Ⅰ和Ⅱ型曲柄摇杆机构的计算机辅助设计
|
摘要
定量分析比较了Ⅰ和Ⅱ型曲柄摇杆机构的传力性能和传动平稳性,推导出Ⅰ和Ⅱ型曲柄摇杆机构的各杆长关系、极位夹角θ的最大值、曲柄位置角ф的可行域,证明了各自最小传动角γ_(min)的出现位置。建立了摇杆摆角φ、极位夹角θ、杆长、位置角ф和最小传动角γ_(min)之间的数理关系。基于Mathematica编制了计算及绘图程序,可迅速直观地确定最小传动角最大的A点位置,快速实现摆角、行程速比系数且传力性能最优的Ⅰ和Ⅱ型曲柄摇杆机构的尺度设计。
The power transmission and transmission stability performance of Ⅰ and Ⅱ type crank-rocker mechanism were analyzed and compared quantitatively, the relations on the bar length, the maximum value of extreme position angle θ, the feasible region of the position angle ф were derived, and the position of the minimum transmission angle γ_(min)was proved. The mathematical relations between the angular stroke of rocker φ, the extreme position angle θ, the length, the position angle ф and the minimum transmission angle γ_(min)was established. Basing on Mathematica, the program of calculation and drawing were established, which can confirm the position of the maximum A corresponding to the minimum transmission angle quickly and directly, can finish the dimensional design of Ⅰ and Ⅱ type crank-rocker mechanism with the optimum transmission performance in angular stroke of rocker and travel velocity-ratio coefficient known.
The power transmission and transmission stability performance of Ⅰ and Ⅱ type crank-rocker mechanism were analyzed and compared quantitatively, the relations on the bar length, the maximum value of extreme position angle θ, the feasible region of the position angle ф were derived, and the position of the minimum transmission angle γ_(min)was proved. The mathematical relations between the angular stroke of rocker φ, the extreme position angle θ, the length, the position angle ф and the minimum transmission angle γ_(min)was established. Basing on Mathematica, the program of calculation and drawing were established, which can confirm the position of the maximum A corresponding to the minimum transmission angle quickly and directly, can finish the dimensional design of Ⅰ and Ⅱ type crank-rocker mechanism with the optimum transmission performance in angular stroke of rocker and travel velocity-ratio coefficient known.
引文
[1]张静,王占英,刘春东,等.按最小传动角设计曲柄摇杆机构的解析方法[J].机械设计,2008,25(10):63-65.
[2]叶金虎,程友联.基于传动角函数的偏置曲柄摇杆机构优化设计[J].机械设计与研究,2014,30(4):31-34.
[3]程友联,吴晓红.按最佳传动角设计偏置曲柄摇杆机构的闭式解[J].机械设计与研究,2009,25(6):28-30.
[4]苏有良.按最小传动角最大的曲柄摇杆机构优化设计[J].机械设计,2014,31(6):29-33.
[5]刘学良.四杆机构深度解析[J].煤矿机械,2016,37(4):84-87.
[6]于潇雁,蓝兆辉.具有急回特性的曲柄摇杆机构的综合新探[J].机械设计与研究,2007,23(6):43-45.
[7]常勇,李延平.基于辅助角方法的平面曲柄摇杆机构性能与设计线图丛的研究[J].机械设计,2002,19(1):20-23.
[8]冯立艳.机械原理[M].北京:机械工业出版社,2012.
[9]曹茹.曲柄摇杆机构的参数化图解法优化设计[J].中国农机化学报,2015,36(1):50-53.
[10]杨爱民,刘春凤,屈静国.大学数学实验[M].北京:科学出版社,2012.
[2]叶金虎,程友联.基于传动角函数的偏置曲柄摇杆机构优化设计[J].机械设计与研究,2014,30(4):31-34.
[3]程友联,吴晓红.按最佳传动角设计偏置曲柄摇杆机构的闭式解[J].机械设计与研究,2009,25(6):28-30.
[4]苏有良.按最小传动角最大的曲柄摇杆机构优化设计[J].机械设计,2014,31(6):29-33.
[5]刘学良.四杆机构深度解析[J].煤矿机械,2016,37(4):84-87.
[6]于潇雁,蓝兆辉.具有急回特性的曲柄摇杆机构的综合新探[J].机械设计与研究,2007,23(6):43-45.
[7]常勇,李延平.基于辅助角方法的平面曲柄摇杆机构性能与设计线图丛的研究[J].机械设计,2002,19(1):20-23.
[8]冯立艳.机械原理[M].北京:机械工业出版社,2012.
[9]曹茹.曲柄摇杆机构的参数化图解法优化设计[J].中国农机化学报,2015,36(1):50-53.
[10]杨爱民,刘春凤,屈静国.大学数学实验[M].北京:科学出版社,2012.