

[0010] Preferably, the projections of all the flow holes in the direction along the center line have an overlapping figure, the overlapping figure has a center of gravity G, and the effective diameter value D of the flow hole is between the minimum distance and the maximum distance between the center of gravity G and the overlapping figure.

[0011] Preferably, the angle between the center line and the surface of the substrate is θ2,

[0012]

[0013] Wherein f(x) is the distance between the flow hole and the plate surface of the substrate away from the fins, X is the overall width of the radiator, Y is the overall height of the radiator, P is the heat generated by the heat source area, W is the maximum heat exchange of the radiator, D is the effective diameter value, y1 is the distance between the head end flow hole and the plate surface of the substrate away from the fins, y2 is the distance between the head end flow hole and the plate surface of the substrate where the fins are installed, x1 is the distance between the heat source area and the head end fin in the arrangement direction of the fins, and x2 is the length of the heat source area in the arrangement direction of the fins.

[0014] Preferably, the middle flow hole is located in the shuttle-shaped area, wherein two end points of the shuttle-shaped area are respectively the centers of the first end flow hole and the terminal end flow hole.

[0015] Preferably, the shuttle-shaped region is formed by combining a first conical region and a second conical region, wherein the first conical region is a conical region formed with the center of the head flow hole as the origin, a%θ1 as the cone angle, and the center line as the rotation axis, and the second conical region is a conical region formed with the center of the end flow hole as the origin, a%θ1 as the cone angle, and the center line as the rotation axis.

[0016] Preferably, the middle flow hole is located in the shuttle-shaped area, wherein the two endpoints of the shuttle-shaped area are the centers of the head flow hole and the tail flow hole respectively, and the shuttle-shaped area is formed by combining the first conical area and the second conical area, wherein the first conical area is a conical area formed by taking the center of the head flow hole as the origin, b%θ2 as the cone angle, and the center line as the rotation axis, and the second conical area is a conical area formed by taking the center of the tail flow hole as the origin, b%θ2 as the cone angle, and the center line as the rotation axis.

[0017] Preferably, a≤40, preferably, a≤30.

[0018] Preferably, the heat source region is a region where the heat flux density of the substrate is used as the heat dissipation object, and the equipotential surface is drawn for the heat flux density value, and the heat flux density of the lowest equipotential surface and the heat flux density of the highest equipotential surface account for 5% to 100%.

[0019] The heat sink provided by the present application includes a substrate and fins. A plurality of fins are arranged at intervals on the substrate. Each fin is provided with a flow hole. The fin and the direction of the airflow form a preset angle. Along the direction of the airflow, the fin includes a head fin that first contacts the airflow and a terminal fin that last contacts the airflow. The flow hole located on the head fin is the head flow hole, the flow hole located on the terminal fin is the terminal flow hole, the flow hole between the head flow hole and the terminal flow hole is the middle flow hole, and the middle flow holes are all located on the center line of the head flow hole and the terminal flow hole. The present application changes the airflow flow mode of the heat sink, so that the direction of the airflow is not along the extension direction of the fin, but along the arrangement direction of the flow holes, so that the airflow can effectively change the flow state of the airflow in the process of flowing along the flow holes, thereby breaking the laminar state on the fin surface of the heat sink, improving the air flow field between the fins and around the fins, and enhancing the heat dissipation efficiency of the heat-generating components. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 A diagram showing the distribution structure of flow holes of a heat sink in a top view according to an embodiment of the present application;

[0021] Figure 2 A diagram showing the distribution structure of flow holes of a heat sink in a front view according to an embodiment of the present application;

[0022] Figure 3 A schematic diagram of the range of the flow hole setting area of ​​the radiator according to an embodiment of the present application;

[0023] Figure 4 A diagram of the process of determining the effective diameter value of the flow hole of the heat sink according to an embodiment of the present application.

[0024] The reference numerals are:

[0025] 1. Base plate; 2. First end fin; 3. End fin; 4. First end flow hole; 5. End flow hole; 6. Middle flow hole; 7. Heat source area. DETAILED DESCRIPTION

[0026] See also Figures 1 to 4 As shown, according to an embodiment of the present application, a heat sink includes a substrate 1 and fins, a plurality of fins are arranged at intervals on the substrate 1, and each of the fins is provided with a flow hole, the fins form a preset angle with the direction of the airflow, and along the direction of the airflow, the fins include a head end fin 2 that first contacts the airflow and an end fin 3 that last contacts the airflow, the flow hole located on the head end fin 2 is the head end flow hole 4, the flow hole located on the end fin 3 is the end flow hole 5, the flow hole between the head end flow hole 4 and the end flow hole 5 is the middle flow hole 6, and the middle flow holes 6 are all located on the center line OF of the head end flow hole 4 and the end flow hole 5.

[0027] The present application changes the airflow pattern of the radiator so that the direction of the airflow is not along the extension direction of the fins, but along the arrangement direction of the flow holes. Therefore, the main flow channel of the airflow is not the gap between adjacent fins, but the flow holes. As a result, the airflow can effectively change the flow state in the process of flowing along the flow holes, thereby breaking the laminar state on the fin surface of the radiator, improving the air flow field between and around the fins, and enhancing the heat dissipation efficiency of the heat-generating components.

[0028] In the present application, after the airflow enters the fin along the flow hole, it will be continuously blocked by the fins during the process of flowing in the flow hole in sequence. Therefore, part of the airflow will flow through the flow hole and reach the next flow hole, and the other part of the airflow will enter the gap between the fin where the flow hole is located and the fin where the next flow hole is located, and then flow along the fin gap. After the airflow passes through the last flow hole, there will be two situations. One situation is that the flow hole runs through all the fins. At this time, the airflow leaves the radiator after passing through the flow hole and takes away the heat of the radiator; the other situation is that the flow hole passes through some fins, and no flow hole is set on the other part of the fins. At this time, after the airflow passes through the flow hole, it will be blocked at the next fin position, and then flow around along the gap between the fin and the previous fin, taking away the heat of the radiator.

[0029] Since the airflow enters the fin gap from the flow hole and then flows around along the fin gap, it is different from the existing heat dissipation method in which the airflow flows from the fin to the other side. The airflow in the present application disperses from the flow hole, the airflow path is shorter, and it is easier to bring out the heat. In addition, since this airflow flows from the flow hole to the surroundings and is blocked by the fins, this flow can break the laminar state on the fin surface, improve the air flow field between and around the fins, and enhance the heat dissipation efficiency of the heat-generating components.

[0030] The above-mentioned preset angle is an angle greater than 0°. Preferably, the preset angle is greater than or equal to 45°, preferably 90°, that is, the airflow flows in a direction perpendicular to the fin surface, thereby ensuring that the airflow mainly enters the fin from the flow hole, thereby ensuring the flow effect of the airflow.

[0031] In the present application, preferably, in order to ensure the flow effect of the airflow, the area and / or shape of at least some of the flow holes are different, so that the airflow will inevitably collide with the fins during the flow process, ensuring that the airflow can generate turbulence and improve the heat exchange effect between the airflow and the fins. In this case, the preset angle can be 90 degrees. Since the area or shape of the flow holes through which the airflow flows changes during the flow process, it can ensure that the airflow collides with the fins, thereby effectively ensuring the flow effect of the airflow.

[0032] In the present application, preferably, in order to ensure the flow effect of the airflow, the airflow can also flow in a direction inclined relative to the fin surface, that is, the center line OF of the head flow hole and the end flow hole is inclined relative to the fin surface. In this case, the area and / or shape of all the flow holes can be different, or the area and shape of all the holes can be the same. Since the flow holes are set along the inclined direction, even if the area and shape of all the flow holes are the same, as long as the flow direction of the airflow is controlled not to be parallel to the center line OF of the head flow hole and the end flow hole, the effect desired to be achieved by the present application can still be achieved.

[0033] By adopting the above-mentioned scheme of the present application, turbulence can be generated in the airflow near the heat source. The heat exchange is not enhanced simply by increasing the heat exchange area, but the flow pattern of the airflow is changed. In this way, the average temperature of the heating module of the unit can be reduced by 5°C and the maximum temperature can be reduced by 16°C.

[0034] The above-mentioned flow holes can be circular holes, elliptical holes, strip holes or polygonal holes, or a combination of holes of various shapes, that is, the flow holes on different fins have different shapes, or at least the flow holes on some fins have different shapes.

[0035] Preferably, the flow hole on each fin is a single hole, which can ensure the singleness of the flow direction of the airflow along the flow hole.

[0036] In one embodiment of the present application, the angle between the center line OF and the first plane is θ1,

[0037]

[0038] The first plane is a plane perpendicular to both the windward side of the fin and the plate surface of the substrate 1, Z1 is the distance between the center of the head end flow hole 4 and the second plane, the second plane is parallel to the first plane, passes through the heat source area 7 and has the largest distance from the center of the head end flow hole 4, Z2 is the distance between the center of the head end flow hole 4 and the third plane, the third plane is parallel to the first plane, passes through the heat source area 7 and has the smallest distance from the center of the head end flow hole 4, t is the value angle of θ1, L is the distance between the windward side of the head end fin 2 and the heat source area 7, and D is the effective diameter of the flow hole. The value of L is between the maximum distance and the minimum distance between the windward side of the head end fin 2 and the heat source area 7, or is the maximum distance or the minimum distance.

[0039] In the top view of the radiator, the center of the initial head-end flow hole 4 is located outside the heat source area 7, and the center line OF of the head-end flow hole 4 and the terminal flow hole 5 is inclined from the center of the head-end flow hole 4 toward the heat source area 7, and passes through the central area of ​​the heat source area 7, so that the fins located below the central area of ​​the heat source area 7 are all distributed with flow holes, which can form a more effective heat dissipation for the heat source area 7 and improve the heat dissipation effect. Preferably, the terminal flow hole 5 is also located outside the heat source area 7, so as to ensure that the entire heat source area 7 can be cooled by the flow hole 7, thereby improving the overall cooling effect of the heat source area 7.

[0040] The effective diameter of the flow hole is the effective area that the airflow can pass through when it flows through all the flow holes, which is equivalent to the diameter of the circular hole, and represents the effective flow area of ​​the airflow after passing through all the flow holes.

[0041] In one embodiment, the projections of all the flow holes in the direction along the center line OF have an overlapping figure, and the overlapping figure is the effective flow cross-section of the airflow. It is assumed that the minimum distance between the overlapping figure and the center line OF is D1, and the maximum distance is D2, where D∈[D1, D2]. Since the minimum distance between the overlapping figure and the center line OF is D1, and the maximum distance is D2, when the overlapping figure formed is a circle, D=D1=D2, and when the overlapping figure formed is a spliced ​​figure of multiple figures, the effective area of ​​the overlapping figure is between the area of ​​the circle with D1 as the diameter and the area of ​​the circle with D2 as the diameter, that is, the value of D is between D1 and D2.

[0042] See also Figure 4 As shown, in another embodiment, the projections of all the flow holes in the direction along the center line OF have an overlapping figure, the overlapping figure has a center of gravity G, and the effective diameter value D of the flow hole is located between the minimum distance D1 and the maximum distance D2 between the center of gravity G and the overlapping figure, and includes two endpoints, that is, D∈[D1, D2]. The method of determining the effective diameter value in this embodiment is roughly the same as that in the previous embodiment, the difference is that the center of the effective diameter value D selected by the two may be different.

[0043] By the above method, the effective diameter of the flow holes can be effectively determined, and then the accurate angle θ1 can be determined, so that the flow holes can be arranged along the optimal angle, ensuring that the heat sink has the best heat dissipation effect for the heat dissipation area 7.

[0044] After determining the effective diameter of the flow hole, the optimal volume of the effective cavity formed by the flow hole can be determined to be πD / 22*H, where H is the length of the center line OF of the head end flow hole 4 and the end flow hole 5. The optimal volume of the effective cavity ranges between πD / 22*H1 and πD / 22*H2, where H1 is the minimum overall width of the fin with the flow hole, and H2 is the diagonal length of the three-dimensional structure formed by the fin with the flow hole.

[0045] In another embodiment of the present application, the angle between the center line OF and the surface of the substrate 1 is θ2.

[0046]

[0047] Wherein f(x) is the distance between the flow hole and the plate surface of the substrate 1 away from the fins, X is the overall width of the radiator, Y is the overall height of the radiator, P is the heat generated by the heat source area 7, W is the maximum heat exchange of the radiator, D is the effective diameter value, y1 is the distance between the head end flow hole 4 and the plate surface of the substrate 1 away from the fins, y2 is the distance between the head end flow hole 4 and the plate surface of the substrate 1 where the fins are installed, x1 is the distance between the heat source area 7 and the head end fin 2 in the arrangement direction of the fins, and x2 is the length of the heat source area 7 in the arrangement direction of the fins.

[0048] In this embodiment, in order to ensure that the flow holes can be opened in a suitable area and ensure the flow effect of the airflow, in one embodiment, the middle flow hole 6 is located in a shuttle-shaped area, wherein the two end points of the shuttle-shaped area are respectively the centers of the head flow hole 4 and the end flow hole 5.

[0049] Specifically, the shuttle-shaped region is formed by combining a first conical region and a second conical region, wherein the first conical region is a conical region formed by taking the center of the head end flow hole 4 as the origin, a%θ1 as the cone angle, and the center line OF as the rotation axis, and the second conical region is a conical region formed by taking the center of the end flow hole 5 as the origin, a%θ1 as the cone angle, and the center line OF as the rotation axis.

[0050] In another embodiment, the intermediate flow hole 6 is located in a shuttle-shaped area, wherein the two endpoints of the shuttle-shaped area are the centers of the head flow hole 4 and the tail flow hole 5, respectively, and the shuttle-shaped area is formed by combining a first conical area and a second conical area, wherein the first conical area is a conical area formed by taking the center of the head flow hole 4 as the origin, b%θ2 as the cone angle, and the center line OF as the rotation axis, and the second conical area is a conical area formed by taking the center of the tail flow hole 5 as the origin, b%θ2 as the cone angle, and the center line OF as the rotation axis.

[0051] Regardless of the shape of the flow hole, it is preferred that the shape does not exceed the range of the above-mentioned tapered area.

[0052] The above-mentioned a≤40, that is, the flow holes are all located in the shuttle-shaped area formed by the rotation of the center line OF of the head end flow hole 4 and the tail end flow hole 5 after the deflection of ±20%θ1.

[0053] Preferably, a≤30, which can further limit the setting area of ​​the flow hole, thereby further accurately determining the setting position of the flow hole and further improving the heat dissipation effectiveness of the flow hole.

[0054] The above-mentioned b≤40, preferably, b≤30.

[0055] Since the flow holes are all located within the shuttle-shaped area, the setting position and size of the flow holes can be accurately defined to avoid the flow holes deviating too far from the center line OF and reducing the effective flow area of ​​the airflow, and to avoid the flow holes being too large and causing adverse effects on the function of the flow holes.

[0056] In this embodiment, the heat source region 7 is a region where the heat flux density of the substrate 1 is used as the heat dissipation object, and the heat flux density is plotted as an equipotential surface, wherein the heat source region 7 is a region where the heat flux density of the equipotential surface accounts for 5% to 100% of the heat flux density of the highest equipotential surface. Figure 1 For example, when the heat source area is a rectangular area, the maximum heat flux density equipotential line of the heat source area 1 is the line connecting the centers of the two opposite sides of the rectangular area, and L is the distance between the windward side of the head end fin 2 and the maximum heat flux density equipotential line of the heat source area 7.

[0057] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0058] The above are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present application shall be included in the protection scope of the present application. The above are only preferred implementations of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present application, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. A radiator, characterized in that: It comprises a base plate (1) and fins, wherein a plurality of fins are arranged at intervals on the base plate (1), and each fin is provided with a flow hole, wherein the fin forms a preset angle with the direction of the airflow, and along the direction of the airflow, the fin comprises a head end fin (2) which first contacts the airflow and a tail end fin (3) which last contacts the airflow, the flow hole located on the head end fin (2) is the head end flow hole (4), the flow hole located on the tail end fin (3) is the tail end flow hole (5), the flow hole between the head end flow hole (4) and the tail end flow hole (5) is the middle flow hole (6), and the middle flow holes (6) are all located on the center line connecting the head end flow hole (4) and the tail end flow hole (5); The angle between the center line and the first plane is θ1, The first plane is a plane perpendicular to both the windward side of the fin and the plate surface of the substrate (1); Z1 is the distance between the center of the head end flow hole (4) and the second plane; the second plane is a plane parallel to the first plane, passing through the heat source area (7) and having the largest distance from the center of the head end flow hole (4); Z2 is the distance between the center of the head end flow hole (4) and the third plane; the third plane is a plane parallel to the first plane, passing through the heat source area (7) and having the smallest distance from the center of the head end flow hole (4); t is the value angle of θ1; L is the distance between the windward side of the head end fin (2) and the heat source area (7); and D is the effective diameter of the flow hole; the effective diameter of the flow hole is the effective area that can be passed through when the airflow passes through all the flow holes, which is equivalent to the diameter of the circular hole.

2. The heat sink according to claim 1, characterized in that: The projections of all the through-holes in the direction along the center line have overlapping figures, the minimum distance between the overlapping figures and the center line is D1, and the maximum distance is D2, where D∈[D1, D2].

3. The heat sink according to claim 1, characterized in that: The projections of all the flow holes in the direction along the center line have an overlapping figure, and the overlapping figure has a center of gravity G. The effective diameter value D of the flow hole is located between the minimum distance and the maximum distance between the center of gravity G and the overlapping figure.

4. The radiator according to any one of claims 1 to 3, characterized in that: The angle between the center line and the surface of the substrate (1) is θ2, Wherein f(x) is the distance between the flow hole and the plate surface of the substrate (1) away from the fins, X is the overall width of the radiator, Y is the overall height of the radiator, P is the heat generated by the heat source area (7), W is the maximum heat exchange capacity of the radiator, D is the effective diameter of the flow hole, y1 is the distance between the head end flow hole (4) and the plate surface of the substrate (1) away from the fins, y2 is the distance between the head end flow hole (4) and the plate surface of the substrate (1) where the fins are installed, x1 is the distance between the heat source area (7) and the head end fin (2) in the arrangement direction of the fins, and x2 is the length of the heat source area (7) in the arrangement direction of the fins.

5. The heat sink according to claim 1, characterized in that The middle flow hole (6) is located in the shuttle-shaped area, wherein the two end points of the shuttle-shaped area are respectively the centers of the first end flow hole (4) and the end end flow hole (5).

6. The heat sink according to claim 5, characterized in that: The shuttle-shaped region is formed by combining a first conical region and a second conical region, wherein the first conical region is a conical region formed by taking the center of the head end flow hole (4) as the origin, a%θ1 as the cone angle, and the center line as the rotation axis, and the second conical region is a conical region formed by taking the center of the end flow hole (5) as the origin, a%θ1 as the cone angle, and the center line as the rotation axis.

7. The heat sink according to claim 4, characterized in that: The intermediate flow hole (6) is located in a shuttle-shaped area, wherein the two endpoints of the shuttle-shaped area are respectively the centers of the head flow hole (4) and the tail flow hole (5), and the shuttle-shaped area is formed by combining a first conical area and a second conical area, wherein the first conical area is a conical area formed by taking the center of the head flow hole (4) as the origin, taking b%θ2 as the cone angle, and taking the center line as the rotation axis, and the second conical area is a conical area formed by taking the center of the tail flow hole (5) as the origin, taking b%θ2 as the cone angle, and taking the center line as the rotation axis.

8. The heat sink according to claim 6, characterized in that a≤40。 9. The heat sink according to claim 8, characterized in that: a≤30。 10. The radiator according to claim 1 or 3, characterized in that: The heat source region (7) is a region where the heat flux density of the substrate (1) is used as the heat dissipation object, and an equipotential surface is drawn for the heat flux density value, and the heat flux density of the lowest equipotential surface and the heat flux density of the highest equipotential surface account for 5% to 100%.

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