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本文的第一种方法是把轮齿看成由许多薄片迭成的,每片之间没有作用力,因而齿向载荷分布是线性的。可由失准度F_(βy)、刚度Cr和载荷Fm/b算得K_(Hβ);再利用文献的公式(经笔者处理)计算K_(Fβ)。计算结果和ISO60/6199E的公式一样,导出的K_(Fβ)=K_(Hβ)~N中的N值也是N=((b/h)~2)/(1+(b/h)+(b/h)~2) 本文的第二种方法是以无限宽的悬臂板为基础,利用文献的公式(经笔者处理),对具体的轮齿参数求解齿面载荷分布曲线,然后再计算K_(Hβ)和K_(Fβ)。这应该较为准确。但
The first method in this paper is to treat the teeth as a stack of many sheets with no force between the sheets, so that the tooth load distribution is linear. The K_ (Hβ) can be calculated from the degree of misalignment F_ (βy), the stiffness Cr and the load Fm / b, and the K_ (Fβ) can be calculated by the formula of the literature. The calculation result is the same as the formula of ISO60 / 6199E, and the derived N value of K_ (Fβ) = K_ (Hβ) ~N is also N = (b / h) ~ 2) / 1+ (b / h) + b / h) ~ 2) The second method in this paper is based on an infinitely wide cantilever plate. Using the formula of the literature (by the author), the gear tooth load distribution curve is solved for the specific gear tooth parameters, (Hβ) and K_ (Fβ). This should be more accurate. but