基于Fluent的散热系统扩流结构内部流场分析及优化

doi:10.13229/j.cnki.jdxbgxb.20221159

摘要/Abstract

摘要：

针对风冷散热系统中气体扩流不充分的问题，提出在扩流结构内部安装导流片的解决方案。利用流体动力学软件Fluent搭建了扩流结构的仿真模型并对扩流结构进行了内部流场分析，得出的结论有：流体在扩流结构的不同平面内的局部水头损失分别为3.24 m和1.21 m；在简化模型中，流体低速、大面积分布的散热效率比流体高速、小面积分布的散热效率高8%。利用正交试验研究导流片参数对散热效率的影响，结果表明，针对系统的散热效率，影响程度从大到小的排序为：导流片组距入口端的最短距离L>导流片表面孔的半径R>导流片与流速方向的倾角 $θ$ >导流片在流速方向上的投影长度h>导流片在垂直于流速方向上的最短间距d。对优化后的扩流结构进行实体化改造，试验结果表明：当分别用3、4、5、6 V的输出电压驱动风机工作产生冷流体时，散热系统的散热效率分别提高了7.67%、3.62%、4.26%、6.93%。

关键词: 流体机械与工程, 导流片, 水头损失, 正交试验, Fluent

Abstract:

In order to solve the problem of insufficient gas diffusion in air-cooled heat dissipation system， this paper proposes a solution of installing diversion plates inside the expansion structure. The fluid dynamics software Fluent was used to build the simulation model of the expanded flow structure and analyze the internal flow field of the expanded flow structure. The conclusions are as follows： The local head loss of fluid in different planes of the diffuser structure is 3.24 m and 1.21 m respectively. In the simplified model， the heat dissipation efficiency of fluid with low speed and large area distribution is 8% higher than that of fluid with high speed and small area distribution. The orthogonal test is used to study the influence of the deflector parameters on the heat dissipation efficiency. The results show that for the heat dissipation efficiency of the system， the order of the degree of influence from large to small is： the shortest distance L between the deflector group and the inlet end， the radius R of the surface hole of the deflector， the inclination angle between the deflector and the flow direction $θ$ ， the projection length h of the deflector in the flow direction， and the shortest distance d of the deflector in the direction perpendicular to the flow direction. The experimental results show that the cooling efficiency of the heat dissipation system is increased by 7.67%， 3.62%， 4.26% and 6.93% when the fan is driven by output voltage of 3， 4， 5， 6 V respectively to produce cold fluid.

Key words: fluid machinery and engineering, deflector, headloss, orthogonal test, Fluent

中图分类号:

TK89

刘昕晖,相志霖,谭鹏,陈伟,冯吉宇. 基于Fluent的散热系统扩流结构内部流场分析及优化[J]. 吉林大学学报(工学版), 2024, 54(7): 1831-1843.

Xin-hui LIU,Zhi-lin XIANG,Peng TAN,Wei CHEN,Ji-yu FENG. Analysis and optimization of internal flow field of diffuser structure of cooling system based on Fluent[J]. Journal of Jilin University(Engineering and Technology Edition), 2024, 54(7): 1831-1843.

图/表 26

图1

图2

图3

图4

表1

图5

表2

不同方案仿真数据"

试验

气体出口温度/℃

液体出口温度/℃

换热面

面积/ $m 2$

流体与壁面温差/℃

方案一

23.125

79.882

1.58 × 10 - 4

3.296

方案二

24.906

79.871

2.86 × 10 - 4

3.159

表2

表3

正交试验所需因素和水平"

序号	因素	水平1	水平2	水平3
A	$L z$ /mm	20、80	20	80
B	d/mm	10	20	/
C	h/mm	10	20	/
D	R/mm	0	3	5
E	$θ$ /（°）	20	30	45

表3

表4

正交试验结果表"

试验组别	因素					X方向平均速度 $V x ˉ / (m ? s - 1)$	Z方向平均速度 $V z ˉ / (m ? s - 1)$
试验组别	A	B	C	D	E	X方向平均速度 $V x ˉ / (m ? s - 1)$	Z方向平均速度 $V z ˉ / (m ? s - 1)$
1	1	1	1	1	1	4.674	4.971
2	1	2	2	2	2	4.041	5.260
3	1	2	1	3	3	4.452	5.222
4	1	1	2	3	1	4.466	5.390
5	2	1	2	3	2	4.415	4.582
6	2	2	1	1	3	3.981	4.458
7	2	1	2	1	2	4.625	4.428
8	2	2	1	2	1	4.263	4.309
9	3	1	2	3	2	5.160	5.648
10	3	2	2	3	1	5.148	4.893
11	3	2	1	2	1	4.572	4.679
12	3	1	2	1	3	4.870	4.657
13	3	1	1	2	3	5.058	4.592
14	2	2	1	1	3	4.405	3.505
15	2	1	2	1	1	3.808	5.231
16	3	1	1	3	2	5.071	4.576

表4

图6

图7

图8

图9

表5

正交试验极差分析表"

结果	水平	因素
结果	水平	A	B	C	D	E
X方向平均速度 $V x ˉ / (m ? s - 1)$	1	$K ˉ A 1 = 4.408$	$K ˉ B 1 = 4.683$	$K ˉ C 1 = 4.560$	$K ˉ D 1 = 4.394$	$K ˉ E 1 = 4.489$
	2	$K ˉ A 2 = 4.250$	$K ˉ B 2 = 4.409$	$K ˉ C 2 = 4.567$	$K ˉ D 2 = 4.483$	$K ˉ E 2 = 4.663$
	3	$K ˉ A 3 = 5.002$	/	/	$K ˉ D 3 = 4.786$	$K ˉ E 3 = 4.553$
	$R i$	$R A = 0.752$	$R B = 0.274$	$R C = 0.007$	$R D = 0.392$	$R E = 0.11$
Z方向平均速度 $V z ˉ / (m ? s - 1)$	1	$K ˉ A 1 = 5.145$	$K ˉ B 1 = 4.897$	$K ˉ C 1 = 4.539$	$K ˉ D 1 = 4.542$	$K ˉ E 1 = 4.912$
	2	$K ˉ A 2 = 4.419$	$K ˉ B 2 = 4.618$	$K ˉ C 2 = 5.010$	$K ˉ D 2 = 4.711$	$K ˉ E 2 = 4.839$
	3	$K ˉ A 3 = 4.841$	/	/	$K ˉ D 3 = 5.052$	$K ˉ E 3 = 4.487$
	$R i$	$R A = 0.726$	$R B = 0.279$	$R C = 0.471$	$R D = 0.51$	$R E = 0.425$

表5

图10

表6

表7

各因素综合评分表"

综合评分	A	B	C	D	E
$Y 1$	4.890	4.812	4.547	4.483	4.743
$Y 2$	4.351	4.534	4.833	4.619	4.812
$Y 3$	4.893	/	/	4.945	4.513
R	0.542	0.278	0.286	0.462	0.299

表7

图11

图12

图13

图14

图15

表8

优化结构仿真数据表"

端口	平均压力/Pa	平均速度/（ $m ? s - 1$ ）
入口	-912	43.29
出口	597	11.93

表8

图16

图17

表9

不同风机输出电压下提升的散热效率"

输出电压/V	$Q a i V / (J ? s - 1)$	$Q b i V / (J ? s - 1)$	$a i V$ /%
3	-5 709.56	-6 147.41	7.67
4	-7 741.19	-8 021.41	3.62
5	-9 037.22	-9 422.53	4.26
6	-9 352.48	-10 000.49	6.93

表9

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	平均压力/Pa	平均速度/（m·s^-1）
入口端	-101	43.29
出口端	391	13.03

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