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车辆通风式制动盘内部通道对流换热研究综述

李杰 陶龙 顾佳玲 陈诚 陈颖

李杰, 陶龙, 顾佳玲, 陈诚, 陈颖. 车辆通风式制动盘内部通道对流换热研究综述[J]. 交通运输工程学报, 2022, 22(2): 19-40. doi: 10.19818/j.cnki.1671-1637.2022.02.002
引用本文: 李杰, 陶龙, 顾佳玲, 陈诚, 陈颖. 车辆通风式制动盘内部通道对流换热研究综述[J]. 交通运输工程学报, 2022, 22(2): 19-40. doi: 10.19818/j.cnki.1671-1637.2022.02.002
LI Jie, TAO Long, GU Jia-ling, CHEN Cheng, CHEN Ying. Review on convective heat transfer in internal channel of ventilated brake disc of vehicle[J]. Journal of Traffic and Transportation Engineering, 2022, 22(2): 19-40. doi: 10.19818/j.cnki.1671-1637.2022.02.002
Citation: LI Jie, TAO Long, GU Jia-ling, CHEN Cheng, CHEN Ying. Review on convective heat transfer in internal channel of ventilated brake disc of vehicle[J]. Journal of Traffic and Transportation Engineering, 2022, 22(2): 19-40. doi: 10.19818/j.cnki.1671-1637.2022.02.002

车辆通风式制动盘内部通道对流换热研究综述

doi: 10.19818/j.cnki.1671-1637.2022.02.002
基金项目: 

国家自然科学基金项目 51675494

北京建筑大学金字塔人才培养工程 JDJQ20200308

详细信息
    作者简介:

    李杰(1977-),男,黑龙江齐齐哈尔人,北京建筑大学教授,工学博士,从事车辆传动技术、高能摩擦与制动、智能仿生结构设计研究

  • 中图分类号: U270.11

Review on convective heat transfer in internal channel of ventilated brake disc of vehicle

Funds: 

National Natural Science Foundation of China 51675494

Pyramid Talent Training Project of Beijing University of Civil Engineering and Architecture JDJQ20200308

More Information
  • 摘要: 总结了通风式制动盘内部通道对流换热的研究成果,从内部通道的质量流量、对流换热系数和有效散热表面积三方面,分析了不同结构设计对制动盘内部通道换热的影响;从解析法、数值分析法和试验测试法三方面,综述了国内外在对流换热分析和检测方法的研究概况。研究结果表明:在径向叶片制动盘通道内,主要存在2种流动方式,由紧邻叶片吸力侧气流分离引起的回流和在径向通道内部旋转的二次流,抑制回流区的形成可以提高泵送空气质量流量,使通道内的温度分布更加均匀,二次流将促进通道间的空气混合流动和湍流的发展,加强局部剪切应力,改善制动盘散热性能;综合应用射流冲击强化方式(多束流、旋流和多方向射流等)、高孔隙率和类柱状结构优化设计也能够改变流体在通道中的流动状态,这些措施都会使得通道内流体扰动增大,热边界层变薄,壁面附近的速度梯度增大,有效提高了制动盘的对流换热系数,增强了散热能力;采用解析法和数值分析法得到的结果具有很强的理论参考价值,而采用试验测试法所获得的结果更加接近制动盘实际内部温度和气体流速的变化,因此,若能将三者无缝结合,实现优势互补,则最具有科学研究价值;在对高速车辆制动盘结构进行优化设计时,为了获得最大的散热效率,往往忽略了通道内摩擦压降和流动阻力,因此,如何平衡散热与摩擦压降、流动阻力之间的关系,还需进一步深入探索与研究。

     

  • 图  1  通风式制动盘结构

    Figure  1.  Structures of ventilated brake disc

    图  2  流入角β的形成

    Figure  2.  Formation of inflow angle β

    图  3  叶片数量对空气质量流量和传热速率的影响

    Figure  3.  Effects of number of blades on air mass flow and heat transfer rate

    图  4  空气质量流量随转速的变化

    Figure  4.  Variation of air mass flow rate with rotational speed

    图  5  不同出口角度的制动盘

    Figure  5.  Brake discs with different exit angles

    图  6  仿真结果与经验预测结果比较

    Figure  6.  Comparison between simulation results and empirical prediction results

    图  7  制动盘摩擦表面上热电偶的位置

    Figure  7.  Positions of thermocouples on friction surface of brake disc

    图  8  热电偶测试系统

    Figure  8.  Thermocouple test system

    图  9  使用烟雾发生器的流动模式

    Figure  9.  Flow pattern using smoke generator

    图  10  PIV装置

    Figure  10.  PIV device

    图  11  PIV系统的试验台

    Figure  11.  PIV testbed

    图  12  热线风速仪结构

    Figure  12.  Structure of hot wire anemometer

    表  1  不同类型制动盘通过的质量流量

    Table  1.   Mass flows through different types of brake discs

    制动盘类型 直径向
    叶片
    向后弯曲
    叶片
    径向弯曲
    叶片
    向前弯曲
    叶片
    质量流量/(g·s-1) 39 37 40 41
    下载: 导出CSV

    表  2  制动盘对流传热系数方程

    Table  2.   Equations of convective heat transfer coefficient of brake disc

    文献 研究对象 关联式 参数范围
    [1] 制动系统 NuRe0.8 Re≤1.0×106
    [7] 通风气流 hch=h0+C1ur0.8
    [27] 通风气流 Nu=0.045Re0.8(D/2)0.2[1+6.6(D/2)0.8]
    [31] 叶片角度 Nu=0.533 9(ωD2/4v)0.509 4 30°倾斜叶片层流
    Nu=0.013 9(ωD2/4v)0.817 2 30°倾斜叶片湍流
    [50] X晶格 Nu=CRen C=0.092 7,n=0.0580 6,SRV
    C=0.461 9,n=0.652 6,X晶格
    [62] 内侧和外侧 Nu=0.043 6Re0.8 Re=UD/v
    [63] 空气横流 $N u=0.06\left[2 R e^{2}+4\left({Re}_{\mathrm{t}} \frac{R_{\mathrm{R}}}{R_{0}}\right)^{2}\right]^{1 / 3}$ Rew=ωR02/v
    Ret=UsR0/v
    [64] 奈升华传热传质 Nu=0.667Rew0.814
    Nur=0.709Nu(r/R0)-0.38
    Rew=ωR02/v
    [65] 奈升华传热传质 Nu=0.667Rew0.793 1ra-0.220 8Pr0.4 2 753≤Rew≤24 155
    0.684≤ra≤0.909
    [66] 叶片 h=1.86(RePr)1/3(dh/l)0.33(λ/dh) Re≤1.0×104
    Nu=0.023[1+(dh/l)0.67]Re0.8Pr0.33 Re>1.0×104
    [67] 旋转圆盘 Nu=0.335Re0.5 1.0×105Re≤2.0×105
    [68] 光滑对流 Nu=0.024[1+(dh/l)2/3]Re0.786Pr0.45 Re>2 350
    [69] 径向叶片 Nu=A+BRe0.8Pr0.4
    注:Ret为横流雷诺数;RR为滚动半径;Nur为局部努塞尔数;Us为横流速度;v为运动黏度;r为小轮半径;Cn为经验常数;其他变量在文中有解释。
    下载: 导出CSV

    表  3  制动盘数值分析方法

    Table  3.   Numerical analysis methods of brake disc

    文献 湍流模型 数值仿真条件 研究类型 研究目的
    [1] RNG k-ε 环境温度为26 ℃,列车最高运行速度为160 km·h-1 制动盘和垫片 描述制动盘内部温度分布
    [4] RNG k-ε 环境温度为20 ℃,制动盘表面温度为500 ℃,列车行驶速度为140 km·h-1 整车制动系统 制动系统的总传热计算
    [5] k-ε 环境温度为25℃,车辆行驶速度为300 km·h-1 径向叶片 温度和热应力分析
    [6] k-ε 环境温度为30 ℃,考虑辐射额,发射率为0.55,漫反射率为1 径向叶片 分析通过制动盘的气流,计算传热系数
    [15] SST k-ω 环境温度为300 K,压力为1 atm,制动盘表面温度为900 K 径向叶片和立柱类 分析不同速度下通道的换热系数和换热速率
    [28] k-ε 环境温度为300 K,制动盘表面温度为800 K,制动盘转速为60 rad·s-1 长短叶片 优化叶片形状
    [29] Standard k-ε 制动盘转速为44 rad·s-1,制动盘表面温度为900 K 径向叶片 计算传热速率
    [45] SST k-ω 无量纲壁面距离小于1,进口角度为37.5° 叶片凸起 分析了不同形状凸起对压气机流场细节及损失特性的影响
    γ-θ
    [46] SST k-ω 环境温度为300 K,无量纲壁面距离小于2,6 100<Re<13 800 凸肋通道 分析导流装置对传热和流动性能的影响
    [47] k-ε 环境温度为20 ℃,制动盘表面温度为100 ℃,2.8×104Rew≤2.2×105 径向叶片 分析经过径向叶片的气流和对流冷却
    [48] Standard k-ε 制动盘表面温度为800 K,制动盘转速范围为500~2 000 r·min-1 立柱 分析几何形状对内部流场特性影响
    [53] k-ε 环境温度为20 ℃,制动盘表面温度为150 ℃, Re>2.0×105 径向叶片 获得平均对流传热系数
    [74] SST k-ω 无量纲壁面距离小于1,空气流速范围为2.7~12.6 m·s-1 X晶格 研究X晶格对流传热
    [81] Standard k-ε 制动盘表面温度为600 K 径向叶片 找到合适的湍流模型预测制动盘内部和周围的流场温度
    SST k-ω
    Spalart-Allmaras
    [82] RNG k-ε 制动盘表面温度为600 ℃ 旋转车轮和通风制动盘 对整车瞬态温度场和流场进行研究
    [83] Standard k-ε 制动盘转速为750 r·min-1 立柱和钻孔 预测排气的质量流量和内部通道传热系数
    下载: 导出CSV
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