电子膨胀阀制冷剂流量系数的试验研究

在自搭建的液环法节流机构流量特性试验台上,采用R22制冷剂,试验研究节流阀开度(流通面积)、节流前后压差、入口密度、入口过冷度、出口比容、干度以及阀头半锥角和径向间隙对电子膨胀阀制冷剂流量系数的影响,获得了流量系数的量化关系并进行了试验验证.结果表明,误差在±10.5%以内.     

短管节流流量特性实验研究

通过毛细管与短管节流气态流量特性的实验研究,对比分析两者的气态流量特性,得出节流短管气态流量与孔径的函数关系,证明节流短管内制冷剂的流量函数与N2的流量函数类似,短管节流与毛细管节流具有相似的气态流量特性,可以将节流短管当作长度较短的毛细管进行研究。     

毛细管的进出口状态参数对制冷剂流量的影响

本文建立了绝热毛细管的分布参数仿真模型,分析了毛细管内制冷剂的流动特性,得出了毛细管进口压力、进口过冷度和出口压力对制冷剂流量的影响情况.     

机房空调负落差长连管系统膨胀阀前过冷度研究

机房空调在负落差长连管安装方式下会产生启动时低压报警和过冷度较小等问题,对机组运行的稳定性、可靠性和性能产生影响。本文理论计算R407C制冷剂名义工况下不同负落差时膨胀阀前过冷度和压缩机排气压力,发现膨胀阀前过冷度与负落差呈负相关关系,制冷剂在膨胀阀中可能会闪发。基于此,采用带储液罐的空调机组,试验分析储液罐分别位于冷凝器出口处和膨胀阀进口处时膨胀阀前的过冷度,结果表明,储液罐位于膨胀阀进口处可以有效保障膨胀阀前过冷度并降低压缩机排气压力。     

采用R134a和R600a制冷剂系统毛细管特性分析

建立毛细管模型并通过实验数据验证了模型,给出制冷剂的干度x、温度t、速度W、压力P沿毛细管长度的变化关系,研究了毛细管的内直径、长度、冷凝温度、过冷度等因素对毛细管内R134a、R600a两种制冷剂的质量流量的影响.     

制冷剂充注量对冷藏车用制冷机组性能的影响

为了研究制冷剂充注量对冷藏车用制冷机组性能的影响,在数值模拟得到的制冷剂标准充注量的基础上,试验研究制冷剂充注量对压缩机吸/排气压力、吸/排气温度、蒸发器出口过热度、冷凝器出口过冷度及制冷能力的影响。研究表明,数值模拟方法得到的制冷剂标准充注量适用于实际制冷机组。     

翅片管换热器过冷管设计对系统性能影响研究

试验对比研究在翅片管换热器底部设置1根U形管过冷、2根并联U形管过冷、2根串联U形管过冷的过冷效果,测试数据表明用2根U形管串联进行过冷的效果最好。当把2根铜管串联用于过冷时,对R22制冷剂在B工况测试条件下,与没有过冷相比,过冷度增加了1．1℃,能效比高出0．33W／W,提高了8．25％;对R410A制冷剂在B工况测试条件下,与没有过冷相比,过冷度增加了2．0℃,能效比高出0．10W／W,提高了2．69％。     

分体式空调器长连接管制冷剂追加量的试验研究

基于制冷量为12 kW的风管送风式空调(热泵)机组进行试验研究,分析节流位置、工况等因素对长连接管制冷剂追加量的影响,得出9.52 mm液管和15.88 mm气管条件下R410A制冷剂追加量的参考值。研究发现,对于单冷型空调器,节流位置会对长连接管的制冷剂追加量产生较大影响,室内机节流时的追加量大于室外机节流;而对于热泵型空调器,节流位置对长连接管制冷剂追加量的影响较小。     

R134a闭式喷雾冷却传热性能实验研究

本文搭建了以R134a为工质的闭式喷雾冷却系统实验台,通过实验分析了稳态下制冷剂流量,过冷度和充注量对传热性能的作用规律,其中制冷剂流量范围为0.20~0.25 U/min,过冷度范围为5~8 ℃,充注量范围为0.95~1.25 kg。研究表明:在制冷剂流量为0.184 L/min,充注量为0.95 kg条件下,实验获得最大热流密度为105.25 W/cm2 ,最大表面传热系数为2.54W/（cm2?℃）。低热流密度(45.93~72.55 W/cm2)条件下,随着制冷剂流量,过冷度和充注量的增大,表面传热系数总体呈上升趋势;高热流密度(84.02~105.25 W/cm2)条件下,随着流量的增大,表面传热系数逐渐增大,而随着过冷度及充注量的增大,表面传热系数先增大再趋于稳定。雅各布数随着制冷剂充注量的增大逐渐减小,这对高热流密度下表面传热系数的提升不利,存在一个最佳充注量使得闭式唢雾冷却系统传热性能最佳。     

采用非共沸混合工质机械过冷的跨临界CO_2制冷循环性能分析

本文提出了非共沸混合工质机械过冷跨临界CO_2制冷循环。在最优排气压力和最优过冷度下循环取得最大COP。最大COP、最优排气压力和过冷度与混合制冷剂的温度滑移密切相关。当选取合理温度滑移的混合工质作为机械过冷循环的制冷剂时,可明显提升CO_2制冷循环能效,降低排气压力。与基本CO_2制冷循环相比,在蒸发温度为-40℃、环境温度为35℃时,采用R32/R152a(40/60)循环总COP可提升46.53%,CO_2排气压力可降低2.758 MPa。总COP的提升程度受混合制冷剂的温度滑移影响显著,推荐机械过冷循环使用温度滑移合理的混合制冷剂。在温暖和炎热的气候地区及冷冻冷藏等低温应用领域,采用非共沸混合制冷剂机械过冷跨临界CO_2制冷循环整体性能的提升更加显著。     

Mass flow rate of R-410A through short tubes working near the critical point

Experimental data were taken to examine R-410A mass flow rate characteristics through short tube restrictors at upstream pressures approaching the critical point. Four short tube restrictors were tested by varying upstream pressure from 2619 to 4551 kPa (corresponding to saturation temperature from 43.9 to 71.7 °C), upstream subcooling from 2.8 to 11.1 °C and downstream pressure from 772 to 1274 kPa. The experimental data were represented as a function of major operating parameters and short tube diameter. As compared to mass flow trends at typical upstream pressures, flow dependency on upstream subcooling was more significant at high upstream pressures due to a higher density change. Based on the database obtained from this study and literature, an empirical correlation was developed from a power law form of dimensionless parameters generated by the Buckingham Pi theorem. The post-predictions of the new correlation yielded average and mean deviations of 0.11 and 2.4%, respectively.     

Experimental investigation of two-phase flow characteristics of HFC-134a through short-tube orifices

The two-phase flow characteristics of HFC-134a, including flow pattern, mass flow rate, pressure distribution and temperature distribution through short-tube orifices are experimentally investigated. Short tube diameters ranging between 0.605 and 1.2 mm with length-to-diameter ratios ranging between 8.3 and 33 are used in the experiments. The test runs are performed at upstream pressure ranging between 900 and 1300 kPa, downstream pressure ranging between 300 and 400 kPa, and degree of subcooling ranging between 1 and 12 °C. Two groups of short-tube orifices are used in the experiment. The first is used to visualise the flow pattern. The second is used to measure temperature and pressure distributions along the tube. The results from the present experiment show that metastable flow and choked flow phenomena exist inside the short-tube orifices over the whole range of experimental conditions. The metastable liquid flow region increases with increasing degree of subcooling and upstream pressure. The mass flow rate is directly proportional to upstream pressure and degree of subcooling. The results of pressure distribution inside the short-tube orifices indicate that accelerational pressure drop at the inlet and outlet has a significant effect on the total pressure drop across the short-tube orifice.     

Analysis of refrigerant flow and deformation for a flexible short-tube using a finite element model

A finite element model was used to simulate single-phase flow of R-22 through flexible short-tubes. The numerical model included the fluid-structure interaction between the refrigerant and the deformation of the short-tube as upstream pressure was varied. The finite element model was developed using a commercially available finite element package. Short-tubes with moduli of elasticity ranging from 5513 to 9889 kPa were studied. Four upstream and downstream pressures were applied and the upstream subcooling was held at a constant value of 16.7 °C. Mass flow rates from the numerical model were compared to available published experimental results. The study showed that upon deformation the short-tube resembled the shape of a converging-diverging nozzle. Both tube inlet and outlet had a chamfered-like shape after deformation which reduced the pressure drop at the tube inlet. The smaller the modulus of the tube, the larger the chamfered-like angle at the inlet and the higher the pressure drop along the tube due to the higher tube contraction. The results illustrated that as the upstream pressure was increased by 45%, there was almost a 60% decrease in the flow area. The more flexible (5513 kPa) short-tube restricted the mass flow rate more than the most rigid (9889 kPa) short-tube used in this study. The mass flow rates estimated with the finite element model were as much as 14% higher than those from experimental results reported in the literature.     

Capillary tube selection for HCFC22 alternativesSélection de capillaires pour les frigorigènes de remplacement du HCFC22

In this paper, pressure drop through a capillary tube is modeled in an attempt to predict the size of capillary tubes used in residential air conditioners and also to provide simple correlating equations for practicing engineers. Stoecker's basic model was modified with the consideration of various effects due to subcooling, area contraction, different equations for viscosity and friction factor, and finally mixture effect. McAdams' equation for the two-phase viscosity and Stoecker's equation for the friction factor yielded the best results among various equations. With these equations, the modified model yielded the performance data that are comparable to those in the ASHRAE handbook. After the model was validated with experimental data for CFC12, HFC134a, HCFC22, and R407C, performance data were generated for HCFC22 and its alternatives, HFC134a, R407C, and R410A under the following conditions: condensing temperature; 40, 45, 50, 55°C, subcooling; 0, 2.5, 5°C, capillary tube diameter; 1.2–2.4 mm, mass flow rate; 5–50 g/s. These data showed that the capillary tube length varies uniformly with the changes in condensing temperature and subcooling. Finally, a regression analysis was performed to determine the dependence of mass flow rate on the length and diameter of a capillary tube, condensing temperature, and subcooling. Thus determined simple practical equations yielded a mean deviation of 2.4% for 1488 data obtained for two pure and two mixed refrigerants examined in this study.     

Experimental investigation on diabatic flow of R-134a through spiral capillary tube

The present experimental investigation has been carried out to investigate the effects of various geometric parameters on the mass flow rate of R-134a through diabatic spiral capillary tube. In diabatic flow, the capillary tube is bonded with the compressor suction-line to form a counter-flow exchanger. The lateral type of diabatic capillary tube has been investigated in the present experimental study. The major geometric parameters investigated are capillary tube diameter, capillary tube length and coil pitch. In addition, effect of inlet subcooling on the mass flow rate through diabatic spiral capillary tube is also done. A comparison of the performance of diabatic spiral capillary tube has been made with adiabatic spiral capillary tube. Generalized empirical correlation for diabatic spiral capillary tube has also been proposed. It has been found that the predictions of the proposed correlation lie in the error band of ±7%.     

采用制冷剂R410A的绝热毛细管特性仿真

基于能量守恒、动量守恒、质量守恒方程,建立描述绝热毛细管特性的数学模型.毛细管内制冷剂流量的模型仿真结果与实测数据的差别小于5%,说明仿真结果具有可信度.用模型研究了通过毛细管的制冷剂质量流量随毛细管的内直径、长度、冷凝温度和蒸发温度的变化关系.仿真结果可以用于指导采用R410A的空调系统的设计和实验,具有很好实际应用价值.     

Intensive parameter analysis of adiabatic capillary tube using approximate analytic solution

Parameter analysis is helpful to have an insight into the flow characteristics of capillary tubes. Based on the approximate analytic solutions developed by the author, influences of geometrical parameters (inner diameter and length) and inlet operating parameters (pressure, subcooling or quality) on the mass flow rate through an adiabatic capillary tube have been intensively studied in this work. Some simple theoretical relations have been developed. The relations show that the mass flow rate is the power function of the geometries. For the subcooled inlet, good generic linearity between (2−C₂) power of the mass flow rate and the inlet operating parameters was deduced. With further approximation, some well-known linear trends could be theoretically interpreted. For the low quality inlet, good linearity between (C₂−2) power of the mass flow rate and the inlet quality was proposed. Approximately, the reciprocal of the mass flow rate is linear with the inlet quality. Experimental data supplemented by numerical data for R22, R410A and R407C are employed to verify the relations.     

R134a喷雾冷却系统换热性能研究

本文建立了以R134a为冷却工质的封闭式喷雾冷却系统,研究了工质过冷度、质量流量和热流密度对喷雾冷却系统换热性能的影响。其中,工质过冷度由喷嘴入口前的过冷段控制,质量流量通过变频齿轮泵调节,热流密度通过改变加热电源电压和电流控制。实验结果表明,在热流密度和质量流量保持不变时,改变过冷度对热源表面温度和换热系数的影响并不明显;在热流密度和过冷度保持不变的条件下,系统存在一个临界质量流量值,在质量流量达到临界值之前,热源表面温度随质量流量的增大而降低,当质量流量高于临界值时,热源表面温度随质量流量的增大而升高;当质量流量和过冷度保持不变时,存在一个热流密度使液滴的蒸发量等于补充量,在此热流密度下热源表面系数能达到最大。     

A comparison of critical flow models for estimating two-phase flow of HCFC22 and HFC134a through short tube orifices

An experimental study to investigate the critical flow of refrigerants through short tube orifices has been performed by measuring the mass flowrates and pressure profiles along the short tube orifice. Eight critical flow models have been examined and their results compared with the experimental data for HCFC22 and HFC134a. These models include four homogeneous equilibrium models, two homogeneous frozen models, and two non-homogeneous equilibrium models. The data indicate that the flow was choked when downstream pressures were lower than the saturation pressure corresponding to the upstream temperature. The observed flows through short tube orifices included a lack of equilibrium due to short time of expansion and homogeneous mist flow at the exit plane. These flow trends would be more consistent with the basic assumptions of the homogeneous frozen models. Based on the comparison of the existing critical flow models and experimental data, the homogeneous frozen models showed the best agreement with the measured data except for exit qualities below 0.06.     

Analysis and modelling of water based bubble pump at atmospheric pressure

Bubble pump (BP), an essential component in coffee percolators, is used to drive solar water heating systems and single pressure absorption refrigerators. However, its mass flow rate cannot be readily predicted. Heat input, tube diameter and submergence ratio affect its mass flow rate. BP has the same working concept as air-lift pump, but its flow is complicated due to the condensation of vapour bubbles. Neither curve fitting models, nor air-lift pump models, can predict the mass flow rate with high fidelity. A new model based on the pumping characteristics of BP is presented and verified by a water based setup at atmospheric pressure. Results show that the average errors for the BP with tube diameter of 6–12 mm, and for the BP with submergence ratio of 0.5–0.8 are 13% and 11%, respectively. The BP performance increases when the tube diameter decreases or the submergence ratio increases.