微通道换热器波纹片的结构优化

对窗片形式的微通道换热器进行CFD仿真并与试验关联式计算结果进行对比,结果表明KimBullard和Chang-Wang关联式预测的传热因子j与CFD仿真值相比低约0~30%,Kim-Bullard关联式预测的摩擦因子f与CFD仿真值接近,仿真结果具有一定的可靠性。进一步对微通道换热器波纹片进行数值模拟,使用单位迎风面积换热量-单位迎风面积理论功耗曲线评价方法给出2组综合性能较佳的波纹片结构参数,较佳的波纹倾角为13.5°左右。     

微通道换热器空调系统性能试验分析

本文通过对两套采用微通道换热器的KFR-72LW空调器样机（1号机：室内外换热器均采用微通道换热器;2号机：室外机为微通道换热器,室内机为管翅式换热器）,分别进行性能测试,对比分析采用微通道换热器与管翅式换热器的空调器性能差异。试验结果分析显示：微通道换热器空调器具有高效（强制冷性能）、减排（减少制冷剂充注量）、低成本（换热器小型化）等优点;但制热工况下,因室外机采用微通道换热器,换热面积大幅度减小,蒸发压力过低,导致制热效果不良、系统频繁除霜等问题,有待于进一步研究解决。     

微通道换热器和翅片管式换热器性能对比试验研究

采用一种用于比较不同换热器传热性能的测试方法和数据分析方法,对比分析一款风冷涡旋式冷水机组使用的微通道换热器和9.52 mm管翅片管式换热器的传热性能差异。分别在25.0℃,35.0℃和43.3℃环境温度下,当压缩机的运行频率在12~50 Hz范围内变化时,对换热器性能进行测试,评估换热器的传热性能差异和整机性能差异。测试数据表明,当修正的冷凝传热温差相同时,在25.0℃,35.0℃和43.3℃环境温度工况下,微通道换热器的冷凝传热量比翅片管式换热器分别高约8.6%~11.3%,13.5%~28.6%和16.4%~36.6%。微通道换热器相比翅片管式换热器在冷凝传热性能方面具有一定优势。     

微通道换热器用于家用柜机空调时整机性能的对比实验研究

微通道换热器的应用日益普遍。文章通过将微通道换热器引入3 HP柜式家用空调,并对系统性能和充注量等进行了对比研究。实验表明:当只更换室内换热器,室内微通道换热器翅片间距为1.4 mm时,系统性能达到最优:与原机相比,系统充注量降低15.9%,制冷量基本相当,制冷COP提高2.2%;制热量比原机提高3.9%,制热COP则提高了11.2%。当将室内外换热器都更换为微通道换热器后,系统的充注量降低54%,与原机相比:制冷量提高0.8%,系统COP提高5.2%;当制冷剂更换为R290时,系统最优充注量降为500 g。     

亲水涂层对微通道换热器空气侧性能的影响

对微通道换热器进行了亲水表面处理,并对其性能进行了实验研究,分析了亲水处理对微通道换热器湿工况性能的影响。实验表明,亲水处理对换热器性能有利:与无涂层换热器相比,亲水处理换热器换热量最多增大7.0%,压降减小0.7%～18.9%。而随着翅片间距的减小和芯体厚度的增加,亲水处理带来的性能提升减弱。     

两种换热器在车用四通阀热泵系统中的对比研究

PTC加热效率较低对电动汽车行驶里程影响较大,因此开发效率更高的热泵系统十分必要。实验搭建了四通阀热泵系统,并将两种不同流程排布的小管径换热器与微通道换热器分别被用于室外侧,在制冷、制热模式下进行了实验对比,由实验结果可知,在制热模式低风速下,小管径换热器相比微通道换热器,能力可以高出10.5%,而COP与微通道换热器相近;在制冷模式低风速下,小管径换热器样件能力可高出3.8%,COP可高出22.8%。但随风速的提高,小管径换热器能力和COP提升并不明显,而微通道换热器随风速提升幅度较大,由上可知,在风速较低的怠速和城市工况中,使用小管径换热器作为车用热泵的外侧换热器使用拥有一定的优势。     

小管径铜管换热器的性能及成本分析

对比分析采用R410A制冷剂的Ф7mm铜管换热器与Ф5mm铜管换热器的性能与成本。测试结果表明,在相同的测试工况和迎风尺寸下,Ф5mm铜管换热器的换热效果比Ф7mm铜管换热器的好,可以节约大量铜材和铝材,且制冷剂充注量减少。     

表面处理对微通道换热器湿工况性能及长效特性的影响

对翅片间距为1.1mm的微通道换热器进行了亲水和疏水表面处理,并对其不同工况下的性能进行了实验研究,分析了表面处理对微通道换热器湿工况性能和长效特性的影响。实验表明,疏水表面处理在低风速下会造成换热器性能衰减：与原换热器相比,经过疏水表面处理的换热器换热量最大减小14%,衰减随着风速的变大而减小;而压降除了高风速高湿度工况,其余工况下均升高130%以上。亲水表面处理对换热器性能影响较小：与原换热器相比,经过亲水表面处理的换热器在不同工况下性能衰减2%-8%;压降仅在高湿度低风速下明显变大17%,其余大部分工况得到改善,在高湿度高风速下压降仅为原换热器的50%。亲水表面处理在防腐蚀方面具有一定作用,同时进行盐雾腐蚀260h后,表面亲水处理的换热器在不同工况下比原换热器性能提升4%-6%,压降降低14%-16%。     

颗粒物污染室外换热器对家用空调系统性能影响研究

分别配置了采用传统铜管铝翅片换热器与采用全铝微通道换热器的1.5匹分体式家用空调,将其置于相同的大气环境中长期连续运行,测试了大气颗粒物污染的两台家用空调换热器的堵塞率和空调系统的长效性能。测试结果表明:换热器的堵塞率呈指数性增长趋势,采用管片式换热器的原机被大气颗粒物污染后制冷量衰减2.1%,功耗上升了6.2%,能效比下降了7.8%;采用微通道换热器的机组性能衰减明显高于原机,制冷量衰减了23.2%,功耗增加了34.6%,能效衰减了43.1%。相比之下微通道换热器更易受颗粒物污染的影响。     

错流微通道低温交叉换热等体积补偿机理研究

建立了错流微通道低温交叉换热系统物理模型、不同尺度错流微通道单元数学模型及传热单元数值模型。针对不同错流微通道模型,提出了等体积补偿理论计算模型及计算方法,并进行了单元模型传热数值模拟研究。构建了不同尺度及形状错流微通道实验模型并对单元理论模型及数值模型进行了实验验证。研究表明:等体积补偿法可用于解决复杂错流微通道换热器换热面的工程计算难题,为不同尺度不同结构的微通道错流交叉换热设计提供理论依据及工程设计计算方法。     

圆孔和半圆孔交叉翅片管的传热与流阻性能研究

本文提出一类可用于结霜和灰尘较多场合的新型翅片——圆孔和半圆孔交叉翅片。为了考察这类翅片的性能特征,对9种不同几何参数的单排肋管式换热器样件在吸风式直流热风洞内进行了实验。这些几何参数包括圆孔、半圆孔的直径和位置。通过多元线性回归法将实验数据整理为以雷诺数和换热器几何参数为自变量的j和f关联式。结果表明开孔参数对换热性能有明显影响,而对阻力影响不显著。与平片相比,样片3的平均当量换热系数提高18.3％,节约金属耗材12％。     

平行流换热器在空调机上的应用研究

介绍全铝平行流换热器与传统铜管套翅片式换热器的结构区别,并从结构上分析全铝平行换热器的寿命、换热性能、阻力、重量等方面比传统铜管套翅片式换热器优化的情况,同时,通过在风冷式空调机上的测试,和传统铜管套翅片式换热器进行换热性能和空调系统性能对比,探讨平流式换热器在风冷式空调机上的应用可行性,为今后平行流换热器在风冷式空调...     

一种新型板式换热器

介绍一种区别于传统人字形波纹板式换热器的新型微板换热器,该换热器具有压降小而换热能力强,材料消耗少,可靠性好,制冷剂充注量小,设计灵活等特点,同时介绍其在应用和节能减排上的优势。     

容器内板翅式换热器(CIV)的设计开发

介绍容器内板翅式换热器的特点及其应用领域,阐述CIV换热器设计过程中的要点和难点,提出为解决难点所采取的设计方案。     

Effectiveness of crossflow plate heat exchanger for indirect evaporative cooling: Efficacité des échangeurs thermiques à plaques, à courants croises pour refroidissement indirect évaporatif

A short-cut method for calculating the effectiveness of wet surface crossflow plate heat exchangers is developed. It introduces a correction for the effectiveness estimated according to the method of Maclaine-cross and Banks. For this purpose a new model with a water film that flows down, corresponding to the real conditions in these heat exchangers, is developed. The method of Maclaine-cross and Banks is improved by an approach to determine the mean water surface temperature and by derivation of an equation for calculating the ratio of total to sensible heat taking into account the barometric pressure. Performance predictions by this method for wet surface crossflow plate heat exchangers are found to agree with the finite difference solutions.     

制冷剂种类与翅片管换热器管径的匹配特性

针对空调用翅片管换热器,本文研究了4种制冷剂在管内的流动阻力及表面传热系数随换热器管径的变化,通过模拟计算给出不同制冷剂对应的最佳换热器管径。根据实际空调器系统确定相关参数,计算得到管内流动阻力损失由大到小依次为R22、R290、R410A、R32,表面传热系数由大到小依次为R32、R410A、R290、R22。在空调器制冷工况,满足换热量需求的条件下,冷凝器入口压力(压缩机排气压力)越低,系统效率越高;根据模拟计算,换热量为2 000 W时,随着换热器管径的增大,不同制冷剂对应的冷凝器入口压力先降低后增加,得到最适宜的换热器管径:R22为7～7.5 mm,R410A与R32为6～6.5 mm,R290为6.5～7 mm。     

Non-ideal regenerator performance — the effect of void volume fluid heat capacity

The performance of thermal regenerators is analysed for a range of parameters of particular interest for low temperature refrigeration. Using a time-dependent one-dimensional, incompressible flow, numerical model we show that the void volume fluid heat capacity can strongly influence regenerator behaviour. Inclusion of the void volume term gives significant improvements in the predicted effectiveness when the void volume and matrix heat capacities are of the same order. For some regimes of low thermal loads increasing the matrix heat capacity may actually reduce the effectiveness.     

Thermal design method of bayonet-tube evaporators and condensers

The paper describes an effectiveness-NTU design method of bayonet-tube evaporators and condensers. Including the effect of the wall superheat on the shell-side film coefficient, and using an energy balance on the tube, differential equations for the steady-state fluid temperatures are formulated. Because of the nonlinear nature of the governing equations, the fourth-order Runge-Kutta method is employed to the solution of the finite difference equations. The results are iterated with the combination of integration techniques. An upper bound to the numerical error being ±5% the fluid temperature distribution as well as the exchanger effectiveness are determined, and presented as a function of the Hurd number, the number of heat transfer units and the flow arrangement. For flow entering through the inner tube, the temperature distribution displays the occurrence of a minimum at a point other than the tube-tip of the exchanger. In an extension of the analysis, an effort is made to illustrate the deviation of the results obtained by uniform film coefficient from the present study, and the differences are outlined.     

Estimation of performance of a J-T refrigerators operating with nitrogen-hydrocarbon mixtures and a coiled tubes-in-tube heat exchanger

The exergy efficiency of Joule-Thomson (J-T) refrigerators operating with mixtures (MRC systems) strongly depends on the choice of refrigerant mixture and the performance of the heat exchanger used. Helically coiled, multiple tubes-in-tube heat exchangers with an effectiveness of over 96% are widely used in these types of systems. All the current studies focus only on the different heat transfer correlations and the uncertainty in predicting performance of the heat exchanger alone. The main focus of this work is to estimate the uncertainty in cooling capacity when the homogenous model is used by comparing the theoretical and experimental studies. The comparisons have been extended to some two-phase models present in the literature as well.Experiments have been carried out on a J-T refrigerator at a fixed heat load of 10 W with different nitrogen-hydrocarbon mixtures in the evaporator temperature range of 100–120 K. Different heat transfer models have been used to predict the temperature profiles as well as the cooling capacity of the refrigerator. The results show that the homogenous two-phase flow model is probably the most suitable model for rating the cooling capacity of a J-T refrigerator operating with nitrogen-hydrocarbon mixtures.     

On the generation of entropy in a counterflow heat exchanger

Entropy generation in a counterflow heat exchanger has been analysed in detail and expressions have been derived in terms of relevant non dimensional parameters. In the case of nearly ideal heat exchangers with nearly balanced capacity rate, an expression for entropy production has been derived which matches closely with exact calculation.