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从已知条件出发,在直齿圆柱齿轮的齿数为7时确定了变位系数x的极限值为x_(min)>x_(max)。但是,考虑到必要的齿顶高的变化后必须指出,保证设计出齿顶圆的最小齿厚S_(an)=0.2m的齿轮仍然是可能的。此外,考虑到基圆处因齿廓过渡部分的适当限制,本文指出,仅在齿数Z_n>12时才是可能的。本文也注意到斜齿圆柱齿轮基圆的合理数值问题。在这个基圆上,可确定螺旋角β的五个数值:从9°到29°30′。为此,切齿刀具和齿面检验也应合理化。从径向变位系数极限值、最小端面重合度ε_α和齿顶以及齿根的每一较大的滑动速度比的观点出发,进行了齿数从Z_1=7到Z_1=17的直齿圆柱齿轮副以及螺旋角β=21°21′(=α_t)时齿数Z_1=6和Z_1=7的斜齿圆柱齿轮副的组合和优化。此时,在相当大的程度上保持着这种趋势:中心距a和齿顶圆直径d_s(对于m_n=1毫米)为标准值或者至少是有理数,且能充分显示出确实的优点。从附表中可以看出,用优化方法实际得到与具有临界齿数的小齿轮相啮合的大齿轮最多齿数。本文研究这一范围内的所有问题,得到的结果能直接用于所研究的齿轮副的设计和制造。
Starting from the known conditions, the limit value of the displacement coefficient x is determined as x min (min) when the number of teeth of the spur gear is 7. However, it must be pointed out that it is still possible to design a gear with a minimum tooth thickness S anam = 0.2 m in consideration of the necessary addendum height variation. In addition, given the appropriate restrictions at the base circle due to the transition of the tooth profile, it is pointed out here that this is possible only when the number of teeth Z_n> 12. This paper also notices the reasonable numerical problem of helical cylindrical gear base circle. On this base circle, five values of helix angle β can be determined: from 9 ° to 29 ° 30 ’. To this end, cutting tooth and tooth surface inspection should be rationalized. From the point of view of the radial displacement coefficient limit value, the minimum end face coincidence degree ε_α, and each of the large slide speed ratios of the tooth top and the tooth root, a spur gear pair with a tooth number of Z_1 = 7 to Z_1 = 17 And the combination and optimization of helical spur gear pairs with helical angles β = 21 ° 21 ’(= α_t) with Z_1 = 6 and Z_1 = 7. In this case, the tendency is maintained to a considerable extent: the center distance a and the diameter of the addendum circle d_s (for m_n = 1 mm) are standard or at least rational numbers, and the true advantages are fully demonstrated. It can be seen from the attached table that the optimal method is used to obtain the maximum gear number of the gear wheel that meshes with the pinion gear with the critical gear number. In this paper, we study all the problems in this area, and the results obtained can be directly used in the design and manufacture of gear pairs studied.