齿轮齿条钻机传动机构力学特性研究

发布时间：2018-05-24 14:55

本文选题：齿轮齿条 + 钻机　；参考：《东北石油大学》2015年博士论文

【摘要】：齿轮齿条钻机是一种新型主动加压钻机,与传统钻机相比,不仅钻进速度更快,而且在浅层钻进过程中优势更明显,同时还具有增强定向井、从式井、水平井、侧钻井等特殊井的钻进能力,充分体现了多功能性的特点,在当前国际油气资源开发竞争日趋激烈的形势下,成为各国争相发展的一种高效钻机。然而,作为该钻机最核心部件的齿轮齿条传动机构一般采用超静定的结构布局,长期暴露于十分恶劣的环境中,在钻井作业时,由于不断的升降、启停及各种任务需要,齿轮齿条关键部件承受复杂的时变低速重载作用,同时诸多不确定特殊工况的影响使得齿轮齿条传动机构强度和运动同步平稳性的力学性能要求难以保证,对钻机整体的安全性和工作性能产生制约。因此,本文围绕齿轮齿条钻机传动机构力学特性进行了如下几方面的研究工作：根据钻机传动机构工作要求,按照齿根弯曲疲劳强度进行了齿轮齿条结构参数设计,并利用传统齿轮强度计算公式求得齿根最大弯曲应力与齿面最大接触应力。采用有限元数值方法,建立了齿轮齿条啮合过程的二维有限元接触模型,确定出齿轮齿条各自齿根弯曲应力与齿面接触应力的变化规律,找出了相应的危险啮合位置。综合运用Solidwork建模与ANSYS有限元分析方法,建立了齿轮齿条在不同危险啮合位置时的瞬时静态三维有限元接触模型,分析得到齿轮齿条在相应位置的应力分布情况。通过将有限元计算结果与传统齿轮强度计算结果进行对比,结果表明本文所建立的齿轮齿条接触有限元分析方法是一种更加准确、可靠及方便的齿轮强度计算方法。将齿轮齿条啮合视为弹簧-质量-阻尼系统,同时考虑时变啮合刚度和齿侧间隙误差的影响,利用牛顿第二定律建立了该模型的动力学方程。为了简化分析,先将钻杆以等效刚度、等效阻尼和等效质量进行替代,建立了传动机构系统整体的多刚体动力学模型,并通过拉格朗日方程法得到相应的多刚体动力学方程。为了考虑实际柔性钻杆弹性变形的影响,利用多体动力学理论,建立了传动机构分别考虑钻杆纵向振动和横向振动时的刚柔耦合动力学模型,并给出了相应模态空间变换下的解析求解过程。综合应用ADAMS多刚体建模与ANSYS柔性体建模方法,在上述两种理论模型的基础上分别建立了相应的传动机构多刚体动力学仿真模型与刚柔耦合动力学仿真模型。针对正常工况(如不同升降状态、不同末端负载及不同提升速度等)和特殊工况(如考虑钻杆纵向振动、钻杆横向振动、单个齿轮失效、对称位置齿轮失效和非对称位置齿轮失效等),进行了两种仿真模型下各因素对齿轮啮合力曲线的影响规律对比分析研究。结果表明不同特殊工况对传动机构载荷分配的均匀性与运动同步的平稳性有着显著的差别,同时说明了本文建立的刚柔耦合动力学模型能够更加准确地揭示传动机构实际动力学特性,为研究齿轮齿条钻机传动机构力学特性提供了有效依据。在原钻机模型方案的基础上,通过相似理论方法,按照几何相似比为0.1研制了一套齿轮齿条钻机模型试验台。针对钻机各工况下不同升降状态、末端负载、齿轮马达流量、钻杆振动及齿轮马达失效等因素的影响,采用正交试验法开展了齿轮齿条传动机构应力测量和振动测量试验研究。将实验测量结果与仿真分析结果进行对比,并对试验误差及其成因进行了分析。结果表明应力测量试验与振动测量试验结论具有良好的一致性,进一步验证了上述传动机构动力学理论模型与仿真模型的有效性。
[Abstract]:The gear rack drilling rig is a new type of active pressure drilling rig. Compared with the traditional drill, it not only has faster drilling speed, but also has more obvious advantages in the process of shallow drilling. It also has the drilling ability of special wells, such as directional well, from type well, horizontal well and side drilling, fully embodies the characteristics of multi-function, and in the current international oil and gas resources. However, the gear rack drive mechanism, which is the core part of the drilling machine, generally uses a statically indeterminate structure layout, and is exposed to a very bad environment for a long time. In the drilling operation, due to continuous lifting, starting and stopping, and various tasks, the gear is required. The key parts of the rack are subjected to complex time-varying low speed heavy load. At the same time, the influence of many uncertain special conditions makes the mechanical properties of the gear rack drive mechanism strength and motion synchronous stability difficult to guarantee, and restrict the safety and performance of the drill. Therefore, this paper revolves around the gear rack drilling machine transmission mechanism. The mechanical characteristics are studied in the following aspects: according to the working requirements of the drilling machine, the structure parameters of the gear rack are designed according to the bending fatigue strength of the tooth root, and the maximum bending stress of the tooth root and the maximum contact stress of the tooth surface are obtained by the formula of the traditional gear strength calculation. The two dimensional finite element contact model of the gear tooth meshing process is used to determine the change law of the bending stress and the contact stress of the tooth root of the gear rack, and find out the corresponding dangerous meshing position. The instantaneous static three of the gear rack in different dangerous meshing positions is established by using the Solidwork modeling and the ANSYS finite element method. The stress distribution of the gear rack in the corresponding position is analyzed by the dimensional finite element contact model. The results of the finite element calculation are compared with the traditional gear strength calculation results. The results show that the finite element method for gear rack contact finite element analysis established in this paper is a more accurate, reliable and convenient method for calculating gear strength. The gear and rack meshing is regarded as a spring mass damping system, and the dynamic equation of the model is established by Newton's second law. In order to simplify the analysis, the drill rod is replaced by equivalent stiffness, equivalent damping and equivalent mass, and the whole system of transmission mechanism is established. In order to consider the effect of elastic deformation of practical flexible drill rod, the dynamic model of rigid body dynamics is obtained by the Lagrange equation method. In order to consider the effect of the elastic deformation of practical flexible drill rod, the rigid flexible coupling dynamic model of the transmission mechanism considering the longitudinal and transverse vibration of the drill rod is established by using the multi body dynamics theory, and the corresponding modal space is given. The ADAMS multi rigid body modeling and ANSYS flexible body modeling method are applied synthetically. On the basis of the above two theoretical models, the corresponding multi rigid body dynamics simulation model and rigid flexible coupling dynamic simulation model are established respectively. And the different lifting speeds and special conditions (such as the longitudinal vibration of the drill rod, the lateral vibration of the drill rod, the failure of single gear, the failure of symmetrical position gear and the unsymmetrical position gear, etc.), the influence rules of the two simulation models on the gear meshing force curve are compared and analyzed. The results show that the transmission of different special conditions is on the transmission. There is a significant difference between the uniformity of the load distribution of the motive force and the stability of the motion synchronization. At the same time, the rigid flexible coupling dynamic model established in this paper can reveal the actual dynamic characteristics of the transmission mechanism more accurately, and provide an effective basis for the study of the mechanical characteristics of the gear rack drill mechanism. On the basis of the similarity theory method, a gear rack rig model test rig is developed according to the geometric similarity ratio 0.1. The gear rack transmission mechanism should be carried out by orthogonal test in view of the influence of different elevations, the load of the end, the flow of the gear motor, the vibration of the drill rod and the failure of the gear motor, according to the geometric similarity ratio. The experimental results are compared with the results of the simulation analysis, and the test errors and their causes are analyzed. The results show that the stress measurement test is in good agreement with the conclusions of the vibration measurement test, and further validates the theoretical and simulation models of the above transmission mechanism. Efficiency.
【学位授予单位】：东北石油大学
【学位级别】：博士
【学位授予年份】：2015
【分类号】：TE922

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