小型平板CPL蒸发器耦合计算及优化设计研究

本文建立了小型平板CPL蒸发器毛细多孔芯内汽液两相流动与传热的模型以及金属外壁和工质区的导热模型,并进行耦合求解.分析了金属侧壁效应对蒸发器性能的影响,提出小型平板CPL存在着侧壁效应传热极限.数值结果表明,工质蒸发发生在多孔芯加热表面附近,蒸发器采用单一金属外壁时由于侧壁效应导致系统传热极限低,而上壁采用导热系数大,侧壁及下壁采用导热系数小的新型结构能够明显的提高系统的传热能力,同时使加热表面的温度维持在较低的水平.     

小型平板CPL蒸发器优化设计研究

本文建立了小型平板CPL蒸发器二维的整场数学模型,并用SIMPLE程序对蒸发器进行整场耦合求解.研究表明,平板型CPL蒸发器存在着侧壁效应传热极限,减小液体补偿腔的高度,减小侧壁以及下壁的厚度以及增加毛细芯的高度可以提高CPL的传热能力.     

小温差喷雾碰壁蒸发的实验研究

本文对小温差下垂直平面的喷雾碰壁蒸发传热特性进行了实验研究,研究了喷嘴在不同的流量和喷距下热流密度、壁温和换热系数之间的关系.实验中,测量范围还扩展到无沸腾区域.实验发现,在常压下,水雾在加热表面开始沸腾的过热度约为10℃,这时的沸腾换热系数将急剧增大,壁温上升的斜率显著下降.本文的研究结果对新型蒸发器的开发有指导作用.     

稳态平板法测量导热系数的若干影响因素分析

研究发现,热源温度和环境温度等因素通过试样的侧面散热影响平板稳态法测量导热系数的精度,散热铜板的上下表面散热功率不一致也将影响导热系数测量的准确性.用大空间自然对流理论对实验数据处理公式修正后,可有效减小侧面散热对测量的影响.在设计实验时应首先获得散热铜板的散热功率曲线,选择合适的散热铜板温度,而后通过综合考虑试样厚度和热源温度以控制传热温差,使测量时散热铜板温度处于最佳温度附近.     

工质及材料对基于AMTEC多孔芯蒸发器性能的影响

以基于AMTEC的碟式太阳能热发电系统的毛细抽吸两相回路多孔芯蒸发器为对象,建立轴对称恒温相变模型,研究了分别以钠、钾、钠钾合金为工质时的毛细多孔芯及液体通道内压力、速度和温度分布,以及多孔芯材料分别为高温陶瓷、不锈钢、镍时的蒸发器内热质传输特性。结果表明,以钠钾合金为工质的多孔芯内表面温度要明显低于钠和钾;以高温陶瓷为多孔芯材料时,多孔芯内表面温度最低,使用镍为多孔芯材料时,内表面温度最高。     

带肋气膜冷却平板的数值模拟研究

本文对不带肋和带45°肋气膜冷却平板的三维对流换热与导热耦合传热问题进行了数值模拟。网格划分采用非结构化网格,湍流模型为SSTκ-ε模型,近壁处采用壁面函数法,采用SIMPLEC算法求解速度和压力的耦合。计算获得了不带肋和带45°肋气膜冷却平板的流场分布和平板内外表面的换热系数值。结果表明带45°肋的气膜冷却平板通道流场结构比较复杂,平板表面平均温度较无肋气膜冷却平板表面平均温度下降,而在近气膜孔区域冷、热表面平均换热系数较无肋时增大。     

粘土空心砖结构优化的数值模拟

本文采用有限容积法对50种具有不同孔数及排列方式的240×115×90粘土空心砖进行了当量导热系数的三维数值模拟研究.模拟中考虑了粘土空心砖的孔内表面辐射、孔数及排列方式以及室内外温差对其当量导热系数的影响.模拟结果表明:孔内表面辐射对当量导热系数有不可忽略的作用,孔数及排列方式直接影响当量导热系数的值,存在具有最低当量导热系数的粘土空心砖结构.在该结构下空心砖的当量导热系数几乎不随室内外温差的变化而变.模拟结果对粘土空心砖的结构选型、工程设计及建筑节能具有重要的意义.     

工质对平板型LHP运行特性影响的实验研究

本文研制了一套以不锈钢丝网为毛细芯的平板式蒸发器、风冷管翅式冷凝器的环路热管,并着重研究其以甲醇和丙酮为工质时运行特性的差异。实验结果表明,小型平板式LHP具有良好的启动特性和适应变热负荷能力,在相同的工况条件下,以丙酮为工质的LHP温度波动较小,系统启动较快且蒸发器壁面温度较低,但其极限热负荷能力低于甲醇。     

热管吸液芯的研究进展

文中对热管内吸液芯的研究进展进行了阐述,着重从对热管传热性能起主要影响作用的比表面积、孔隙率、渗透率、有效毛细半径、密度、有效导热系数等结构参数方面进行了分析,最后介绍了多孔泡沫金属这一新型的热管吸液芯,并指出了今后的研究方向.     

平板型环路热管泡沫金属毛细芯优化研究

本文设计了一种制备简单,成型规则,参数易控制的泡沫金属毛细芯,通过对其基本参数的研究测试分析,发现控制其孔隙率可以有效控制其平均孔径和有效导热系数。进一步采用不同孔隙率层复合布置的方式对泡沫金属毛细芯进行优化,并搭建实验台对其性能参数进行表征。结果表明：当复合毛细芯的加热侧和吸液侧分别布置为低孔隙率层和高孔隙率层时,其抽吸传质特性及蒸发传热特性均得到了优化。     

Thermal Performance of a Capillary Pumped Loop for Automotive Cooling

The design and test results for a capillary pumped loop (CPL) for thermal management of up to 210 W at the source and heat transfer over a distance of 1 m are discussed. The design configuration of the CPL evaporator consists of an internally grooved aluminum evaporator, 31.70-mm outer diameter and 500-mm long, fitted with a porous ultra-high molecular weight polyethylene wick, 8- to 15-μm pore radius, and 38% porous volume. Heat was transferred using a stainless steel tube of 4.5-mm internal diameter for vapor and liquid lines. High-grade acetone (99.99% pure) was used as the heat transfer fluid inside the loop. In the tests, thermal characteristics of the CPL were specifically studied with respect to the temperature control capability using an active thermal device on the reservoir and to the start-up process through pressure priming of the capillary evaporator. The loop was able to start-up successfully at both low and high heat loads, although proper priming of the wick structure before start-up was necessary to attain low evaporator temperatures during steady-state operation. While maintaining constant reservoir temperature through active means, the loop was able to control evaporator temperature within 55 ± 3°C, even with changing input heat from 30 to 210 W. Total thermal resistance from the evaporator surface to the surroundings was 0.19° to 1.15° C/W with the minimum value achieved at the maximum heat load of 210 W. This study is intended to illustrate the thermal potential of the CPL as an effective temperature control device in automotive applications.     

Coefficient de transfert, à l'interface de vaporisation,d'une boucle fluide diphasique à pompage thermocapillaire

Heat transfer coefficient at vaporisation interface of a two phase capillary loop. In this article, we present the results of heat transfer coefficient measurements at the vaporisation interface of a capillary pumped two-phase loop for two different types of evaporators and various powers. High contact between the evaporator wall and the porous wick, which induces capillary pumping, prevents vapor from escaping and being forced back into the wick and inhibits the device starting up. First, the surface state of the evaporator wall, then the minimum distance between wall and porous wick necessary to optimize operating conditions have been established.     

照明用大功率LED回路热管散热器的研究

分析了照明用大功率LED封装的散热特性,提出了一种用于大功率LED系统散热的回路热管;研究了热负荷、倾角、加热方式等对热管的起动性、均温性、热阻等的影响。试验结果表明,所设计的热管散热器的热阻在0.19K/W~3.1K/W之间,蒸发器的均温性被控制在1.5℃以内,满足大功率LED封装的均温性要求,在热负荷为100W时,蒸发器的温度被控制在100℃以下,满足大功率LED结点温度的控制要求。     

燕尾形轴向槽道热管瞬态特性实验研究及热阻模型

实验研究燕尾形轴向槽道热管启动/关闭及负荷变化的瞬态响应特性。建立了燕尾形轴向槽道热管的热阻理论预测模型,分析工作温度和热负荷及对热管总热阻的影响。结果表明:热管在负荷突然增加或减小时,响应特性良好;热管在启动过程中,热管的蒸发段、绝热段和冷凝段的温度都在增大;总热阻随热负荷的增大而增大;然而,总热阻受工作温度的影响较小;比较总热阻和平均温差的实验测量和计算值,两者符合较好。     

Thermal hydraulic characterization of stainless steel wicks for heat pipe applications

Heat pipe design and manufacturing require the knowledge of the thermal hydraulic performance of the wicks. The aim of the present work is the thermal hydraulic characterization of stainless steel wicks (sintered porous media and gauzes) to be employed in our experimental water heat pipe. Commercial sintered porous media (able to capture 90 % of 90 μm particles and 99.9 % of 130 μm particles) and gauzes (nominal wire size 0.11 mm, square mesh opening 0.209 mm) have been used. Thermal hydraulic characterization of the wicks is obtained through the experimental measurement of: capillary height (through which the equivalent porous radius can be evaluated), liquid hydraulic head (through which the liquid pressure drop in the wick is evaluated) wick permeability is also evaluated from the hydraulic head (through Darcy's law), heat flux, wick mass flow rate during the evaporation (through which, from the knowledge of other measured wick parameters, the wick two-phase pressure drop is calculated) and wick porosity (through which the thermal conductivity of the wick saturated with liquid can be determined). Concerning the heat flux, it is found to be dependent on the distance between the liquid level and the evaporating zone, the evaporating zone length, the wall superheat and the water subcooling, the contact between the heater and the wick and the superficial boundary conditions of the wick.     

MEASUREMENT TECHNIQUES FOR HORIZONTAL FLOW BOILING HEAT TRANSFER WITH PURE AND MIXED REFRIGERANTS

Abstract

A test rig and measurement techniques for horizontal flow boiling of pure and mixed refrigerants are described. Local heat transfer coefficients were measured for R22/R114 and R12/R152a mixtures as well as the corresponding pure components. The test section consists of an S-m-long, 9.1-mm-i.d., electrically heated stainless steel tube and has the distinctive feature of variable heated length. Details of pressure, composition, and fluid and wall temperature measurements are discussed. The composition of subcooled liquid entering test section varied from test to test, and it is recommended that it be measured for each test. For the R22/R114 mixture, local composition measurements in the annular liquid film revealed a composition variation of up to 0.07 mole fraction around the circumference of the heated tube.     

Recent Advances in Loop Heat Pipes with Flat Evaporator

The focus of this review is to present the current advances in Loop Heat Pipes (LHP) with flat evaporators, which address the current challenges to the wide implementation of the technology. A recent advance in LHP is the design of flat-shaped evaporators, which is better suited to the geometry of discretely mounted electronics components (microprocessors) and therefore negate the need for an additional transfer surface (saddle) between component and evaporator. However, various challenges exist in the implementation of flat-evaporator, including (1) deformation of the evaporator due to high internal pressure and uneven stress distribution in the non-circular casing; (2) heat leak from evaporator heating zone and sidewall into the compensation chamber; (3) poor performance at start-up; (4) reverse flow through the wick; or (5) difficulties in sealing, and hence frequent leakage. This paper presents and reviews state-of-the-art LHP technologies; this includes an (a) review of novel manufacturing methods; (b) LHP evaporator designs; (c) working fluids; and (d) construction materials. The work presents solutions that are used to develop or improve the LHP construction, overall thermal performance, heat transfer distance, start-up time (especially at low heat loads), manufacturing cost, weight, possibilities of miniaturization and how they affect the solution on the above-presented problems and challenges in flat shape LHP development to take advantage in the passive cooling systems for electronic devices in multiple applications.     

Experimental Investigation of Opposing Mixed Convection in a Channel with an open Cavity Below

Abstract

In this article, mixed convection in an open cavity with a heated wall bounded by a horizontal unheated plate is investigated experimentally. The heated wall is on the opposite side of the forced inflow. The results are reported in terms of wall temperature profiles of the heated wall and flow visualization. The range of pertinent parameters used in this experiment are Reynolds numbers (Re) from 100 to 2,000 and Richardson numbers (Ri) from 4.3 to 6,400. Also, the ratio between the length and the height of cavity (L/D) ranges from 0.5–2.0, and the ratio between the channel and cavity height (H/D) is equal to 1.0. The lack of experimental results on mixed convection in a channel with an open cavity below was an impetus for investigating this configuration when one cavity vertical wall is heated at uniform heat flux. The present results show that at the lowest investigated Reynolds number, the surface temperatures are lower than the corresponding surface temperatures for Re = 2,000 at the same ohmic heat flux. The flow visualization shows that for Re = 1,000, there are two nearly distinct fluid motions: a parallel forced flow in the channel and a recirculation flow inside the cavity. For Re = 100, the effect of a stronger buoyancy determines a penetration of thermal plumes from the heated plate wall into the upper channel. Moreover, the flow visualization shows that for lower Reynolds numbers, the forced motion penetrates inside the cavity, and a vortex structure is adjacent to the unheated vertical plate. At higher Reynolds numbers, the vortex structure has a larger extension while L/D is held constant.