矿井回风中蕴含大量低温余热资源，若能有效回收利用，不仅可以用于井口防冻和矿区供暖，还能降低能源消耗和碳排放。但用于余热利用的板式换热器必须加装在主要通风机出风口，并由主要通风机来克服相应的通风阻力，这增加了主要通风机不稳定运行的因素。众所周知板式换热器具有较高的换热效率，但其阻力特性未知，这限制了板式换热器在矿井回风余热利用系统中的实际应用。为此本文对矿井板式换热器的阻力特性进行研究，这对保证风机加装余热利用换热器后的矿井通风系统的安全可靠性具有重要意义。

本文构建了基于板式换热器的回风余热利用系统，提出了板式换热器堆叠设计与风阻叠加计算方法，并得到了板式换热器实验件和标准件的风阻值。当板式换热器以串联方式堆叠时，总风阻为单个板式换热器风阻与堆叠数量的乘积；而以并联方式堆叠时，总风阻为单个板式换热器风阻除以堆叠数量的平方。对板式换热器实验件进行了变风量工况下的阻力测定实验，得到了板式换热器实验件的风阻为1956 Ns²/m⁸，并基于实验数据推导，得到了板式换热器标准件的风阻为33.04 Ns²/m⁸。将该参数与风阻叠加计算方法相结合可求得任意规模换热器组的风阻。

用CFD方法对实验件风阻值进行了模拟验证，并得到了板式换热器实验件的热回收效率。以板式换热器实验件为原型建模，通过模拟11组风量下的进出口静压差，得到了实验件的模拟风阻值为1901 Ns²/m⁸，与实验值的相对误差为2.83%。并利用该数值模型开展了板式换热器实验件的热回收效率模拟研究，模拟涵盖了1~3 m/s的风速范围以及15~25℃的冷热流体进口温差条件，明确了通过增加风速和冷热流体之间的温差，可以提升板式换热器的换热性能。

提出了两种白鹭煤矿回风余热利用方案，并评估了其可行性。两种方案中由标准件组合而成的板式换热器尺寸分别为2×4×9 m（方案一）和4×4×9 m（方案二），热回收效率分别为65.2%和69.3%。通过风阻叠加公式计算，得到了方案一和方案二的板式换热器风阻分别为0.0510 Ns²/m⁸和0.1020 Ns²/m⁸，对应风量为64.1 m³/s时的阻力分别为210 Pa和419 Pa。基于风机当前的工况点（64.1 m³/s，880 Pa），通风系统的总风阻为0.2142 Ns²/m⁸。方案一中风机的工况点将偏移至（59.5 m³/s，939.1 Pa），风量下降了4.6 m³/s，为恢复风量，需将风机叶片角度调至0°、运行频率调至39 Hz，风机新工况点为（64.7 m³/s，1111 Pa）。同理，方案二风机工况点将偏移至（55.7 m³/s，980.7 Pa），仍需通过将风机叶片角度调至0°、运行频率调至42 Hz的方法来恢复风量，风机新工况点为（65.4 m³/s，1354.1 Pa）。由于方案二有更高的热回收效率，因此选用方案二作为实施方案。综上，尽管安装板式换热器会导致矿井实际排风量减少，但这种不利影响可以通过利用风机冗余能力调节风机工况点来消除。

Mine return air contains a large amount of low-temperature waste heat resources, which can be effectively recycled and utilized not only for anti-freezing of the shaft and heating of the mine area, but also to reduce energy consumption and carbon emissions. However, the plate heat exchanger for waste heat utilization must be installed at the outlet of the main ventilator, and the main ventilator to overcome the corresponding ventilation resistance, which increases the unstable operation of the main ventilator. It is well known that plate heat exchanger has high heat transfer efficiency, but its resistance characteristics are unknown, which limits the practical application of plate heat exchanger in mine return air waste heat utilization system. For this reason, this paper studies the resistance characteristics of the plate heat exchanger in the mine, which is of great significance to ensure the safety and reliability of the mine ventilation system after the fan is retrofitted with the waste heat utilization heat exchanger.

In this paper, a return air waste heat utilization system based on plate heat exchangers is constructed, the stacking design and wind resistance stacking calculation method of plate heat exchangers are proposed, and the wind resistance values of experimental and standard parts of plate heat exchangers are obtained. When the plate heat exchangers are stacked in series, the total wind resistance is the product of the wind resistance of individual plate heat exchangers and the number of stacks, and when they are stacked in parallel, the total wind resistance is the wind resistance of individual plate heat exchangers divided by the square of the number of stacks. The resistance measurement experiment of the plate heat exchanger test piece under variable air volume conditions was carried out, and the wind resistance of the plate heat exchanger test piece was 1956 Ns²/m⁸. Based on the experimental data, the wind resistance of the plate heat exchanger standard part was 33.04 Ns²/m⁸. This parameter, combined with the method of calculation of wind resistance stacking, can be used to find out the wind resistance of heat exchanger groups of any size.

The CFD method was used to simulate and verify the wind resistance value of the experimental piece, and the heat recovery efficiency of the experimental piece of the plate heat exchanger was obtained. The plate heat exchanger test piece was modeled as a prototype. By simulating the static pressure difference between the inlet and outlet under 11 sets of air volume, the simulated wind resistance value of the test piece was 1901 Ns²/m⁸, and the relative error with the experimental value was 2.83%. The numerical model was also used to carry out a simulation study on the heat recovery efficiency of the experimental piece of plate heat exchanger, and the simulation covered the range of wind speed from 1 to 3 m/s and the temperature difference between the inlet and outlet of hot and cold fluids from 15 to 25°C. It was clarified that the heat exchange performance of the plate heat exchanger could be improved by increasing the wind speed and the temperature difference between hot and cold fluids.

Two scenarios for the utilization of return air waste heat from the White Heron Coal Mine are proposed and their feasibility is assessed. The sizes of plate heat exchangers assembled from standard parts in the two schemes are 2 × 4 × 9 m (Scheme I) and 4 × 4 × 9 m (Scheme II), and the heat recovery efficiencies are 65.2% and 69.3%, respectively. Calculated by the wind resistance superposition formula, the wind resistance of the plate heat exchanger was obtained as 0.0510 Ns²/m⁸ and 0.1020 Ns²/m⁸ for Scenarios I and II, respectively, corresponding to 210 Pa and 419 Pa at an air volume of 64.1 m³/s. Based on the fan's current operating point (64.1 m³/s, 880 Pa), the total wind resistance of the ventilation system is 0.2142 Ns²/m⁸. The working condition point of the fan in scheme 1 will be shifted to (59.5 m³/s, 939.1 Pa), and the airflow will decrease by 4.6 m³/s. In order to recover the airflow, the blade angle of the fan needs to be adjusted to 0 °, and the operating frequency is adjusted to 39 Hz, and the new working condition point of the fan is (64.7 m³/s, 1111 Pa). Similarly, the fan operating point of Scenario 2 will be shifted to (55.7 m³/s, 980.7 Pa), which still needs to restore the airflow by adjusting the fan blade angle to 0° and the operating frequency to 42 Hz, and the new fan operating point is (65.4 m³/s, 1354.1 Pa). Since Option 2 has a higher heat recovery efficiency, Option 2 was chosen as the implementation plan. In summary, although the installation of the plate heat exchanger will result in a reduction in the actual air discharge from the mine, this adverse effect can be eliminated by adjusting the fan operating point by utilizing the redundant capacity of the fan.

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