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

Abstract

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

CLC Number:

TK89

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.

Figures/Tables 26

Fig.1

Fig.2

Fig.3

Fig.4

Table 1

Fig.5

Table 2

Simulation data of different schemes"

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

Table 2

Table 3

Table of Factors and levels required for orthogonal test"

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

Table 3

Table 4

Table of orthogonal test results"

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

Table 4

Fig.6

Fig.7

Fig.8

Fig.9

Table 5

Range analysis table of orthogonal test"

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	$K ˉ A 3 = 4.841$	/	/	$K ˉ D 3 = 5.052$	$K ˉ E 3 = 4.487$
	$R i$	$R A = 0.726$	$R B = 0.279$	$R C = 0.471$	$R D = 0.51$	$R E = 0.425$

Table 5

Fig.10

Table 6

Table 7

Comprehensive scoring table for each evaluation factor"

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

Table 7

Fig.11

Fig.12

Fig.13

Fig.14

Fig.15

Table 8

Table of simulation data of the optimized structure"

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

Table 8

Fig.16

Fig.17

Table 9

Improved heat dissipation efficiency under different fan output voltages"

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

Table 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

Analysis and optimization of internal flow field of diffuser structure of cooling system based on Fluent

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