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深井提升动力学研究

何满潮

何满潮. 深井提升动力学研究. 力学进展, 2021, 51(3): 702-728 doi: 10.6052/1000-0992-21-032
引用本文: 何满潮. 深井提升动力学研究. 力学进展, 2021, 51(3): 702-728 doi: 10.6052/1000-0992-21-032
He M C. Research on deep shaft hoisting dynamics. Advances in Mechanics, 2021, 51(3): 702-728 doi: 10.6052/1000-0992-21-032
Citation: He M C. Research on deep shaft hoisting dynamics. Advances in Mechanics, 2021, 51(3): 702-728 doi: 10.6052/1000-0992-21-032

深井提升动力学研究——

doi: 10.6052/1000-0992-21-032
基金项目: 国家重点研发计划专项(2016YFC0600900)资助.
详细信息
    作者简介:

    何满潮, 矿山工程岩体力学专家、中国科学院院士、全国政协第十三届委员、俄罗斯矿业科学院院士、阿根廷国家工程院院士、中国矿业大学(北京)教授, 兼任国际岩爆专委会主席、中国岩石力学与工程学会理事长、中国矿业科学协同创新联盟理事长、中国矿业知识产权联盟理事长, 曾任国际岩石力学学会副主席、教育基金会主席. 全国杰出科技人才奖(2016年)、全国创新争先奖状(2017年)和何梁何利科技进步奖(2014年)获得者.  主要从事矿山岩体大变形灾害控制理论和技术研究. 提出了“缓变型”和“突变型”大变形灾害的理论体系, 研发了多套大变形灾害机理实验系统, 创建了深部岩体力学实验室. 形成了无煤柱自成巷110/N00工法技术体系,引领了矿业科学技术第三次革命. 提出了“双体灾变力学”理论, 研发了基于NPR锚索传感技术的地质灾害牛顿力远程监测预警系统, 成功预测滑坡灾害17次, 均提前3.5 ~ 20小时发出临滑预警, 挽救了百余人生命和数以亿计的财产损失. 获国家技术发明二等奖1项, 国家科技进步二等奖3项, 中国专利金奖1项, ISRM技术发明奖1项

    通讯作者:

    hemanchao@263.net

  • 中图分类号: O343,O424

Research on deep shaft hoisting dynamics

More Information
  • 摘要: 随着浅部煤炭资源的日益枯竭, 我国煤炭开采朝着深部化和大型化方向发展, 新建和改扩建的大型立井年生产能力已达1000万吨, 开采最大深度已达1500 m. 千米深井在提升过程中, 造成提升钢丝绳、容器振荡, 特别是自由悬挂平衡尾绳大幅度摆动, 严重影响多绳摩擦提升系统向高速度、深度化发展. 在国家重点研发计划“深地资源勘查开采”重点专项“煤矿深井建设与提升基础理论及关键技术”支持下, 建立了单元数量自动调整的自由悬挂平衡尾绳提升系统动力学模型, 揭示了传统提升系统诱发平衡尾绳大摆动的机理; 提出了深井SAP提升新模式, 构建了多元耦合下的SAP提升系统动力学模型与非光滑动力学模型, 揭示了多参数影响下系统的非光滑动力学特性及非线性振动演化规律; 研发了适用于深部提升的SAP提升技术与装备, 开展了SAP提升技术与装备的现场研究, 解决了大强煤矿立井提升系统运行过程中尾绳大摆动、提升容器大振动等关键问题, 提高了提升系统高速运行的安全性, 消除了尾绳大摆动难控制的问题.

     

  • 图  1  传统提升系统. (a)单滚筒缠绕, (b)双滚筒缠绕, (c)塔式摩擦, (d)落地式摩擦

    图  2  立井摩擦提升系统简化模型及平衡尾绳简化模型. (a)立井摩擦提升系统简化模型, (b)平衡尾绳模型, (c) 平衡尾绳简化模型

    图  3  平衡尾绳节点单元转换示意图

    图  4  平衡尾绳单元转换流程图

    图  5  单元转换后动能相对误差率

    图  6  左右两侧平衡尾绳距离容器中心线最大摆动位移. (a) 左侧平衡尾绳距离左侧容器中心线最大摆动位移图, (b) 右侧平衡尾绳距离右侧容器中心线最大摆动位移图

    图  7  SAP提升系统动力学模型

    图  8  张紧牵引系统(蓝线)与传统(红线)牵引系统纵向固有频率比较

    图  9  不同张紧轮质量作用下张紧轮处的纵向响应. (a) Terminal tension = 7.0 × 104, (b) Terminal tension = 1.0 × 105, (c) Terminal tension = 1.5 × 105, (d) Terminal tension = 2.0 × 105

    图  10  不同导向阻尼作用下的张紧导向轮纵向响应时频特性. (a) Damping = 0, (b) Damping = 5.0 × 104 N/s, (c) Damping = 2.0 × 105 N/s

    图  11  系统上升侧(a)和下降侧(b)纵向振动的最大振幅随时间的变化. (a)系统上升侧, (b)系统下降侧

    图  12  调节轮跳动情况分析示意图

    图  13  不同频率的顶部激励作用下调节轮的非光滑动力学特性. (a)基频激励作用, (b) 三倍频激励作用

    图  14  SAP提升系统关键装备现场安装图

    图  15  SAP提升系统满载常速运行监控图

    图  16  SAP系统与原系统不同工况下尾绳摆动对比

    图  17  SAP提升系统与原提升系统尾绳振动对比曲线

    图  18  空载时不同加速度尾绳位移曲线. (a)加速过程, (b) 减速过程

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出版历程
  • 收稿日期:  2021-06-03
  • 录用日期:  2021-09-22
  • 网络出版日期:  2021-09-27
  • 刊出日期:  2021-09-25

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