相变悬浮液射流冲击变形状多孔层覆盖壁面的热分析

doi:10.11949/0438-1157.20251211

摘要/Abstract

摘要：

针对高热通量、高集成度电子设备的散热需求，提出一种基于相变悬浮液射流冲击覆盖多孔介质受热面的强化冷却方案。通过数值方法研究了射流流体和构型、多孔介质孔隙率、孔径以及不同射流速度与悬浮液质量分数对散热性能的影响，并与裸板冷却模式进行了对比。研究发现，相对于水，在相同射流速度下，相变悬浮液在射流冲击裸板模式下的壁面温度升高、传热系数降低。当孔隙率和孔径较小时，倒梯形与三角形射流模式具有更高的平均传热系数；而在孔隙率和孔径较大时，矩形与倒梯形射流模式的平均传热系数更高。在低速、高质量分数条件下，倒梯形射流构型的平均传热系数高于三角形构型；但在高速、低质量分数条件下，三角形构型反而更具优势。这些发现可为利用相变悬浮液的冷却系统设计提供有价值的指导。

关键词: 相变悬浮液, 射流冲击, 湍流, 多孔介质, 传热强化, 数值模拟

Abstract:

Aiming at the heat dissipation requirements of high heat flux and highly integrated electronic devices, an enhanced cooling scheme based on the phase change suspension jet impinging on the heating surface covered with porous medium is proposed. The effects of jet fluid and configuration, porosity and pore size of the porous medium, as well as jet velocity and mass fraction of suspension on the heat dissipation performance were studied numerically, and compared with the cooling mode of bare plate. The study found that, relative to water at identical jet velocities, phase change suspension under the jet impingement on a bare plate mode demonstrate an increased wall temperature and a reduced heat transfer coefficient. The inverted trapezoidal and triangular jet modes have higher average heat transfer coefficients when the porosity and pore size are small, while the rectangular and inverted trapezoidal jet modes have higher average heat transfer coefficients when the porosity and pore size are large. Under low velocity and high mass fraction conditions, the average heat transfer coefficient of the inverted trapezoidal jet configuration is higher than that of the triangular configuration; however, under high velocity and low mass fraction conditions, the triangular configuration becomes more advantageous. These findings may provide valuable guidance for the design of cooling systems utilizing phase change suspensions.

Key words: phase change suspension, jet impingement, turbulent flow, porous media, heat transfer enhancement, numerical simulation

中图分类号:

TK124

戴浩, 刘燚, 刘迎文. 相变悬浮液射流冲击变形状多孔层覆盖壁面的热分析[J]. 化工学报, DOI: 10.11949/0438-1157.20251211.

Hao DAI, Yi LIU, Yingwen LIU. Thermal analysis of phase change suspension jet impinging on wall surface covered with variable-shape porous layer[J]. CIESC Journal, DOI: 10.11949/0438-1157.20251211.

图/表 16

表1 相关材料的热物理性质

Table 1 Thermophysical properties of related materials

物性	水	相变微胶囊	相变悬浮液（c_m = 5%）	相变悬浮液（c_m = 10%）	相变悬浮液（c_m = 15%）	相变悬浮液（c_m = 20%）	钢	铜
ρ (kg·m^-3)	981.3	867.2	974.9	968.6	962.3	956.1	8030	8978
C_p (J·kg^-1·K^-1)	4189	1899	4075	3960	3846	3731	502.48	381
λ (W·m^-1·K^-1)	0.643	0.1643	0.608	0.5744	0.5426	0.5121	16.27	387.6
μ (kg·m^-1·s^-1)	5.98×10^-4	–	6.98×10^-4	8.37×10^-4	1.04×10^-3	1.34×10^-3	–	–

表2 计算域的相关控制方程

Table 2 Related governing equations of the computational domain

域名	名称	方程式
流体域	连续性方程	$∇ ⋅ U ⃗ = 0$
	动量方程	$ρ f (U ⃗ ⋅ ∇) U ⃗ = - ∇ P + μ f ∇ 2 U ⃗ + ρ f g$
	能量方程	$∇ ⋅ (c v, i U ⃗ (ρ i C p, i T + P)) = λ f ∇ 2 T$
	组分方程	$∇ ⋅ (c m, i ρ i U ⃗) = - ∇ J ⃗ i$
	湍流动能k方程	$∇ ⋅ (ρ k U ⃗) = (μ + μ t σ k) ∇ 2 k + ρ G k - ρ ε$
	湍流耗散率ε方程	$∇ ⋅ (ρ ε U ⃗) = (μ + μ t σ ε) ∇ 2 ε + C 1 ε ε k ρ G k - C 2 ε ε k ρ ε$
多孔域	连续性方程	$∇ ⋅ U ⃗ = 0$
	动量方程	$ρ f ϕ 2 (U ⃗ ⋅ ∇) U ⃗ = - ∇ P + μ f ϕ ∇ 2 U ⃗ - (μ f K + ρ f C F K U ⃗) U ⃗ + ρ f g$
	能量方程	$∇ ⋅ (ϕ c v, i U ⃗ (ρ i C p, i T + P)) = λ e f f ∇ 2 T$
	组分方程	$∇ ⋅ (c m, i ρ i U ⃗) = - ∇ J ⃗ i$
固体域	能量方程	$λ s ∇ 2 T = 0$

表2 计算域的相关控制方程

Table 2 Related governing equations of the computational domain

域名	名称	方程式
流体域	连续性方程	$∇ ⋅ U ⃗ = 0$
	动量方程	$ρ f (U ⃗ ⋅ ∇) U ⃗ = - ∇ P + μ f ∇ 2 U ⃗ + ρ f g$
	能量方程	$∇ ⋅ (c v, i U ⃗ (ρ i C p, i T + P)) = λ f ∇ 2 T$
	组分方程	$∇ ⋅ (c m, i ρ i U ⃗) = - ∇ J ⃗ i$
	湍流动能k方程	$∇ ⋅ (ρ k U ⃗) = (μ + μ t σ k) ∇ 2 k + ρ G k - ρ ε$
	湍流耗散率ε方程	$∇ ⋅ (ρ ε U ⃗) = (μ + μ t σ ε) ∇ 2 ε + C 1 ε ε k ρ G k - C 2 ε ε k ρ ε$
多孔域	连续性方程	$∇ ⋅ U ⃗ = 0$
	动量方程	$ρ f ϕ 2 (U ⃗ ⋅ ∇) U ⃗ = - ∇ P + μ f ϕ ∇ 2 U ⃗ - (μ f K + ρ f C F K U ⃗) U ⃗ + ρ f g$
	能量方程	$∇ ⋅ (ϕ c v, i U ⃗ (ρ i C p, i T + P)) = λ e f f ∇ 2 T$
	组分方程	$∇ ⋅ (c m, i ρ i U ⃗) = - ∇ J ⃗ i$
固体域	能量方程	$λ s ∇ 2 T = 0$

表3 网格独立性测试结果

Table 3 Grid independence test results

网格编号 (n)	节点数	ΔT_max (K)	$Δ T m a x (n) - Δ T m a x (Ⅳ) Δ T m a x (Ⅳ) × 100$ (%)	$h ¯$ (W·m^-2·K^-1)	$h ¯ (n) - h ¯ (Ⅳ) h ¯ (Ⅳ) × 100$ (%)
Mesh (I)	78×47	14.09	1.08	83837.05	2.42
Mesh (II)	128×79	13.89	0.36	86148.97	0.27
Mesh (Ⅲ)	252×163	13.92	0.14	86169.75	0.29
Mesh (Ⅳ)	350×231	13.94	–	85917.30	–

表3 网格独立性测试结果

Table 3 Grid independence test results

网格编号 (n)	节点数	ΔT_max (K)	$Δ T m a x (n) - Δ T m a x (Ⅳ) Δ T m a x (Ⅳ) × 100$ (%)	$h ¯$ (W·m^-2·K^-1)	$h ¯ (n) - h ¯ (Ⅳ) h ¯ (Ⅳ) × 100$ (%)
Mesh (I)	78×47	14.09	1.08	83837.05	2.42
Mesh (II)	128×79	13.89	0.36	86148.97	0.27
Mesh (Ⅲ)	252×163	13.92	0.14	86169.75	0.29
Mesh (Ⅳ)	350×231	13.94	–	85917.30	–

图1 (a) 射流冲击被不同形状多孔介质覆盖的受热面，以及 (b) 多孔介质形状分别为 (Ⅰ) 三角形、(Ⅱ) 梯形、(Ⅲ) 矩形和 (Ⅳ) 倒梯形的不同射流构型的示意图

Fig.1 The schematic diagrams of (a) jet impinging on the heating surface covered by porous media of different shapes, and (b) different jet configurations with porous media shapes of (Ⅰ) triangular, (Ⅱ) trapezoidal, (Ⅲ) rectangular, and (Ⅳ) inverted trapezoidal, respectively

图2 基于 (a) Zhang等[27]及 (b) Jeng等[38]的结果比较

Fig.2 Comparison based on the results of (a) Zhang et al. [27] and (b) Jeng et al. [38]

图3 水为工质时不同射流模式下 (a) 局部壁温与 (b) 局部传热系数随x位置的变化

Fig.3 Variation of (a) local wall temperature and (b) local heat transfer coefficient along the x-position under different jet modes with water as the working fluid

图4 相变悬浮液（cm= 10%）为工质时不同射流模式下 (a) 局部壁温与 (b) 局部传热系数随x位置的变化

Fig. 4 Variation of (a) local wall temperature and (b) local heat transfer coefficient along the x-position under different jet modes with phase change suspension (cm = 10%) as the working fluid

图5 不同工质射流冲击裸板构型时的温度和速度矢量场

Fig.5 Temperature and velocity vector fields during jet impingement of different working fluids on a bare plate configuration

图6 不同射流模式下平均传热系数随孔隙率的变化

Fig.6 Variation of average heat transfer coefficient with porosity under different jet modes

图7 不同射流模式下平均传热系数随孔径的变化

Fig.7 Variation of average heat transfer coefficient with pore size under different jet modes

图8 不同射流模式下平均传热系数随射流速度的变化

Fig.8 Variation of average heat transfer coefficient with jet velocity under different jet modes

图9 相变悬浮液在不同射流速度下射流冲击三角形和倒梯形构型时的温度和速度矢量场

Fig.9 Temperature and velocity vector fields during jet impingement of phase change suspension on triangular and inverted trapezoidal configurations at varied velocities

图10 不同射流模式下平均壁面温度和温度均匀度随相变悬浮液射流速度的变化

Fig.10 Variation of average wall temperature and temperature uniformity with jet velocity of phase change suspension under different jet modes

图11 不同射流模式下平均传热系数随相变悬浮液质量分数的变化

Fig.11 Variation of average heat transfer coefficient with mass fraction of phase change suspension under different jet modes

图12 相变悬浮液射流冲击三角形构型时微胶囊中相变材料的液相分数及相变百分比随质量分数的变化

Fig.12 Variation of liquid fraction and phase change percentage of phase change material in microcapsules with mass fraction under jet impingement of phase change suspension on a triangular configuration

图13 相变悬浮液在不同质量分数下射流冲击三角形和倒梯形构型时的温度和速度矢量场

Fig.13 Temperature and velocity vector fields during jet impingement of phase change suspension on triangular and inverted trapezoidal configurations at different mass fractions

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