施加流速边界条件的格子Boltzmann模型的沸腾传热模拟

doi:10.16085/j.issn.1000-6613.2025-0451

摘要/Abstract

摘要：

沸腾传热现象会直接影响换热器的换热效率，采用伪势格子Boltzmann模型对池沸腾传热进行数值模拟，并与实验结果进行对比分析，验证其可行性。本文采用改进流速边界条件的伪势格子Boltzmann模型对固液换热面对流传热进行数值模拟，分析核态沸腾、过渡沸腾和膜态沸腾全周期演化规律，探究施加流速对固液换热面气泡动力学与传热特性的影响机制，实现了二维矩形截面内气液两相流的多尺度耦合模拟。结果表明，采用伪势格子Boltzmann模型对池沸腾传热进行数值模拟是可行的；施加流速会不同程度缩短核态沸腾和过渡沸腾阶段，延长膜态沸腾阶段；相较于无流速，在核态沸腾阶段施加0.005m/s<R<0.050m/s的流速，第一沸腾气泡脱离时间缩短12%~35%，临界热流密度峰值达6102.0 $W / m 2$ ，提升了5.5%，传热系数峰值达 $56.9 ~ 58.0 W / (m 2 · K)$ ，提升了1.5%~10.5%；在过渡沸腾阶段施加R>0.050m/s的流速时，气泡逐渐合并为气膜，并迅速横向铺展，提前诱发膜态沸腾；膜态沸腾阶段，流动减小气膜厚度，热流密度曲线形成达920 $W / m 2$ 的周期性热流尖峰，但施加流速将恶化传热。

关键词: 数值模拟, 伪势格子Boltzmann模型, 沸腾传热, 流速, 气泡动力学, 传热系数

Abstract:

The boiling heat transfer phenomenon significantly influences heat exchanger efficienc. In this study, the pseudo-potential lattice Boltzmann model was used to simulate the pool boiling heat transfer, and the results were compared with the experimental results to verify its feasibility. A pseudo-potential lattice Boltzmann model with improved velocity boundary conditions was adopted to numerically simulate convective heat transfer on solid-liquid heat exchange surfaces. The full-period evolution laws of nucleate boiling, transition boiling, and film boiling were analyzed. The mechanisms by which imposed flow velocities influence bubble dynamics and heat transfer characteristics at the solid-liquid interface were also explored. Multiscale coupled simulations of gas-liquid two-phase flow in a two-dimensional rectangular cross-section were successfully conducted. The results showed that the pseudo-potential lattice Boltzmann model provided an effective approach for pool boiling simulations. The applied flow rate would shorten the nucleate boiling and transition boiling stages and prolong the film boiling stage to varying degrees. Compared with no flow rate, during the nucleate boiling stage, imposing flow velocities in the range of 0.005m/s<R<0.050m/s shortened the departure time of the initial boiling bubble by approximately 12%—35%, the peak value of critical heat flux was 6102.0W/m², which was increased by 5.5%. Additionally, the heat transfer coefficient reached a maximum of $56.9 — 58.0 W / (m 2 · K)$ ,which was increased by 1.5%—10.5%; During the transition boiling stage, imposing a flow velocity greater than $0.050 m / s$ resulted the bubbles gradually merge into a gas film and spread rapidly horizontally, triggering the onset of film boiling earlier. In the film boiling stage, the flow reduced the film thickness, and the heat flux density curve formed a periodic heat flux peak of 920 $W / m 2$ . But imposed flow velocity deteriorated heat transfer performance.

Key words: numerical simulation, pseudo-potential lattice Boltzmann model, boiling heat transfer, flow velocity, bubble dynamics, heat transfer coefficient

中图分类号:

TK121

徐海天, 徐艳英, 翟明. 施加流速边界条件的格子Boltzmann模型的沸腾传热模拟[J]. 化工进展, 2025, 44(S1): 84-91.

XU Haitian, XU Yanying, ZHAI Ming. Boiling heat transfer simulation using lattice Boltzmann model with flow velocity boundary conditions[J]. Chemical Industry and Engineering Progress, 2025, 44(S1): 84-91.

图/表 14

图1 典型的沸腾曲线[2]

图2 数值模拟模型

图3 D2Q9模型

表1 各物理单位与格子单位之间的转化关系

参数	格子数值	物理数值
比热容 $c V$ /kJ·kg^-1·K^-1	6	5.31
重力加速度 $g$ /m·s^-2	0.00003	9.8
共存温度 $T s$ /K	0.0941	556.55
格子长度 $δ x$ /m	1	0.0000743
格子时间步长 $δ t$ /s	1	0.000015
液相密度 $ρ l$ /kg·m^-3	6.4989	774.29
气相密度 $ρ v$ /kg·m^-3	0.3797	35.06
流速R/m·s^-1	0.001	0.005

表1 各物理单位与格子单位之间的转化关系

参数	格子数值	物理数值
比热容 $c V$ /kJ·kg^-1·K^-1	6	5.31
重力加速度 $g$ /m·s^-2	0.00003	9.8
共存温度 $T s$ /K	0.0941	556.55
格子长度 $δ x$ /m	1	0.0000743
格子时间步长 $δ t$ /s	1	0.000015
液相密度 $ρ l$ /kg·m^-3	6.4989	774.29
气相密度 $ρ v$ /kg·m^-3	0.3797	35.06
流速R/m·s^-1	0.001	0.005

图4 沸腾传热实验模型

图5 实验与模拟的传热系数对比

图6 R = 0.050m/s，ΔT = 94.6K、171.5K、218.9K时密度的时间演化图像

表2 不同流速条件下的第一沸腾气泡脱离时间和与R=0相比的变化百分比

流速/m·s^-1	$Δ T = 94.6 K$		$Δ T = 171.5 K$		$Δ T = 218.9 K$
流速/m·s^-1	脱离时间	百分比/%	脱离时间	百分比/%	脱离时间	百分比/%
$0$	17000	—	18000	—	17000	—
0.005 $~$ 0.050	11000 $~$ 15000	-35 $~$ -12	16000	-11	15000 $~$ 16000	-12 $~$ -6
0.025~0.050	11000	-35	19000 $~$ 23000	6 $~$ 28	17000 $~$ 18000	0 $~$ 6

表2 不同流速条件下的第一沸腾气泡脱离时间和与R=0相比的变化百分比

流速/m·s^-1	$Δ T = 94.6 K$		$Δ T = 171.5 K$		$Δ T = 218.9 K$
流速/m·s^-1	脱离时间	百分比/%	脱离时间	百分比/%	脱离时间	百分比/%
$0$	17000	—	18000	—	17000	—
0.005 $~$ 0.050	11000 $~$ 15000	-35 $~$ -12	16000	-11	15000 $~$ 16000	-12 $~$ -6
0.025~0.050	11000	-35	19000 $~$ 23000	6 $~$ 28	17000 $~$ 18000	0 $~$ 6

图7 ΔT = 94.6K、171.5K、218.9K，不同流速条件下第一沸腾气泡脱离时密度的时间演化图像

图8 ΔT = 94.6K时，施加不同流速的瞬态热流密度随时间的变化

图9 ΔT = 171.5K时，施加不同流速的瞬态热流密度随时间的变化

图10 ΔT = 218.9K时，施加不同流速的瞬态热流密度随时间的变化

图11 不同流速条件下的预测沸腾曲线（壁面平均热流密度）

图12 施加不同流速条件下的传热系数变化

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