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AMT
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AMT汽车变速器设计,AMT,汽车,变速器,设计
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河南理工大学万方科技学院本科毕业设计（论文）开题报告题目名称AMT汽车变速器设计学生姓名庞振超专业班级08机制4班学号0828050041一选题的目的和意义：AMT用先进的电子技术改造传统的手动变速器,既保留了原手动变速器齿轮传动的效率高、成本低、结构简单、易制造的长处，且具有液力自动变速器自动变速的优点。并且弥补了手动变速器不足（换挡冲击.熄火.换挡复杂驾驶疲劳等缺点），它以特有的经济、方便、安全、舒适性而备受驾驶者的欢迎,成为汽车变速器研究的热点之一，是一款非常适合我国国情的机电液一体化自动变速器，且具有很高的性价比。同时，易于驾驶、省油和降低排放的因素促进了AMT变速器在车辆上的应用，拥挤的交通、非专业驾驶员对“驾驶员友好”型设备的需求等使AMT变速器具有广阔的发展前景。AMT 实际上是由一个机器人系统来完成纵离合器和选档两个动作，其核心技术是控制。驾驶员通过加速踏板和操纵杆向电子控制单元（ECU）传递控制信号；电子控制单元采集发动机转速传感器、车速传感器等信号，时刻掌握着车辆的行驶状态；电子控制单元（ECU）根据这些信号按存储于其中的最佳程序，最佳换档规律、离合器模糊控制规律、发动机供油自适应调节规律等，对发动机供油、离合器的分离与结合、变速器换档三者的动作与时序实现最佳匹配。从而获得优良的燃油经济性和动力性，实现平稳起步和迅速换档，以达到驾驶员所期望的结果。通常AMT包括以下三个部分：1、执行机构：包括电动机（步进电动机和直流电动机）、电磁阀（普通电磁阀和高速 电磁阀）、液压缸（离合器作动缸和选、换档油缸）等；2、传感器：包括速度传感器 (发动机转速传感器、输入轴转速传感器、车速传感器)；油门开度传感器、档位传感器等；3、电控单元（ECU）：包括 CPU、ROM、RAM、I/ O 接口等。将自动变速控制系统中要直接控制的对象：油门、离合器以及选换档装置的动作采取电动机带动的方式。相对于电控液动AMT而言，电控电动AMT在以下几个方面具有进一步的优势：取消了液压系统，从而使整个控制系统的结构更加简单，重量更轻。由于直接采用易于控制、精度更高的电动机取代液压执行元件，减少了液压元件动作的误差，使得系统的控制方法简单，控制精度进一步提高，反应动作更加准确。在原有的电控液动的基础上，只须对软件和硬件以及控制方法上作少许的改动就能对电控电动AMT系统进行控制。在电控电动AMT中的执行电动机的特点是：可控性好、精度高、反应快、可靠性强、并且对环境的适应性好。电控电动AMT主要是电控离合器、电控发动机和电控选换档三大部分。电子控制单元（ECU）根车辆行驶工况（车速、加速度、档位）和驾驶员的驾驶意图（加速踏板、换档控制杆）按照设定的换档规律，选择合适的档位和换档时机，控制换档执行机构模拟熟练驾驶员的换档动作（包括对离合器、变速箱和发动机的联合控制）进行选档和换档。当然，全电式AMT的这些动作是靠电动机的旋转而实现的。换档系统的能源是整个控制系统各机构的动力源。三种形式的选换档系统都需要控制电路所需的直流电流，但执行机构的动力源不同。全电式选换档系统采用电动机（直流电动机、步进电动机）作为动力源；自动换档系统的自调性能很重要，但还必须同时配有相适应的它调系统，才称得上是最理想的控制系统。它调是为驾驶员提供干预自动换档系统的可能性。换档范围选择的作用是限制自动换档的排档范围。三种选换档形式的AMT均可使用旋钮或控制杆作为档位指示器。自动换档是按控制参数的变化才实现换档的，故必须有反映该参数的信号发生系统。车辆的控制参数有三类：单参数多为车速；两参数多为车速和发动机油门开度；三参数为车速、发动机油门开度和加速度。动态三参数控制是最理想的控制。测车速用电磁转速传感器，油门开度用油门电位器测量。测加速度用加速度传感器。换档控制器接受换档范围与换档规律选择机构和控制参数信号发生器传来的信号，进行比较和处理，并按照预定的换档规律选择档位和换档时刻，同时发出相应的换档指令给换档执行机构进行选换档，是系统的核心部分，在全电式AMT中主要是电子控制单元ECU和电动机的驱动电路。换档执行机构接受换档控制器的指令，完成变速器中档位的变换。包括选档和换档两部分。换档品质控制机构的作用是控制换档过程平稳、无冲击，防止产生大的动载荷。电控电动系统主要是增加档位传感器检测换档行程，由ECU控制选换档动作，从而减少同步器超越和换档冲击，提高换档品质。全电式AMT具有价格低、结构简单、性能价格比高、生产继承性好等优点；其硬件开发与软件研制对各种车型汽车都适合。我国不仅有自主知识产权，而且在“动态三参数最佳换档规律”、“动态闭环控制技术”、“自适应控制技术”、模糊控制技术”等自动变速理论方面在排在世界前列。由于AMT没有变矩器，因此换档时发动机扭矩变动很容易传给司机。在换档时能控制马达吸收扭矩的变动，就能更平衡地进行变速。使马达通过减速装置与AMT终端传动直接相连的单马达式并行混合系统，避免换挡冲击等等。因而，有针对性地开展高档轿车AMT半自动变速器设计具有重要意义。二国内外研究现状简述：由于汽车自动变速器的广泛应用,对其的研究开发日益重要。为合理、实用的试验项目,目前还有待研究。中国汽车变速器市场正处于快速发展变化的时期。我国的汽车的变速器的质量和性能上和发达国家存在一定的差距，主要原因就是设计手段落后。为改变我国车辆零部件的生产和设计手段的落后状况，缩短新产品的开发周期，提高市场的竞争力，有必要开发一些适合中国国情的汽车零部件的CAD系统，对以开发的系统需进一步提高和完善。2009年汽车变速器行业研究报告，全面总结汽车变速器概况；深入分析了我国汽车变速器行业需求和供给市场态势，分析了行业内国内外品牌竞争格局以及中国主要汽车变速器生产企业经营状况；并对中国汽车变速器产业发展趋势及投资形势进行了预测。是汽车变速器行业相关企业单位和个人等准确了解目前行业市场动态，把握行业发展趋势，制作市场策略的不可多得的决策参考。 三、毕业设计（论文）所采用的研究方法和手段：在文献调研及资料收集的基础上，掌握通用典型结构及工作原理，在此基础上利用机械原理、理论力学及材料力学等所学专业基础知识，进行变速器结构设计与相关的强度计算。利用机械制图的相关知识，以及P to-E CAD等工具完成图纸工作。四、主要参考文献与资料获得情况：1 陈伟;张洪坤;葛安林;电机换挡的结构设计J. 电机, 2008.062 李志强.ATM电控机械式自动变速汽车换挡智能控制D重庆大学, 20033 丁俊,王灵犀. ATM车辆综合性换挡规律的研究J. 沈阳理工大学学报, 2008, (04)4 孟庆勇.电控电动机械式自动变速器无选档换挡系统的研究D吉林大学, 2005 .5 A Research on the Synthetical Shifting Gear Schedule of the AMT Automobiles 5 吉林大学 王望予主编.汽车设计(第四版).北京:机械工业出版社，20046 吉林大学 陈家瑞主编.汽车构造(下册).北京:机械工业出版社，20057 邱宣怀 主编.机械设计.北京：高等教育出版社，1997五、毕业设计（论文）进度安排（按周说明）1.第5-9周（3月214月28日）资料收集、调研，完成开题报告；2、第10周（3月29日4月3日）初步方案设计，草图绘制，必要的初步设计计算；3、第11-12周（4月7日4月23日）完成结构改进设计方案，主要图纸工作和设计计算工作：4、第13-14周（4月24日5月1日）完成正式图纸及设计说明明书撰写工作：6、第15-16周（5月2日5月13日）整理、形成论文正稿，准备答辩。六、指导教师审批意见（对选题的可行性、研究方法、进度安排作出评价，对是否开题作出决定）： 指导教师： （签名）年 月 日 河南理工大学万方科技学院本科毕业设计（论文）中期检查表指导教师： 张跃敏 职称： 副教授 所在院（系）：河南理工大学机械学院 教研室（研究室）： 机械工程基础教学部题 目低速货车变速器设计学生姓名庞振超专业班级08机制4班 学号0828050041一、 选题质量：所选题目低速货车变速器设计，符合机械设计制造及其自动化专业的培养目标，能够充分地体现综合训练要求。题目难度程度和工作量适中，且与现实生活联系紧密，有较大的实用性。此变速器的齿轮都为标准齿轮，档位和传动比与发动机参数匹配，保证了汽车具有有良好的动力性和经济性。该变速器具有操纵简单，方便，传动效率高，制造容易，成本低廉，维修方便的特点，适合低速载货汽车的使用。在日常生活中有很大的使用空间，特别是在路面状况不好的情况下，能显示优势。与农用机械联系紧密，适合配备在农用运输机车上。二、开题报告完成情况：开题报告在选题的目的和意义方面有很强的针对性，国内外研究综述比较详细，并且论述了国内外的发展情况和完成这次毕业设计所用的工具和方法。同时列出了主要参考文献与资料的获得情况，以及按周说明了毕业设计的具体进度安排。三、阶段性成果：经过前期大量收集资料，和认真学习了解变速器相关方面的知识，已经做出了论文的框架。经过详细的计算和验算，论文说明书已经形成初稿。表达变速器的零件图也绘制出来了，正在完成最难的部分，装配图的绘制。自己也是一边学习一边做，感觉确实学到了很多东西，比单纯学一本课程更有收获。四、存在主要问题：论文的说明书只是形成了初稿，里面还有很多的问题和疑惑，还没有通过老师的审查，还有许多需要修改的细节。还有图纸结构方面自己还有很多疑惑，这些都需要进一步学习完善，都需要进一步修改整理。还有对手动变速器有了新的认识，但还有很多更高级的变速器自己还搞不清楚，需要继续学习。五、指导教师对学生在毕业实习中，劳动、学习纪律及毕业设计（论文）进展等方面的评语指导教师： （签名） 年 月 日2河南理工大学万方科技学院本科毕业论文附录外文资料和中文翻译外文资料GEAR AND SHAFT INTRODUCTIONAbstract: The important position of the wheel gear and shaft cant falter in traditional machine and modern machines.The wheel gear and shafts mainly install the direction that delivers the dint at the principal axis box.The passing to process to make them can is divided into many model numbers, useding for many situations respectively.So we must be the multilayers to the understanding of the wheel gear and shaft in many ways .Key words: Wheel gear; ShaftIn the force analysis of spur gears, the forces are assumed to act in a single plane. We shall study gears in which the forces have three dimensions. The reason for this, in the case of helical gears, is that the teeth are not parallel to the axis of rotation. And in the case of bevel gears, the rotational axes are not parallel to each other. There are also other reasons, as we shall learn.Helical gears are used to transmit motion between parallel shafts. The helix angle is the same on each gear, but one gear must have a right-hand helix and the other a left-hand helix. The shape of the tooth is an involute helicoid. If a piece of paper cut in the shape of a parallelogram is wrapped around a cylinder, the angular edge of the paper becomes a helix. If we unwind this paper, each point on the angular edge generates an involute curve. The surface obtained when every point on the edge generates an involute is called an involute helicoid.The initial contact of spur-gear teeth is a line extending all the way across the face of the tooth. The initial contact of helical gear teeth is a point, which changes into a line as the teeth come into more engagement. In spur gears the line of contact is parallel to the axis of the rotation; in helical gears, the line is diagonal across the face of the tooth. It is this gradual of the teeth and the smooth transfer of load from one tooth to another, which give helical gears the ability to transmit heavy loads at high speeds. Helical gears subject the shaft bearings to both radial and thrust loads. When the thrust loads become high or are objectionable for other reasons, it may be desirable to use double helical gears. A double helical gear (herringbone) is equivalent to two helical gears of opposite hand, mounted side by side on the same shaft. They develop opposite thrust reactions and thus cancel out the thrust load. When two or more single helical gears are mounted on the same shaft, the hand of the gears should be selected so as to produce the minimum thrust load.Crossed-helical, or spiral, gears are those in which the shaft centerlines are neither parallel nor intersecting. The teeth of crossed-helical fears have point contact with each other, which changes to line contact as the gears wear in. For this reason they will carry out very small loads and are mainly for instrumental applications, and are definitely not recommended for use in the transmission of power. There is on difference between a crossed helical gear and a helical gear until they are mounted in mesh with each other. They are manufactured in the same way. A pair of meshed crossed helical gears usually have the same hand; that is ,a right-hand driver goes with a right-hand driven. In the design of crossed-helical gears, the minimum sliding velocity is obtained when the helix angle are equal. However, when the helix angle are not equal, the gear with the larger helix angle should be used as the driver if both gears have the same hand. Worm gears are similar to crossed helical gears. The pinion or worm has a small number of teeth, usually one to four, and since they completely wrap around the pitch cylinder they are called threads. Its mating gear is called a worm gear, which is not a true helical gear. A worm and worm gear are used to provide a high angular-velocity reduction between nonintersecting shafts which are usually at right angle. The worm gear is not a helical gear because its face is made concave to fit the curvature of the worm in order to provide line contact instead of point contact. However, a disadvantage of worm gearing is the high sliding velocities across the teeth, the same as with crossed helical gears.Worm gearing are either single or double enveloping. A single-enveloping gearing is one in which the gear wraps around or partially encloses the worm. A gearing in which each element partially encloses the other is, of course, a double-enveloping worm gearing. The important difference between the two is that area contact exists between the teeth of double-enveloping gears while only line contact between those of single-enveloping gears. The worm and worm gear of a set have the same hand of helix as for crossed helical gears, but the helix angles are usually quite different. The helix angle on the worm is generally quite large, and that on the gear very small. Because of this, it is usual to specify the lead angle on the worm, which is the complement of the worm helix angle, and the helix angle on the gear; the two angles are equal for a 90-deg. Shaft angle.When gears are to be used to transmit motion between intersecting shaft, some of bevel gear is required. Although bevel gear are usually made for a shaft angle of 90 deg. They may be produced for almost any shaft angle. The teeth may be cast, milled, or generated. Only the generated teeth may be classed as accurate. In a typical bevel gear mounting, one of the gear is often mounted outboard of the bearing. This means that shaft deflection can be more pronounced and have a greater effect on the contact of teeth. Another difficulty, which occurs in predicting the stress in bevel-gear teeth, is the fact the teeth are tapered. Straight bevel gears are easy to design and simple to manufacture and give very good results in service if they are mounted accurately and positively. As in the case of squr gears, however, they become noisy at higher values of the pitch-line velocity. In these cases it is often good design practice to go to the spiral bevel gear, which is the bevel counterpart of the helical gear. As in the case of helical gears, spiral bevel gears give a much smoother tooth action than straight bevel gears, and hence are useful where high speed are encountered. It is frequently desirable, as in the case of automotive differential applications, to have gearing similar to bevel gears but with the shaft offset. Such gears are called hypoid gears because their pitch surfaces are hyperboloids of revolution. The tooth action between such gears is a combination of rolling and sliding along a straight line and has much in common with that of worm gears.A shaft is a rotating or stationary member, usually of circular cross section, having mounted upon it such elementsas gears, pulleys, flywheels, cranks, sprockets, and other power-transmission elements. Shaft may be subjected to bending, tension, compression, or torsional loads, acting singly or in combination with one another. When they are combined, one may expect to find both static and fatigue strength to be important design considerations, since a single shaft may be subjected to static stresses, completely reversed, and repeated stresses, all acting at the same time.The word “shaft” covers numerous variations, such as axles and spindles. Anaxle is a shaft, wither stationary or rotating, nor subjected to torsion load. A shirt rotating shaft is often called a spindle.When either the lateral or the torsional deflection of a shaft must be held to close limits, the shaft must be sized on the basis of deflection before analyzing the stresses. The reason for this is that, if the shaft is made stiff enough so that the deflection is not too large, it is probable that the resulting stresses will be safe. But by no means should the designer assume that they are safe; it is almost always necessary to calculate them so that he knows they are within acceptable limits. Whenever possible, the power-transmission elements, such as gears or pullets, should be located close to the supporting bearings, This reduces the bending moment, and hence the deflection and bending stress.Although the von Mises-Hencky-Goodman method is difficult to use in design of shaft, it probably comes closest to predicting actual failure. Thus it is a good way of checking a shaft that has already been designed or of discovering why a particular shaft has failed in service. Furthermore, there are a considerable number of shaft-design problems in which the dimension are pretty well limited by other considerations, such as rigidity, and it is only necessary for the designer to discover something about the fillet sizes, heat-treatment, and surface finish and whether or not shot peening is necessary in order to achieve the required life and reliability.Because of the similarity of their functions, clutches and brakes are treated together. In a simplified dynamic representation of a friction clutch, or brake, two inertias I1 and I2 traveling at the respective angular velocities W1 and W2, one of which may be zero in the case of brake, are to be brought to the same speed by engaging the clutch or brake. Slippage occurs because the two elements are running at different speeds and energy is dissipated during actuation, resulting in a temperature rise. In analyzing the performance of these devices we shall be interested in the actuating force, the torque transmitted, the energy loss and the temperature rise. The torque transmitted is related to the actuating force, the coefficient of friction, and the geometry of the clutch or brake. This is problem in static, which will have to be studied separately for eath geometric configuration. However, temperature rise is related to energy loss and can be studied without regard to the type of brake or clutch because the geometry of interest is the heat-dissipating surfaces. The various types of clutches and brakes may be classified as fllows: 1. Rim type with internally expanding shoes2. Rim type with externally contracting shoes3. Band type4. Disk or axial type5. Cone type6. Miscellaneous typeThe analysis of all type of friction clutches and brakes use the same general procedure. The following step are necessary: 1. Assume or determine the distribution of pressure on the frictional surfaces.2. Find a relation between the maximum pressure and the pressure at any point3. Apply the condition of statical equilibrium to find (a) the actuating force, (b) the torque, and (c) the support reactions.Miscellaneous clutches include several types, such as the positive-contact clutches, overload-release clutches, overrunning clutches, magnetic fluid clutches, and others.A positive-contact clutch consists of a shift lever and two jaws. The greatest differences between the various types of positive clutches are concerned with the design of the jaws. To provide a longer period of time for shift action during engagement, the jaws may be ratchet-shaped, or gear-tooth-shaped. Sometimes a great many teeth or jaws are used, and they may be cut either circumferentially, so that they engage by cylindrical mating, or on the faces of the mating elements.Although positive clutches are not used to the extent of the frictional-contact type, they do have important applications where synchronous operation is required.Devices such as linear drives or motor-operated screw drivers must run to definite limit and then come to a stop. An overload-release type of clutch is required for these applications. These clutches are usually spring-loaded so as to release at a predetermined toque. The clicking sound which is heard when the overload point is reached is considered to be a desirable signal.An overrunning clutch or coupling permits the driven member of a machine to “freewheel” or “overrun” because the driver is stopped or because another source of power increase the speed of the driven. This type of clutch usually uses rollers or balls mounted between an outer sleeve and an inner member having flats machined around the periphery. Driving action is obtained by wedging the rollers between the sleeve and the flats. The clutch is therefore equivalent to a pawl and ratchet with an infinite number of teeth. Magnetic fluid clutch or brake is a relatively new development which has two parallel magnetic plates. Between these plates is a lubricated magnetic powder mixture. An electromagnetic coil is inserted somewhere in the magnetic circuit. By varying the excitation to this coil, the shearing strength of the magnetic fluid mixture may be accurately controlled. Thus any condition from a full slip to a frozen lockup may be obtained.中文翻译：齿轮和轴的介绍摘要:在传统机械和现代机械中齿轮和轴的重要地位是不可动摇的。齿轮和轴主要安装在主轴箱来传递力的方向。通过加工制造它们可以分为许多的型号，分别用于许多的场合。所以我们对齿轮和轴的了解和认识必须是多层次多方位的。关键词: 齿轮； 轴在直齿圆柱齿轮的受力分析中，是假定各力作用在单一平面的。我们将研究作用力具有三维坐标的齿轮。因此，在斜齿轮的情况下，其齿向是不平行于回转轴线的。而在锥齿轮的情况中各回转轴线互相不平行。像我们要讨论的那样，尚有其他道理需要学习，掌握。斜齿轮用于传递平行轴之间的运动。倾斜角度每个齿轮都一样，但一个必须右旋斜齿，而另一个必须是左旋斜齿。齿的形状是一溅开线螺旋面。如果一张被剪成平行四边形（矩形）的纸张包围在齿轮圆柱体上，纸上印出齿的角刃边就变成斜线。如果我展开这张纸，在血角刃边上的每一个点就发生一渐开线曲线。直齿圆柱齿轮轮齿的初始接触处是跨过整个齿面而伸展开来的线。斜齿轮轮齿的初始接触是一点，当齿进入更多的啮合时，它就变成线。在直齿圆柱齿轮中，接触是平行于回转轴线的。在斜齿轮中，该先是跨过齿面的对角线。它是齿轮逐渐进行啮合并平稳的从一个齿到另一个齿传递运动，那样就使斜齿轮具有高速重载下平稳传递运动的能力。斜齿轮使轴的轴承承受径向和轴向力。当轴向推力变的大了或由于别的原因而产生某些影响时，那就可以使用人字齿轮。双斜齿轮（人字齿轮）是与反向的并排地装在同一轴上的两个斜齿轮等效。他们产生相反的轴向推力作用，这样就消除了轴向推力。当两个或更多个单向齿斜齿轮被在同一轴上时，齿轮的齿向应作选择，以便产生最小的轴向推力。交错轴斜齿轮或螺旋齿轮，他们是轴中心线既不相交也不平行。交错轴斜齿轮的齿彼此之间发生点接触，它随着齿轮的磨合而变成线接触。因此他们只能传递小的载荷和主要用于仪器设备中，而且肯定不能推荐在动力传动中使用。交错轴斜齿轮与斜齿轮之间在被安装后互相捏合之前是没有任何区别的。它们是以同样的方法进行制造。一对相啮合的交错轴斜齿轮通常具有同样的齿向，即左旋主动齿轮跟右旋从动齿轮相啮合。在交错轴斜齿设计中，当该齿的斜角相等时所产生滑移速度最小。然而当该齿的斜角不相等时，如果两个齿轮具有相同齿向的话，大斜角齿轮应用作主动齿轮。蜗轮与交错轴斜齿轮相似。小齿轮即蜗杆具有较小的齿数，通常是一到四齿，由于它们完全缠绕在节圆柱上，因此它们被称为螺纹齿。与其相配的齿轮叫做蜗轮，蜗轮不是真正的斜齿轮。蜗杆和蜗轮通常是用于向垂直相交轴之间的传动提供大的角速度减速比。蜗轮不是斜齿轮，因为其齿顶面做成中凹形状以适配蜗杆曲率，目的是要形成线接触而不是点接触。然而蜗杆蜗轮传动机构中存在齿间有较大滑移速度的缺点，正像交错轴斜齿轮那样。 蜗杆蜗轮机构有单包围和双包围机构。单包围机构就是蜗轮包裹着蜗杆的一种机构。当然，如果每个构件各自局部地包围着对方的蜗轮机构就是双包围蜗轮蜗杆机构。着两者之间的重要区别是，在双包围蜗轮组的轮齿间有面接触，而在单包围的蜗轮组的轮齿间有线接触。一个装置中的蜗杆和蜗轮正像交错轴斜齿轮那样具有相同的齿向，但是其斜齿齿角的角度是极不相同的。蜗杆上的齿斜角度通常很大，而蜗轮上的则极小，因此习惯常规定蜗杆的导角，那就是蜗杆齿斜角的余角；也规定了蜗轮上的齿斜角，该两角之和就等于90度的轴线交角。当齿轮要用来传递相交轴之间的运动时，就需要某种形式的锥齿轮。虽然锥齿轮通常制造成能构成90度轴交角，但它们也可产生任何角度的轴交角。轮齿可以铸出，铣制或滚切加工
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