A method for heat dissipation using porous fins

Abstract

The present invention relates to a porous fin heat dissipation method, which belongs to the field of heat dissipation and cooling. The porous fin heat dissipation device comprises a plurality of fin units, which are arranged side by side. The fin units comprise a base and a fin, one end of the fin is fixedly connected to one end of the base, both sides of each base are fixedly connected to one side of an adjacent base, and a plurality of through holes are evenly distributed on the fin, so as to improve the heat dissipation performance of the heat dissipation device.

Description

Technical Field

[0001] The invention relates to the field of heat dissipation and cooling, and in particular to a multi-porous fin heat dissipation method. Background Art

[0002] Traditional thermal management technologies, such as air cooling, liquid cooling, and heat pipe cooling, have their own advantages in different application scenarios, but they also have many limitations. For example, although air-based thermal management technology has a simple structure and low cost, its heat transfer efficiency is low, and it is often difficult to meet cooling requirements when dealing with high heat flux density situations, resulting in low heat dissipation performance. Although liquid cooling technology has high heat transfer efficiency, it takes up more space, and the system is complex and costly, resulting in low heat dissipation performance. Heat pipe technology performs well in some applications, but it is heavy and requires the use of multiple heat pipes in combination, which not only imposes a large burden on the system, but also reduces heat dissipation performance.

[0003] Therefore, a porous fin heat dissipation method is provided to solve the problems raised in the above background technology. Summary of the invention

[0004] The present invention provides a multi-porous fin heat dissipation method in order to solve the technical problem, with the aim of improving the heat dissipation performance of a heat dissipation device.

[0005] The technical solution of the present invention to solve the above technical problems is as follows: a porous fin heat dissipation method, a porous fin heat dissipation device includes a plurality of fin units, the plurality of fin units are arranged side by side, the fin unit includes a base and a fin, one end of the fin is fixedly connected to one end of the base, both sides of each of the bases are fixedly connected to one side of an adjacent base, and a plurality of through holes are evenly distributed on the fin.

[0006] The beneficial effect of the present invention is that the staff installs the bases of multiple fin units on the surface of electronic devices or heat-generating bodies that need to dissipate heat. The heat of the electronic devices or heat-generating bodies will be quickly transferred from the base to the fins and dissipated through the multiple through holes on the fins, effectively improving the heat dissipation performance of the thermal management technology.

[0007] Based on the above technical solution, the present invention can also be improved as follows.

[0008] Furthermore, the plurality of through holes have the same size.

[0009] The beneficial effect of adopting the above further solution is that the multiple through holes can increase the surface area of ​​the electronic device heat in contact with the fins, and dissipate the heat of the electronic device quickly and evenly.

[0010] Furthermore, the length of the base is a, the width is b, and the height is c, the volume of the base V1 = a*b*c, the length of the fin is a, the width is e, and the height is f, the volume of the fin V2 = a*e*f, and the spatial volume of the fin unit V T =a*b*(c+f), the sum of the volume V1 of the base and the volume V2 of the fin and the spatial volume V of the fin unit T The ratio Φ is 0.5.

[0011] The beneficial effect of adopting the above further solution is that the sum of the volume V1 of the base and the volume V2 of the fin is equal to the spatial volume V T When the ratio Φ is 0.5, the existing fin geometry is optimized to achieve the best volume ratio of the structure in the fin unit. This not only improves the overall heat dissipation performance of the fin unit, but also strengthens the local heat dissipation performance of the fin unit.

[0012] The porous fin heat dissipation method further comprises the following steps:

[0013] Step 1: input the preset number N of the fin units determined according to the volume of the electronic device or the heat generating body, the fixed length L of the N fin units along the Y-axis direction, the porosity ε of the heat dissipation material of the fin unit, the volume parameters of the fin unit and the inlet parameters of the air fluid into the ANSYS Workbench software for solution to obtain the temperature distribution table of the fin unit and the pressure distribution table of the air fluid;

[0014] Step 2: Based on the temperature distribution table of the fin unit and the pressure distribution table of the air fluid, obtain the maximum temperature difference ΔT between the highest temperature of the fin unit and the inlet temperature of the air fluid and the maximum pressure difference ΔP between the inlet average pressure of the air fluid and the outlet average pressure of the air fluid;

[0015] Step 3: presetting the mass flow rate of the air fluid inlet and the average density of the air fluid in advance, and calculating the pump power consumption of the fin unit in combination with the maximum pressure difference ΔP of the air fluid;

[0016] Step 4: Based on the initial value of the maximum pressure difference of the fin unit, the initial value of the pump power consumption of the fin unit is calculated, and the dimensionless pump power consumption of the fin unit is calculated according to the initial value of the pump power consumption of the fin unit and the pump power consumption of the fin unit, and the dimensionless maximum temperature difference of the fin unit is calculated according to the initial value of the maximum temperature difference of the fin unit and the maximum temperature difference ΔT of the fin unit;

[0017] Step 5: Linearly weight the dimensionless pump power and the dimensionless maximum temperature difference of the fin unit to obtain a composite function of the fin unit, and calculate the composite values ​​corresponding to different numbers of fin units based on the composite function of the fin unit, select the number of fin units corresponding to the minimum value in the composite values ​​as the optimal number of fin units in the heat dissipation device, and arrange the heat dissipation device according to the optimal number of fin units.

[0018] The beneficial effect of adopting the above further scheme is that for different electronic devices or heat-generating bodies, the optimal number of fin units in the heat dissipation device can be obtained through the composite function of the fin units, thereby realizing a heat dissipation device with optimal heat dissipation performance and controlling production costs.

[0019] Further, in step 1, the volume parameter of the fin unit includes the spatial volume V of the fin unit T , the volume V1 of the base and the volume V2 of the fin and the spatial volume V T The air fluid inlet parameters include the mass flow rate of the air fluid inlet and the air fluid inlet temperature T in .

[0020] Further, in step 3, the formula for calculating the pump power consumption of the fin unit is as follows:

[0021]

[0022] Among them, W P Pump power consumption, represents the mass flow rate of the air fluid inlet, ΔP represents the maximum pressure difference of the air fluid ΔP, ρ g Represents the average density of air fluid.

[0023] Further, in step 4, the formula for calculating the dimensionless pump power consumption of the fin unit is as follows:

[0024]

[0025] in, Represents the dimensionless pump power consumption of the fin unit, W p Indicates the pump power consumption of the fin unit, W po Indicates the initial value of the fin unit pump power consumption.

[0026] Further, in step 4, the formula for calculating the dimensionless maximum temperature difference of the fin unit is as follows:

[0027]

[0028] in, represents the dimensionless maximum temperature difference of the fin unit, ΔT represents the maximum temperature difference of the fin unit, ΔT o Indicates the initial value of the maximum temperature difference of the fin element.

[0029] Furthermore, the formula of the composite function of the fin unit is as follows:

[0030]

[0031] Among them, F tw represents the composite value of the composite function, λ o represents the weighting coefficient, represents the dimensionless maximum temperature difference of the fin unit, ΔT represents the maximum temperature difference of the fin unit, ΔT o represents the initial value of the maximum temperature difference of the fin unit, Represents the dimensionless pump power consumption of the fin unit, W p Indicates the pump power consumption of the fin unit, W po Indicates the initial value of the fin unit pump power consumption.

[0032] Further, the initial value of the fin unit pump power is the pump power when the preset number N of the fin units is 5, and the initial value of the maximum temperature difference of the fin unit is the maximum temperature difference when the preset number N of the fin units is 5. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 It is a structural schematic diagram of the porous fin heat dissipation device of the present invention;

[0034] Figure 2 It is a structural schematic diagram of the fin unit of the present invention;

[0035] Figure 3 It is a schematic diagram of the structure of the fin of the present invention;

[0036] Figure 4 is a schematic structural diagram of the substrate of the present invention;

[0037] Figure 5 It is a schematic diagram of the spatial volume of the fin unit of the present invention;

[0038] Figure 6 When the fin unit material is foam copper, the dimensionless maximum temperature difference and dimensionless pump power consumption of the fin unit and the change curve of the number of fin units N;

[0039] Figure 7 When the fin unit material is foam copper, the composite function changes with the number of fin units N at different air fluid inlet mass flow rates.

[0040] In the accompanying drawings, the components represented by the reference numerals are listed as follows:

[0041] 1. fin unit; 101. base; 102. fin; 103. through hole. DETAILED DESCRIPTION

[0042] The principles and features of the present invention are described below in conjunction with the accompanying drawings. The examples given are only used to explain the present invention and are not used to limit the scope of the present invention.

[0043] like Figure 1-Figure 7 As shown, this embodiment provides a porous fin heat dissipation method, the porous fin heat dissipation device includes a plurality of fin units 1, the plurality of fin units 1 are arranged side by side, the fin unit 1 includes a base 101 and a fin 102, one end of the fin 102 is fixedly connected to one end of the base 101, both sides of each of the bases 101 are fixedly connected to one side of the adjacent base 101, and a plurality of through holes 103 are evenly distributed on the fin 102.

[0044] The staff installs the bases 101 of multiple fin units 1 on the surface of electronic devices or heat-generating bodies that need to dissipate heat. The heat of the electronic devices or heat-generating bodies will be quickly transferred from the base 101 to the fins 102 and dissipated through the multiple through holes 103 on the fins 102, effectively improving the heat dissipation performance of the thermal management technology.

[0045] Specifically, Figure 1 As shown, in this embodiment, the heat dissipation device includes a plurality of fin units 1 , and each fin 102 has eight through holes 103 evenly distributed at intervals.

[0046] like Figure 2 As shown, there are two rows of through holes on the rib 102, and four through holes are distributed in each row. The staff can also set different numbers of through holes according to actual conditions, as long as the gaps between each through hole are the same. For example, three rows of through holes can be set on each rib 102, and four through holes are distributed in each row.

[0047] In addition, in this embodiment, the substrate 101 is a rectangular parallelepiped. The substrate 101 can also be set as a polygon of different shapes, such as a cube or a cylinder, according to the surface shape of the actual electronic device or heat generating body.

[0048] Specifically, the materials of the base 101 and the fins 102 are both heat dissipation materials, which greatly increase the thermal conductivity of the base 101 and the fins 102, thereby achieving efficient heat exchange of the porous fins.

[0049] The heat dissipation material includes but is not limited to foam metal, such as foam copper, foam aluminum or foam graphene, etc. In this embodiment, the heat dissipation material of the fin 102 is foam copper.

[0050] Based on the above solution, the plurality of through holes 103 have the same size.

[0051] The plurality of through holes 103 can increase the surface area where the heat of the electronic device contacts the fins 102 , and dissipate the heat of the electronic device quickly and evenly.

[0052] Specifically, Figure 2 As shown, the shape of the through hole 103 is a square. The staff can also set the through hole 103 to different shapes, such as a rectangle or a regular pentagon, according to actual conditions.

[0053] The length of the through hole 103 along the Y-axis direction is equal to the width e of the fin 102 , which increases the contact area between the air fluid and the fin 102 , thereby achieving enhanced heat dissipation on the porous fin surface.

[0054] On the basis of the above scheme, the length of the base 101 is a, the width is b, and the height is c. The volume V1 of the base 101 is a*b*c. The length of the fin 102 is a, the width is e, and the height is f. The volume V2 of the fin 102 is a*e*f. The spatial volume V T =a*b*(c+f), the sum of the volume V1 of the base 101 and the volume V2 of the fin 102 and the spatial volume V of the fin unit 1 T The ratio Φ is 0.5.

[0055] When the ratio Φ of the sum of the volume V1 of the base 101 and the volume V2 of the fin 102 to the spatial volume V of the fin unit 1 is 0.5, the existing fin geometric structure is optimized to achieve the optimal volume ratio of the structure in the fin unit 1. This not only improves the overall heat dissipation performance of the fin unit 1, but also enhances the local heat dissipation performance of the fin unit 1.

[0056] Specifically, the spatial volume V of the fin unit 1 is T The volume V1 of the base 101 and the volume V2 of the fin 102 are fixed, so that the material volume of the base 101 and the material volume of the fin 102 are fixed, which facilitates controlling the production cost of the fin unit 1.

[0057] The porous fin heat dissipation method further comprises the following steps:

[0058] Step 1: Input the preset number N of the fin units 1 determined according to the volume of the electronic device or the heat generating body, the fixed length L of the N fin units 1 along the Y-axis direction, the porosity ε of the heat dissipation material of the fin unit 1, the volume parameters of the fin unit 1 and the inlet parameters of the air fluid into the ANSYS Workbench software for solution to obtain the temperature distribution table of the fin unit 1 and the pressure distribution table of the air fluid;

[0059] Step 2: Based on the temperature distribution table of the fin unit 1 and the pressure distribution table of the air fluid, obtain the maximum temperature difference ΔT between the highest temperature of the fin unit 1 and the inlet temperature of the air fluid and the maximum pressure difference ΔP between the inlet average pressure of the air fluid and the outlet average pressure of the air fluid;

[0060] Step 3: presetting the mass flow rate of the air fluid inlet and the average density of the air fluid in advance, and calculating the pump power consumption of the fin unit 1 in combination with the maximum pressure difference ΔP of the air fluid;

[0061] Step 4: Based on the initial value of the maximum pressure difference of the fin unit 1, the initial value of the pump power consumption of the fin unit 1 is calculated, and the dimensionless pump power consumption of the fin unit 1 is calculated according to the initial value of the pump power consumption of the fin unit 1 and the pump power consumption of the fin unit 1, and the dimensionless maximum temperature difference of the fin unit 1 is calculated according to the initial value of the maximum temperature difference of the fin unit 1 and the maximum temperature difference ΔT of the fin unit 1;

[0062] Step 5: Linearly weight the dimensionless pump power and the dimensionless maximum temperature difference of the fin unit 1 to obtain a composite function of the fin unit 1, and calculate composite values ​​corresponding to different numbers of fin units 1 based on the composite function of the fin unit 1, select the number of fin units 1 corresponding to the minimum value in the composite values ​​as the optimal number of fin units 1 in the heat dissipation device, and arrange the heat dissipation device according to the optimal number of fin units 1.

[0063] For different electronic devices or heat-generating bodies, the optimal number of fin units 1 in the heat dissipation device can be obtained through the composite function of the fin unit 1, thereby realizing a heat dissipation device with optimal heat dissipation performance and controlling production costs.

[0064] Specifically, three key assumptions are made in this embodiment: first, the air flow is considered to be a stable, incompressible laminar flow, and there is no slip phenomenon when it contacts the surface of electronic devices or heat-generating bodies; second, the physical properties of the air fluid and the foam metal remain unchanged throughout the process; finally, the effects of radiation heat transfer and energy dissipation due to viscosity on the system are ignored.

[0065] The air fluid may be cold air, and the air fluid flows along the X-axis direction and wraps the entire heat dissipation device.

[0066] Specifically, since the temperature distribution of each fin unit 1 in the heat sink is the same, when solving with ANSYS Workbench software, in order to reduce the amount of calculation, just select one of the fin units 1 for calculation. Therefore, the maximum temperature difference of a fin unit 1 is equal to the temperature difference of a fin 102, and also equal to the maximum temperature difference of the entire heat sink.

[0067] Specifically, the number N of fin units, the length L, the material porosity ε, the fin volume and the air fluid inlet parameters all have an impact on the temperature of the fin unit 1 and the pressure of the air fluid.

[0068] Specifically, Figure 6 As shown, at ε = 0.8, Φ = 0.5, T in =300K, L=8mm, V T =200mm 3 When the parameters are fixed, the preset number N of fin units 1 determined according to the volume of the electronic device or the heat-generating body is input into the ANSYS Workbench software as a variable parameter, and the change curves of the dimensionless maximum temperature difference and the dimensionless pump power consumption of the fin unit 1 under different preset numbers N of fin units 1 are obtained.

[0069] Among them, from Figure 6 From the change curve in , it can be seen that the dimensionless maximum temperature difference of fin unit 1 decreases with the increase of the preset number N of fin unit 1, and the dimensionless pump power of fin unit 1 increases with the increase of the preset number N of fin unit 1. Therefore, no matter how the preset number N of fin unit 1 changes, the dimensionless maximum temperature difference and dimensionless pump power of fin unit 1 are a pair of contradictory performances, with opposite change trends, and cannot be designed through single target optimization. Therefore, it is necessary to establish a composite function in step five to study the comprehensive performance of heat transfer and flow of fin unit 1.

[0070] Among them, Figure 6 Middle, L = 8mm, V T =200mm 3 In the case of fixed parameters, as the preset number N of fin units 1 continues to change, the width and height of the base 101 and the fins 102 in each fin unit 1 are constantly changing, thereby driving the size change of the through hole 103 in the fin 102, thereby realizing the influence of fin units 1 with different volume parameters on the heat dissipation performance.

[0071] Specifically, Figure 7 As shown, at ε = 0.8, Φ = 0.5, T in =300K, L=8mm, V T =200mm 3When the parameters are fixed, the preset number N of fin units 1 determined according to the volume of the electronic device or the heat generating body is used as a variable parameter, and the different air fluid inlet mass flow rates are respectively The data were input into ANSYS Workbench software to obtain the change curves of the preset number N of fin units 1, the dimensionless maximum temperature difference of fin unit 1 and the dimensionless pump power consumption at three different air fluid inlet mass flow rates.

[0072] Among them, Figure 7 As shown, when The composite value of the composite function F tw Both lower than and The composite value of the composite function F tw .

[0073] However, in The composite value of the composite function F tw When N = 13, the composite value F of the composite function tw It is at the lowest value, that is, N=13 is the optimal number of fin units 1. At this time, the heat dissipation device is the optimal heat dissipation device with the best heat dissipation performance.

[0074] Based on the above solution, in step 1, the volume parameters of the fin unit 1 include the spatial volume V of the fin unit 1 T , the volume V1 of the base 101 and the volume V2 of the fin 102 and the spatial volume V of the fin unit 1 T The air fluid inlet parameters include the mass flow rate of the air fluid inlet and the air fluid inlet temperature T in .

[0075] Specifically, according to the volume parameters of different fin units 1 and the inlet parameters of different air fluids, the temperature distribution table of different fin units and the pressure distribution table of air fluids can be obtained through ANSYS Workbench software, so as to study the heat dissipation performance of different heat dissipation devices.

[0076] Based on the above solution, in step 3, the formula for calculating the pump power consumption of the fin unit 1 is as follows:

[0077]

[0078] Among them, W P Pump power consumption, represents the mass flow rate of the air fluid inlet, ΔP represents the maximum pressure difference of the air fluid ΔP, ρ g Represents the average density of air fluid.

[0079] On the basis of the above scheme, in step 4, the formula for calculating the dimensionless pump power consumption of the fin unit 1 is as follows:

[0080]

[0081] in, Represents the dimensionless pump power consumption of fin unit 1, W p Represents the pump power consumption of fin unit 1, W po Indicates the initial value of the pump power consumption of fin unit 1.

[0082] Based on the above solution, in step 4, the formula for calculating the dimensionless maximum temperature difference of the fin unit 1 is as follows:

[0083]

[0084] in, represents the dimensionless maximum temperature difference of fin unit 1, ΔT represents the maximum temperature difference of fin unit 1, ΔT o Indicates the initial value of the maximum temperature difference of fin unit 1.

[0085] Based on the above solution, the formula of the composite function of the fin unit 1 is as follows:

[0086]

[0087] Among them, F tw represents the composite value of the composite function, λ o represents the weighting coefficient, represents the dimensionless maximum temperature difference of fin unit 1, ΔT represents the maximum temperature difference of fin unit 1, ΔT o represents the initial value of the maximum temperature difference of fin unit 1, Represents the dimensionless pump power consumption of fin unit 1, W p Represents the pump power consumption of fin unit 1, W po Indicates the initial value of the pump power consumption of fin unit 1.

[0088] Specifically, the staff can adjust the o To take values, such as λ o The possible values ​​are 0.2 or 0.3.

[0089] Based on the above scheme, the initial value of the pump power consumption of the fin unit 1 is the pump power consumption when the preset number N of the fin units 1 is 5, and the initial value of the maximum temperature difference of the fin unit 1 is the maximum temperature difference when the preset number N of the fin units 1 is 5.

[0090] Specifically, in this embodiment, when the preset number N of fin units 1 is 5, it is the initial state of the heat sink, and the side length L of the heat sink composed of 5 fin units 1 is 8×8 mm, the height c+f of the heat sink is 2.19 mm, and the heat flux density value of the base 101 evenly distributed is 16000 W / m 2 The material of the fin unit 1 is foam copper, the width b of the base 101 is 1.6 mm, the height f of the fin 102 is 0.457 mm, and the height c of the base 101 is 0.94 mm.

[0091] The staff input the above parameters into the ANSYS Workbench software, and obtained the temperature distribution table of the fin unit 1 and the pressure distribution table of the air fluid when the preset number N of the fin unit 1 is 5, and then obtained the initial value of the maximum temperature difference ΔT of the fin unit 1 and the initial value of the maximum pressure difference ΔP of the fin unit 1. By obtaining the formula for the pump power consumption of the fin unit 1, the initial value of the pump power consumption of the fin unit 1 is obtained.

[0092] As shown in Table 1 below, Table 1 is , a comparison diagram of the maximum temperature difference and pump power consumption of the fin units in the optimal heat dissipation device (N=13), the initial heat dissipation device (N=5) and the optimal heat dissipation device without holes (N=13, but no through hole 103 is set on each fin 102).

[0093]

[0094] Table 1

[0095] As shown in Table 1, the maximum temperature difference of the optimal heat dissipation device (N=13) is reduced by 54.6% compared with the initial heat dissipation device (N=5); the maximum temperature difference of the optimal heat dissipation device (N=13) is reduced by 5.65% compared with the optimal heat dissipation device without holes (N=13, but each fin 102 is not provided with a through hole 103). It can be seen that the optimal heat dissipation device (N=13) greatly improves the heat dissipation performance, but it will bring a certain increase in pump power consumption.

[0096] In the description of the present invention, it is necessary to understand that the terms "length", "width", "thickness", "up", "down", "front", "back", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0097] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0098] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being "above", "above" or "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below", "below" or "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0099] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, without contradiction.

[0100] Although the embodiments of the present invention have been shown and described above, it is to be understood that the above embodiments are exemplary and are not to be construed as limitations of the present invention. A person skilled in the art may change, modify, replace and vary the above embodiments within the scope of the present invention.

Claims

1. A porous fin heat dissipation method, characterized in that: The porous fin heat dissipation device comprises a plurality of fin units (1), wherein the plurality of fin units (1) are arranged side by side, the fin unit (1) comprises a base (101) and a fin (102), one end of the fin (102) is fixedly connected to one end of the base (101), both sides of each base (101) are fixedly connected to one side of an adjacent base (101), and a plurality of through holes (103) are evenly spaced on the fin (102); The porous fin heat dissipation method comprises the following steps: Step 1: inputting the preset number N of the fin units (1) determined according to the volume of the electronic device or the heat generating body, the fixed length L of the N fin units (1) along the Y-axis direction, the porosity ε of the heat dissipation material of the fin unit (1), the volume parameters of the fin unit (1) and the inlet parameters of the air fluid into ANSYS Workbench software for solving, and obtaining a temperature distribution table of the fin unit (1) and a pressure distribution table of the air fluid; Step 2: Based on the temperature distribution table of the fin unit (1) and the pressure distribution table of the air fluid, obtain the maximum temperature difference ΔT between the highest temperature of the fin unit (1) and the inlet temperature of the air fluid and the maximum pressure difference ΔP between the inlet average pressure of the air fluid and the outlet average pressure of the air fluid; Step 3: presetting the mass flow rate of the air fluid inlet and the average density of the air fluid in advance, and calculating the pump power consumption of the fin unit (1) in combination with the maximum pressure difference ΔP of the air fluid; Step 4: Based on the initial value of the maximum pressure difference of the fin unit (1), the initial value of the pump power consumption of the fin unit (1) is calculated, and the dimensionless pump power consumption of the fin unit (1) is calculated according to the initial value of the pump power consumption of the fin unit (1) and the pump power consumption of the fin unit (1), and the dimensionless maximum temperature difference of the fin unit (1) is calculated according to the initial value of the maximum temperature difference of the fin unit (1) and the maximum temperature difference ΔT of the fin unit (1); Step 5: linearly weighting the dimensionless pump power consumption and the dimensionless maximum temperature difference of the fin unit (1) to obtain a composite function of the fin unit (1), and calculating composite values ​​corresponding to different numbers of the fin units (1) based on the composite function of the fin unit (1), selecting the number of the fin units (1) corresponding to the minimum value in the composite values ​​as the optimal number of the fin units (1) in the heat dissipation device, and arranging the heat dissipation device according to the optimal number of the fin units (1); The plurality of through holes (103) have the same size; The length of the base (101) is a, the width is b, and the height is c. The volume V1 of the base (101) is equal to a*b*c. The length of the fin (102) is a, the width is e, and the height is f. The volume V2 of the fin (102) is equal to a*e*f. The spatial volume V T =a*b*(c+f), the sum of the volume V1 of the base (101) and the volume V2 of the fin (102) and the spatial volume V of the fin unit (1) T The ratio Φ=(V1+V2) / V T =0.

5.

2. A porous fin heat dissipation method according to claim 1, characterized in that: In step 1, the volume parameters of the fin unit (1) include the spatial volume V of the fin unit (1) T , the volume V1 of the base (101) and the volume V2 of the fin (102) and the spatial volume V of the fin unit (1) T The air fluid inlet parameters include the mass flow rate of the air fluid inlet and the air fluid inlet temperature T in .

3. A porous fin heat dissipation method according to claim 1, characterized in that: In step 3, the formula for calculating the pump power consumption of the fin unit (1) is as follows: Among them, W P Pump power consumption, represents the mass flow rate of the air fluid inlet, ΔP represents the maximum pressure difference of the air fluid ΔP, ρ g Represents the average density of air fluid.

4. A porous fin heat dissipation method according to claim 1, characterized in that: In step 4, the formula for calculating the dimensionless pump power consumption of the fin unit (1) is as follows: in, represents the dimensionless pump power consumption of the fin unit (1), W p represents the pump power consumption of the fin unit (1), W po Indicates the initial value of the pump power consumption of the fin unit (1).

5. A porous fin heat dissipation method according to claim 1, characterized in that: In step 4, the formula for calculating the dimensionless maximum temperature difference of the fin unit (1) is as follows: in, represents the dimensionless maximum temperature difference of the fin unit (1), ΔT represents the maximum temperature difference of the fin unit (1), ΔT o Indicates the initial value of the maximum temperature difference of the fin unit (1).

6. A porous fin heat dissipation method according to claim 1, characterized in that: The formula of the composite function of the fin unit (1) is as follows: Among them, F tw represents the composite value of the composite function, λ o represents the weighting coefficient, represents the dimensionless maximum temperature difference of the fin unit (1), ΔT represents the maximum temperature difference of the fin unit (1), ΔTo represents the initial value of the maximum temperature difference of the fin unit (1), represents the dimensionless pump power consumption of the fin unit (1), W p represents the pump power consumption of the fin unit (1), W po Indicates the initial value of the pump power consumption of the fin unit (1).

7. A porous fin heat dissipation method according to claim 1, characterized in that: In step 4, the initial value of the pump power consumption of the fin unit (1) is the pump power consumption when the preset number N of the fin units (1) is 5, and the initial value of the maximum temperature difference of the fin unit (1) is the maximum temperature difference when the preset number N of the fin units (1) is 5.

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