基于R1234yf和R134a制冷剂的太阳能-空气源复合热泵性能对比

随着化石能源的过度消耗与环境问题日益加剧,发展清洁可再生能源势在必行。针对太阳能-空气源复合热泵系统性能进行分析,结果表明:模式二时,太阳能热泵系统与空气源热泵系统的COP分别为6.55和4.81;平板式太阳能集热器的热效率高达67.86%;在相同制热功率条件下,与模式一相比,模式二时空气源热泵耗功平均降低87.81%,太阳能热泵耗功平均降低16.17%;采用R1234yf的系统耗功比R134a系统高2%~3.17%,但R1234yf的温室效应值极低。     

R134a在水平高效强化蒸发管内流动沸腾传热特性的实验研究

本文阐述了新型替代工质HFC—134a在内螺旋微翅片强化蒸发管内水平流动沸腾换热实验研究。归纳总结了大量沸腾换热性能曲线，揭示了壁面温度沿轴向变化的规律以及沸腾换热系数与热流密度及质量流量等的因变关系，并获得了强化管的换热强化倍率。     

超临界R134a在ORC系统中的换热特性分析

采用有限元分析软件FLUENT对超临界有机朗肯循环系统中的换热器进行数值分析,进而对其进行设计和优化。超临界R134a在长为2 100 mm,直径为4 mm的光管换热器中分别进行向上流动和向下流动。换热边界条件是定热流密度,流体的进口压力P为4.5 MPa,进口温度Tin为349 K。分别探究热流密度q、质量流量G、热流质量比q/G和浮升力对传热特性的影响。采用无量纲数Bo来预判浮升力对传热的影响。虽然Morky的工作流体不是超临界R134a,但他们的经验公式也能用来更好地预测超临界R134a在光管中向上流动的传热特性。     

三维微肋螺旋管内R134a沸腾环状流区的传热与关联式

首次实验研究了制冷剂R134a在三维微肋螺旋管内流动沸腾环状流区的流动与传热性能。对流型的可视化观察发现：当质量流速大于100kg／(m^2s)时。螺旋管内才开始出现环状流。环状流的起始干度为0．3、0．4。在流型图上给出了环状流区与其它主要流型的分区。回归了实验环状流区的传热实验数据，得到的传热关联武计算值与实验值的平均绝对误差为9．1％。     

R1234yf/R152a用作汽车空调制冷剂的配比范围研究

使用PR方程结合vdW法则建立了R1234yf/R152a的热物性模型,在此基础上结合余函数法编制了R1234yf/R152a的热力性质和制冷系统循环性能计算程序。在汽车空调制冷工况下,获得了R1234yf/R152a在不同摩尔组分比下的压力比、排气温度、COP、单位质量制冷量、单位体积制冷量和压缩机吸气口比容,并与R134a和R1234yf/R134a(0.89/0.11)进行了比较。之后,结合燃烧速度、GWP与循环性能获得了适宜的摩尔组分比范围。当R1234yf的液相摩尔分数在0.65～0.67时,R1234yf/R152a为近共沸混合物,具有较高的安全性,且制冷循环性能与R134a较为接近。     

基于ASOG-VISCO基团贡献理论的胺类溶液黏度模型

收集了三乙胺、三丙胺、三正丁胺与正己烷、正辛烷、异辛烷、正十四烷、2-戊酮、3-戊酮、4-甲基-2-戊酮、三氯甲烷、苯、环己烷以及醇类物质所组成的16种含有胺类物质二元溶液的运动黏度实验数据,并且结合绝对速率理论以及ASOG基团贡献法建立了一种用以计算胺类混合溶液运动黏度的理论模型,利用文献实验数据在该模型的基础上回归...     

不同状态方程计算螺杆膨胀机膨胀过程的比较

膨胀过程是螺杆膨胀机工作的基本过程,利用实际气体状态方程来计算该过程可为分析问题带来方便。本研究通过采用计算膨胀过程的一般方法,分别导出了利用RKS方程和BB方程计算膨胀过程的公式,并针对R245fa有机工质在螺杆膨胀机内的膨胀过程,利用RKS方程、BB方程与工质物性计算软件Ref Prop对螺杆膨胀机的膨胀过程进行了计算比较。结果发现,RKS方程和BB方程都有较高的计算精度,计算结果的相对误差均在4%以内,但RKS方程的精度更高,其相对误差比BB方程小1%左右,因此,更适合以R245fa为工质的螺杆膨胀机膨胀过程的计算。     

湖泊富营养化因子对叶绿素a影响的SEM分析

根据湖泊富营养化成因机理,采用结构方程模型(SEM),引入物理环境、有机物、营养盐和浮游植物4个潜变量,并结合选取的5个影响因子,建立了富营养化结构方程模型,以便模拟各因子对巢湖流域南淝河入巢湖口水体中叶绿素a的影响。结果表明,该模型揭示了富营养化各要素与叶绿素a之间的复杂关系,与其他方法相结合可直接预测叶绿素a的浓度。     

加入少量R290对R744热泵热水器性能变化的模拟分析

本文针对R744热泵热水器系统,考虑系统部件结构参数,建立了系统仿真模型。利用该模型分析了加入少量R290对R744热泵热水器系统性能变化的影响,发现当加入3%的R290时,相比纯R744装置,系统性能最优,其系统制热系数略有增加,最优放热侧压力稍有降低,并预测分析了该配比下,热汇水出水温度为45℃、50℃、55℃、60℃、65℃时系统主要循环性能。结果表明,在纯质R744中加入少量R290组成混合工质既可以提高系统循环性能,又能降低系统放热侧压力。     

Comparison of R 134a and R 12 refrigerants in a vapour-compression system

The performance of a vapour-compression system was examined with both R12/mineral oil and R134a/mineral oil charges. The mineral oil was then removed from the system using a multiple flushing method and the experiments repeated using a charge of R134a and an ester-based lubricant to establish the effect of the oil on the performance of the system. Results were compared with theoretical data for R134a and R12 refrigerants.     

Experimental study of R152a and R32 to replace R134a in a domestic refrigerator

This paper presents an experimental study of R152a and R32, environment-friendly refrigerants with zero ozone depletion potential (ODP) and low global warming potential (GWP), to replace R134a in domestic refrigerator. A refrigerator designed and developed to work with R134a was tested, and its performance using R152a and R32 was evaluated and compared with its performance when R134a was used. The results obtained showed that the design temperature and pull-down time set by International Standard Organisation (ISO) for small refrigerator were achieved earlier using refrigerant R152a and R134a than using R32. The average coefficient of performance (COP) obtained using R152a is 4.7% higher than that of R134a while average COP of R32 is 8.5% lower than that of R134a. The system consumed less energy when R152a was used. The performance of R152a in the domestic refrigerator was constantly better than those of R134a and R32 throughout all the operating conditions, which shows that R152a can be used as replacement for R134a in domestic refrigerator.     

Shell-and-tube evaporator model performance with different two-phase flow heat transfer correlations. Experimental analysis using R134a and R1234yf

This work presents a model of a shell-and-tube evaporator using R1234yf and R134a as working fluids. The model uses the effectiveness-NTU method to predict the evaporation pressure and the refrigerant and secondary fluid temperatures at the evaporator outlet, using as inputs the geometry of the evaporator, the refrigerant mass flow rate and evaporator inlet enthalpy, and the secondary fluid volumetric flow rate and evaporator inlet temperature. The model performance is evaluated using different two-phase flow heat transfer correlations through model outputs, comparing predicted and experimental data. The output parameter with maximum deviations between the predicted and experimental data is the evaporating pressure, being the deviations in outlet temperatures less than 3%. The evaporator model using Kandlikar's correlation obtains the highest precision and the lowest absolute mean error, with 4.87% in the evaporating pressure, 0.45% in the refrigerant outlet temperature and 0.03% in the secondary fluid outlet temperature.     

Effect of void fraction models on the two-phase friction factor of R134a during condensation in vertical downward flow in a smooth tube

The void fraction of R134a condensing inside a vertical smooth tube is experimentally investigated in this study. The vertical test section is a 0.5 m long countercurrent flow double tube heat exchanger with refrigerant flowing down the inner tube and cooling water flowing upward in the annulus. The inner tube is made from smooth copper tubing and has an 8.1 mm inner diameter. The test runs are done at an average saturated condensing temperature of 40 °C. The average qualities are between 0.8 and 0.99 while the mass fluxes are 300 kg m^− 2s^− 1 and the heat fluxes are between 22 and 39.8 kW m^− 2. The void fractions are indirectly determined using relevant measured data together with various void fraction models and correlations reported in the open literature. The friction factors obtained from various void fraction models and correlations are compared with each other and also with those determined from graphical information provided by Bergelin et al. The effect of void fraction alteration on the momentum pressure drop is also presented.     

Comparative study on evaporator heat transfer characteristics of revolving heat pipes filled with R134a, R22 and R410A

Heat pipes are used extensively in various applications including the heating, ventilating and air conditioning (HVAC) systems. The high thermal conductivity of the device, attributed from the two-phase heat transfer processes within the heat pipe, made them superior heat exchanger devices. Heat pipes had been widely used in HVAC applications in energy conservation, dehumidification enhancement, heat dissipation, etc. A number of researches have been conducted to expand the applicability of heat pipes in HVAC in Malaysia, especially in air-to-air heat recovery using stationary heat pipes. However, the potential usage of rotating heat pipe in heat recovery in tropical countries like Malaysia was yet to be explored. Hence, the potential of rotating heat pipe in the HVAC systems used in tropics was explored through a parametric study that incorporates rotational speeds, off-axis displacements and varied refrigerants. The rotating heat pipes charged with R134a, R22 and R410A were tested with varied radial displacement from the rotational axis. The straight and leveled heat pipe with the furthest radial displacement yields the most significant heat transfer, which was attributed to the magnitude of the generated centrifugal force, and effective distribution of liquid in the evaporator.     

Performance of a scroll compressor with R134a at medium temperature heat pump conditions

The isentropic and volumetric efficiency of a scroll hermetic compressor is measured using R134a under medium temperature heat pump conditions. The evaporating temperature ranges from 3 to 36°C and the condensing temperature from 34 to 78°C. The efficiency parameters are fitted to functions of the suction and discharge pressures. At the same port pressures, there are only small differences between the isentropic and volumetric efficiency parameters for R134a and those for R22, the latter determined from the manufacturer's data. The efficiency parameters for R134a are used to compare the performance of the compressor with R12, R134a and R152a in a medium temperature heat pump cycle. The COP and heating capacity exhibit trends similar to those in previous experimental data for a reciprocating compressor.     

A solar ejector cooling system using refrigerant R134a in the Athens area

This paper describes the performance of an ejector cooling system driven by solar energy and R134a as working fluid. The system operating in conjunction with intermediate temperature solar collector in Athens, is predicted along the 5 months (May–September). The operation of the system and the related thermodynamics are simulated by suitable computer codes and the required local climatologically data are determined by statistical processing over a considerable number of years. It was fount that the COP of ejector cooling system varied from 0.035 to 0.199 when the operation conditions were: generator temperature (82–92 °C), condenser temperature (32–40 °C) and evaporator temperature (−10–0 °C). For solar cooling application the COP of overall system varied from 0.014 to 0.101 with the same operation conditions and total solar radiation (536–838 W/m²) in July.     

Study of flow boiling characteristics of R134a in annulus of enhanced surface tubing

The paper presents an experimental study of the flow-boiling heat-transfer characteristics of R12 and R134a in the annulus of a horizontal enhanced-surface-tubing evaporator. The test section has an inner-tube bore diameter of 17.5 mm, an envelope diameter of 28.6 mm and an outer smooth tube of 32.3 mm inside diameter. The ranges of heat flux and mass velocity covered in the tests were 5–25 kW/m² and 180–290 kg/m²/s, respectively, at a pressure of 365 kPa. In order to establish the flow regime conditions at the inlet to the test section, the test rig allows for the visualization of refrigerant flow through the preheater. The experiments show two regions of heat transfer: a nucleate boiling region where the heat transfer depends mainly on heat flux, and a forced convective region where the heat transfer depends only on the refrigerant flow rate.     

The effect of heating direction on flow boiling heat transfer of R134a in micro-channels

This paper presents effects of heating directions on heat transfer performance of R134a flow boiling in micro-channel heat sink.The heat sink has 30 parallel rectangular channels with cross-sectional dimensions of 500μm width 500μm depth and 30mm length.The experimental operation condition ranges of the heat flux and the mass flux were 13.48 to 82.25 W/cm2 and 373.3 to 1244.4 kg/m2s respectively.The vapor quality ranged from 0.07 to 0.93.The heat transfer coefficients of top heating and bottom heating both were up to 25 kW/m2 K.Two dominate transfer mechanisms of nucleate boiling and convection boiling were observed according to boiling curves.The experimental results indicated that the heat transfer coefficient of bottom heating was 13.9％ higher than top heating in low heat flux,while in high heat flux,the heat transfer coefficient of bottom heating was 9.9％.higher than the top heating,because bubbles were harder to divorce the heating wall.And a modified correlation was provided to predict heat transfer of top heating.     

Considerations about evaporator thermal design in a vapour compression liquid chiller. Experimental analysis with HFC fluids (R134a and R407C)

In this paper, the predicted performance of a shell‐and‐tube (1‐2) evaporator installed in a vapour compression liquid chiller is analysed. The classical thermal design methods are applied to the evaporator performance with two HFC refrigerants, a pure fluid (R134a) and a zeotropic blend with an appreciable glide (R407C). From the experimental results obtained it is possible to discuss the validation of the simplificatory assumptions usually taken, evaluating the resulting error introduced due to the no consideration of pressure drops and temperature glide (in the case of zeotropic blends) at the evaporator. Concluding that is not possible to consider the behaviour of a zeotropic refrigerant as a pure refrigerant, rejecting the glide. Whereas the assumption of no pressure drops in evaporator, leads to an error of about 5% in cooling capacity calculation. Copyright © 2004 John Wiley & Sons, Ltd.