Wind turbine response to parameter variation of analytic inflow vortices

As larger wind turbines are placed on taller towers, rotors frequently operate in atmospheric conditions that support organized, coherent turbulent structures. It is hypothesized that these structures have a detrimental impact on the blade fatigue life experienced by the wind turbine. These structures are extremely difficult to identify with sophisticated anemometry such as ultrasonic anemometers. This study was performed to identify the vortex characteristics that contribute to high‐amplitude cyclic blade loads, assuming that these vortices exist under certain atmospheric conditions. This study does not attempt to demonstrate the existence of these coherent turbulent structures. In order to ascertain the idealized worst‐case scenario for vortical inflow structures impinging on a wind turbine rotor, we created a simple, analytic vortex model. The Rankine vortex model assumes that the vortex core undergoes solid body rotation to avoid a singularity at the vortex centre and is surrounded by a two‐dimensional potential flow field. Using the wind turbine as a sensor and the FAST wind turbine dynamics code with limited degrees of freedom, we determined the aerodynamic loads imparted to the wind turbine by the vortex structure. We varied the size, strength, rotational direction, plane of rotation, and location of the vortex over a wide range of operating parameters. We identified the vortex conformation with the most significant effect on the blade root bending moment cyclic amplitude. Vortices with radii on the scale of the rotor diameter or smaller caused blade root bending moment cyclic amplitudes that contribute to high damage density. The rotational orientation, clockwise or counter‐clockwise, produces little difference in the bending moment response. Vortices in the XZ plane produce bending moment amplitudes significantly greater than vortices in the YZ plane. Published in 2005 by John Wiley & Sons, Ltd.     

INTERACTION OF VORTICES WITH A PROGRESSIVE SURFACE WAVE

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多机系统水力振动与能量损失分析

针对多机系统的机组振动差异问题,采用RANS-LES数值计算方法,模拟一管双机组内部流场,利用监测点压力脉动信息分析过流部件的振动强度,计算能量损失与机组效率。结果表明,部分开度下,岔管的水流分配不平衡导致两机组流场存在差异,影响过流部件压力脉动与振动强度。数据对比发现2号机组尾水管涡带极不稳定,振动更强,导致能量损失更多,效率下降更严重。     

煤矿管道瓦斯流量计量技术研究

阐述了煤矿管道瓦斯流量计量技术的发展现状,分析了孔板流量计、涡街流量计、皮托管流量计、旋进漩涡流量计、V锥流量计的优缺点;针对瓦斯流量测量准确度受气体中的杂质和瓦斯体积分数变化影响的问题,提出了解决办法;建议煤矿瓦斯抽放管网中的主管、干管、支管采用V锥流量计,汇流管以及各评价单元采用多点采样的插入式流量计;指出煤矿管道瓦斯流量计量应根据不同的现场状况、工况条件及测量需求选择相应的流量计。     

多喷孔活塞式调流调压阀空化流动特性分析

以DN200多喷孔活塞式调流调压阀为研究对象,基于数值模拟,结合Realizable k-ε湍流模型和Zwart-Gerber-Belamri空化模型,研究了小开度、中等开度和大开度下空化流动特性以及节流孔内空化的形成机制,并且分析了开度和空化数对空化流动的影响。结果表明,节流孔处存在较大的压力和流速梯度,节流孔进口边缘附近会出现流动分离,在节流孔壁面形成附壁剪切旋涡,流动分离和附壁剪切旋涡是节流孔内空化的形成机制。同时,固定阀门进出口压力,随着开度逐渐增大,空泡体积线性增加,各开度空化强度相差不大。另外,随着空化数逐渐减小,流量系数呈现出先保持稳定后略微增加再急剧减小的变化趋势。本研究结果可以为该类型阀门的结构优化与运行维护提供参考。     

工况变化对贯流式水轮机叶顶间隙流态的影响

贯流式水轮机是低水头水能资源开发的主力机型之一,而转轮叶片叶顶间隙流动特性是影响其空化、稳定性能的关键因素。基于数值模拟的方法,本文研究了工况变化引发转轮叶片叶顶间隙泄漏涡初生位置、形态变化的机理,分析了间隙泄漏涡形态改变对水轮机空化、稳定性的影响规律,主要结果表明：工况变化必然伴随导叶开度变化,导叶开度的改变使得转轮叶片外缘头部冲角改变,进而对间隙泄漏涡的初生位置及三维形态产生影响;间隙泄漏涡初生位置及形态的变化是转轮叶片外缘空化特性改变的根源之一;间隙泄漏涡会提高其扫略区域内测点的压力脉动幅值,泄漏涡的影响可导致测点的压力脉动幅值提高一倍以上。     

刹车盘结构对车轮及整车流场的影响

为研究车轮刹车盘结构对旋转车轮和整车流场气动特性的影响,针对是否存在刹车盘两种情况分别建立等比例模型,采用可实现的k-ε两方程模型计算,对比分析气动升、阻力因数,表面压力因数及整体与局部流场,发现刹车盘结构在简化车体上对车轮局部和整车流场都具有突出影响,指出在整车气动特性模拟中刹车盘存在的必要性.进一步进行计算模型选择的研究,发现旋转壁面模型与多坐标参考系(Multiple Reference Frame,MRF)模型对旋转车轮的流场特性模拟结果有差异,在近车轮区域表现尤为明显.     

超高水头竖井旋流泄洪洞不同湍流模型数值模拟

基于VOF法,分别选取标准k-ε紊流模型、RNG k-ε紊流模型和Realizable k-ε紊流模型,对某一超高水头、大泄量竖井旋流泄洪洞的水力特性进行数值模拟,并将紊流模型计算结果与模型实验数据进行了对比分析。结果表明:3种紊流模型模拟计算所得的空腔直径、竖井壁面压强、旋流角等参数变化趋势与模型试验测试结果基本相同,但量值有所差别。相比较而言,Realizable k-ε紊流模型计算所得旋转水流的空腔直径、压坡底板与部分竖井壁面压强、旋流角在量值上更接近试验测量值。因此,Realizable k-ε紊流模型能够更好地模拟这种具有超高水头、大泄量、强旋转并带有自由液面旋转水流的水力特性。     

Effect of Vortex Restructuring on Heat Transfer in an “Inverted” Flame

The papers deals with formation of vortex structures during combustion of a fuel gas–air mixture injected vertically down through a hole in a flat plate. It has been established that the shape, position, and number of vortex cells are determined by the flow rate and composition of the fuel mixture. It is shown that as the flow rate increases from the minimum critical value for which a vortex structure arises, the number of vortex cells decreases from five or six to one. A further increase in the gas flow rate leads to transition to turbulence of the combustion product flow. The presence of a vortex structure increases the critical Reynolds number at which the flow becomes turbulent. Reverse transition to the structure with an increased number of vortex cells occurs with a delay in the gas flow rate (gas discharge hysteresis). Variation in flow rate is accompanied by bifurcation of the number of vortex cells.     

Numerical study of particle dispersion in the wake of gas-particle flows past a circular cylinder using discrete vortex method

A numerical investigation on the particle dispersion in the wake of particle-laden gas flows past a circular cylinder at Reynolds number of 10⁵ is presented. In the numerical method, the Discrete Vortex Method with the diffusion velocity model is employed to calculate the unsteady gas flow fields and a Lagrangian approach is applied to track individual particles. A dispersion function is defined to represent the dispersion scale of the particle. The distributions of gas velocities and vortex blobs, the trajectories and dispersion functions as well as distributions for particles with various Stokes numbers ranging from 0.01 to 1000 are obtained. The numerical results show that: (1) very small sized particles with St = 0.01 can distribute both in the vortex core and around the vortex periphery, whereas intermediate sized particles with St = 1.0, 10 are distributed around the vortex periphery, and very large sized particles with St = 1000 do not feel the gas flow; (2) only at small Stokes number (St = 0.01, 0.1) the particles do not impact with the cylinder; (3) the particle's dispersion intensity decreases precipitously as St is increased from 0.01 to 10.