壁面脉动传热对气波制冷性能影响研究

doi:10.11949/0438-1157.20201736

摘要/Abstract

摘要：

振荡管内气体温度周期性变化，管束壁面会与管内气体进行同频脉动传热作用，对制冷产生一定影响。搭建振荡管静止式气波制冷实验平台，对壁面温度进行测量研究；同时建立非定常流动传热数值模型，对对流换热量进行研究。实验结果表明，管束壁面最终形成一定温度分布，减薄振荡管束外壁面厚度以改变轴向导热面积，会使稳定后的壁面温度分布更陡峭。数值计算表明，冷端壁面与冷气的对流换热会加热冷气，降低制冷深度。将管束壁厚从10 mm降低至5 mm，制冷性能实验结果表明最大制冷深度提升0.2 K（1.6膨胀比）、0.5 K（1.8膨胀比）与0.4 K（2.0膨胀比），验证了脉动壁面传热对制冷性能的影响。

关键词: 制冷, 非定常流动, 热传导, 数值分析, 对流

Abstract:

The gas temperature in the oscillating tube changes periodically, and the wall surface of the tube bundle will perform the same frequency pulsation heat transfer with the gas in the tube, which will have a certain impact on refrigeration. The static experimental platform of oscillating tube was built to measure the wall temperature. At the same time, the numerical model of unsteady flow and heat transfer was established to study the convective heat transfer. The experimental results show that a certain temperature distribution is formed on the wall of the tube bundle, and the temperature distribution on the stable wall will be steeper by thinning the outer wall thickness of the oscillating tube bundle to change the axial heat conduction area. The numerical calculation shows that the convection heat transfer between the cold end wall and the cold air will make the cold air heated, and finally reduce the refrigeration depth. The experimental results show that the maximum cooling depth increases by 0.2 K (1.6 expansion ratio), 0.5 K (1.8 expansion ratio) and 0.4 K(2.0 expansion ratio) when the wall thickness of tube bundle is reduced from 10 mm to 5 mm, which verifies the effect of pulsating wall heat transfer on refrigeration performance.

Key words: refrigeration, unsteady flow, heat conduction, numerical analysis, convection

中图分类号:

TQ 051.5

刘庭江, 王静娴, 于洋, 赵一鸣, 胡大鹏. 壁面脉动传热对气波制冷性能影响研究[J]. 化工学报, 2021, 72(8): 4073-4080.

Tingjiang LIU, Jingxian WANG, Yang YU, Yiming ZHAO, Dapeng HU. Research of wall pulsating heat transfer on performance of gas wave refrigeration[J]. CIESC Journal, 2021, 72(8): 4073-4080.

图/表 13

图1 实验流程示意图

Fig.1 Schematic diagram of the experimental process

图2 实验装置现场图

Fig.2 Field diagram of experimental device

表1 设备设计参数

Table 1 Design specifications

设备参数	数值
通道长度/mm	330
通道高度/mm	18
通道数量/个	72
转子半径/mm	250
转速/(r/min)	≤2800
间隙尺寸/mm	≤0.02
HP与HT喷嘴偏角/(°)	12.5

图3 不同壁厚气波管束

Fig.3 Gas-wave tube bundles with different wall thicknesses

图4 传热数值计算物理模型及其网格划分

Fig.4 Physical model and meshing of heat transfer numerical calculation

表2 网格与时间步长无关性验证

Table 2 Grid and time step independence test

序号	第一层边界层高度/mm	计算时间步长/s	与1号壁面对流换热量计算结果差异/%
1	0.0015	1×10^-7	0
2	0.0015	1×10^-6	11.4
3	0.0015	1×10^-8	0.48
4	0.0010	1×10^-7	0.21
5	0.0030	1×10^-7	2.18

图5 热通量和壁温实验与计算结果

Fig.5 Experimental and numerical calculation results of heat flux and wall temperature

表3 壁面温度测量实验工况

Table 3 Experimental conditions for temperature measurement

工况编码	膨胀比	高压口温度/K	低温口温度/K	转速/(r/min)
1	1.6	288.5	276.6	2142
2	1.8	287.7	270.0	2322
3	2.0	285.5	265.5	2232

图6 不同壁面厚度轴向温度

Fig.6 Axial temperature of gas-wave tube under different wall thickness

图7 工况2下轴向导热量

Fig.7 Axial heat conduction under working condition 2

图8 温度与对流换热云图

Fig.8 Temperature and convective heat transfer nephogram

图9 不同转速制冷深度

Fig.9 Refrigeration depth at different rotating speeds

表4 不同壁厚制冷深度

Table 4 The refrigeration depth with defferent thickness

膨胀比	转速n/(r/min)	制冷深度?T/K
膨胀比	转速n/(r/min)	10 mm	5 mm
1.6	2308	11.9	12.1
1.8	2412	17.0	17.5
2.0	2520	20.3	20.7

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