Identification of Heat Transfer Coefficients by Use Conditions of Quenching Oil

Heat transfer coefficients of the quench medium are necessary for heat-treatment simulation. Cooling characteristics of quenching oil vary with kinds and usage greatly. Users are selecting oil solutions that come up to their desired hardness and quenching distortion requirements. In particular cooling performance rises by agitation and decompression. Therefore we identified a heat transfer coefficient by usage and kinds of quenching oil. Cooling characteristics are different greatly by a kind of quenching oil. A difference of a cooling characteristic by a kind of oil depends on a temperature range of a boiling stage and the maximum heat transfer coefficient mainly. On the other hand, in a convection stage, there are few changes in a boiling stage. Even if quenching oil temperature is changed, heat transfer coefficients do not change greatly. When quenching oil stirred, heat transfer coefficients of vapor blanket stage and a convection stage rise, but there are a few changes in a boiling stage. When quenching oil is decompressed a temperature range of a high heat transfer coefficient moves to the low temperature side. In addition, a heat transfer coefficient in a vapor blanket stage comes down. For precision improvement of heat-treatment simulation, it is important that the heat transfer coefficient is calculated in conformity to the on-site use reality.

Experimental Study on the Thermal Performances of a Tube-Type Indirect Evaporative Cooler

The so-called indirect evaporative cooling technology is widely used in air conditioning applications.The thermal characterization of tube-type indirect evaporative coolers,however,still presents challenges which need to be addressed to make this technology more reliable and easy to implement.This experimental study deals with the performances of a tube-type indirect evaporative cooler based on an aluminum tube with a 10 mm diameter.In particular,the required tests were carried out considering a range of dry-bulb temperatures between 16℃ and 18℃ and a temperature difference between the wet-bulb and dry-bulb temperature of 2℃∼4℃.The integrated convective heat transfer coefficient inside the tube in the drenching condition has been found to lie in the range between 36.10 and 437.4(W/(m^(2)⋅K)).

Ammonia corrosion analysis of copper tubes and experimental research on non-copper improvement for heat exchanger in power plant

Ammonia corrosion in copper tube will affect the safety of boiler running in power plant. Therefore, no copper in heating system has become a technical orientation in heat exchanger reconstruction, This paper analyzes the condition and mechanism of ammonia corrosion occurring in copper tube used in coal-fired power plants. Using a general steam condensation testing equipment only for horizontal single tube, with water vapor and water as working fluid, on two types of steel tube with 2-side enhancement heat transfer, namely, a spirally fluted tube and a ratchet tube with internal spiral groove （RISG tube） which was developed recently, a set of experimental tests are conducted to investigate the characteristics of heat transfer and hydromeehanics. In order to compare easily, both one copper smooth tube and one steel smooth tube are also used in the experiment. The experimental results, which get from single horizontal tube, show that the overall heat transfer coefficient of steel spirally fluted tube are improved by 10%o to 17%, and that of the steel RISG tube（22%-28%） is better than steel spirally fluted tube, its flow resistance coefficient is only increased by 22% to 66% when compared with smooth tube. Based on a lot of experimental data, the steel spirally fluted tube and the steel RISG tube were applied in a low pressure preheater and an oil-cooler of some or other power plant respectively. The field testing results showed that their heat transfer coefficient with each types of enhancement heat transfer tubes were improved by 2.5% and 21%-45% comparing with copper smooth tube heat exchangers. Both basic and field experiment indicates that the steel tube with 2-side enhancement heat transfer is an ideal choice for heat exchanger reconstruction in no copper issue in power plants.

板式气冷器中超临界CO_(2)侧表面换热系数研究

为了探究板式气冷器中主导超临界CO_(2)侧表面换热系数h最值出现的因素及最值点的中移对平均换热系数大小的影响,采用基于MATLAB的换热器分布参数分析方法,研究了超临界CO_(2)侧表面换热系数h沿气冷器板片上的分布规律,并针对h最值出现的主导因素、改变板片尺寸和流量使最值点移动对平均换热系数的影响进行研究。结果表明,伪临界温度对板式气冷器中h最值的出现更具有决定性;一定压力下的C_(p)最大值会随着压力的增加不断增大,但伪临界温度逐渐降低;减小板片尺寸或者增大质量流量,可以使得平均换热系数增加,对应的换热量也会增大,而且由质量流量增加所带来的换热量增加幅度在3种工况下分别为12.72%,12.79%,11.75%,同时压降也会增加;当h最大值保持在6170 W/(m^(2)·K)或5120 W/(m^(2)·K)附近时,最值点中移不会使平均换热系数增加明显,而且对应的换热量也会减小。

基于动态规划的原油管道运行能耗优化技术研究

随着管道老化和站内设备劣化,原油管道整体能耗呈逐年上升趋势。在考虑泵状态、加热炉状态、变频器状态、泵转速、加热炉功率、节流阀压降等决策变量的基础上,建立了以总运行费用最小为目标函数的原油管道运行能耗优化模型,结合总传热系数和水力摩阻系数修正值,采用动态规划算法对最优运行方案进行求解。结果表明,参数修正后,进站温度的平均相对误差为3.41%,进站压力的平均相对误差为3.60%,满足后续优化需求;水力优化结果考虑了沿程站场电价的影响,站内节流阀均保持常开,说明站间没有剩余压力浪费;热力优化结果保证了进站温度均高于原油凝点2~5℃,没有剩余进站温度浪费;总运行费用较优化前降低了12.4%,经济效益明显。研究结果可为原油管道节能运行方案的制定和实施提供理论依据。

油冷却器及热虹吸油冷却系统设计

热虹吸油冷却系统被广泛应用于螺杆式压缩机组,为更好地指导热虹吸油冷却系统设计,本文采用HTRI对热虹吸油冷却系统和管壳式油冷却器进行设计计算,搭建热虹吸油冷却系统测试试验台,并进行试验验证。结果表明:利用HTRI计算油冷却器换热量的误差为4.6%,计算压降的误差为3.6%;随进液管内径和回气管内径的增大、静压头的升高,油冷却器的换热量逐渐增大,但是换热量的增大幅度逐渐减小。

油冷器强化传热研究

1 引言 广泛用于机械设备的润滑油冷却器,由于油的粘度大,操作流速低,若使用光滑管设计制造,其传热性能差,一般总传热系数为350W/（m^2·℃）左右。近年来,螺纹翅片管已在工业油冷器中应用,因其肋化系数可达2.5～3,能有效地扩展传热面,故对油冷器的紧凑化起到重要作用。但是,由于螺纹翅片间距小,翅间湍流度低,按实际翅片面积计算的总传热系数常仅180～200W/（m^2·℃）,当取肋化系数2.7,以光坯管面积计算油冷器总传热系数可达520W/（m^2·℃）,比光滑管油冷器节省光坯管面积约33%,但因加工螺纹翅片需增大管壁厚度,加工后单位管长比光滑管增重约30%,故一般只比光滑管油冷器节省管材百分之几。因此,仅凭加大翅片肋化系数,用扩展传热面强化传热,其节材效果不够明显,提高翅片利用效率,关键在于提高翅间流体湍流度,强化翅面上流体传热。

椭圆管矩形翅片空冷器流体流动与传热特性数值分析

对电站空冷器椭圆管矩形翅片空气侧的流动与传热特性进行了数值模拟,分析了翅片间距、翅片厚度、迎面风速以及环境温度对翅片侧流体与壁面之间的表面传热系数以及流动阻力的影响。数值模拟结果表明:随着迎面风速的增加,表面传热系数和流动阻力显著增加;翅片间距对表面传热系数影响不大,但对流动阻力和总散热量的影响显著;表面传热系数和流动阻力随翅片厚度的增加呈单调增加的趋势。本文数值模拟结果可为电站空冷器的设计与实验提供参考。

动态淬火介质冷却特性及换热系数的研究

为了研究工业生产条件下淬火油在不同流速下的冷却特性曲线及换热系数 ,用超声波多普勒流量计测定了淬火油槽的流速 ,按ISO9950标准测定冷却特性曲线 ,用 1 2 0mm× 1 2 0mm× 2 0mm平板状试样和反传热法测定与计算了换热系数。结果表明 ,随着介质流速的增加冷却特性曲线的冷速最大值及换热系数的最大值均呈增加趋势 ,当搅拌使介质中产生气泡时 ,介质的冷却能力明显降低。最后指出换热系数曲线能更好地反映表面热量传递的真实情况。

喷雾强化空气冷却器的实验研究

文献上常采用有效膜传热系数的方法来考虑管外水膜传热传质的综合效果，用析湿系数考虑对空气增湿降温的效果，这种基于对数平均温差或ε～ＮＴＵ方法对湿式空冷器进行热计算是比较粗糙和近似的．本文基于Ｍｅｒｋｅｌ的焓差法，用容积散质系数的方法对水膜的传热传质进行分析．在实验过程中改变了空气质流量以及喷水强度，测得有关数据，整理得出βｘｖ值．用多元回归方法得出的βｘｖ关联式。

润滑油对R32在水平光管内流动沸腾换热特性及压降的影响

对R32在φ5mm和φ7mm的水平光管内的流动沸腾时,润滑油对换热与压降特性的影响进行了试验研究,试验的质量流量范围为100~500 kg/(m^2·s),润滑油的含量在0~5%之间。结果表明,沸腾换热系数随着质量流量的增大而增大。在低干度区,换热系数随干度的增大而增大,当干度达到0.7~0.8时,换热系数达到最大。随着润滑油含量的增大,局部换热系数在减小。压降随着管径的减小和质量流量的增大而增大。润滑油含量的增大,导致压降的增大。在5mm管内,润滑油含量对换热系数和压降影响比较明显。

淬火油动态下换热系数的测量及计算

为了测量和计算工业条件下淬火油在不同流速下的换热系数 ,采用超声波多普勒流量计测定了介质的流速 ,用 12 0× 12 0× 2 0 (mm)平板状试样和反传热法测定与计算了换热系数。结果表明 ,换热系数曲线能更好地反映表面热量传递的真实情况 ;随着介质流速的增加 ,换热系数的最大值呈增加趋势 ,当搅拌使介质中产生气泡时 ,介质的换热系数明显降低。

纳米流体柴油机机油冷却器传热试验设计

为了研究新型冷却介质——纳米流体在内燃机冷却系统中的换热效果,自行设计了适用于多种冷却介质的传热性能试验台,并根据纳米流体的性能改进了加热方法,以纳米流体、水和防冻液为冷却介质在柴油机机油冷却器中进行了传热性能试验.结果表明,当冷却介质进口温度为85,℃时,纳米流体的换热能力比水和防冻液分别提高了4.6%和19.0%;当进口温度升至120,℃时,纳米流体的换热能力比防冻液增强了63.7%.随温度升高,纳米流体自身换热能力的增幅明显高于防冻液,这突出了纳米流体在内燃机高温冷却技术上的应用优势.

熔融盐(LiNO_3)强制对流换热实验

由于熔融盐使用温度高、热稳定性和传热性能好,被认为是太阳能塔式发电系统和新一代槽式发电系统中最有前途的传热蓄热介质之一。本文通过搭建高温熔融盐传热试验台,成功实现了LiNO_3熔融盐与导热油的强制对流换热试验循环,得到了总的对流换热系数,初步得到了在旺盛紊流区熔融LiNO_3在不同雷诺数下对应的努塞尔数。

蒸发式冷却器的传热传质试验研究

对蒸发式冷却器传热传质试验结果的数据处理进行了讨论，重点是它的容积散质系数以及工艺水到水膜的传热系数．介绍了试验台和各测试仪表，给出了对两个试件的测试结果，整理了βｘｖ和Ｋ的变化规律。

滑油冷却器强化换热试验研究

对3个采用整体针翅管的滑油冷却器实验体进行了对比实验研究。结果表明:当换热管长度和油质量流量相同,且针翅管数量比光管减少一半时,针翅管滑油冷却器的换热系数是光管滑油冷却器的2.2倍。对实验结果的分析说明了针翅管滑油冷却器具有管板数量少、强化传热效果好的特点。

开孔矩形翅片椭圆管流动及传热特性的数值模拟

对电站空冷凝汽器矩形翅片椭圆管空气侧的流动与传热特性进行了数值模拟,分析了翅片上有无扰流孔两种情况下矩形翅片表面的局部表面传热系数分布规律。对影响空气侧传热和流动性能的因素,包括扰流孔数、扰流孔尺寸、扰流孔位置进行了优化分析。数值模拟结果表明:随着扰流孔数的增加,表面传热系数和流动阻力逐渐增加,在一定范围内,换热量也不断增加;随着扰流孔的尺寸增大,表面传热系数和流动阻力均增大,但是总换热量减少;相对来说,扰流孔的位置对表面传热系数和流动阻力的影响不大。

螺旋隔板花瓣管换热器的传热强化研究

比较了螺旋用板花瓣管和螺旋隔板低肋管润滑油冷却器和空气冷却器的传热性能，实验结果表明，无论是作为油冷却器，还是作为空气冷却器，螺旋隔板花瓣换热器的综合传热性能明显优于螺旋隔板低肋管换热器，且螺旋隔板花瓣换热器还能节省３０％以上的铜管重量．

结霜工况下的冷风机传热性能试验研究

文中对冷风机在结霜工况下的传热性能进行了试验研究 ,简述了结霜工况下传热系数测试的原理、方法和主要过程。根据实验结果对影响冷风机传热性能的主要因素进行了分析 。

稠油废水降膜蒸发回收蒸馏水的试验研究

利用管式降膜蒸发器蒸发油田稠油废水以回收蒸馏水,是处理稠油废水的有效措施。试验研究了利用蒸汽为热源的垂直管降膜蒸发系统蒸发稠油废水过程中传热系数和蒸馏水品质的影响因素。结果表明,在连续蒸发操作并将稠油废水浓缩到61倍的过程中,由于加热管双侧液膜厚度随着蒸发负荷、废水循环线速率和传热温差的增加而增加,蒸发器的综合传热系数随上述参数的增大而减小。蒸馏水的电导率起初随着浓缩倍数的增大而减小;超过30倍后又随着浓缩倍数的上升而增大。蒸馏水的品质与油田注气锅炉给水要求相比,除含油量外均能满足给水标准,而水中微量的油可以用其它方式去除。研究表明这种热回收系统具有很好的实际应用价值。