共查询到20条相似文献,搜索用时 109 毫秒
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本文阐述高速透平齿轮齿形修整的意义和方法。根据斜齿轮啮合特点及轮齿受载条件,提出了斜齿轮齿形修整的计算模型,应用空间等参数元素法,在空间力作用下,得出了轮齿变形量,从而在装置无误差的前提下,确定齿轮理论修整量。 相似文献
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文章阐述了齿轮失效的类型和成因,当齿轮出现失效时,可以通过对齿轮振动信号的边频带分析得到不同的失效类型,文章归纳和总结了齿轮不同失效类型所对应齿轮振动信号频谱的特征。 相似文献
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本文通过对船用透乎齿轮齿宽载荷分布的计算及螺旋线修正的论述,分析了影响轮齿载荷分布的诸种因素,并举例说明采用螺旋线修正改善轮齿载荷分布的效果。 相似文献
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本文通过对摩托车齿轮的分析研究,提出增加JH70、JH125离合器齿轮系数,齿上径,从而增加轮齿柔度、重合系数,达到降低齿轮噪声激发系数的目的。 相似文献
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文玉英 《小型内燃机与摩托车》1996,(3)
本文通过对摩托车齿轮的分析研究,提出增加JH70、JH125离合器齿轮顶隙系数,齿顶圆直径,从而增加轮齿柔度、重合系数,达到降低齿轮噪声激发系数的目的。 相似文献
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柴油机机带齿轮油泵容积效率的探讨 总被引:2,自引:0,他引:2
<正> 1 前言柴油机的机带齿轮油泵一般多由一对外啮合的渐开线齿轮和泵体组成。这一对齿轮置于泵体之中,在齿轮的齿顶方向(径向)和齿轮侧面都与壳体保持一定的间隙,保证齿轮在高速旋转及承受负荷下不致发生卡死现象。同时由于轮齿在啮合过程中,两轮齿逐渐互相嵌入对方的齿谷而强行挤出在齿谷中装载的油,形成压力油。因此为了消除齿轮油泵的困油现象,一般在泵体和泵盖端面开有卸荷槽。为此油泵的品质应以两方面来衡量:a.静态品质(包括平均流量、平均压力及各种效率指标);b.动态品质(包括油 相似文献
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考虑啮合齿面间润滑油黏度对斜齿轮传动振动的影响,根据pyбин推断,建立了啮合齿面的接触模型;考虑润滑油的黏压效应及斜齿轮啮合的特殊性,对接触区诱导压力进行等效变换,推导出斜齿轮传动的弹流润滑振动模型;求解模型,得到润滑油黏度在0.02~0.048,Pa.s内输出轴振动加速度的脉动均方根(RMS)值;通过试验得到在同一工况下输出轴振动加速度值,并绘制其RMS值变化曲线.试验曲线和模型仿真计算结果变化趋势吻合,均表明齿轮的振动随润滑油黏度的减小而增强,验证了模型的正确性,对齿轮传动减振降噪分析设计具有一定参考价值. 相似文献
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针对风电增速箱故障率偏高的问题,在对风电机组传动系统的振动响应机理进行分析的基础上,提出一种同时考虑齿根裂纹与齿面摩擦2种因素耦合情况下计算风电增速箱行星轮系动态响应的方法。首先分析考虑不同滑动摩擦因素时,含齿根裂纹缺陷的齿轮其啮合刚度的变化情况;随后运用集中参数法建立一种同时考虑平移和扭转2种力学效应相互影响作用的行星轮系动态响应计算模型。使用该模型在考虑齿根裂纹、齿面滑动摩擦2种因素耦合情况下,对行星轮系时变啮合刚度影响作用进行仿真计算。结果表明,齿面间的滑动摩擦力将导致行星齿轮扭转振动响应在低频区域受到抑制、中频区域得到增强,而齿根裂纹会导致系统出现调制效应且该效应会使行星齿轮的扭转振动频谱响应在行星轮与太阳轮间的啮合频率附近出现调制边频带现象。 相似文献
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An analytical formulation was developed to estimate the load‐sharing and planetary loads of a three‐point suspension wind turbine drivetrain considering the effects of non‐torque loads, gravity and bearing clearance. A three‐dimensional dynamic drivetrain model that includes mesh stiffness variation, tooth modifications and gearbox housing flexibility was also established to investigate gear tooth load distribution and non‐linear tooth and bearing contact of the planetary gears. These models were validated with experimental data from the National Renewable Energy Laboratory's Gearbox Reliability Collaborative. Non‐torque loads and gravity induce fundamental excitations in the rotating carrier frame, which can increase gearbox loads and disturb load sharing. Clearance in the carrier bearings reduces the bearing stiffness significantly. This increases the amount of pitching moment transmitted from the rotor to the gear meshes and disturbs the planetary load share, thereby resulting in edge loading. Edge loading increases the likelihood of tooth pitting and planet‐bearing fatigue, leading to reduced gearbox life. Additionally, at low‐input torque, the planet‐bearing loads are often less than the minimum recommended load and thus susceptible to skidding. Copyright © 2014 John Wiley & Sons, Ltd. 相似文献
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This work develops an optimization algorithm for the definition of gear microgeometry modifications (MGM) on a gearbox belonging to an offshore 10-MW wind turbine. Subsequently, the impact of the gear microgeometry on the performance of gears and bearings is quantified: First, under rated load conditions and, second, accounting for the environmental conditions to estimate the long-term damage. To fulfil this task, a high-fidelity numerical model of the drivetrain is used, which meets the design requirements of the Technical University of Denmark (DTU) 10-MW reference offshore wind turbine. The optimization achieves a uniform distribution of the contact stress along the tooth flank, shifts its maximum value to the central position, and eliminates edge contact. These enhancements increase the gear safety factors. Nevertheless, the most significant improvement concerns planetary bearings, for which optimum gear MGM achieve a homogeneous share of the load among bearings. Moreover, deviations of the microgeometry with respect to the defined optimum are also addressed. In gears, lead slope deviations are counteracted by crowning modifications to restrain the increase of the load offset. Concerning planetary bearings, slope deviations can be beneficial or detrimental depending on whether they overload downwind or upwind planetary bearings, respectively. Finally, accumulated damage to planetary bearings after 20 years of service is assessed. Before MGM, results predict a premature failure of planetary bearings, while optimum MGM extend their predicted life above 20 years by achieving a reduction of the maximum accumulated fatigue damage by a factor of 4.4. 相似文献