抗振轴承结构分析

对以调心滚子轴承和圆柱滚子轴承为基本形式的抗振轴承作了分析对比。其中，CC型抗振调心滚子轴承是较理想的抗振轴承，但加工难度较大。而M型抗振调心滚子轴承与我国现阶段生产的调心浪子轴承结构相近，且加工工艺较成熟。附图7幅，参考文献2篇。叙词：##4抗振轴承;;调心滚子轴承;;圆柱滚子轴承;;结构;;分析     

推力圆锥轴承调心球面磨削工艺研究

根据范成法磨削原理。确定推力圆锥滚子轴承调心球面磨削参数，解决该类结构轴承调心球面的磨削问题。     

工业齿轮箱中调心滚子轴承应用特点分析

调心滚子轴承在工业齿轮箱中的应用十分广泛,研究调心滚子轴承在齿轮箱中的应用特点对齿轮箱的设计具有重要意义。通过Bearinx的计算分析,相对于相同外形尺寸的圆锥滚子轴承和圆柱滚子轴承,调心滚子轴承具有更高的基本额定动载荷和角度不对中补偿能力,但是轴承的修正额定寿命计算值则更低,滚动体的接触应力更大。通过Caba3d模拟的调心滚子轴承的运动状态,调心滚子轴承单列受载时各列滚动体和保持架的运动状态存在很大差异,当载荷变化时,运动状态的变化将会使保持架和滚动体承受额外的冲击载荷。     

实体保持架调心滚子轴承优化设计

调心滚子轴承优化设计已于 1 993年完成 ,同时推出三种结构型式 8个直径系列 2 79个型号轴承的优化设计方法及统一表格图册 ,对行业产品结构的更新换代奠定了基础。现对实体保持架调心滚子轴承优化设计中的有关问题加以说明。轴承结构见图 1。图 1　调心滚子轴承1　中挡圈由于实体保持架结构的主参数与冲压保持架结构的主参数通用 ,使得实体保持架结构的中挡圈尺寸受到限制 ,例如 2 2 2 0 5( 5350 5)、 2 30 2 4( 30 531 2 4 )调心滚子轴承中挡圈尺寸如下 :2 2 2 0 5( 5350 5) :内径 d F=33.99mm,外径 DF= 36.76mm;宽度 BF=1 .39mm2 30 2 …     

双列调心凹面滚子轴承接触载荷分析

在考虑滚子与套圈、滚子与保持架以及保持架与引导套圈作用力的条件下,建立双列调心凹面滚子轴承动力学模型.以某双列调心凹面滚子轴承为研究对象,与静力学分析模型滚子最大接触载荷计算结果对比,验证了模型的正确性.并分析了工况条件(轴向载荷、径向载荷、倾覆力矩、转速)和结构参数(滚子数量、滚子长度、径向游隙)对滚子最大接触载荷的...     

游梁式抽油机用滚动轴承免维护方案探讨北大核心

针对某油田游梁式抽油机用轴承维护成本高的问题,分析了游梁式抽油机曲柄销、尾轴、中央轴用轴承的结构和使用情况,并将抽油机轴承分为调心滚子轴承和圆柱滚子轴承两类介绍了免维护轴承的研究现状。根据经验提出将曲柄销和尾轴调心滚子轴承改进为自带密封的调心滚子轴承,中央轴配对圆柱滚子轴承更换为某铁路货车密封双列圆锥滚子轴承的改进方案,优化方案可保证轴承8~10年的免维护周期。     

调心球面滚子轴承径向游隙的测量

近年来,调心球面滚子轴承的应用领域愈来愈广,但在使用过程中出现的问题也越来越多。为了推广普及调心球面滚子轴承的一些基本知识,针对调心球面滚子轴承在应用中的主要问题———径向游隙的检测进行了介绍。     

国内最大的CC型调心滚子轴承研制成功

近日，中机洛阳轴承科技有限公司为国外某知名公司成功研制了国内最大的CC型；中压保持架调心滚子轴承。该轴承内径尺寸630mm，外径尺寸920mm。在此之前，国内生产的最大的冲压保持架调心滚子轴承内径尺寸仅为360mm。CC型冲压保持架调心滚子轴承与MB、CA型实体保持架调心滚子轴承相比，具有承载能力高，应力分布均匀，耐冲击，较高的极限转速和较低的摩擦损耗，     

CA型宽系列调心滚子轴承装滚子缺口优化设计

针对调心滚子轴承设计标准中装滚子缺口设计并不适用于宽系列产品的问题,给出了CA型宽系列调心滚子轴承装滚子缺口深度和缺口圆弧半径的设计方法,实际应用表明,轴承合套率明显提高,掉滚子现象得到遏制。     

圆锥滚子轴承与调心滚子轴承用于平行轴减速器的效果对比

对比减速器在分别使用圆锥滚子轴承与调心滚子轴承时的轴承寿命、箱体变形量、轴承倾斜角度调整能力,利用有限元法完成减速器箱体分析,获得箱体的受力变形分布图和轴承孔的倾斜角度。通过对比分析结果,得出在实际工况条件下合理选用圆锥滚子轴承与调心滚子轴承的结论。     

Minimal Realization of Linear Graph Models for Multi-physics Systems

An engineering system may consist of several different types of components,belonging to such physical"domains"as mechanical,electrical,fluid,and thermal.It is t...     

INTEGRAL EQUATION METHOD＇S APPLICATION IN HOLE-EDGE STRESS OF COMPOSITE MATERIAL PLATE WITH DIFFERENT SHAPED HOLES

The strength of composite plate with different hole-shapes is always one of the most important but complicated issues in the application of the composite material. The holes will lead to mutations and discontinuity to the structure. So the hole-edge stress concentration is always a serious phenomenon. And the phenomenon makes the structure strength decrease very quickly to form dangerous weak points. Most partial damage begins from these weak points. According to the complex variable functions theory, the accurate boundary condition of composite plate with different hole-shapes is founded by conformal mapping method to settle the boundary condition problem of complex hole-shapes. Composite plate with commonly hole-shapes in engineering is studied by several complex variable stress fimction. The boundary integral equations are founded based on exact boundary conditions. Then the exact hole-edge stress analytic solution of composite plate with rectangle holes and wing manholes is resolved. Both of offset axis loadings and its influences on the stress concentration coefficient of the hole-edge are discussed. And comparisons of different loads along various offset axis on the hole-edge stress distribution of orthotropic plate with rectangle hole or wing manhole are made. It can be concluded that hole-edge with continuous variable curvatures might help to decrease the stress concentration coefficient; and smaller angle of outer load and fiber can decrease the stress peak value.     

Non-monotonic material contrast in scanning ion and scanning electron images

30 keV Ga⁺ focused ion beam induced secondary electron (iSE) imaging was used to determine the relative contrast between several materials. The iSE signal compared from C, Si, Al, Ti, Cr, Ni, Cu, Mo, Ag, and W metal layers does not decrease with an increase in target atomic number Z₂, and shows a non-monotonic relationship between contrast and Z₂. The non-monotonic relationship is attributed to periodic fluctuations of the stopping power and sputter yield inherent to the ion–solid interactions. In addition, material contrast from electron-induced secondary electron (eSE) and backscattered electron (BSE) images using scanning electron microscopy (SEM) also shows non-monotonic contrast as a function of Z₂, following the periodic behavior of the stopping power for electron–solid interactions. A comparison of the iSE and eSE results shows similar relative contrast between the metal layers, and not complementary contrast as conventionally understood. These similarities in the contrast behavior can be attributed to similarities in the periodic and non-monotonic function defined by incident particle–solid interaction theory.     

Application of Feature Extraction through Convolution Neural Networks and SVM Classifier for Robust Grading of Apples

This paper proposes a novel grading method of apples,in an automated grading device that uses convolutional neural networks to extract the size,color,texture,an...     

分布动态载荷识别的抗噪处理

针对正交多项式频域法在用多种响应对矩形薄板进行载荷识别中抗噪性较差的问题,综合运用平均法、矩阵预处理和奇异值截断法等方法对之进行改善,并引入空间映射的思想,将该方法的应用范围拓展为复杂的模型.利用仿真算例,证实了该方法具有较好的抗噪性.     

基于MELTAC-N平台的核电厂安全级DCS环网研究与测试

针对工程实践中环网通讯相关问题的处理缺乏理论基础及国产化安全级DCS平台的开发缺乏成熟经验借鉴问题,对基于MELTAC-N平台核电厂安全级DCS环网的软硬件实现进行了研究。提出了安全级DCS环网双环网冗余设计、光切换开关设计等硬件设计方法,以及以RPR协议为基础,采用全数据收发策略的软件设计方法。在CPR1000安全级DCS平台上对安全级DCS环网的可靠性及实时性进行了评价,并进行了容错能力、响应时间及响应时间稳定性测试验证实验。结果表明,基于MELTAC-N平台安全级DCS环网软硬件设计具有较好的容错能力及响应时间稳定性。     

Short-Term Relay Quality Prediction Algorithm Based on Long and Short-Term Memory

The fraction defective of semi-finished products is predicted to optimize the process of relay production lines, by which production quality and productivity ar...     

End-to-End Multiview Gesture Recognition for Autonomous Car Parking System

The use of hand gestures can be the most intuitive human-machine interaction medium.The early approaches for hand gesture recognition used device-based methods....     

The laboratory simulation of abrasive wear

Abrasive wear has long been recognised as one of the most potentially serious tribological problems facing the operators of many types of plant and machinery; several industrial surveys have indicated that wear by abrasion can be responsible for more than 50% of unscheduled machine and plant stoppages. Locating the operating point of a tribological contact in an appropriate operational ‚map’︁ can provide a useful guide to the likely nature and origins of the surface degradation experienced in use, though care must be exercised in choosing the most suitable parameters for the axes of the plot. Laboratory testing of materials and simulations of machine contacts are carried out for a number of purposes; at one level for the very practical aims of ranking candidate materials or surface hardening treatments in order of their wear resistance, or in an attempt to predict wear lives under field conditions. More fundamentally, tests may be aimed at elucidating the essential physical mechanisms of surface damage and loss, with the longer term aim of building an analytical and predictive model of the wear process itself. In many cases, component surface damage is brought about by the ingress of hard, particulate matter into machine bearing or sealing clearances. These may be running dry although, more usually, a lubricant or service fluid is present at the interface. A number of standardised wear test geometries and procedures have been established for both two- and three-body wear situations, and these are briefly described. Although abrasive wear is often modelled as following an ‚Archard’︁ equation (i.e. a linear increase in material loss with both load and time, and an inverse dependence on specimen hardness) both industrial experience and laboratory tests of particularly lubricated contacts show that this is not always the case: increasing the hardness differential in an abrasively contaminated lubricated pair may not always reduce the rate of damage to the harder surface.     

ANGULAR DISTORTION ALLOWABLE VALUE AND ASSESS METHOD OF WELD ON COKE TOWER

A graph as the new engineering method for estimate the safety of bulging deformation of coke tower is proposed. Through stresses analysis of circumferential weld of coke tower and comparing the stresses produced by pressure with heat stress of steady state, residual stress, bending stress produced by both itself weight and wind loads, it showed that the stresses produced by pressure on the angle distortion are the main factor of equivalent stress of the combined stress. After comparing four kinds of stress controlling conditions, the relation to stress with depth of angular distortion, grade of curvature of angular distortion and half of region of angular distortion has been inferred. Graph of deformation allowable value of coke tower for different condition by angular distortion and half of region of angular distortion has been plotted. The five steps for its engineering use have been explained. The lighter the grade of curvature is, the larger of bulge allowance, may be, and the bigger of depth of angular distortion may pose too. For the coke tower with a popular structure of Dg 5 400 mm×28 mm, the result by graph is nearly more than the result of two formulas formed by other research, the error is less than 7.0%. But, the graph can be easily applied to different size of angular distortion.