典型离散翅片微通道流动沸腾特性研究

王玉兵; 张大林; 詹宏波; 刘世睿; 朱光亚

doi:10.13224/j.cnki.jasp.20250344

典型离散翅片微通道流动沸腾特性研究

doi: 10.13224/j.cnki.jasp.20250344

王玉兵^{1, 2,},
张大林^1,*, ,,
詹宏波²,
刘世睿¹,
朱光亚¹

1.
南京航空航天大学航空学院飞行器环境控制与生命保障工信部重点实验室，南京 210016
2.
中航工业金城南京机电液压工程研究中心航空机电系统综合航空科技重点实验室，南京 211106

基金项目: 航空科学基金（20240028052003）

详细信息

作者简介:
王玉兵（1980-），男，研究员，博士生，研究方向为飞行器环境控制。E-mail：wangyb_njzx@163.com

通讯作者:
张大林（1970-），男，教授，博士，研究方向为飞行器环境控制。E-mail：zhangdalin@nuaa.edu.cn

中图分类号: V245.3
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出版历程
- 收稿日期: 2025-07-21
- 网络出版日期: 2025-11-10

Investigation on flow boiling characteristics in mini channels of typical discrete fin

WANG Yubing^{1, 2
,},
ZHANG Dalin^{1,*
, ,},
Zhan Hongbo²,
LIU Shirui¹,
ZHU Guangya¹

1.
Key Laboratory of Aircraft Environment Control and Life Support，Ministry of Industry and Information Technology，College of Aerospace Engineering，Nanjing University of Aeronautics and Astronautics，Nanjing 210016，China
2.
Aviation Key Laboratory of Science and Technology on Aero Electromechanical System Integration，Jincheng Nanjing Institute of Aircraft System，Aviation Industry Corporation of China，Limited，Nanjing 211106，China

摘要

摘要:
基于离散翅片微通道流动沸腾的多相流换热器是一种可工程化的热沉技术，可应对高热流密度的飞行器散热需求。实验研究了R134a制冷剂在4种典型离散翅片微通道中的流动沸腾换热特性。微通道的当量直径为0.67 mm，实验工况范围为：干度为0～1，质量流率为150～300 kg/（m²·s），热流密度为10～25 kW/m²。实验结果表明：微通道流动沸腾压降和传热系数随工质质量流率和热流密度的增大而提高，不同翅片之间对比结果表明：翅片形状对于压降的影响相比于传热系数更为显著，以质量流率为150 kg/（m²·s）、热流密度为10 kW/m²工况为例，方形、圆形和正弦形翅片的压降相较于菱形翅片高出约272.4%、116.9%、48.7%，平均沸腾传热系数相较于菱形翅片仅提高20.6%、11.0%、2.7%；以质量流率为300 kg/（m²·s）、热流密度为25 kW/m²工况为例，方形、圆形和正弦形翅片压降相对于菱形翅片分别增加351.1%、121.1%、94.7%，平均沸腾传热系数较于菱形翅片分别提高约24.7%、11.0%、8.8%。基于试验数据修正了离散翅片微通道流动沸腾压降和传热预测关联式，并进行不同翅片综合性能的对比分析，结果表明菱形翅片综合性能更优。
- 微通道 /
- 离散翅片 /
- 流动沸腾 /
- 压降特性 /
- 传热性能
Abstract:
Mini channels with micro pin fins are engineerable heat sinks that can address the high heat flux dissipation for aerospace cooling systems. An experimental investigation of R134a flow boiling heat transfer was conducted in mini channels with circular, square, diamond, and sinusoidal fins, all of which had a hydraulic diameter of 0.67 mm. The experimental parameters covered a dryness range of 0 to 1, mass flux rates ranging from 150 to 300 kg/(m²·s), and heat flux between 10 and 25 kW/m². Results indicated that both the flow boiling pressure drop and the heat transfer coefficient in mini channels increased with higher mass flux and heat flux. A comparative analysis revealed that fin shape had a more pronounced effect on the pressure drop than on the heat transfer coefficient. e.g., when the mass flux was 150 kg/(m²·s) and the heat flux density was 10 kW/m², the pressure drops of square, circular, and sinusoidal fins were approximately 272.4%, 116.9%, and 48.7% higher than those of diamond-shaped fins, while the average boiling heat transfer coefficients only increased by 20.6%, 11.0%, and 2.7% compared with diamond-shaped fins. When the mass flux was 300 kg/(m²·s) and the heat flux density was 25 kW/m², the pressure drops of square, circular, and sinusoidal fins rose by 351.1%, 121.1%, and 94.7% in contrast to diamond-shaped fins, and their average boiling heat transfer coefficients went up by about 24.7%, 11.0%, and 8.8%, respectively, in relative to diamond-shaped fins. Based on the experimental test data, the prediction correlation for discrete fin microchannel flow boiling pressure drop and heat transfer was revised, and a comparative analysis of the overall performance of different fins was carried out. The results demonstrated that diamond-shaped fins had superior overall performance.
- mini channel /
- discrete fins /
- flow boiling /
- pressure drop /
- heat transfer

HTML

图 1 试验系统示意图

Figure 1. Schematic diagram of experimental system

下载: 全尺寸图片幻灯片

图 2 实验件布置示意图^[21]

Figure 2. Schematic diagram of the arrangement of test sections^[21]

下载: 全尺寸图片幻灯片

图 3 不同形状翅片CAD模型图^[21]

Figure 3. CAD model for different pin fins^[21]

下载: 全尺寸图片幻灯片

图 4 不同形状离散翅片微通道压力随干度变化趋势图

Figure 4. Pressure variation of flow boiling in microchannels with different shapes of discrete fins with different mass flow rate and heat flux

下载: 全尺寸图片幻灯片

图 5 局部沸腾传热系数沿程变化（p_sat,in=700 kPa）

Figure 5. Variation of local boiling heat transfer coefficient along the channels （p_sat,in=700 kPa）

下载: 全尺寸图片幻灯片

图 6 试验值与修正后预测值对比图

Figure 6. Comparison between experimental test and correlation predictions

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图 7 不同形状翅片微通道性能综合指标对比图（p_sat,in=700 kPa，G= 300 kg/（m²·s））

Figure 7. Overall performance comparison between various pin fins （p_sat,in=700 kPa，G= 300 kg/（m²·s））

下载: 全尺寸图片幻灯片

表 1 不同形状翅片尺寸设计

Table 1. Geometry parameters of different pin fins

参数	翅片形状
参数	菱形	方形	圆形	正弦形
翅片高度h_fin/mm	0.5	0.5	0.5	0.5
翅片长度L_fin/mm	1.73	1	1	1.73
翅片宽度W_fin/mm	1	1	1	1
纵向间距S_{t, fin}/mm	2	2	2	2
横向间距S_{l, fin}/mm	2.8	2.8	2.8	2.8
水力直径D_h/mm	0.67	0.67	0.67	0.67
翅片列数N_{l, fin}	108	108	108	108

下载: 导出CSV

表 2 摩擦压降倍率因子和换热关联式修正系数

Table 2. Friction pressure drop multiplier and heat transfer correlation correction coefficient

参数	关联式	修正系数
参数	关联式	菱形	方形	圆形	正弦形
摩擦压降倍率因子	$\phi _{\text{l}}^2 = 1 + \dfrac{C}{X} + \dfrac{1}{{{X^2}}}$	C=11	C=45	C=20	C = 8
传热系数	${h_{{\text{tp}}}} = {\xi ^a}{ （\phi _{\text{l}}^2） ^b}{h_{{\text{sp,lo}}}} + C$	a=0.2，b=0.03，C=2500	a=0.2，b=0.03，C=4500	a=0.2，b=0.03，C=3500	a=0.2，b=0.03，C=3500
注：$ \xi $为放大系数；${h}_{\mathrm{s}\mathrm{p},\mathrm{l}\mathrm{o}} $为单液相传热系数；$a、b、C $为常数；${X} $为洛马参数。

下载: 导出CSV

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