棋盘拓扑矩形通道换热器的流动及换热特性研究

选取矩形换热器的最基本换热单元，通过数值模拟方法对不同截面尺寸的矩形通道换热器的流动和换热特性进行了探究。研究发现：在截面高宽比相同的情况下，随着水力直径的增加，流动阻力逐渐减少，传热性能下降，但换热器的综合换热性能提高；当中心矩形截面面积不变的前提下增大截面高宽比，水力直径不断降低，流动阻力随之增大，换热性能与高宽比并非为线性关系，在研究范围内高宽比为4的结构换热效果最佳。     

小尺度圆柱涡流发生器的传热与流动特性

应用大涡模拟对设置小尺度圆柱涡流发生器矩形槽道底面的流动与传热特性进行研究,小尺度圆柱涡流发生器置于湍流边界层内。分析不同间隙比对槽道流动结构、槽道底面Nusselt数、摩擦因数以及综合性能系数的影响。此外,采用大涡模拟所得槽道计算结果与前人直接数值模拟结果一致性很好,验证所采用数值方法的准确性与可靠性。研究结果表明,与未设置小尺度圆柱涡流发生器的矩形槽道相比,设置小尺度圆柱涡流发生器槽道底面的换热性能可以得到显著提高,同时其流动阻力的增加亦得到有效抑制。当间隙比为2.0时,槽道底面换热性能最佳,其Nusselt数可提高18.76%;而当间隙比为0.5时,槽道底面减阻效果最佳,摩擦因数可减小3.77%。     

斜截椭圆柱式涡流发生器强化传热的大涡模拟

对流体在放置斜截椭圆柱式涡流发生器矩形槽道内的流动与传热特性进行大涡模拟,得出流场中速度、温度与压力参数的瞬态变化特性,再现温度场、压力场及诱导旋涡的变化过程,并对流动结构及涡流发生器强化传热的机理进行分析。为验证大涡模拟计算结果的准确性,在相同条件下对未布置涡流发生器的空槽道分别采用湍流模型和大涡模拟进行对比计算,两者的计算结果符合较好。计算结果表明：流场中布置的涡流发生器可以诱导漩涡,而由其所诱导的流向涡对强化传热起主要作用。与相同条件下未布置涡流发生器的情况相比,局部对流换热系数可提高64%～105%,平均对流换热系数则可提高17%～36%;涡流发生器附近位置的对流换热系数提高幅度最大,传热面附近流体的流动状况及流动结构与传热密切相关。     

湍流边界层内钝体扰流的流动与传热特性

应用大涡模拟方法对小尺度开缝圆柱涡流发生器强化传热和流动减阻的机理进行研究。水平开缝圆柱置于充分发展湍流边界层内,分析不同间隙比对开缝圆柱尾流、湍流边界层拟序结构以及槽道底面流动与换热特性的影响。为验证所采用数值方法的准确性与可靠性,将矩形空槽道的计算结果与前人直接数值模拟结果及与采用相关准则关系式所得结果进行对比。计算结果表明：湍流边界层内钝体扰流的尾迹流与壁面边界层的相互作用能够显著提高槽道的换热性能。与未开缝的基准圆柱相比,间隙比小于2.0时,开缝圆柱通道的整体热性能较好;间隙比为2.0时,其综合性能系数最大;间隙比大于2.0时,整体热性能较差。与矩形空槽道相比,最大努塞尔数可提高17.45%,最小摩擦因数可减小4.94%。     

螺旋曲面三维肋强化传热的数值模拟研究

利用计算流体力学软件Fluent6.3研究普通直型三维肋和螺旋曲面三维肋分别用于矩形流体通道的流动换热特性,分析两者在雷诺数Re为2000～10000、迎流攻角β均为45°时的传热与阻力特性。研究结果表明:矩形流体通道内加螺旋曲面三维肋时平均努赛尔数Nu和平均阻力系数f皆大于普通直型三维肋,并随着Re的增大而增大。同时,利用综合评价准则数G对其传热进行综合判定,G值大于1。螺旋曲面三维肋的综合性能优于普通直型三维肋。     

水平槽道内几种周期性结构的传热与流动研究

采用数值模拟方法,对流体在不同周期性结构二维水平槽道内的传热性能与流动特性进行研究。分析不同雷诺数条件下,布置于槽道下壁面的障碍块表面时均努塞尔数Nu及表面摩擦因数μ的变化规律。计算结果表明,当障碍块之间量纲一距离分别为0.50和0.25、雷诺数Re=1 000时;槽道上、下壁面均布置障碍块的传热性能较仅在槽道下壁面布置障碍块的传热性能有了显著提高,前者比后者的传热性能分别提高393%和574%。当雷诺数Re=500、障碍块之间量纲一距离为0.50时,对在槽道中间设置一斜板与不设置斜板两种情况进行比较后发现,设置斜板的槽道比不设置斜板的槽道传热性能提高27.1%。当在下壁障碍块右上角处放置一小圆柱体后发现:传热性能并未得到有效提高,但流动摩擦因数有所减小,从而使得输送流体的泵功降低。     

稀薄效应对空气静压导轨速度边界和温度特性的影响

当空气静压导轨气膜厚度为微米级别时,依据Kn数定义可知此时气膜内流动可能处于滑移区,气浮支撑的内部压力和承载特性会受到稀薄效应的影响,最典型的表现为边界速度滑移和温度跃迁现象。将基于格子Boltzmann方法研究稀薄效应对空气静压导轨速度边界和温度特性的影响,得到气膜径向速度和温度分布。通过机理分析和数值计算发现:随着Kn数的增大,速度滑移程度增大;而速度滑移间接引起黏温效应,导致边界温度跳跃现象。温度跳跃相当于在导轨与气膜之间的一个附加热阻,增加流动的摩擦损耗,影响散热。     

微小矩形通道内气体层流换热的数值模拟

在基于贴壁层概念和已经求得的贴壁层内气体热导率变化规律的基础上 ,数值求解了微小矩形通道内气体层流已充分发展时 ,在壁面等热流边界条件下的温度分布和换热 ,得到了矩形微通道在不同截面长宽比 ζ和不同Knudsen数下的量纲一的温度分布和 Nu 值 ,并进行了相应的讨论。     

高宽比对矩形微小通道内流动的影响

为了研究高宽比对矩形微小通道内流动的影响,选定槽道当量直径均为lmm,长度为360mm,矩形截面的高宽比分别为1/10、1/5、1/4、1/2、1、2、4、5和10的微小通道,实验测得煤油在其中的流动压降,算得其沿程的损失系数.结果发现截面高宽比小于1时,沿程流动压降随截面高宽比增大而减小,损失系数随截面高宽比增大而减小;截面高宽比大于1时,沿程流动压降随截面高宽比增大而增大,沿程损失系数随高宽比增大而增大.     

几何尺寸对矩形微通道液体流动和传热性能的影响

基于连续介质方法数值研究液体在不同几何结构微通道中的流动和传热性能。在相同热边界条件下,通过比较水力直径、通道长度和宽高比等几何参数对液体微流动的影响,得到各参数对泊肃叶数(Po)和努塞尔数(Nu)的影响关系。研究发现,截面宽高比越大,Po数越小,且雷诺数对泊肃叶数基本无影响;雷诺数(Re)小于500情况下,水力直径小于0.545 mm时,Po数随水力直径减小而减小,水力直径大于0.545 mm时,水力直径变化对Po数基本无影响;Po数不随通道长度变化而变化,但略受流动雷诺数影响;在Re=20～1 800时,Nu数正比于水力直径和宽高比,但是通道长度对Nu数的作用受流动Re数的影响;在通道材料和流动介质相同的条件下,Nu数和Re数之间的关系受通道几何参数的影响,并且拟合得到其关系式。     

微通道内流体流动及换热特性的数值分析

采用Navier—Stokes方程与滑移边界条件联立的理论分析模型，对等壁温、等热流及无温度梯度工况下，气体在微通道中的流速分布、阻力系数变化趋势（Cf·Re）和传热特性（努塞尔数）进行了数值研究。结果表明：气体稀薄效应可显著减小管内的摩擦阻力和努塞尔数，增大气体流速；壁面的速度滑移和温度跳跃对微圆管内换热特性的影响相反，温度跳跃的影响更大；等热流加热与等壁温加热两种情况下，努塞尔数随克努森数的变化趋势明显不同。     

Slip flow over micron-sized spherical particles at intermediate Reynolds numbers

A numerical investigation has been performed to identify the rarefaction effects on the flow structure of an isolated micron-sized spherical particle. An isothermal sphere in the slip flow regime 10^?3 ?? Kn ?? 10^?1 at intermediate Reynolds numbers (1 ?? Re ?? 50) is considered. The Navier-Stokes equations are solved by a control volume technique in conjunction with the velocity slip boundary condition. It was found that the wake region can shrink considerably as the Knudsen number increases. Furthermore, the skin friction and pressure drag coefficients decrease as the Knudsen number increases due to the reduction in normal velocity gradients and shrinkage of the wake region, respectively. Engineering correlations for predicting the total drag coefficient in the slip flow regime are presented.     

Heat transfer characteristics of gaseous slip flow in a micro-channel

Two-dimensional compressible momentum and energy equations with slip boundary conditions are solved to obtain the heat transfer characteristics of gaseous slip flow in a micro-channel with CWT (constant wall temperature) whose temperature is lower or higher than the inlet temperature (cooled case or heated case). The numerical methodology is based on the Arbitrary-Lagrangian-Eulerian (ALE) method. The stagnation temperature is fixed at 300 K and the computations were done for the wall temperature which ranges from 250 K to 350 K. The channel height ranges from 2 to 10 μm and the channel aspect ratio is 200. The stagnation pressure is chosen in such a way that the exit Mach number ranges from 0.1 to 0.7. The outlet pressure is fixed at atmospheric condition. The bulk temperature and the total temperature of the heated case are compared with those of the cooled case and also compared with temperatures of the incompressible flow in a conventional sized channel. Heat transfer characteristics of the gaseous flow are different from those of the liquid flow. And they are also different from each cooled and heated case. A correlation for the prediction of the heat transfer rate of the gaseous slip flow in a micro-channel is proposed.     

Effect of channel and plenum aspect ratios on the performance of microchannel heat sink under different flow arrangements

Microchannels based heat sinks are considered as potential thermal management solution for electronic devices. The overall thermal performance of a microchannel heat sink depends on the flow characteristics within microchannels as well as within the inlet and outlet plenum and these flow phenomena are influenced by channel aspect ratio, plenum aspect ratio and flow arrangements at the inlet and outlet plenums. In the present research work an experimental investigation has been carried out to understand how the heat transfer and pressure drop attributes vary with different plenum aspect ratio and channel aspect ratio under different flow arrangements. For this purpose microchannel test pieces with two channel aspect ratios, 4.72 and 7.57 and three plenum aspect ratios, 2.5, 3.0 and 3.75 have been tested under three flow arrangements, namely U-, S- and P-types. Test runs were performed by maintaining three constant heat inputs, 125 W, 225 W and 375 W in the range 224.3 ?? R_e ?? 1121.7. Reduction in channel width (increase in aspect ratio, defined as depth to width of channel) in the present case has shown about 126 to 165% increase in Nusselt number, whereas increase in plenum length (reduction in plenum aspect ratio defined as width to length of plenum) has resulted in 18 to 26% increase in Nusselt number.     

Aspect ratio effects of an adiabatic rectangular obstacle on natural convection and entropy generation of a nanofluid in an enclosure

In the present study, aspect ratio (AR) effects of a centered adiabatic rectangular obstacle numerically investigated on natural convection and entropy generation in a differentially heated enclosure filled with either water or nanofluid (Cu-water). The governing equations are solved numerically with finite volume method using the SIMPLER algorithm. The study has been done for Rayleigh numbers between 10³ and 10⁶, the aspect ratio of 1/3, 1/2, 1, 2 and 3 and for base fluid as well as nanofluid. It is found that, using the nanofluid leads to increase the flow strength, average Nusselt number and entropy generation and decrease the Bejan number especially at high Rayleigh numbers. At low Rayleigh numbers entropy generation is very low. By increasing Rayleigh number, entropy generation and Bejan number increases. It is observed that the viscose entropy generation is more considerable than the thermal entropy generation and has dominant role in total entropy generation. The maximum entropy generation occurs at AR = 1/3 and 3 and the minimum entropy generation occurs at AR = 1 and 1/2. It is observed that the effect of AR on Nusselt number, entropy generation and Bejan number depends on Rayleigh number.     

Influence of an aspect ratio of rectangular channel on the cooling performance of a multichip module

Experiments were performed by using PF-5060 and water to investigate the influence of an aspect ratio of a horizontal rectangular channel on the cooling characteristics from an in-line 6×1 array of discrete heat sources which were flush mounted on the top wall of the channel. The experimental parameters were aspect ratio of rectangular channel, heat flux of simulated VLSI chip, and channel Reynolds number. The chip surface temperatures decreased with the aspect ratio at the first and sixth rows, and decreased more rapidly at a high heat flux than at a low heat flux. The measured friction factors at each aspect ratio for both water and PF-5060 gave a good agreement with the values predicted by the modified Blasius equation within ±7%. The Nusselt number increased as the aspect ratio decreased, but the increasing rate of Nusselt number reduced as the aspect ratio decreased. A 5∶1 rectangular channel yields the most efficient cooling performance when the heat transfer and pressure drop in the test section were considered simultaneously.     

滑移边界对微型气浮轴承稳态性能的影响

根据气膜厚度的Knudsen数,确定滑移流为微型气浮轴承内部的润滑机制。引入二阶滑移流边界条件对连续流的状态方程进行修改,得到滑移流机制下修正的雷诺方程。利用有限差分法对雷诺方程求解,得到两种情况下的气压分布,进而得到相应的承载能力和偏位角。经过对比分析,发现在滑移流机制下气浮轴承的力学性能与连续流机制的情况有较大差异。在相同的转速和偏心率下,滑移流效应降低了气压分布的曲率,进而降低了气浮轴承所能够提供的承载能力。     

The effects of the compressibility of the subsonic flow on heat transfer characteristics in a microscale impinging slot jet

We experimentally investigated the effects of both the compressibility and nozzle width on the local heat transfer distribution of microscale unconfmed slot jets impinging on a uniformly heated flat plate. We made heat transfer measurements under the following experimental conditions; Reynolds numbers of Re = 4000~10000, Mach numbers of Ma = 0.13~0.68, nozzle-to-plate distances of H/B = 3~25, lateral distances of x/B = 0~25, and nozzle widths of B = 300~700 μm having a nozzle aspect ratio of y/B = 30. A thermal infrared imaging technique was used to measure the impingement plate temperature. The experimental results show that for all tested Re and H/B values at a nozzle width of B = 300 μm, the Nusselt number maximum occurred nearly at the stagnation point and then monotonically decreased along the downstream. However, at B = 500 and 700 μm, the maximum Nusselt number point shifted toward x/B ≈ 1.5~2.0. And the Nusselt number increased, as x/B increased, from the stagnation point to the shifted maximum point and monotonically decreased afterward. This shifted maximum point may be attributable to vortex rings promoting sudden flow acceleration and entrainment of surrounding air moving along the jet axis. For the same Reynolds number, the Nusselt number in the stagnation region increased as the nozzle width increased due to a momentum increase of the jet flow caused by the formation of vortices. And, the Nusselt numbers for the smallest nozzle width of B = 300 μm (or highest Mach number at a given Reynolds number) at all H/B and Reynolds numbers tested significantly deviated from those for B = 500 and 700 μm in the downstream region corresponding to x/B > 5, suggesting that the compressibility, when it is high, can affect the heat transfer in the downstream region.

     

Extended Graetz Problem Including Axial Conduction and Viscous Dissipation in Microtube

Extended Graetz problem in microtube is analyzed by using eigenfunction expansion to solve the energy equation. For the eigenvalue problem we applied the shooting method and Galerkin method. The hydrodynamically isothermal developed flow is assumed to enter the microtube with uniform temperature or uniform heat flux boundary condition. The effects of velocity and temperature jump boundary condition on the microtube wall, axial conduction and viscous dissipation are included. From the temperature field obtained, the local Nusselt number distributions on the tube wall are obtained as the dimensionless parameters (Peclet number, Knudsen number, Brinkman number) vary. The fully developed Nusselt number for each boundary condition is obtained also in terms of these parameters.