Condensation heat transfer coefficients of flammable refrigerants

In this study, external condensation heat transfer coefficients (HTCs) of six flammable refrigerants of propylene (R1270), propane (R290), isobutane (R600a), butane (R600), dimethylether (RE170), and HFC32 were measured at the vapor temperature of 39 °C on a plain tube of 19.0 mm outside diameter with a wall subcooling of 3–8 °C under a heat flux of 7–23 kW m⁻². Test results showed a typical trend that external condensation HTCs decrease with the wall subcooling. No unusual behavior or phenomenon was observed for these flammable refrigerants during experiments. HFC32 and DME showed 28–44% higher HTCs than those of HCFC22 due to their excellent thermophysical properties. Propylene and butane showed the similar HTCs as those of HCFC22 while propane and isobutane showed 9% lower HTCs than those of HCFC22. Finally, a general correlation was made by modifying Nusselt's equation based upon the measured data of eleven fluids of various vapor pressures including halogenated refrigerants. The general equation showed an excellent agreement with all data exhibiting a deviation of less than 3%.     

Condensation of pure refrigerants R12, R134a and their mixtures on a horizontal tube with capillary structure: An experimental study

We experimentally studied free convection condensation heat transfer of pure refrigerants R12, R134a, and their mixtures on a horizontal single tube. Approximately equimolar mixtures of these refrigerants are azeotropic. The outside surface of the tube used had a capillary structure. The tube was integrated in an experimental set-up in a way that allowed its rotation around the axis. Movable thermocouples inserted in the tube wall enabled the determination of the average surface temperature. This temperature, the vapour bulk temperature, and the heat flux obtained from condensate collection served for the determination of the heat transfer coefficient. The condensation heat transfer of the pure refrigerants examined is observed to change with the driving temperature difference largely in accordance with the Nusselt theory. The experimental values of the heat transfer coefficient on the tube used, however, are by a factor of 2 larger than those on a smooth tube according to this theory. Under comparable conditions, the refrigerant R134a shows by 10 to 15% better heat transfer than R12. The heat transfer of mixtures decisively depends on the compositions of their phases. Basically, the stronger the compositions of the phases differ from each other, the lower the heat transfer coefficients; they always lie below those of R134a. In the range of low temperature difference, the heat transfer coefficient of mixtures increases with the temperature difference. This is the region of the so-called partial condensation. At a larger temperature difference, a local total condensation of the mixtures takes place and the heat transfer qualitatively follows the Nusselt theory.     

Condensation of steam on a vertical tube in a granulated material

The heat transfer enhancement was studied during condensation of steam on a chilled vertical surface of a tube packed into a granulated material with different contact angles of wetting. The dimensionless values of heat transfer at condensation on a surface in filling, obtained for a vertical tube in the range of Reynolds numbers from 70 up to 400, exceed Nu* values for a smooth tube by the factor of 2–3. The intensification of heat transfer on a vertical tube, housed in a granulated layer, is conditioned by the several interdependent phenomena: 1 — capillary ascent of some liquid near the meniscuses, and as a consequence, reduction of the mean film thickness; 2 — burble of a film at the points of sphere contact with a surface of condensation at Re>10; 3 — removal of some film liquid by a granulated layer; accompanied by simultaneous film burble at the points of sphere contact with a cooling surface at Re>83. Results of the current research can be used for the development of heat exchanging devices under the conditions of microgravitation.     

Condensation of R407C in a horizontal microfin tube

This paper describes experimental results that show the effects of mass velocity and condensation temperature difference on the local heat transfer characteristics during condensation of R407C in a horizontal microfin tube. The experiments were performed at the saturation temperature of 40 °C, the refrigerant mass velocity of 50, 100, 200 and 300 kg m⁻² s⁻¹, and the condensation temperature difference of 1.5, 2.5 and 4.5 K. A superficial heat transfer coefficient for the vapor phase was obtained by subtracting the heat transfer resistance of condensate film estimated by using a previously developed theoretical model of film condensation of pure vapor from the overall heat transfer resistance. On the basis of the analogy between heat and mass transfer, an empirical equation for the superficial vapor phase heat transfer coefficient was developed. The heat transfer coefficient predicted by the combination of the previously developed theoretical model of film condensation of pure vapor and the empirical equation of the superficial vapor phase heat transfer coefficient agreed with the measured values with the r.m.s. error of 9.2%.     

Condensation of a chemically reactive gas on a horizontal tube

A numerical solution is presented for a system of differential equations of heat and mass transfer in a boundary layer in the laminar condensation of a gas on a horizontal tube.Notation g acceleration due to gravity - r external radius of tube - r_k latent heat of condensation - Pr Prandtl number - Sc Schmidt number - T temperature - x distance along circumference - y distance along radius beyond the cylindrical surface - viscosity - density - kinematic viscosity Indices s saturated - liquid-gas interface - h gas - q liquid - wl wall Translated from Inzhenerno-Fizicheskii Zhurnal, Vol. 40, No. 5, pp. 793–799, May, 1981.     

Condensation stage of a pulse tube pre-cooled dilution refrigerator

In our article, experiments with a pulse tube (PTR) pre-cooled dilution refrigerator (DR) are presented, where an upgraded ³He condensation stage has been tested. The DR had a ³He flow rate of up to 1.1 mmol/s. The ³He gas entering the refrigerator was first pre-cooled to a temperature of ～50 K at the first stage of the PTR. In the next cooling step, the ³He was run through a recently installed heat exchanger, which was attached to the regenerator of the second stage of the pulse tube cryocooler; at the outlet of this heat exchanger the temperature of the ³He was as low as ～4 K. Due to the non-ideality of the helium gas, the second regenerator of a two stage PTR has excess cooling power which can be made use of without affecting the base temperature of this stage, and it is this effect which was put to work, here. Finally, the ³He was further cooled in a heat exchanger, mounted at the second stage of the PTR, before it entered the dilution unit of the cryostat.The installation of a heat exchanger at the regenerator of the second stage of the PTR is especially important for the construction of DRs with high refrigeration capacities; in addition, it allows for a plain design of the subsequent Joule–Thomson (JT) stage, and herewith facilitates considerably the construction of “dry” DRs. The condensation rate of the ^3,4He mash prior to an experiment was increased. The pressure during condensation could be kept near 1 bar, and thus a compressor was no longer necessary with the modified apparatus.     

地铁列车双锥内嵌隔板矩形管的耐撞性优化

为设计具有良好耐撞性能的地铁列车吸能结构,将矩形吸能管的一组对称面引入锥度,并在内部嵌入多个隔板.建立该双锥内嵌隔板矩形管和传统矩形管的有限元模型,对两者耐撞性进行对比,通过准静态轴向压缩试验验证有限元分析的准确性.以双锥内嵌隔板矩形管三个部分的厚度为设计变量,进行试验设计并建立代理模型,为最大化比吸能和最小化峰值力,...     

Condensation of pure and near-azeotropic refrigerants in microfin tubes: A new computational procedure

Microfin tubes are widely used in air cooled and water cooled heat exchangers for heat pump and refrigeration applications during condensation or evaporation of refrigerants. In order to design heat exchangers and to optimize heat transfer surfaces, accurate procedures for computing pressure drops and heat transfer coefficients are necessary. This paper presents a new simple model for the prediction of the heat transfer coefficient to be applied to condensation in horizontal microfin tubes of halogenated and natural refrigerants, pure fluids or nearly azeotropic mixtures. The updated model accounts for refrigerant physical properties, two-phase flow patterns in microfin tubes and geometrical characteristics of the tubes. It is validated against a data bank of 3115 experimental heat transfer coefficients measured in different independent laboratories all over the world including diverse inside tube geometries and different condensing refrigerants among which R22, R134a, R123, R410A and CO₂.     

Condensation of refrigerants in horizontal microfin tubes: comparison of correlations for frictional pressure drop

This paper presents a comprehensive comparison of eight previously proposed correlations with available experimental data for the frictional pressure drop during condensation of refrigerants in helically grooved, horizontal microfin tubes. Calculated values are compared with experimental data for seven refrigerants (R11, R123, R134a, R22, R32, R125 and R410A) and eight tubes and with mass velocity from 78 to 459 kg/m² s. The tubes had inside diameter at the fin root between 6.41 and 8.91 mm; the fin height varied between 0.15 and 0.24 mm; the fin pitch varied between 0.34 and 0.53 mm and helix angle between 13 and 20°. The results show that the overall r.m.s. deviations of relative residuals of frictional pressure gradient for all tubes and all refrigerants taking together decreased in the order of the correlations of Nozu et al. [Exp. Therm. Fluid Sci. 18 (1998) 82], Newell and Shah [Refrigerant heat transfer, pressure drop, and void fraction effects in microfin tubes. In: Proc. 2nd Int. Symp. on Two-Phase Flow and Experimentation, vol. 3. Italy: Edizioni ETS; 1999. p. 1623–39], Kedzierski and Goncalves [J. Enhanced Heat Transfer 6 (1999) 161], Cavallini et al. [Heat Technol. 15 (1997) 3], Goto et al. (b) [Int. J. Refrigeration 24 (2001) 628], Choi et al. [Generalized pressure drop correlation for evaporation and condensation in smooth and microfin tubes. In: Proc. of IIF-IIR Commision B1, Paderborn, Germany, B4, 2001. p. 9–16], Haraguchi et al. [Condensation heat transfer of refrigerants HCFC134a, HCFC123 and HCFC22 in a horizontal smooth tube and a horizontal microfin tube. In: Proc. 30th National Symp. of Japan, Yokohama, 1993. p. 343–5], and Goto et al. (a) [Int. J. Refrigeration 24 (2001) 628], i.e., this final correlation (Goto et al. (a)) gives the best overall representation of the data.     

Condensation of refrigerants in horizontal microfin tubes: comparison of prediction methods for heat transfer

A comparison was made between the predictions of previously proposed empirical correlations and theoretical model and available experimental data for the heat transfer coefficient during condensation of refrigerants in horizontal microfin tubes. The refrigerants tested were R11, R123, R134a, R22 and R410A. Experimental data for six tubes with the tube inside diameter at fin root of 6.49–8.88 mm, the fin height of 0.16–0.24 mm, fin pitch of 0.34–0.53 mm and helix angle of groove of 12–20° were adopted. The r.m.s. error of the predictions for all tubes and all refrigerants decreased in the order of the correlations proposed by Luu and Bergles [ASHRAE Trans. 86 (1980) 293], Cavallini et al. [Cavallini A, Doretti L, Klammsteiner N, Longo L G, Rossetto L. Condensation of new refrigerants inside smooth and enhanced tubes. In: Proc. 19th Int. Cong. Refrigeration, vol. IV, Hague, The Netherlands, 1995. p. 105–14], Shikazono et al. [Trans. Jap. Sco. Mech. Engrs. 64 (1995) 196], Kedzierski and Goncalves [J. Enhanced Heat Transfer 6 (1999) 16], Yu and Koyama [Yu J, Koyama S. Condensation heat transfer of pure refrigerants in microfin tubes. In: Proc. Int. Refrigeration Conference at Purdue Univ., West Lafayette, USA, 1998. p. 325–30], and the theoretical model proposed by Wang et al. [Int. J. Heat Mass Transfer 45 (2002) 1513].     

Condensation heat transfer and two-phase frictional pressure drop in a single minichannel with R1234ze(E) and other refrigerants

R1234ze(E), trans-1, 3, 3, 3-tetrafluoropropene, is a fluorinated propene isomer which may be a substitute of R134a for refrigeration applications. R1234ze(E) has a much lower GWP_100-years than that of R134a. In this paper, the local heat transfer coefficient during condensation of R1234ze(E) is investigated in a single minichannel, horizontally arranged, with hydraulic diameter equal to 0.96 mm. Since the saturation temperature drop directly affects the heat transfer rate, the pressure drop during adiabatic two phase flow of R1234ze(E) is also measured. Predictive models are assessed both for condensation heat transfer and pressure drop. A comparative analysis is carried out among several fluids (R1234ze(E), R32, R134a and R1234yf) starting from experimental data collected at the same conditions and using the Performance Evaluation Criteria (PEC) named Penalty Factor (PF) and Total Temperature Penalization (TTP) to rank the tested refrigerants in forced convective condensation.     

The parameters of nonequilibrium microwave discharge in nitrogen in a tube in a rectangular waveguide

Computer codes are developed for the processing of emission spectra of nonequilibrium plasma in nitrogen for the purpose of obtaining information about the translational T _g and rotational T _rot temperatures, the populations of vibrational levels in the ground electron and electron-excited states, the electron energy distribution function, the electron concentration N _e , and the electric field intensity E. The computer codes are used to determine the parameters of microwave-discharge plasma in nitrogen in discharge systems of two types, namely, in a discharge tube (with a radius of 1 cm), which crosses a rectangular waveguide (plasmatron on the H ₁₀ wavelength, at a pressure of 1.7 torr and absorbed power density of 1.5 W/cm³), and in a discharge section of similar structure on the basis of prismatic resonator (at a pressure of 1.0 torr and absorbed power density of 0.4 W/cm³). The mechanisms of population of the N₂(C ³Π_u) state are treated.     

Condensing two-phase pressure drop and heat transfer coefficient of propane in a horizontal multiport mini-channel tube: Experimental measurements

This article reports the condensing flow heat transfer coefficient and pressure drop results of propane (R290) flowing through a square section horizontal multiport mini-channel tube made of aluminium having an internal diameter of 1.16 mm and a condensing length of 259 mm. Pressure drop and two phase flow experiments were performed at saturation temperatures of 30, 40 and 50 °C. Heat flux was varied from 15.76 to 32.25 kWm⁻² and mass velocity varied from 175 to 350 kg m⁻² s⁻¹. The results show that the two-phase friction pressure gradient increases with the increase of mass velocity and vapour quality and with the decrease of saturation temperature. The heat transfer coefficients showed to increase with increases of vapour quality and mass velocity while increases of saturation temperature were observed to reduce heat transfer coefficient. The two phase frictional pressure drop correlations of Sun and Mishima and Agarwal and Garimella, and the two-phase flow heat transfer correlations of Koyama et al. and Wang et al. predicted well the experimental results.     

Experimental study on forced convective boiling heat transfer of pure refrigerants and refrigerant mixtures in a horizontal tube

Convective boiling heat transfer coefficients of pure refrigerants (R22, R32, R134A, R290, and R600a) and refrigerant mixtures (R32/R134a, R290/R600a, and R32/R125) are measured experimentally and compared with Gungor and Winterton correlation. The test section is made of a seamless stainless steel tube with an inner diameter of 7.7 mm and is uniformly heated by applying electric current directly to the tube. The exit temperature of the test section was kept at 12°C ± 0.5°C for all refrigerants in this study. Heat fluxes are varied from 10 to 30 kW m⁻² and mass fluxes are set to the discrete values in the range of 424–742 kg m⁻² s⁻¹ for R22, R32, R134a, R32/R134a, and R32/R125; 265–583 kg m⁻² s⁻¹ for R290, R600a, and R290/R600a. Heat transfer coefficients depend strongly on heat flux at a low quality region and become independent as quality increases. The Gungor and Winterton correlation for pure substances and the Thome-Shakil modification of this correlation for refrigerant mixtures overpredicts the heat transfer coefficients measured in this study.     

Condensation heat transfer coefficients of halogenated binary refrigerant mixtures on a smooth tube

In this study, external condensation heat transfer coefficients (HTCs) of nonazeotropic refrigerant mixtures of HFC32/HFC134a and HFC134a/HCFC123 at various compositions were measured on a horizontal smooth tube of a 19 mm outside diameter. All data were taken at the vapor temperature of 39 °C with a wall subcooling of 3–8 °C. Test results showed that HTCs of the tested mixtures were 19.4–85.1% lower than the ideal values calculated by the mole fraction weighting of the HTCs of the pure components. A thermal resistance due to the diffusion vapor film seemed to be partly responsible for the significant reduction of HTCs with these nonazeotropic mixtures.     

A generalized correlation for two-phase flow of alternative refrigerants through short tube orifices

The objective of this study is to develop a generalized correlation for the prediction of refrigerant flow rate through short tube orifices using alternative refrigerants. The generalized correlations for two-phase and subcooled inlet conditions are separately derived from a power law form of dimensionless parameters generated by the Buckingham Pi theorem. The database for the present correlation includes extensive experimental data for R12, R22, R134a, R407C, R410A, and R502 obtained from the open literature. For subcooled inlet conditions at the short tube entrance, the correlation yields an average deviation of 0.3% and a standard deviation of 6.1% based on the present database, while for two-phase inlet conditons it predicts the database with an average deviation of 0.2% and a standard deviation of 5.0%. The relative deviations of the predictions using the present correlations for two-phase and subcooled inlet conditions range from −21% to 18%.     

Numerical simulation and experimental analysis of refrigerants flow through adiabatic helical capillary tube

In the present study, two-phase refrigerant flow is simulated using drift flux model for straight and helical capillary tubes. The conservation equations of mass, energy and momentum are solved using the 4th order Runge–Kutta method. This model is validated by previously published experimental and numerical results and also by experimental results presented in this work. The effect of various parameters such as inlet pressure, inlet temperature, sub-cooling degree, and geometric dimensions are studied. The results of the present study show that for the same length and under similar conditions, mass flux through helical capillary tube with coil diameter of 40 mm are about 11% less than that through the straight tube, where the helical tube length is about 14% shorter than the straight one for the same refrigerant mass flux.     

Two-phase heat transfer coefficients of three HFC refrigerants inside a horizontal smooth tube, part II: condensation

This paper presents local heat transfer results obtained during the condensation of Isceon 59, R407C and R404A in a smooth horizontal tube. The results have been compared with existing correlations for condensation heat transfer to assess the validity of these models for refrigerant mixtures. Two correlations (Dobson MK, Chato JC. Condensation in smooth horizontal tubes. Journal of Heat Transfer, Transactions of ASME 1998; 120: 193–213, Shah MM. A general correlation for heat transfer during film condensation inside pipes. Int J Heat & Mass Transfer 1979; 22: 547–56) have been considered because they deal with refrigerant blends and their range of applicability suited the experimental test conditions. The Dobson and Chato correlation provided the best prediction for these refrigerant mixtures. The Shah correlation fitted the measurements of the local heat transfer coefficients well and seem to cope well with refrigerant mixtures.     

Two-phase split of refrigerants at a T-junction

The present study experimentally investigated the two-phase flow split of refrigerants at a T-junction. As geometric parameters, the direction of the inlet or branch tube and the tube diameter ratio of branch to inlet tube were chosen. As inlet flow parameters, the inlet mass flux and quality were varied from 100 to 700 kg m⁻² s⁻¹ and from 0.1 to 0.9, respectively, for the condition of distribution header of a multi-pass evaporator in the general refrigeration system. All experiments were performed for R-22, R-134a, and R-410A. The measured data were compared with the values predicted by the models developed for air–water or steam–water mixture in the literature. We propose a modified model for application to the reduced T-junction and vertical orientation of tubes. Among the geometric parameters, the branch tube direction showed the largest sensitivity to the mass flow rate ratio for the gas phase, while the inlet quality showed the largest sensitivity to the mass flow rate ratio among the inlet flow parameters.     

矩形管道内磁性液体涂层流动状态的实验研究

论述了磁性液体粘性减阻技术的原理.在矩形管道实验装置中,研究了水流过磁性液体涂层时磁性液体流动状态的变化以及磁性液体的减阻性能.初步得出在外部磁场的作用下,由于磁性液体内部存在回流,致使其在被传输流体流过时能够稳定存在于管道内壁的结论;并通过实验得出只有当管道内部涂层厚度适当时,磁性液体才有减阻效果的结论.