化纤长丝高速卷绕头系统动力学性能研究
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摘要
纱线卷绕是纺织品生产领域普遍存在的一项重要工艺过程。完成卷绕的转子(锭子)连同纱线卷装构成转子系统,为保持卷绕线速度恒定,系统转速会随着卷绕直径的增加逐渐减慢,形成质量、刚度、转速等参数慢时变系统。化纤长丝卷绕头是典型的参数慢时变转子系统。随着新产品和新工艺的不断发展,研制和生产大(容量)卷装、高速卷绕的化纤长丝卷绕头是降低成本、适应新工艺要求的必然趋势。
卷绕头长丝满卷质量一般是锭轴自身质量4倍以上。在一个卷绕周期内,锭轴的工作转速范围为20000r/min.～4000r/min.,以满足恒卷绕线速度为6000m/min.的工艺要求。如何确保在宽广的转速工作频域内,在质量和刚度时变情况下,锭轴系统能有效避开临界转速而平稳运行是卷绕头设计的关键。空卷时平衡后的锭轴(夹头),如何确保在添加纸筒、卷装增大、胀圈运动、长丝卷绕时的干扰、压辊施压等状态下锭轴系统仍正常工作是卷绕头设计的又一问题。针对以上问题,本文研究工作如下：
首先从卷绕头弹性支承系统入手,搭建了与锭轴相同的弹性支承系统转子试验台,并建立对应梁单元转子有限元模型,通过理论、试验相结合分析了弹性支承转子系统的动力学特点,结果表明：弹性支承系统使转子系统的前几阶非弯曲振型(弹性支承刚性转轴运动)所对应的临界转速大幅下降,形成低阶临界转速和高阶临界转速(对应转轴弯曲振型)间较为宽广的平稳转速区。
弹性支承系统的动力参数涉及难以确定的因素较多,本文通过试验求得其当量刚度和阻尼值。在分析弹性支承转子的非弯曲振型以及相应的临界转速的基础上,完善了试验求取弹性支承系统刚度的方法,并给出试验求取弹性支承系统动力参数时转子系统参数选取的要求。
基于橡胶材料应力—应变关系,利用唯象理论建立橡胶材料的本构关系,并在工作区内线性化；基于赫兹接触理论建立了橡胶圈支承力学模型,结合有限元程序计算分析了橡胶圈支承的静态特性。针对加工的不同质量的转子,通过试验求取弹性支承系统的系列等效动态刚度值,拟合了弹性支承系统等效刚度曲线,分析了弹性支承的特点。同时对试验台的转子系统进行了相同模型的有限元分析,理论计算和试验数据很好吻合,验证了方法的正确性。
其次建立了弹性支承刚性转子的动力学方程,从理论上验证当考虑弹性支承的阻尼作用,弹性支承下的高速旋转转子具有自动定心的特点。建立弹性支承转子系统有限元模型,转子采用实体单元,分析结果表明：改变转子径向弹性支承刚度可显著改变转子椭圆柱形运动振型所对应的临界转速,而同时改变转子轴向弹性支承刚度可显著改变转子椭圆锥形运动所对应的临界转速,改变这两组刚度值可将转子系统的非弯曲振型所对应的临界转速调整到所要求的范围内。当单个夹头上的卷装不断增多,夹头和锭轴长度加长时,弯曲振型所对应的临界转速下降,压缩稳定工作区间,为进一步合理规划临界转速值,本文提出了主动调节转子临界转速的方法,并给出了指导性建议。
最后针对一套典型的长丝卷绕头,设计相应的虚拟样机,建立其有限元模型,利用以上分析方法和结果对锭轴空卷快速升速、满卷快速降速、正常卷绕时参数慢变等状况下的动力学行为进行计算、仿真和分析,揭示了三阶段不同动力学特性,验证了研究结果的正确性和可行性。
The winding is an important process in the filament production, Winding rotor (or spindle) together with the yarn package constitutes a rotor system. In order to maintain a constant winding speed in spinning, the revolving speed of the rotor has to be gradually slowed down with the increase of the winding diameter, which constitutes a parameters slow time-varying system of its mass, stiffness and revolving speed. The filament winding head is a typical form of the rotor system with parameters slow time-varying. In order to develop new products with new technology, reduce costs and adapt to the new requirements, it is an inevitable trend to develop and product new chemical fiber filament winding heads for high speed of winding with the large package.
The full package weight of a filament winding head is generally more than4times its own weight of the spindle. In a winding cycle, the range of the spindle working speed is varying from20000r/min. to4000r/min., which can meet the technological requirements of a spinning speed up to6000m/min.. In the case of the mass and rigidity time-varying, in a wide range of its working speed, how to ensure the spindle system effective working avoiding the critical speed disturbance and to maintain its smooth operation is the key point of the winding head design. In an idle spindle, it has been in a state of equilibrium. When the paper spool is loading, the package wound is increasing, and the compression roll pressing on, they are all disturbing the filament winding effectively. In order to ensure the spindle system working smoothly and to solve all above problem of the winding head design, the main research work is the following:
Start with the elastic support system of the winding head, we built a rotor testing device with the same elastic support system of the spindle and then further established a finite element model of the rotor beam element. By means of theoretical and experimental analysis, we studied the dynamic characteristics of the rotor system. The results show that: the elastic support system cause the critical speeds corresponding to the first orders non-bending mode of the rotor system (motion of the elastic support rigidity shaft) decrease significantly, which lead to a relatively wide range of small variation between the lower order critical speed and the higher order critical speed (according to the smooth running condition).
Secondly, dynamic parameters of the elastic support system involve in many uncertain factors. In this paper, we obtained the equivalent stiffness and damping through the test. In addition, through the analysis of non-bending vibration mode of the rotor with elastic support, as well as the corresponding critical speed, we improved the test method for stiffness of the elastic supporting system, and gave the parameter selection requirements of the rotor system when calculating dynamic parameters of the elastic support system by test.
Based on the rubber material stress-strain relationship, we established its constitutive relation by applying phenomenological theory, and achieved linearization within the work area. Based on Hertzian contact theory, we established a mechanical model of the rubber ring support, and analyzed its static characteristics of the rubber ring by the finite element method. Through the test of the rotor's different mass, we obtained a series of equivalent dynamic stiffness value of the elastic support system and some corresponding fitting curves, and analyzed characteristics of the elastic support. At the same time, the finite element model of the rotor system was established and analyzed. The results show that: the solution of the theoretical calculation and the experimental data agree well, which proves the correctness of the design.
Then, in order to verify theoretically the characteristics of the automatic centering of a high-speed rotating rotor with elastic support, a kinetic equation for a rigid rotor with elastic support was established. In addition, a finite element model for a rotor system with elastic support was established, and the rotor is used a solid element. The analytical results show that:changing the radial stiffness of the elastic support can significantly change the critical speed of rotation corresponding to the elliptic cylindrical movement mode of the rotor. While, at the same time, changing the axial stiffness of the rotor elastic support can significantly change the critical speed of rotation corresponding to the elliptical conical motion mode of the rotor. By changing two groups of the stiffness of the rotor system, the critical speed corresponding to non-bending the mode can be adjusted to a required range. When the package on a single chuck continues to grow, and chuck and spindle lengths increase, the critical speed corresponding to a bending mode will decreasing, which will narrow the range of working stability. In order to rational plan the critical speed value, this paper presents an active regulation method of the rotor critical speed, and gives some suggestions further.
Lastly, based on a typical filament winding head, we designed the corresponding virtual prototype, and established a finite element model. Using the above method and the analysis results, we conducted the calculation, simulation and analysis about the dynamics behavior of the acceleration of the spindle empty package, deceleration of the full package and winding parameters slowly variations etc, which reveals different dynamic characteristics of the three stages. The results verify its correctness and feasibility.
卷绕头长丝满卷质量一般是锭轴自身质量4倍以上。在一个卷绕周期内,锭轴的工作转速范围为20000r/min.～4000r/min.,以满足恒卷绕线速度为6000m/min.的工艺要求。如何确保在宽广的转速工作频域内,在质量和刚度时变情况下,锭轴系统能有效避开临界转速而平稳运行是卷绕头设计的关键。空卷时平衡后的锭轴(夹头),如何确保在添加纸筒、卷装增大、胀圈运动、长丝卷绕时的干扰、压辊施压等状态下锭轴系统仍正常工作是卷绕头设计的又一问题。针对以上问题,本文研究工作如下：
首先从卷绕头弹性支承系统入手,搭建了与锭轴相同的弹性支承系统转子试验台,并建立对应梁单元转子有限元模型,通过理论、试验相结合分析了弹性支承转子系统的动力学特点,结果表明：弹性支承系统使转子系统的前几阶非弯曲振型(弹性支承刚性转轴运动)所对应的临界转速大幅下降,形成低阶临界转速和高阶临界转速(对应转轴弯曲振型)间较为宽广的平稳转速区。
弹性支承系统的动力参数涉及难以确定的因素较多,本文通过试验求得其当量刚度和阻尼值。在分析弹性支承转子的非弯曲振型以及相应的临界转速的基础上,完善了试验求取弹性支承系统刚度的方法,并给出试验求取弹性支承系统动力参数时转子系统参数选取的要求。
基于橡胶材料应力—应变关系,利用唯象理论建立橡胶材料的本构关系,并在工作区内线性化；基于赫兹接触理论建立了橡胶圈支承力学模型,结合有限元程序计算分析了橡胶圈支承的静态特性。针对加工的不同质量的转子,通过试验求取弹性支承系统的系列等效动态刚度值,拟合了弹性支承系统等效刚度曲线,分析了弹性支承的特点。同时对试验台的转子系统进行了相同模型的有限元分析,理论计算和试验数据很好吻合,验证了方法的正确性。
其次建立了弹性支承刚性转子的动力学方程,从理论上验证当考虑弹性支承的阻尼作用,弹性支承下的高速旋转转子具有自动定心的特点。建立弹性支承转子系统有限元模型,转子采用实体单元,分析结果表明：改变转子径向弹性支承刚度可显著改变转子椭圆柱形运动振型所对应的临界转速,而同时改变转子轴向弹性支承刚度可显著改变转子椭圆锥形运动所对应的临界转速,改变这两组刚度值可将转子系统的非弯曲振型所对应的临界转速调整到所要求的范围内。当单个夹头上的卷装不断增多,夹头和锭轴长度加长时,弯曲振型所对应的临界转速下降,压缩稳定工作区间,为进一步合理规划临界转速值,本文提出了主动调节转子临界转速的方法,并给出了指导性建议。
最后针对一套典型的长丝卷绕头,设计相应的虚拟样机,建立其有限元模型,利用以上分析方法和结果对锭轴空卷快速升速、满卷快速降速、正常卷绕时参数慢变等状况下的动力学行为进行计算、仿真和分析,揭示了三阶段不同动力学特性,验证了研究结果的正确性和可行性。
The winding is an important process in the filament production, Winding rotor (or spindle) together with the yarn package constitutes a rotor system. In order to maintain a constant winding speed in spinning, the revolving speed of the rotor has to be gradually slowed down with the increase of the winding diameter, which constitutes a parameters slow time-varying system of its mass, stiffness and revolving speed. The filament winding head is a typical form of the rotor system with parameters slow time-varying. In order to develop new products with new technology, reduce costs and adapt to the new requirements, it is an inevitable trend to develop and product new chemical fiber filament winding heads for high speed of winding with the large package.
The full package weight of a filament winding head is generally more than4times its own weight of the spindle. In a winding cycle, the range of the spindle working speed is varying from20000r/min. to4000r/min., which can meet the technological requirements of a spinning speed up to6000m/min.. In the case of the mass and rigidity time-varying, in a wide range of its working speed, how to ensure the spindle system effective working avoiding the critical speed disturbance and to maintain its smooth operation is the key point of the winding head design. In an idle spindle, it has been in a state of equilibrium. When the paper spool is loading, the package wound is increasing, and the compression roll pressing on, they are all disturbing the filament winding effectively. In order to ensure the spindle system working smoothly and to solve all above problem of the winding head design, the main research work is the following:
Start with the elastic support system of the winding head, we built a rotor testing device with the same elastic support system of the spindle and then further established a finite element model of the rotor beam element. By means of theoretical and experimental analysis, we studied the dynamic characteristics of the rotor system. The results show that: the elastic support system cause the critical speeds corresponding to the first orders non-bending mode of the rotor system (motion of the elastic support rigidity shaft) decrease significantly, which lead to a relatively wide range of small variation between the lower order critical speed and the higher order critical speed (according to the smooth running condition).
Secondly, dynamic parameters of the elastic support system involve in many uncertain factors. In this paper, we obtained the equivalent stiffness and damping through the test. In addition, through the analysis of non-bending vibration mode of the rotor with elastic support, as well as the corresponding critical speed, we improved the test method for stiffness of the elastic supporting system, and gave the parameter selection requirements of the rotor system when calculating dynamic parameters of the elastic support system by test.
Based on the rubber material stress-strain relationship, we established its constitutive relation by applying phenomenological theory, and achieved linearization within the work area. Based on Hertzian contact theory, we established a mechanical model of the rubber ring support, and analyzed its static characteristics of the rubber ring by the finite element method. Through the test of the rotor's different mass, we obtained a series of equivalent dynamic stiffness value of the elastic support system and some corresponding fitting curves, and analyzed characteristics of the elastic support. At the same time, the finite element model of the rotor system was established and analyzed. The results show that: the solution of the theoretical calculation and the experimental data agree well, which proves the correctness of the design.
Then, in order to verify theoretically the characteristics of the automatic centering of a high-speed rotating rotor with elastic support, a kinetic equation for a rigid rotor with elastic support was established. In addition, a finite element model for a rotor system with elastic support was established, and the rotor is used a solid element. The analytical results show that:changing the radial stiffness of the elastic support can significantly change the critical speed of rotation corresponding to the elliptic cylindrical movement mode of the rotor. While, at the same time, changing the axial stiffness of the rotor elastic support can significantly change the critical speed of rotation corresponding to the elliptical conical motion mode of the rotor. By changing two groups of the stiffness of the rotor system, the critical speed corresponding to non-bending the mode can be adjusted to a required range. When the package on a single chuck continues to grow, and chuck and spindle lengths increase, the critical speed corresponding to a bending mode will decreasing, which will narrow the range of working stability. In order to rational plan the critical speed value, this paper presents an active regulation method of the rotor critical speed, and gives some suggestions further.
Lastly, based on a typical filament winding head, we designed the corresponding virtual prototype, and established a finite element model. Using the above method and the analysis results, we conducted the calculation, simulation and analysis about the dynamics behavior of the acceleration of the spindle empty package, deceleration of the full package and winding parameters slowly variations etc, which reveals different dynamic characteristics of the three stages. The results verify its correctness and feasibility.
引文
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