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id="print"> <p><span style="font-size: 18px;">1 摇篮转台有限元模型</span></p><p><span style="font-size: 18px;">摇篮转台主要由工作台、C轴摇篮体、A轴左端支撑及右端支撑等部件组成。为确保有限元分析的准确性与效率，需对三维模型进行合理简化处理:依据圣维南原理，去除装配体中的螺钉、螺母、销钉等小零件及垫圈、垫片等薄型零件;删除模型中较小的螺栓孔、倒角、圆角、窄长槽、小凸台等细小特征;忽略密封圈、拖链及冷却、液压、润滑等附件对转台刚度及振动的影响[11]，简化后结构如图1所示。</span></p><p style="text-align: center;"><span style="font-size: 18px;"><img src="/bethel/upload/images/202608/17876391142050.png" title="17876391142050.png" alt="image.png"/></span></p><p><span style="font-size: 18px;">在ANSYS Workbench中建立摇篮转台的有限元模型时，需对材料属性、连接关系和接触条件进行详细定义。具体设置如下。</span></p><p><span style="font-size: 18px;">(1)材料属性 工作台、摇篮体、轴连接座采用HT300，密度7250kg/m³，杨氏模量120GPa，泊松比0.28;刹车片采用65Mn，密度7250kg/m³，杨氏模量120GPa，泊松比0.28。</span></p><p><span style="font-size: 18px;">(2)连接关系与接触设置 A轴通过HRTG260轴承连接，C轴通过HRTG395轴承连接，轴承内外圈分别与箱体、转轴固定，其中HRTG260轴向刚度6.9kN/μm、径向刚度5.3kN/μm，HRTG395轴向刚度9.9kN/μm、径向刚度5.8kN/μm;刹车片摩擦面与钳夹摩擦面设置为摩擦接触，摩擦系数0.15;其他非摩擦接触的装配面采用固定连接，保证结构整体性。</span></p><p><span style="font-size: 18px;">采用20mm单元尺寸进行自适应网格划分，并对轴承网格进行细化处理，最终得到包含922731个节点和1555417个单元的整机有限元模型，如图2所示。</span></p><p style="text-align: center;"><span style="font-size: 18px;"><img src="/bethel/upload/images/202608/17876391227580.png" title="17876391227580.png" alt="image.png"/></span></p><p><span style="font-size: 18px;">2 静力学分析</span></p><p><span style="font-size: 18px;">为评估摇篮转台载重时的结构安全性与静力学性能，指导后续优化设计，需对其进行有限元静力学分析。结合实际加工场景，摇篮转台工作时主要承受惯性载荷(地球重力加速度)与力载荷(工件重力、切削力等)，本文重点评估结构承载能力，仅考虑工件重力影响，设计4种典型工况开展分析，静力学分析结果如图3所示，力学性能分析结果见表1。</span></p><p style="text-align: center;"><span style="font-size: 18px;"><img src="/bethel/upload/images/202608/17876391428657.png" title="17876391428657.png" alt="image.png"/></span></p><p style="text-align: center;"><span style="font-size: 18px;"><img src="/bethel/upload/images/202608/17876391556362.png" title="17876391556362.png" alt="image.png"/></span></p><p><span style="font-size: 18px;">由图3可知，分析的4种加工工况中，A轴摆动角度为0°即工作台水平无载荷时A轴刹车对整体变形量几乎没有影响;而在载荷15000N的情况下，A轴刹车启动时整体变形量为0.0263mm，刹车松开时变形量为0.0264mm。A轴摆动角度为90°，载荷7500N的情况下A轴刹车对整体变形量影响较小。从静力学分析结果可知，摇篮转台整体变形量较小，静刚度较高，结构有优化空间。</span><br/></p><p><span style="font-size: 18px;">3 模态分析</span></p><p><span style="font-size: 18px;">为获取摇篮转台的整体振动特性，需对其进行模态分析。考虑到五轴摇篮转台主要受低频激励影响，重点分析前4阶固有频率与振型，以精准评估结构振动特性，0°、90°转台时模态分析结果如图4、图5所示，模态分析结果见表2。</span></p><p><span style="font-size: 18px;">由表2可知，摇篮转台的各阶振型与摇篮体的形状和支撑结构密切相关。这意味着摇篮体是摇篮转台的薄弱环节，应对摇篮体进行优化设计，以避免在工作状态下产生共振。</span></p><p style="text-align: center;"><span style="font-size: 18px;"><img src="/bethel/upload/images/202608/17876392512745.png" title="17876392512745.png" alt="image.png"/></span></p><p style="text-align: center;"><span style="font-size: 18px;"><img src="/bethel/upload/images/202608/17876392641737.png" title="17876392641737.png" alt="image.png"/></span></p><p style="text-align: center;"><span style="font-size: 18px;"><img src="/bethel/upload/images/202608/17876392752768.png" 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