【作者】 贺元成；

【导师】 程维明；

【作者基本信息】 上海大学 ， 机械电子工程， 2009， 博士

【摘要】 在冶金、建材、化工等行业,由于工艺的需要,存在一些重型的回转设备,如烧结机、氧气转炉、回转窑等。重载低速传动系统在这些重型设备的运行中占据着重要的地位,国外从20世纪50年代开始研制应用柔性传动技术,发展很快。我国从70年代后期起逐步研制多柔传动装置,并引进了不少该类成套设备。本文致力于重载低速传动末级小齿轮自调位装置的研究,对多柔传动和自调位小齿轮传动的结构、理论及设计进行研究,为我国在该领域的发展和应用提供技术参考。本文通过对BF型、BFP型及BFT型多柔传动的机理及优缺点进行分析,结合BF型、BFP型的特点,重点介绍了创新设计的双轨道型、双点啮合单驱动BF型多柔传动装置及特点。由于BF型(含特殊BF型)、BFP型传动共有的弊端是其滚轮必须承受一定的轮压,以此保证大小齿轮的正常中心距并稳定运行,而该轮压必然导致轮与轨的磨损,在实际运行中不但滚轮更换较频繁,也降低了大齿轮的使用寿命。双轨道型多柔传动装置的成功研制,使其在单点啮合条件下滚轮与轨道间轮压在理论上可为零并具多项功能,较好地解决了这一问题。该新型传动在任一啮合点,即在单点啮合条件下的运转功能不是单一的,而是具有BOGILEX?传动全部运转功能,且按BF及BFP方式运转时轮压可很小。双点啮合单驱动BF型多柔传动装置,通过在悬挂小车内设置两个小齿轮共同来驱动一个大齿轮,使其承载能力提高一倍。对某企业Ф3200煅烧炉末级传动装置出现了末级小齿轮过度磨损,使得小齿轮使用寿命大大缩短这一情况,本文提出了采用末级传动改造为自调位小齿轮装置形式,以解决末级传动啮合不良的问题。由于自调位小齿轮传动装置的最大特点是利用鼓形齿来传递动力和自调位偏转,通过对其传动机理、结构及受力状况的分析,在消化DMGH传动的基础上,根据煅烧炉末级传动的要求,创新设计了三种自调位小齿轮结构型式方案,并给出了具体改造设计方案及鼓形齿轮的结构设计。为了对自调位小齿轮装置鼓形齿轮传动系统的动力学特性进行研究,研制了重载低速传动末级自调位小齿轮实验装置,并投入实验使用。针对现行的BFT型多柔传动理论计算公式存在的问题,本文通过建立新的坐标体系,对BFT型多柔传动末级不均载的三种情况进行力学分析,解决了各种不均载条件下的精确理论计算问题,得出了在全均载及其他不同程度均载条件下的精确理论计算公式,并根据这些公式可以方便工程计算。同时,提出了确定最佳结构参数的两种方法,并通过实例进行了验证。一种是试凑法,可以快速地找出比较合适的结构参数,也为其他型式的多柔传动设计提供了类似的解决方案。第二种优化设计法,通过优化设计实现了多柔传动装置的结构优化、参数优化。由于自调位小齿轮装置的应用在国外也是最近几年,其设计、制造方法属于专利范围,未见有公开资料。本文通过对自调位小齿轮装置的受力进行分析,给出了装置的核心零件鼓形齿的设计方法,并应用所给出的方法设计了自调位小齿轮实验装置。根据所设计的参数和结构,成功制造出了自调位小齿轮装置样机进行实验,为装置及系列装置的设计提供了依据。为了便于分析自调位小齿轮装置中鼓形齿齿向位移、棱边卡死现象及说明某一轮齿所处周向位置,本文参考鼓形齿联轴器的啮合分析,把鼓形齿内、外齿面的运动简化为展开的平面运动。先建立鼓形齿齿面方程,根据非共轭齿面的啮合条件,得到一系列非线性方程组,再运用MATALAB优化求解啮合点的数值解,最后得出内外齿啮合运动的规律。本文通过对鼓形齿与小齿轮上内齿轮的配合分析和自调位小齿轮装置机构偏载分析,引入柔性多体动力学理论,建立了自调位小齿轮系统柔性多体系统动力学模型。由于本传动的小齿轮自调位机构为一可自适应转动的柔性部件,首先建立该传动机构的多刚体动力学模型,并在该模型基础上进行了运动传递分析,然后在其基础上再引入柔性多体系统的动力学模型。最后在实验的基础上,对自调位小齿轮装置扭矩波动的振动性质进行了分析,给出了不同挠性转角情况下的扭矩与应力关系。更多还原

【Abstract】 With the needs of technology, in metallurgy, building materials and chemical industries etc, there are some heavy-duty rotating equipment, such as sintering machine, oxygen converters and rotary device etc. Heavy-load low-speed driving system occupies an important position in the heavy–duty operation. From 1950s in the 20th century, foreign countries started to develop the application of flexible-transmission technology. In the late of 1970s, China gradually developed the multi-channel engaging device, and introduced a number of such complete sets of equipment. This paper dedicates to research on last-stage pinion device with self-aligning in heavy-load low-speed driving and study on its structure, theory and design of multi-channel engaging and self-aligning pinion in order to provide our country the technical references for the development and application in this field.Based on analysis of the mechanism, advantages and disadvantages of BF-type, BFP-type, and BFT-type, multi-channel engaging, combining the features of BF-type, and BFP-type,, the paper introduces the innovative design of the dual-track type, dual-point meshing with single-drive BF multi-channel engaging device and its features.Because the common malpractice of BF-type (including particular BF type), BFP-type transmission is that the rotating wheel must endure a certain degree of the wheel-pressure in order to maintain the distance between centers of big and small gears and operate stably, as a result that the wheel-pressure will inevitably cause the abrasion between the wheel and track, in actual operation, not only will the wheel has more frequent replacement, but also the gear will reduce its service life.The successful development of double-track flexible driving with multi-channel engaging makes it possible that the wheel-pressure can be zero in theory with lots of functions between the rotating-wheel and track in the condition of the single-point meshing. The operation function of this new transmission device is not single but contains all functions of BOGILEX transmission in any single meshing point, also when it operates in BF and BFP way, the wheel-pressure is likely to be lower. The dual-point meshing in single-drive BF flexible-transmission device will promote its bearing capacity by two small pinions which are setting in a small slung trolley to driving big one altogether.To aim at the last-stage pinion excessive wear, which causes the reduction of its service time in the last-stage transmission device inф3200 incinerator in an enterprise, the paper suggests a kind of device changing the last-stage transmission into the self-aligning engaging so as to solve bad meshing problem in the last-stage transmission.Due to the most prominent feature of self-aligning engaging device is to transfer engine power by drum-shape gear and self-aligning defluxion, This paper analyzes its transmission mechanism, structure and stress distribution based on the understanding of DMGH transmission theory; and according to the requirements of the last-stage transmission in incinerator, creatively designs 3 different types for self-aligning pinion structures, demonstrates the detail reforming proposals and drum-shape pinion structure design. Also, in order to make deeper research on dynamics of drum-shape gear transmission system of self-aligning pinion device, this paper presents the last-stage self-aligning pinion experimental device in heavy-load and low-speed transmission and puts it into experimental use.Directed towards the current exist problems for calculating formula in BFT flexible-driving theory, the paper establishes the new coordinate system; makes 3 different dynamic analysis of BFT flexible-driving in the last-stage uneven loading; solves the issue of the precise theoretical calculation in all kinds of uneven loading condition so that the precise theoretical calculating formula is obtained in the condition of the whole and uneven degree loading, and makes convenient project calculation with these formula.Meanwhile, the paper proposes 2 ways to determine the optimum structure parameters and verifies by examples that the one is Attempting Method, which can identify the more suitable parameters quickly and provide the similar solution to the other pattern flexible-driving design; the second is Optimizing Design Method, which can optimize structure and parameters for the flexible-driving device.Since the self-aligning pinion device has been applied in recent years in foreign countries and its design and manufacturing methods belong to the scope of patents, there is no any public information. The paper demonstrates the design method for the nucleus part, drum-shape gear based on the stress distribution analysis of the self-aligning pinion device and uses the method to design a self-aligning pinion experimental device according to the parameters and structures, successfully makes experiments with a prototype of self-aligning pinion to provide a basis for the device and series of devices.For the easy analyzing the tooth displacement and seamed-edge block phenomenon in drum-shape pinion in self-aligning pinion device and explaining a tooth circumferential position, the paper consults in the meshing analysis of the shift jointer of the drum-shape gear, simplifies the inner and outer movement of the drum-shape pinion to an unfolded planar motion; firstly, the paper sets equations for its tooth surface according to non-conjugating tooth meshing condition so as to obtain a series of nonlinear equations; then, uses MATALAB optimization to solve the numerical value of the meshing points coming to the conclusion for both inner and outer tooth meshing movement disciplines.Based on the co-analysis between the drum-shape pinion and inner gear on the pinion, and the bias loading analysis for the self-aligning pinion device structure, the paper introduces the flexible-multi-body dynamics theory, establishes a dynamics model for self-aligning pinion system, the flexible-multi body system. Since this self-aligning device in this transmission belongs to a self-adaptive rotating flexible component, we need to set up the multi-rigid dynamics model and to analyze its movement transmission based on this model, then, to introduce dynamics model of the flexible-multi-body system; at last, to identify the vibration characteristic of the torque fluctuations in self-aligning pinion device resulting in the relations between the torque and the stress in different slight deformed angles.更多还原