换热管内置开边槽扭带的阻力与传热特性研究＊

将21种不同结构参数的铝制扭带分别置入换热管进行冷态和热态实验,研究并分析了换热管内置开三角形边槽扭带的阻力和传热特性。实验结果表明,插入开边槽扭带后管内的流动阻力和传热系数都有较大的提高。通过多元线性回归分析,得到了相应的阻力系数关联式和换热系数关联式。由强化传热性能评价分析,得到评价因子φ=1．05～1．35,证明了所研究的扭带具有强化传热的应用价值。     

换热管内插入间隔自旋扭带流阻与传热特性的实验研究

通过实验研究了内置间隔自旋扭带的换热管的传热和流阻特性。实验结果表明,间隔扭带的换热系数和摩擦系数都低于全长扭带;扭转比越大,间距对换热管阻力和传热特性的影响越小。此外,作者还建立了包含间隔扭带结构参数在内的流阻与传热特性的经验关联式。     

Ф42mm换热管内置铝制扭带强化传热特性的研究

对Ф42mm换热管插入扭带后的阻力特性和传热特性进行了分析,发现插入扭带以后,传热系数和流动阻力均增加,并且二者均随扭带的带宽增大而增大;通过非线性回归分析,得到插入铝制扭带后换热管摩擦阻力系数关联式和给热系数关联式;对插入扭带的换热管进行了强化传热性能评价分析,传热性能评价因子的数值在1．09～1．44范围之间,研究的扭带均具有强化传热的应用价值。     

Φ42mm换热管内置铝制扭带强化传热特性的研究

对Ф42mm换热管插入扭带后的阻力特性和传热特性进行了分析,发现插入扭带以后,传热系数和流动阻力均增加,并且二者均随扭带的带宽增大而增大;通过非线性回归分析,得到插入铝制扭带后换热管摩擦阻力系数关联式和给热系数关联式;对插入扭带的换热管进行了强化传热性能评价分析,传热性能评价因子的数值在1．09～1．44范围之间,研究的扭带均具有强化传热的应用价值。     

螺旋槽管槽深对定子水冷器传热与阻力特性的影响

螺旋槽管与折流栅组合的高效水冷器的传热和阻力特性与其管、壳程的结构因素密切相关,本文就螺旋槽管槽深对水冷器管、壳程传热与阻力特性的影响进行了实验研究.结果表明：壳程流速变化对水冷器传热系数的影响更加明显,即壳侧热阻相对较大,强化传热应以强化壳侧换热为主要目标;螺旋槽管槽深对水冷器传热系数的影响很大,应在实际工程设计中确保实际槽深符合设计要求;槽深越深,管壳程阻力也相应增加,即传热的强化是以阻力增加为代价.根据实验结果还得到了不同结构水冷器的管、壳程换热与阻力计算关联式.     

上行换热管内宽型扭带的转动特性实验研究设计

采用不同的宽型扭带在上行换热管内进行转动特性实验研究.通过对扭带转速的分析,得出了转速关联经验公式,实验结果表明宽型扭带具有在线除垢防垢的应用价值.     

单头螺旋槽管管内强化传热机理分析及优化设计

针对一定范围在前人研究的基础上对单头螺旋槽管的传热和阻力特性实验关联式进行了分析整合,得到了0.03≤e/d≤0.045,0.45≤p/d≤0.65,2x104≤Re≤5x104范围内与实验曲线拟合较好的传热和阻力特性实验关联式.在相同的内径,换热面积、平均传热温差、压力损失、质量流量条件下,以单头螺旋槽管与光管换热量比值为最优化目标函数,利用复合形法在研究范围内对其进行了数学优化,得到了研究范围内使目标函数达到最优值时单头螺旋槽管的最佳结构参数.     

换热管内置螺旋形扭带阻力与传热特性的实验研究

为了研究螺旋形扭带阻力与传热特性,选取了不同宽度（6、7和8 mm）的3种扭率（2.0、3.0、4.0）、3种螺距比（1.5、2.0、2.5）的参数组合下共27根螺旋形扭带插入换热管内进行实验.实验结果表明,插入螺旋形扭带后换热管内流动阻力和传热效果都有明显提高.通过对实验数据的多元线性回归分析,建立了相应的阻力系数和努赛尔数关联式.并且由强化传热综合性能评价分析,在实验雷诺数范围内得出强化传热综合性能评价因子φ=1.063～1.587,证明了实验研究的扭带具有强化传热的应用价值.     

换热管内插组合扭带强化传热的实验研究

以水为介质,对换热管内插入组合扭带的强化传热进行实验研究,分析其阻力和传热特性。实验结果表明,内插入组合扭带管的流动阻力和努塞尔数都得到了提高。其中,组合扭带管的摩擦系数比开孔扭带管的平均提高了10.5%;扭带管的努塞尔数比空管的平均提高了13.01%~20.38%,此外,组合扭带管的努塞尔数比开孔扭带管的平均提高了6.52%。换热管内插入组合扭带的传热综合性能评价因子φ均大于1,最大值达到1.16,这说明了换热管内插入组合扭带后,传热性能确实得到了提高。     

内置偏心多螺旋扭带换热管的传热特性研究

通过数值模拟对内置偏心多螺旋扭带换热管的传热特性进行了计算与分析,结果表明:换热管的对流传热强度随着扭带数量的增加而提高,随着扭带扭率的减小而提高。流动阻力损失相对于空管有很大程度的提高。传热性能评价指标在湍流时普遍较低,故多螺旋扭带换热管的使用应考虑流动阻力损失的影响。     

粗糙管换热器带自旋流的复合强化传热技术

介绍了粗糙管换热器中沿传热管轴向间隔分置旋流片的两区协同强化传热方法。旋流片使流体产生螺旋流,螺旋流在离开旋流片之后依靠自身的运动惯性保持一定距离的自旋流,对管道近壁区与中心区产生互动的协同传热强化。此外,该方法也可用于管间,除了对管间管束的机械支撑外,旋流片也可使管间流体产生自旋运动,实现壳程流体的两区协同传热强化。对现有工业系统的换热器技术升级、实现节能降耗意义重大。     

管内插偏重式螺旋轮自转及对流传热特性

针对换热管内污垢在线清洗的难题,提出了管内插偏重式螺旋轮自动防除垢技术。理论分析了螺旋轮获得的自转动力矩,并通过实验研究其自转特性;进一步对管内插偏重式螺旋轮的对流传热特性进行实验研究,对比分析偏重因素对传热强化性能的影响。结果表明:在一正一反交替连接时螺旋轮获得的自转速度最大,更有利于螺旋轮的旋转;传热温差为7℃时,管内插螺旋轮的总传热系数比内插螺旋线、内插扭带时分别提高22.2%和12%;传热温差为15℃时,内插不同偏重式螺旋轮的总传热系数与光管相比分别提高89%和112%,与内插普通螺旋轮的传热系数相比分别提高12%和25%,但相应的沿程阻力损失随之增加。考虑传热和阻力两方面因素,对上述管内插物的综合性能进行比较,结果显示内插偏重式螺旋轮的综合性能最好。     

Heat transfer and pressure drop characteristics of enhanced titanium tubes

The present study investigated the characteristics of heat transfer and pressure drop for various types of enhanced titanium tubes. The heat transfer experiments were conducted using a steam-condensing flow facility at a constant inlet temperature of cooling water, and the Reynolds number range varied from 15,000 to 65,000. The heat transfer coefficients were determined using a modified version of the Wilson plot technique and the friction factors were calculated from pressure drop measurements. The experimental results reported enable practical design to be achieved for the heat exchanger using enhanced titanium tubes and optimization of tube geometry for specific conditions.     

新型管内插入物——立交盘强化传热的实验与模拟

对装有新型强化传热管内插入物-立交盘的管路压降与传热情况进行了实验研究,并利用计算流体力学方法模拟了结构参数变化对传热及压降的影响。实验方面,通过不同黏度的测量物系,测定了Reynolds数为2×10^-4～4×10⁴时装有立交盘管路的压降,得到了摩擦系数与Reynolds数的关系曲线,并拟合了关联式,结果表明相同条件下装有立交盘的管路其压降为空管的7～40倍。其次,利用蒸气加热麦芽糖浆的传热实验,测量了水平放置与垂直放置条件下空管与装有立交盘时管路传热情况,拟合了相应的传热关联式,结果表明爬流条件下水平放置时传热强化倍数为2～3.5倍,垂直放置时传热强化倍数为2.5～4倍。最后,采用计算流体力学的方法,利用Fluent软件对立交盘的传热及流动过程进行了模拟研究,考察了结构参数变化对传热及压降的影响,整合了内外流道直径比及长径比对传热及压降的影响关联式,为立交盘的优化设计提供了理论依据。     

Study of Single Phase Flow Heat Transfer and Friction Pressure Drop in a Spiral Internally Ribbed Tube

The experimental results of single‐phase flow heat transfer and pressure drop experiments in the turbulent flow regime in a spirally ribbed tube and a smooth tube are presented in this paper. The ribbed tube has an outside diameter of 22 mm and an inside diameter of 11 mm (an equivalent inside diameter of 11.6 mm) and the smooth tube has an outside diameter of 19 mm and an inside diameter of 15 mm. Both tubes were uniformly heated by passing an electrical current along the tubes with a heated length of 2500 mm. The working fluids are water and kerosene, respectively. The experimental Reynolds number is in the range of 10⁴–5 · 10⁴ for water and is in the range of 10⁴–2.2 · 10⁴ for kerosene. The experimental results of the ribbed tube are compared with those of the smooth tube. The heat transfer coefficients of the ribbed tube are 1.2–1.6 fold greater than those in the smooth tube and the pressure drop in the ribbed tube is also increased by a factor of 1.4–1.7 as compared with those in the smooth tube for water. The corresponding values for kerosene are 2–2.7 and 1.5–2, respectively. The heat‐transfer enhancement characteristics of the ribbed tube are assessed. This tube is especially suitable for augmenting single‐phase flow heat transfer of kerosene. Correlations for the heat transfer and the pressure drop for the spirally ribbed tube are proposed, according to the experimental data.     

Optimization of the Heat Transfer Rate and Pressure Drop of Inside Profiled Tubes – Part 1

Nine inside profiled tubes were developed and investigated for optimization of the heat transfer rate and pressure drop behavior. The results of this work are presented in two parts. This part describes the comparative investigation of five tubes with different inside profiles to simulate the heat transfer and friction loss of fired tubular heaters in petrochemical processes. In part 2, a further four tubes with different inside profiles will be compared. To test the efficiency of the new profiles a test rig was modified. Using the similarity laws by Reynolds, the Reynolds number calculated for the gas flow in the heater tubes was converted into the flow rate, as well as the pressure and temperature of a distilled water system. Axial and peripheral velocities were measured using a Laser‐Doppler‐Velocimeter (LDV). Friction pressure drop and heat transfer were measured to determine the efficiency of each tested tube under the constant conditions of the distilled water system. The results of the investigations on these five inside profiles showed that profiles with eight flat and symmetrically distributed straight fins (tube III) or with a twist angle of 30° to the tube axis (tube IV), produced heat transfer rates higher that that of the bare tube by 120 % and 156 %, respectively, with increases in pressure drop only 46 % and 76 %, respectively.     

Thermal performance of tubular heat exchanger with multiple twisted-tape inserts

The paper presents an experimental investigation on enhanced heat transfer and pressure loss characteristics by using single, double, triple, and quadruple twisted-tape inserts in a round tube having a uniform heat-fluxed wal . The investigation has been conducted in the heat exchanger tube inserted with various twisted-tape numbers for co-and counter-twist arrangements for the turbulent air flow, Reynolds number (Re) from 5300 to 24000. The typical single twisted-tape inserts at two twist ratios, y/w=4 and 5, are used as the base case, while the other multiple twisted-tape inserts are at y/w=4 only. The experimental results of heat transfer and pressure drop in terms of Nusselt number (Nu) and friction factor (f), respectively, reveal that Nu increases with the increment of Re and of twisted-tape number. The values of Nu for the inserted tube are in a range of 1.15–2.12 times that for the plain tube while f is 1.9–4.1 times. The thermal enhancement factor of the inserted tube under similar pumping power is evaluated and found to be above unity except for the single and the double co-twisted tapes. The quadruple counter-twisted tape insert provides the maximum thermal performance.     

Simulation Analysis of the Heat Transfer Performance of an N-type Microchannel Heat Exchanger

A microchannel heat exchanger with a triangular wave and symmetrical triangular wave structure was proposed in this paper. In addition, a new N-type microchannel heat exchanger was developed to balance the heat transfer performance and pressure drop. The relationship between different configurations of the N structure of the microchannel and the heat transfer performance was analyzed. The results showed that, at a high inlet flow rate, the symmetrical triangular wave microchannel had the best heat transfer performance, followed by the triangular wave microchannel and the straight channel. At the same flow rate, the degree of disturbance of the fluid was highest in the symmetrical N-structure microchannel, and an excellent heat transfer effect was observed.