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1·Gear mesh is improved resulting in improved durability, less gear noise, and improved engine power transfer.

齿轮相互啮合的情况改善而令到其耐用性、齿轮噪音和引擎力量传送得到改善。

2·Under the precondition of an absence of increase in gear mesh error a rational support parallelism can be set.

在不增加啮合齿向误差的前提下，合理给定支承平行度要求。

3·A calculation method and corresponding formulas are presented by using Hertz contact theory and gear mesh theory.

应用赫兹理论和齿轮啮合理论给出了螺旋齿轮齿面接触应力的计算方法和相关公式。

4·With increase in defect severity, energy is distributed to the sidebands of the gear mesh frequency across supply line frequency.

与增加的缺损严重，能源是分配给边的齿轮啮合频率跨越供电线路的频率。

5·This makes it possible to analyze the effect on gear mesh of such factors as gear box deformation, axial end loading and axial deflection, etc.

用这种方法可以分析多种外界因素对齿轮啮合的影响，如箱体变形、轴端受力、轴线挠曲等；

6·The internal teeth of the ring gear mesh with the planet gear teeth. Thus, the ring gear rotates with the other parts of the planetary gear system.

内齿圈的内齿与行星轮的齿啮合。因此，内齿圈随着行星轮系统的其他配件旋转。

7·The motor position is adjustable to accommodate different gears and to allow adjustment of the gear mesh between the pinion and its mating spur gear.

电机的位置是可调节的，以适应不同的齿轮，并允许该小齿轮及其配对正齿轮之间的调整的齿轮的啮合。

8·With increase in defect severity, not only the defective gear mesh frequency gains energy, but also large impact energy appears in low-frequency regions.

与增加的缺陷的严重性，不仅有缺陷齿轮啮合频率增益能源，并且还大的影响，能源出当前低频区。

9·Through design and calculation, determined soft and rigid gear conjugation coefficient, obtained teeth side clearance when soft and rigid gear mesh transmission.

通过设计计算确定了柔、刚轮的变位系数，得到了柔、刚轮在啮合传动时的齿侧间隙值。

10·The nonlinear gear mesh force and nonlinear oil film force were considered synchronously, the dynamic model of geared rotor-oil journal bearing system was proposed.

同时考虑非线性齿轮啮合力和非线性油膜力的影响，建立齿轮-转子-滑动轴承系统的动力学模型。