CN107958116A - A kind of elevator door-motor driver optimizing thermal solution method based on particle cluster algorithm - Google Patents
A kind of elevator door-motor driver optimizing thermal solution method based on particle cluster algorithm Download PDFInfo
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Abstract
本发明公开了一种基于粒子群算法的电梯门机驱动器散热优化方法，其特征在于，利用电梯门机驱动器散热器的热阻模型，通过电梯门机驱动器散热器的自身热阻R2和电梯门机驱动器散热器与空气的传热热阻R3，计算出总热阻R；以及电梯门机驱动器散热器的工作风量，应用粒子群算法求得当总热阻和电梯门机驱动器散热器的工作风量满足条件时温度控制在指定范围内的散热器参数最优值，得到散热器最小体积；降低散热器成本的同时达到最优的散热效果。
The invention discloses a method for optimizing the heat dissipation of an elevator door machine driver based on a particle swarm algorithm, which is characterized in that, using the thermal resistance model of the elevator door machine Calculate the total thermal resistance R from the heat transfer resistance R3 between the radiator of the elevator door machine and the air; and the working air volume of the radiator of the elevator door machine driver, and apply the particle swarm algorithm to obtain the total thermal resistance and the working air volume of the radiator of the elevator door machine driver When the conditions are met, the temperature is controlled within the optimal value of the radiator parameters within the specified range, and the minimum volume of the radiator is obtained; while reducing the cost of the radiator, the optimal heat dissipation effect is achieved.
Description
技术领域technical field
本发明涉及电梯门机驱动器的技术领域，尤其涉及一种基于粒子群算法的电梯门机驱动器散热优化方法。The invention relates to the technical field of elevator door machine drivers, in particular to a particle swarm algorithm-based heat dissipation optimization method for elevator door machine drivers.
背景技术Background technique
电梯门机是由专用驱动板提供动力，其频繁工作引起的发热，需要设计散热器进行降温，其构建所用电子元件的性能与温度息息相关。随着温度的上升，电子元件的失效率增加，温度每上升10℃，电子器件的可靠性就下降一半。据相关文献统计，电子设备的失效有55％是温度超过规定值所引起的。目前电子产品集成化程度越来越高，散热难度也随着增大。伺服驱动系统作为执行部件，在现代化生产中得到了越来越广泛的应用，为了确保系统运行的可靠性，有必要对驱动器的散热器进行优化设计。The elevator door operator is powered by a special drive board. The heat generated by its frequent work requires the design of a radiator to cool it down. The performance of the electronic components used in its construction is closely related to the temperature. As the temperature rises, the failure rate of electronic components increases, and the reliability of electronic devices decreases by half for every 10°C increase in temperature. According to relevant literature statistics, 55% of the failure of electronic equipment is caused by the temperature exceeding the specified value. At present, the degree of integration of electronic products is getting higher and higher, and the difficulty of heat dissipation is also increasing. Servo drive system, as an executive component, has been more and more widely used in modern production. In order to ensure the reliability of the system operation, it is necessary to optimize the design of the radiator of the drive.
国内外研究学者针对功率器件散热系统的设计做了大量的工作。李玉宝，王建萍等人对矩形肋片散热器在不同结构参数下的模型进行了自然对流散热计算，通过对比分析不同模型的温度和热阻计算结果，探讨了散热器基板参数和肋片参数对其散热性能的影响；李争等人基于有限体积法，对电驱动用功率逆变器进行三维温度场分析，对比了改变散热器材料，加风扇以及将2者结合的散热效果，对逆变器的散热系统进行了优化设计；董梁，徐伟强，李倩倩等人针对电子电气设备散热和均温的需求，提出了一种新型结构形式的异形整体热管散热器：平板热管形式的蒸发段与具有高肋化比翅片的冷凝铜管集成；郭健忠等人运用ATC方法对某型汽车管带式百叶窗散热器进行性能分析及翅片结构优化，建立某型汽车散热器单周期翅片组模型并对其进行不同风速工况下的三维模拟计算并通过实验验证了可行性。申有传以某公司生产的微型纯电动汽车控制器为研究对象，主要从热力学的角度设计散热器，并从结构上对散热器进行优化，最后设计出符合该控制器散热需求的散热器。Domestic and foreign researchers have done a lot of work on the design of power device cooling system. Li Yubao, Wang Jianping and others calculated the natural convection heat dissipation of the models of rectangular fin radiators under different structural parameters. By comparing and analyzing the calculation results of temperature and thermal resistance of different models, they discussed the relationship between the parameters of the substrate of the radiator and the parameters of the fins. The influence of heat dissipation performance; based on the finite volume method, Li Zheng et al. analyzed the three-dimensional temperature field of the power inverter for electric drive, and compared the heat dissipation effects of changing the heat sink material, adding a fan, and combining the two. The heat dissipation system was optimized and designed; Dong Liang, Xu Weiqiang, Li Qianqian and others proposed a new structural form of special-shaped integral heat pipe radiator for the heat dissipation and uniform temperature requirements of electronic and electrical equipment: the evaporation section in the form of a flat heat pipe and the high The integration of condensing copper tubes with rib ratio fins; Guo Jianzhong et al. used the ATC method to analyze the performance and optimize the fin structure of a certain type of automotive tube-belt louver radiator, and established a single-period fin group model for a certain type of automotive radiator. It performs three-dimensional simulation calculations under different wind speed conditions and verifies the feasibility through experiments. Shen Youchuan took the controller of a miniature pure electric vehicle produced by a certain company as the research object, mainly designed the radiator from the perspective of thermodynamics, optimized the radiator from the structure, and finally designed a radiator that meets the cooling requirements of the controller.
发明内容Contents of the invention
基于上述现象，本发明提供一种基于粒子群算法的电梯门机驱动器散热优化方法，应用粒子群算法求得当总热阻和电梯门机驱动器散热器的工作风量满足条件时温度控制在指定范围内的散热器参数最优值，得到散热器最小体积；降低散热器成本的同时达到最优的散热效果。Based on the above phenomenon, the present invention provides a method for optimizing the heat dissipation of the elevator door machine driver based on the particle swarm optimization algorithm. The particle swarm algorithm is used to obtain the temperature control within the specified range when the total thermal resistance and the working air volume of the elevator door machine driver radiator meet the conditions. The optimal value of the radiator parameters is obtained to obtain the minimum volume of the radiator; while reducing the cost of the radiator, the optimal heat dissipation effect is achieved.
利用电梯门机驱动器散热器的热阻模型，通过电梯门机驱动器散热器的自身热阻R2和电梯门机驱动器散热器与空气的传热热阻R3，计算出总热阻R；以及电梯门机驱动器散热器的工作风量，应用粒子群算法求得当总热阻和电梯门机驱动器散热器的工作风量满足条件时温度控制在指定范围内的散热器最小体积；Using the thermal resistance model of the radiator of the elevator door machine driver, the total thermal resistance R is calculated through the self-thermal resistance R2 of the radiator of the elevator door machine driver and the heat transfer thermal resistance R3 between the radiator of the elevator door machine driver and the air; and the elevator door The working air volume of the radiator of the elevator door machine driver, the particle swarm algorithm is used to obtain the minimum volume of the radiator whose temperature is controlled within the specified range when the total thermal resistance and the working air volume of the radiator of the elevator door machine driver meet the conditions;
粒子群算法寻优步骤如下：The optimization steps of the particle swarm optimization algorithm are as follows:
S1：开始；S1: start;
S2：输入参数；粒子群规模设为10，迭代次数设定100，肋片数量的取值范围设为(20，60)，肋片厚度范围设为(0.001，0.01)，散热器的长度范围设为(0.062，0.172)；S2: Input parameters; the particle swarm size is set to 10, the number of iterations is set to 100, the value range of the number of fins is set to (20, 60), the range of fin thickness is set to (0.001, 0.01), and the length range of the radiator Set to (0.062, 0.172);
S3：通过S2计算出总热阻值R和临界散热器的工作风量；S3: Calculate the total thermal resistance R and the working air volume of the critical radiator through S2;
S4：初始化粒子以及粒子速度；S4: Initialize particles and particle speed;
S5：检查散热器的工作风量和总热阻值此，散热器的工作风量过小或是总热阻值R过大，执行S4，重新初始化；S5: Check the working air volume and total thermal resistance of the radiator. If the working air volume of the radiator is too small or the total thermal resistance R is too large, execute S4 and re-initialize;
S6：适应值计算；S6: fitness value calculation;
S7：粒子速度更新；S7: Particle speed update;
S8：粒子位置更新；S8: Particle position update;
S9：检查散热器的工作风量和总热阻值R，散热器的工作风量过小或是总热阻值R过大，执行S7，重新对粒子速度和粒子位置进行更新；S9: Check the working air volume and total thermal resistance R of the radiator. If the working air volume of the radiator is too small or the total thermal resistance R is too large, execute S7 to re-update the particle velocity and particle position;
S10：散热器的工作风量和总热阻值R在正常范围内，进行适应值计算；S10: The working air volume and total thermal resistance R of the radiator are within the normal range, and the adaptive value is calculated;
S11：当前值是否小于局部最优值，如果是进入到S12；如果否，进入到S13；S12：局部最优值更新；S11: Whether the current value is less than the local optimal value, if yes, go to S12; if not, go to S13; S12: Update the local optimal value;
S13：当前值是否小于合局最优值，如果是，进入S14；如果否，进入S15；S13: Whether the current value is less than the optimal value of the game, if yes, go to S14; if not, go to S15;
S14：全局最优值更新；S14: update the global optimal value;
S15：是否到迭代闪数或收敛；如果是，进入S16；S15: whether it has reached iteration speed or convergence; if yes, go to S16;
S16：输出全局最优值；S16: output the global optimal value;
最终得到散热器结构参数的最优适应解，得到最优散热器结构；Finally, the optimal adaptive solution of the structural parameters of the radiator is obtained, and the optimal radiator structure is obtained;
其中，R＝R2+R3 (1)；Wherein, R=R2+R3 (1);
电梯门机驱动器散热器的自身热阻：散热器由n块一端相连的金属平板组成，相连一端组成了基板，金属平板的长宽高分别为L，b，l；电梯门机驱动器散热器金属平板内没有热源，且热流是一维和稳定的，由傅里叶导热方程可得，传导的热量：The thermal resistance of the radiator of the elevator door machine driver: the radiator is composed of n metal plates connected at one end, and the connected end forms the substrate. The length, width and height of the metal plates are L, b, and l respectively; the metal plate of the elevator door machine driver There is no heat source in the plate, and the heat flow is one-dimensional and stable. From the Fourier heat conduction equation, the heat conduction is:
(2)式中：P为传导热量(KCalth/h)，Ks为导热系数(KCalth/h.m.℃)，A为散热器的传热表面积(m2)，T-t为2端面温差(℃)，l为金属平板的高(m)，可得：(2) In the formula: P is the heat conduction (KCalth/h), K s is the thermal conductivity (KCalth/hm℃), A is the heat transfer surface area of the radiator (m 2 ), Tt is the temperature difference between the two ends (℃), l is the height (m) of the metal plate, which can be obtained as follows:
单位换算后可得： After unit conversion, we can get:
Ks为金属平板的导热系数；Ks is the thermal conductivity of the metal plate;
其中，电梯门机驱动器散热器与空气的传热热阻，根据层流和湍流的不同情况进行分析：当Among them, the heat transfer resistance between the radiator of the elevator door machine driver and the air is analyzed according to the different conditions of laminar flow and turbulent flow: when
(1)风冷冷却时，设功率器件工作在一个大气压、相对湿度不超过90％的环境中；(1) When air-cooled, set the power device to work in an environment with an atmospheric pressure and a relative humidity not exceeding 90%;
(2)空气的流速远小于声速，如小于7m/s；(2) The velocity of the air is much lower than the velocity of sound, such as less than 7m/s;
(3)空气的流动处于稳定状态；(3) The flow of air is in a steady state;
(4)散热器工作的环境温度在：-25℃到250℃之间；(4) The working ambient temperature of the radiator is between -25°C and 250°C;
金属平板边界层随着与风机距离增大，雷诺数不断的增大，当超过了雷诺数临界值，即超过了临界距离，层流向湍流过渡，临界距离可由式(5)所得；As the distance between the metal plate boundary layer and the fan increases, the Reynolds number continues to increase. When the critical value of the Reynolds number is exceeded, that is, the critical distance is exceeded, and the laminar flow transitions to the turbulent flow. The critical distance can be obtained by formula (5);
式中：Rec为临界雷诺数，v为空气粘度(m2/s)，us为空气流速(m/s)。In the formula: Re c is critical Reynolds number, v is air viscosity (m 2 /s), u s is air velocity (m/s).
当L＜XC时，边界层处于层流状态，此时的局部努塞尔数为：When L<X C , the boundary layer is in a laminar flow state, and the local Nusselt number at this time is:
Nux＝0.332Rex 1/2Pr1/3＝hx*x/λ (6)Nux＝0.332Re x 1/2 Pr 1/3 ＝h x *x/λ (6)
式中：Rex为x处的雷诺数；Pr为空气的普朗特数，Pr等于空气粘度系数与导热系数之间的比值，无量纲，且与x无关；hx为x处的空气对流传热系数；λ为空气的导热系数。In the formula: Re x is the Reynolds number at x; Pr is the Prandtl number of the air, and Pr is equal to the ratio between the air viscosity coefficient and the thermal conductivity, which is dimensionless and has nothing to do with x; h x is the air pair at x Heat transfer coefficient; λ is the thermal conductivity of air.
对局部努塞尔数在金属平板长度L内积分，再乘以L，可得到平均努塞尔数，如式(7)所示，Integrating the local Nusselt number within the length L of the metal plate, and then multiplying it by L, the average Nusselt number can be obtained, as shown in formula (7),
式中：其它参数同上，In the formula: The other parameters are the same as above,
由式(6)和式(7)可以推出空气对流平均传热系数，如式(8)所示。The average heat transfer coefficient of air convection can be deduced from formula (6) and formula (7), as shown in formula (8).
同上可推出，当L＞XC时，边界层处于湍流的状态，此时的局部努塞尔数为：As above, it can be deduced that when L>X C , the boundary layer is in a turbulent state, and the local Nusselt number at this time is:
Nux＝0.0296Rex 4/5Pr1/3 (9)Nux＝0.0296 Re x 4/5 Pr 1/3 (9)
金属平板边界的临界雷诺数一般取为5×105，可得出L超过临界长度后的平均努塞尔数和平均传热系数分别如式(8)和式(9)所示。The critical Reynolds number of the metal plate boundary is generally taken as 5×10 5 , and the average Nusselt number and average heat transfer coefficient after L exceeds the critical length can be obtained as shown in formula (8) and formula (9), respectively.
Num＝(0.037Re4/5-871)Pr1/3 (10)Num＝(0.037Re 4/5 -871)Pr 1/3 (10)
A为散热器的传热表面积；A is the heat transfer surface area of the radiator;
其中，电梯门机驱动器散热器的工作风量，可以由散热器中风扇的特性曲线和风道的风阻特性曲线的交点求得，风扇的特性曲线由散热器生产厂家提供，风道的特性曲线可由下列公式(14)求得，Among them, the working air volume of the radiator of the elevator door machine driver can be obtained from the intersection point of the characteristic curve of the fan in the radiator and the wind resistance characteristic curve of the air duct. The characteristic curve of the fan is provided by the radiator manufacturer, and the characteristic curve of the air duct can be obtained from the following Formula (14) obtains,
式中：Rs为风力半径(m)；Rf为风道阻力(Pa)；δ为摩擦系数，取0.022；ρ为空气密度(kg/m3)；L为风道长度(m)；u为风速(m/s)；In the formula: R s is the wind radius (m); Rf is the air duct resistance (Pa); δ is the friction coefficient, which is 0.022; ρ is the air density (kg/m 3 ); L is the air duct length (m); u is the wind speed (m/s);
最终得到n，L，l，b的最优适应解；Finally, the optimal adaptive solution of n, L, l, b is obtained;
通过V＝nLlb (15)By V=nLlb (15)
得到最优散热器结构。Get the optimal radiator structure.
本发明的有益效果：Beneficial effects of the present invention:
分析散热器的散热过程，建立了散热器热阻的推导公式，并计算散热器中风扇的工作风量和风阻，应用粒子群算法求得当总热阻和工作风量等满足条件时的散热器最小体积，以达到减小生产成本的目的；并通过有限元分析软件Icepak，对优化前后的散热效果进行了对比，验证了方法的可行性和有效性。Analyze the heat dissipation process of the radiator, establish the derivation formula of the thermal resistance of the radiator, and calculate the working air volume and wind resistance of the fan in the radiator, and apply the particle swarm algorithm to obtain the minimum volume of the radiator when the total thermal resistance and the working air volume meet the conditions , in order to achieve the purpose of reducing the production cost; and through the finite element analysis software Icepak, the heat dissipation effect before and after optimization was compared, and the feasibility and effectiveness of the method were verified.
附图说明Description of drawings
图1是本发明中粒子群算法的寻优流程图；Fig. 1 is the optimization flowchart of particle swarm algorithm among the present invention;
图2是本发明中散热器体积优化曲线图；Fig. 2 is a curve diagram of radiator volume optimization in the present invention;
图3是本发明中散热器结构参数优化曲线图；Fig. 3 is a curve diagram of radiator structure parameter optimization among the present invention;
图4是本发明中散热器风扇工作风量工作点；Fig. 4 is the operating point of radiator fan working air volume in the present invention;
图5是本发明中优化散热器温度分布图；Fig. 5 is the optimized radiator temperature distribution figure among the present invention;
图6是本发明中散热器的结构图。Fig. 6 is a structural diagram of the radiator in the present invention.
具体实施方式Detailed ways
以下详细描述本发明的技术方案。本发明实施例仅供说明具体结构，该结构的规模不受实施例的限制。The technical solution of the present invention is described in detail below. The embodiment of the present invention is only for illustrating a specific structure, and the scale of the structure is not limited by the embodiment.
电梯门机所用永磁同步电机伺服驱动器(或无刷直流电动机)运行过程中的损耗绝大部分来自于整流和逆变电路，二极管和ICBT模块作为主要的功率器件，热量通过它们的管芯传到管壳，再从管壳传递给散热器，散热器通过对流和辐射的方式将热量传递到环境介质中，各部分热阻分别表示为R1，R2和R3。强迫风冷的效率高，成本低在散热器的设计中被广泛的应用。Most of the loss during the operation of the permanent magnet synchronous motor servo driver (or brushless DC motor) used in the elevator door machine comes from the rectification and inverter circuits. Diodes and ICBT modules are the main power devices, and the heat is transmitted through their dies. to the tube shell, and then from the tube shell to the radiator. The radiator transfers heat to the ambient medium through convection and radiation. The thermal resistance of each part is represented by R1, R2 and R3. The high efficiency and low cost of forced air cooling are widely used in the design of radiators.
从管壳到空气之间的散热器总热阻，表示为：The total heat sink thermal resistance from case to air, expressed as:
R＝R2+R3 (1)R＝R2+R3 (1)
其中，R2为散热器自身热阻，R3为散热器与空气的传热热阻；Among them, R2 is the thermal resistance of the radiator itself, and R3 is the heat transfer thermal resistance between the radiator and the air;
粒子群算法寻优步骤如下如图1所示：The optimization steps of the particle swarm optimization algorithm are shown in Figure 1 as follows:
S1：开始；S1: start;
S2：输入参数；粒子群规模设为10，迭代次数设定100，金属平板数量的取值范围设为(20，60)，金属平板厚度范围设为(0.001，0.01)，散热器的长度范围设为(0.062，0.172)；S2: Input parameters; the size of the particle swarm is set to 10, the number of iterations is set to 100, the value range of the number of metal plates is set to (20, 60), the thickness range of the metal plate is set to (0.001, 0.01), and the length range of the radiator Set to (0.062, 0.172);
S3：通过S2计算出总热阻值R和临界散热器的工作风量；S3: Calculate the total thermal resistance R and the working air volume of the critical radiator through S2;
S4：初始化粒子以及粒子速度；S4: Initialize particles and particle speed;
S5：检查散热器的工作风量和总热阻值此，散热器的工作风量过小或是总热阻值R过大，执行S4，重新初始化；S5: Check the working air volume and total thermal resistance of the radiator. If the working air volume of the radiator is too small or the total thermal resistance R is too large, execute S4 and re-initialize;
S6：适应值计算；S6: fitness value calculation;
S7：粒子速度更新；S7: Particle speed update;
S8：粒子位置更新；S8: Particle position update;
S9：检查散热器的工作风量和总热阻值R，散热器的工作风量过小或是总热阻值R过大，执行S7，重新对粒子速度和粒子位置进行更新；S9: Check the working air volume and total thermal resistance R of the radiator. If the working air volume of the radiator is too small or the total thermal resistance R is too large, execute S7 to re-update the particle velocity and particle position;
S10：散热器的工作风量和总热阻值R在正常范围内，进行适应值计算；S10: The working air volume and total thermal resistance R of the radiator are within the normal range, and the adaptive value is calculated;
S11：当前值是否小于局部最优值，如果是进入到S12；如果否，进入到S13；S11: Whether the current value is less than the local optimal value, if yes, go to S12; if not, go to S13;
S12：局部最优值更新；S12: Local optimum value update;
S13：当前值是否小于合局最优值，如果是，进入S14；如果否，进入S15；S13: Whether the current value is less than the optimal value of the game, if yes, go to S14; if not, go to S15;
S14：全局最优值更新；S14: update the global optimal value;
S15：是否到迭代闪数或收敛；如果是，进入S16；S15: whether it has reached iteration speed or convergence; if yes, go to S16;
S16：输出全局最优值；S16: output the global optimal value;
最终得到散热器结构参数的最优适应解，得到最优散热器结构。Finally, the optimal adaptive solution of the structural parameters of the radiator is obtained, and the optimal radiator structure is obtained.
其中，电梯门机驱动器散热器的自身热阻：散热器由n块一端相连的金属平板1组成，相连一端组成了基板2，金属平板的长宽高分别为L，b，l，如图6所示；电梯门机驱动器散热器金属平板内没有热源，且热流是一维和稳定的，由傅里叶导热方程可得，传导的热量：Among them, the thermal resistance of the radiator of the elevator door machine driver: the radiator is composed of n metal plates 1 connected at one end, and the connected ends form the substrate 2. The length, width and height of the metal plates are L, b, and l, respectively, as shown in Figure 6 As shown; there is no heat source in the metal plate of the radiator of the elevator door machine driver, and the heat flow is one-dimensional and stable. It can be obtained from the Fourier heat conduction equation, and the heat conduction is:
(2)式中：P为传导热量(KCalth/h)，Ks为导热系数(KCalth/h.m.℃)，A为散热器的传热表面积(m2)，T-t为2端面温差(℃)，l为金属平板的高(m)，可得：(2) In the formula: P is the heat conduction (KCalth/h), K s is the thermal conductivity (KCalth/hm℃), A is the heat transfer surface area of the radiator (m 2 ), Tt is the temperature difference between the two ends (℃), l is the height (m) of the metal plate, which can be obtained as follows:
单位换算后可得： After unit conversion, we can get:
Ks为金属平板的导热系数；Ks is the thermal conductivity of the metal plate;
其中，电梯门机驱动器散热器与空气的传热热阻，根据层流和湍流的不同情况进行分析：当Among them, the heat transfer resistance between the radiator of the elevator door machine driver and the air is analyzed according to the different conditions of laminar flow and turbulent flow: when
(1)风冷冷却时，设功率器件工作在一个大气压、相对湿度不超过90％的环境中；(1) When air-cooled, set the power device to work in an environment with an atmospheric pressure and a relative humidity not exceeding 90%;
(2)空气的流速远小于声速，如小于7m/s；(2) The velocity of the air is much lower than the velocity of sound, such as less than 7m/s;
(3)空气的流动处于稳定状态；(3) The flow of air is in a steady state;
(4)散热器工作的环境温度在：-25℃到250℃之间；(4) The working ambient temperature of the radiator is between -25°C and 250°C;
金属平板边界层随着与风机距离增大，雷诺数不断的增大，当超过了雷诺数临界值，即超过了临界距离，层流向湍流过渡，临界距离可由式(5)所得；As the distance between the metal plate boundary layer and the fan increases, the Reynolds number continues to increase. When the critical value of the Reynolds number is exceeded, that is, the critical distance is exceeded, and the laminar flow transitions to the turbulent flow. The critical distance can be obtained by formula (5);
式中：Rec为临界雷诺数，v为空气粘度(m2/s)，us为空气流速(m/s)。In the formula: Re c is critical Reynolds number, v is air viscosity (m 2 /s), u s is air velocity (m/s).
当L＜XC时，边界层处于层流状态，此时的局部努塞尔数为：When L<X C , the boundary layer is in a laminar flow state, and the local Nusselt number at this time is:
Nux＝0.332Rex 1/2Pr1/3＝hx*x/λ (6)Nux＝0.332Re x 1/2 Pr 1/3 ＝h x *x/λ (6)
式中：Rex为x处的雷诺数；Pr为空气的普朗特数，Pr等于空气粘度系数与导热系数之间的比值，无量纲，且与x无关；hx为x处的空气对流传热系数；λ为空气的导热系数。In the formula: Re x is the Reynolds number at x; Pr is the Prandtl number of the air, and Pr is equal to the ratio between the air viscosity coefficient and the thermal conductivity, which is dimensionless and has nothing to do with x; h x is the air pair at x Heat transfer coefficient; λ is the thermal conductivity of air.
对局部努塞尔数在金属平板长度L内积分，再乘以L，可得到平均努塞尔数，如式(7)所示，Integrating the local Nusselt number within the length L of the metal plate, and then multiplying it by L, the average Nusselt number can be obtained, as shown in formula (7),
式中：其它参数同上，In the formula: The other parameters are the same as above,
由式(6)和式(7)可以推出空气对流平均传热系数，如式(8)所示。The average heat transfer coefficient of air convection can be deduced from formula (6) and formula (7), as shown in formula (8).
同上可推出，当L＞XC时，边界层处于湍流的状态，此时的局部努塞尔数为：As above, it can be deduced that when L>X C , the boundary layer is in a turbulent state, and the local Nusselt number at this time is:
Nux＝0.0296Rex 4/5Pr1/3 (9)Nux＝0.0296 Re x 4/5 Pr 1/3 (9)
金属平板边界的临界雷诺数一般取为5×105，可得出L超过临界长度后的平均努塞尔数和平均传热系数分别如式(8)和式(9)所示。The critical Reynolds number of the metal plate boundary is generally taken as 5×10 5 , and the average Nusselt number and average heat transfer coefficient after L exceeds the critical length can be obtained as shown in formula (8) and formula (9), respectively.
Num＝(0.037Re4/5-871)Pr1/3 (10)Num＝(0.037Re 4/5 -871)Pr 1/3 (10)
A为散热器的传热表面积；A is the heat transfer surface area of the radiator;
其中，电梯门机驱动器散热器的工作风量，可以由散热器中风扇的特性曲线和风道的风阻特性曲线的交点求得，风扇的特性曲线由散热器生产厂家提供，风道的特性曲线可由下列公式(14)求得，Among them, the working air volume of the radiator of the elevator door machine driver can be obtained from the intersection point of the characteristic curve of the fan in the radiator and the wind resistance characteristic curve of the air duct. The characteristic curve of the fan is provided by the radiator manufacturer, and the characteristic curve of the air duct can be obtained from the following Formula (14) obtains,
式中：Rs为风力半径(m)；Rf为风道阻力(Pa)；δ为摩擦系数，取0.022；ρ为空气密度(kg/m3)；L为风道长度(m)；u为风速(m/s)；In the formula: R s is the wind radius (m); Rf is the air duct resistance (Pa); δ is the friction coefficient, which is 0.022; ρ is the air density (kg/m 3 ); L is the air duct length (m); u is the wind speed (m/s);
最终得到n，L，l，b的最优适应解；Finally, the optimal adaptive solution of n, L, l, b is obtained;
通过V＝nLlb (15)By V=nLlb (15)
得到最优散热器结构。Get the optimal radiator structure.
以一个驱动器的散热器为例，散热部分内部空间尺寸为277mm×196mm×89mm，采用2个型号Nidec[D08A-24TS2]的风扇进行强迫风冷，风扇尺寸为80mm×80mm，最大风量为1.55m3/min，最大风压为70.5N/m2。散热器采用了铝质肋片式，外形尺寸为172mm×170mm×79mm，基板厚度为12mm，金属平板厚为1mm，片数为32。功率模块发热量为375W。散热器的体积V为4.348×10-4m3。当散热器在25℃的环境中运行，将模型导入ICEPAK进行有限元分析，稳定后，最高温度达到了67℃，散热器表面温度在55℃左右。以该驱动器的散热器为对象进行结构参数优化，为了充分发挥风扇的作用我们将散热器外形尺寸的宽跟高依旧取为170mm和79mm。将金属平板数量，金属平板厚度，散热器的长进行优化。便于比较优化效果，将目标温度设置为75℃，环境温度设为25℃。粒子群规模设为10，迭代次数设定100，金属平板数量的取值范围设为(20，60)，金属平板厚度范围设为(0.001，0.01)，散热器的长度范围设为(0.062，0.172)。运行程序，得出优化结果，如下图2和图3所示。当金属平板L取101.7mm，金属平板厚度取1.2mm，金属平板数量取为40时，体积为3.857×10-4m3，比原来的4.348×10-4m3，体积上减少了11.3％，即材料成本上也相应的减少了11.3％；通过绘制风扇特性曲线和风道特性曲线，得到了风扇的实际工作风量为1.509m3/min，工作风压为5.8N/m2，如图5所示，按照得到的优化参数，建立优化后的模型并导入Icepak，进行散热仿真，得到散热器的温度分布图，如图4和图5所示。Taking a drive radiator as an example, the internal space of the heat dissipation part is 277mm×196mm×89mm, and two models of Nidec[D08A-24TS2] fans are used for forced air cooling. The size of the fans is 80mm×80mm, and the maximum air volume is 1.55m 3 /min, the maximum wind pressure is 70.5N/m 2 . The radiator adopts the aluminum fin type, the overall size is 172mm×170mm×79mm, the thickness of the substrate is 12mm, the thickness of the metal plate is 1mm, and the number of pieces is 32. The heat generated by the power module is 375W. The volume V of the radiator is 4.348×10 -4 m 3 . When the radiator operates in an environment of 25°C, the model is imported into ICEPAK for finite element analysis. After stabilization, the maximum temperature reaches 67°C, and the surface temperature of the radiator is around 55°C. Taking the heat sink of the drive as the object to optimize the structural parameters, in order to give full play to the role of the fan, we still take the width and height of the heat sink as 170mm and 79mm. Optimize the number of metal plates, the thickness of the metal plates, and the length of the radiator. To facilitate the comparison of optimization effects, set the target temperature to 75°C and the ambient temperature to 25°C. The size of the particle swarm is set to 10, the number of iterations is set to 100, the value range of the number of metal plates is set to (20, 60), the thickness range of the metal plate is set to (0.001, 0.01), and the length range of the radiator is set to (0.062, 0.172). Run the program to get the optimization results, as shown in Figure 2 and Figure 3 below. When the metal plate L is 101.7mm, the thickness of the metal plate is 1.2mm, and the number of metal plates is 40, the volume is 3.857×10 -4 m 3 , which is 11.3% smaller than the original 4.348×10 -4 m 3 , that is, the material cost is also reduced by 11.3%; by drawing the fan characteristic curve and the air duct characteristic curve, the actual working air volume of the fan is 1.509m 3 /min, and the working air pressure is 5.8N/m 2 , as shown in Figure 5 As shown, according to the optimized parameters obtained, the optimized model is established and imported into Icepak for heat dissipation simulation, and the temperature distribution diagram of the radiator is obtained, as shown in Figure 4 and Figure 5.
将优化后参数带入热阻计算子程序得到的热阻为0.13013℃/W，2者的计算结果基本相同。参数优化后的散热效果有所减弱，温度上上升了5.5℃，但依旧在我们的预设的75℃以内，且成本上我们降低了11.3％。很好地达到了优化的目标。The thermal resistance obtained by bringing the optimized parameters into the thermal resistance calculation subroutine is 0.13013°C/W, and the calculation results of the two are basically the same. After parameter optimization, the heat dissipation effect has been weakened, and the temperature has risen by 5.5°C, but it is still within our preset 75°C, and we have reduced the cost by 11.3%. The goal of optimization is well achieved.
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