冲击-气膜冷却孔排列方式对流动和换热的影响

采用SST湍流模型对冲击孔和气膜孔附近的局部换热特性进行了数值模拟,研究了某型高压导叶不同"冲击-气膜"组合方式对流动和换热的影响。结果表明:减小气膜出流对冲击冷却的削弱作用,能够同时促进冲击冷却和横向对流流动对冲击靶面的换热作用。叶片内部采用倾斜的冲击孔结构,冲击射流能在叶片内表面产生较大面积的冷却区域。综合考虑"冲击占优"和"反向横流对流换热",能够获得最为合理的"冲击-气膜"组合冷却结构。     

阵列射流冲击冷却换热系数的数值研究

采用数值模拟方法对冲击冷却的流动和传热过程进行了三维数值研究.特别研究了在冲击孔叉排方式下,相邻孔间距、冲击距离以及射流入口雷诺数对冲击表面冷却流动传热特性的影响规律.     

阵列射流冲击冷却流场与温度场的数值模拟

采用数值模拟方法对冲击冷却的流动和传热过程进行了三维数值研究。特别研究了在冲击孔叉排方式下,相邻孔间距、冲击距离以及射流入口雷诺数对冲击表面冷却流动传热特性的影响规律。     

某重型燃气轮机燃烧室冲击冷却特性研究

冲击冷却具有较高换热系数,在燃气轮机燃烧室得到重要应用。通过流固耦合传热(Coupled Heat Transfer,CHT)计算方法研究了冲击冷却孔排列方式、冲击高度与冷却孔径之比Z_n/D和初始横流对某重型燃机燃烧室火焰筒冲击冷却特性的影响。得到如下结论:三者对冲击换热效率均有显著影响,其中Z_n/D=3.7时,直列阵列相邻列之间的横流更规则,冷却效果优于错排阵列;当Z_n/D在2.0～6.0范围内时,随着Z_n/D的增大,冷却效率呈现先增大后减小的趋势,存在一个最佳换热范围2.7≤Z_n/D≤4.6,此时射流冷却与对流冷却匹配合理,冷却效率较高;初始横流对冲击冷却性能有很大削弱作用,应在设计时尽量避免。     

横流对振荡射流冲击冷却特性影响的数值研究

为了分析横流条件下振荡射流冲击靶面的换热特性,采用数值计算方法研究了横向排列和纵向排列方式下振荡射流冲击靶面的冷却性能,并对纵向排列下的射流振荡器进行了排布角度修正.结果 表明:横流对冲击换热的作用主要受到两方面影响,即冲击点附近的马蹄涡和冲击点向后偏移程度;对于靶面上的冲击核心区,总体上纵向排列的高换热区域后移程度小...     

纵向涡发生器对涡轮叶片前缘冲击冷却的影响

采用三维数值方法对涡轮叶片前缘射流腔内的流动和换热特性进行了研究。在射流腔内安置一对三角形纵向涡发生器,研究了纵向涡发生器的安置角度、两纵向涡发生器间的距离以及纵向涡发生器距射流孔中心的距离对流动和换热的影响,分析了纵向涡发生器强化冲击换热的机理。结果表明:当在射流孔前的上壁面上增加一对纵向涡发生器后,射流孔前的横流流速减小,射流穿透力增大,射流腔内湍动能增大,从而造成靶面换热极值及高换热区域显著增大;在研究的纵向涡发生器各位置参数范围内,当横流雷诺数较低时,各参数对靶面换热的影响不大。     

内冷通道特性对外表面气膜冷却换热影响研究

采用混合网格和realizable к-ε紊流模型,求解三维N-S方程,对气膜孔入口无横流、仅有横流和横流通道中有扰流肋的情况下,外表面气膜冷却换热特性进行了数值研究.具体分析了横流及肋的存在对气膜冷却外表面换热系数的影响.结果表明,横流及肋的存在使通道流场变得非常复杂,横流提高了外表面的换热系数,且使流动及换热呈现不对称特性分布;而扰流肋的存在减弱了横流对外表面的影响,换热系数相对于仅有横流时降低,且使外表面流动及换热的对称性有所改善.     

阵列射流冲击冷却传热特性的数值研究

以涡轮叶片冷却技术为背景,采用带转捩的剪切应力输运(Transition SST)模型对阵列射流冲击冷却的传热特性进行数值模拟,分析了冲击Re、冲击间距、初始横向流和冲击孔排列方式的影响规律。结果表明:冲击间距对靶面平均Nu的影响存在最优值,在所计算的范围内,Zn/d=2时平均Nu最大;在冲击孔排列方式影响中,当冲击间距Zn/d≤2时,顺排孔冲击冷却传热效果优于错排,而当Zn/d≥3时,错排孔冷却传热效果优于顺排。     

带扰流圆柱肋楔形通道的流动与换热数值研究

建立了带扰流圆柱肋楔形通道内的换热与压力损失数值计算模型,采用ANSYS-CFX商用软件数值研究了楔形通道内叉排和顺排柱肋的换热与压损特性,分析了流动与结构参数的影响规律。结果表明:随雷诺数的增大,柱肋表面、柱肋排以及通道底面的平均努赛尔数呈增大趋势;随着x/D的增大,柱肋表面和柱肋排的平均努赛尔数有所降低;随着楔形通道收缩角的增大,柱肋表面和通道底面的平均努赛尔数略有增强;相同条件下的叉排柱肋换热效果要好于顺排柱肋换热效果。范宁摩擦系数随雷诺数增加而略有增大,随x/D增大有较大的降低,随着收缩角的增大而增大。在计算参数内,叉排柱肋且x/D为1.5时的热力性能系数最高。     

“冲击-气膜”复合式结构冷却效果数值研究

分析了六种不同的"冲击-气膜"复合式冷却结构,将其应用在燃气轮机涡轮导向器叶片中弦区并对其内部流体的流动和换热进行了数值模拟.计算条件采用某燃气轮机的典型工况,流体物性参数随温度变化.将不同"冲击-气膜"复合式冷却结构的计算结果进行对比得出:冲击孔与气膜孔在展向的排列形式对冷却效果有较大影响,叉排明显优于顺排;随着冲击孔的后移,冷却气体对腔内壁的覆盖面积逐渐减小,冷却效果逐渐降低,流阻逐渐增大;在来自冲击冷却和气膜冷却多种影响因素的共同作用下,气膜孔角度和所在面曲率对冷却效果和流阻的影响被大幅度削弱.     

Flow and heat transfer of confined impingement jets cooling using a 3-D transient liquid crystal scheme

It has been shown that the heat transfer coefficients obtained from using the 1-D transient liquid crystal scheme are higher than those obtained from employing the 3-D scheme when surface heat transfer is highly nonuniform such as on a hot surface subject to jet impingement cooling. This is due to the fact that 1-D method does not include the lateral heat flows induced by local temperature gradients. The objective of this study is to provide a new database of heat transfer coefficient distribution on the jet impingement target surface in the confined cavity by employing a 3-D transient liquid crystal scheme. The study is performed with an 8 × 11 array of confined impinging jets with Reynolds numbers ranging from 1039 to 5175. The 1-D results are higher than the 3-D results with the local maximum and minimum heat transfer values being overvalued by about 15–20% and the overall heat transfer by approximately 12%. In addition, hot-film measurements of the flow structure are conducted to gain insight into the effects of cross-flow on heat transfer behavior. The surface mapping of heat transfer coefficient demonstrates a change from columnar pattern to a horizontal pattern and switching back to the columnar pattern as Reynolds number increased consecutively. This pattern switching is thought to be caused by the competition between jet penetration and the cross-flow buffering effect. A nonuniformity index is defined to provide a quantitative measure for cooling effectiveness for various cases. The results indicate that increased cross-flow degrades the heat transfer performance but increase uniformity.     

Experimental Study on the Air-Side Performance of a Multipass Parallel and Counter Cross-Flow L-Footed Spiral Fin-and-Tube Heat Exchanger

This study conducted experiments on the air-side performance of novel L-footed spiral fin-and-tube heat exchangers that were faced with airflow at high Reynolds numbers (3500–13,000). The examined heat exchangers have a multipass parallel-and-counter cross-flow type of water flow arrangement. This flow arrangement is a combination of the parallel cross-flow and the counter cross-flow. This type of water flow arrangement may be the best fit for the reverse-flow system, because it can provide constant heat-exchange effectiveness for every flow reversal direction at the same airflow rate. Ambient air was used as a working fluid on the air side and hot water for the tube side. This way the effect of the number of tube rows on the heat transfer and friction characteristics of L-footed spiral fin-and-tube heat exchangers was clearly observed. The effect of the fin's outside diameter on the pressure drop was also studied. The results show that the number of tube rows has no significant effect on the air-side heat transfer or on friction characteristics at high Reynolds numbers. However, the fin's outside diameter shows a significant effect on the pressure drop. The pressure drop increases as the fin's outside diameter increases for the same number of tube rows.     

Experimental Study on Air Cooling Via a Multiport Mesochannel Cross-Flow Heat Exchanger

The air-side heat transfer and flow characteristics of cross-flow multiport slab mesochannel heat exchanger are investigated experimentally in this article. The multiport slab mesochannel heat exchanger consists of 15 finned aluminum slabs; each slab contains 68 flow channels of 1 mm circular diameter. The cold deionized water at a constant mass flow rate was forced to flow through the mesochannels, whereas the hot air at different velocities was allowed to pass through the finned passages of the heat exchanger core in cross-flow orientation. The heat transfer and fluid flow key parameters were examined in the region of the air-side Reynolds number in the range of 972–2758, with a constant water-side Reynolds number of 135. The effect of air-side Reynolds number on air-side Nusselt number was examined and a general correlation of Nusselt number with Reynolds number was obtained. The Nusselt number value was found to be higher in comparison with other research works for the corresponding Reynolds number range. The multiport mesochannel flat slab geometry has offered uniform temperature distribution into the core. This uniform temperature distribution leads to higher heat transfer over stand-alone inline flow tube bank.     

Effect of number of tube rows on the air-side performance of crimped spiral fin-and-tube heat exchanger with a multipass parallel and counter cross-flow configuration

The air-side performance of crimped spiral fin and tube heat exchangers at high Reynolds number (3000–13,000) is investigated in this study. The test heat exchangers have a new type of multipass parallel and counter cross-flow water flow arrangement which is a combination of parallel cross-flow and counter cross-flow. The test samples are made from copper and aluminium with different number of tube rows (N_row = 2, 3, 4 and 5). The effects of number of tube rows and fin material on the heat transfer and friction characteristics are studied. The results show that no significant effect for either number of tube rows or fin materials on the heat transfer performance is found at high Reynolds number. In addition, the correlation of the air-side performances of this type of the heat exchangers at high Reynolds number is developed for industrial applications.     

Laminar forced convection heat transfer to ordered and disordered single rows of cylinders

We study laminar forced convection heat transfer to or from a single row of equidistantly and non-equidistantly spaced parallel cylindrical wires, perpendicular to the flow direction. We report average Nusselt numbers as a function of geometry and flow conditions, for open frontal area fractions between 0.04 and 0.95, Prandtl numbers between 0.7 and 10, and Reynolds numbers (based on the wire diameter and the free stream velocity) between 0.001 and 600. For equidistantly spaced rows of cylindrical wires we propose a general analytical expression for the average Nusselt number as a function of the Reynolds number, Prandtl number and the open frontal area fraction, as well as asymptotic scaling rules for small and large Reynolds. For all studied Prandtl numbers, equidistant rows exhibit decreasing average Nusselt numbers for decreasing open frontal area fractions at low Reynolds numbers. For high Reynolds numbers, the Nusselt number approaches that of a single cylinder in cross-flow, independent of the open frontal area fraction. For equal open frontal area fractions, the Nusselt number in non-equidistant rows is lower than in equidistant rows for intermediate Reynolds numbers. For very low and high Reynolds numbers, non-uniformity does not influence heat transfer.     

Heat Transfer and Thermal Characteristics Effects on Moving Plate Impinging from Cu-Water Nanofluid Jet

The present article is focused on modelling of flow and heat transfer behaviour of Cu-water nanofluid in a confined slot jet impingement on hot moving plate.Different parameters such as various moving plate velocities,nanoparticles at various concentrations,variation in turbulent Reynolds number and jet nozzle to plate distance have been considered to study the flow field and convective heat transfer performance of the system.Results of distribution of local and average Nusselt number and skin friction coefficients at the plate surface are shown to elucidate the heat transfer and fluid flow process.Qualitative analysis of both stream function and isotherm contours are carried out to perceive the flow pattern and heat transfer mechanism due to moving plate.The results revealed that average Nusselt number significantly rises with plate velocity in addition with jet inlet Reynolds number.Correlations of the average Nusselt numbers are presented.     

Local heat transfer distribution on a smooth flat plate impinged by a slot jet

Experimental investigation of local heat transfer distribution on a smooth flat plate impinged by a normal slot jet is conducted. Present study concentrates on the influence of jet-to-plate spacing (z/b) and Reynolds number on the fluid flow and heat transfer distribution. A single slot jet with an aspect ratio (l/b) of about 50 is chosen to get the fully developed flow at the nozzle exit. Reynolds number based on slot width is varied from 4200 to 12,000 and jet-to-plate spacing (z/b) is varied from 0.5 to 12. The local heat transfer coefficients are estimated from the thermal images obtained from infrared thermal imaging camera. Measurement for the static wall pressure is carried out for various jet-to-plate spacings at a Reynolds number of 12,000. Normalized value of turbulence and velocity are measured using hot wire anemometer along the streamwise direction (x/b) for jet-to-plate spacings (z/b) of 1, 2, 4, 6, 8, 10 and 12. The entire flow field is divided into three regimes namely stagnation region (laminar boundary layer associated with favorable pressure gradient), transition region (associated with increase in turbulence intensities and heat transfer) and turbulent wall jet region. Semi-empirical correlation for the Nusselt number in the stagnation region is proposed. Heat transfer characteristics in the transition region are explained based on the fluid dynamic behavior from the hot wire measurements. Semi-empirical correlation for the Nusselt number in the wall jet region is presented using the velocity profile obtained from the hot wire measurements.     

Experimental Study on Heat Transfer of Heated Falling Film Under Gas–Liquid Cross-Flow Condition

With the influence of the different gas Reynolds numbers and liquid Reynolds numbers on heated falling film heat transfer, an experiment was performed by noncontact thermal infrared imaging technology under the gas–liquid cross-flow condition. The results indicated that during the increase of liquid Reynolds number the thickness and thermal resistance of liquid film increased in the determined temperature of the heating water, which weakened the heat transfer of the liquid film. However, the increase of liquid Reynolds number strengthened liquid film turbulence and therefore enhanced heat transfer. Under the synergistic effect of these two factors, there should be an optimal liquid Reynolds number that minimizes thermal resistance and maximizes the heat transfer coefficient of the liquid film. Temperature plays an important role in heat transfer of laminar liquid film flow. However, the heat transfer of turbulent liquid film flow is not sensitive to liquid film inlet temperature.     

A numerical study of the unsteady flow and heat transfer in a transitional confined slot jet impinging on an isothermal surface

A numerical finite-difference approach was used to compute the steady and unsteady flow and heat transfer due to a confined two-dimensional slot jet impinging on an isothermal plate. The jet Reynolds number was varied from Re=250 to 750 for a Prandtl number of 0.7 and a fixed jet-to-plate spacing of H/W=5. The flow was found to become unsteady at a Reynolds number between 585 and 610. In the steady regime, the stagnation Nusselt number increased monotonically with Reynolds number, and the distribution of heat transfer in the wall jet region was influenced by flow separation caused by re-entrainment of the spent flow back into the jet. At a supercritical Reynolds number of 750 the flow was unsteady and the net effect in the time mean was that the area-averaged heat transfer coefficient was higher compared to what it would have been in the absence of jet unsteady effects. The unsteady jet exhibited a dominant frequency that corresponded to the formation of shear layer vortices at the jet exit. Asymmetry in the formation of the vortex sheets caused deformation or buckling of the jet that induced a low-frequency lateral jet “flapping” instability. The heat transfer responds to both effects and leads to a broadening of the cooled area.