CA6150型卧式车床进给箱设计

合集下载

机械机床毕业设计16CA6150数控车床主轴箱及传动系统系统的设计业设计

机械机床毕业设计16CA6150数控车床主轴箱及传动系统系统的设计业设计一、设计背景目前，数控车床是机械加工行业中常用的一种设备。

其主要作用是通过数控系统控制刀具的运动轨迹，对工件进行加工。

本设计的目标是设计一个适用于16CA6150数控车床的主轴箱及传动系统，以提高车床的加工准确性和效率。

二、设计要求1.主轴箱及传动系统要具备足够的刚性和稳定性，以确保整个车床在工作过程中不发生振动和变形；2.主轴箱传动系统的设计应使得主轴的旋转速度能够达到要求，并且有一定的速度范围可调；3.主轴箱传动系统的设计应保证传动效率高，噪音低，并且易于维护和保养；4.主轴箱和传动系统的设计应满足机械加工的要求，对于各个工件的加工均能保证高精度和高质量。

三、主轴箱设计主轴箱是数控车床中的核心部件，其作用是连接主轴和机床床身，并提供主轴的旋转运动。

为了保证主轴和工件的高精度加工，主轴箱设计应满足以下要求：1.主轴箱整体结构应具备足够的刚性和稳定性；2.主轴箱应具备一定的自冷却和监测功能，以保证主轴的温度和振动处于合理范围内；3.主轴箱应具备一定的调节装置，方便对主轴进行润滑和保养。

四、传动系统设计传动系统是主轴箱的重要组成部分，其作用是将动力传递给主轴，使得主轴能够旋转。

在设计传动系统时，应满足以下要求：1.传动系统应选择合适的传动方式，如齿轮传动、带传动等；2.传动系统的设计应保证传动效率高、噪音低，且易于维护和保养；3.传动系统应满足主轴旋转速度的要求，并具备一定的速度调节范围；4.传动系统应具备自动化控制功能，以便实现数控车床的自动操作。

五、总结本设计对16CA6150数控车床的主轴箱及传动系统进行了设计，并提出了相应的要求。

在设计主轴箱和传动系统时，应注重刚性和稳定性的提升，以及传动效率的提高。

同时，还应考虑主轴箱的自冷却和监测功能，以及传动系统的自动化控制功能。

通过合理设计和选用适当的材料和部件，可以提高数控车床的加工准确性和效率，满足机械加工的要求。

CM6150车床进给箱的三维设计

CM6150车床进给箱的三维设计[摘要]目前，机床对国家工业发展的影响越来越大，而我国在机床研究开发等方面与发达国家相比还有很大的差距。

同时，机床又是机械加工的工作母机，而进给箱是其重要组成部分之一。

所以提高其精度，对机床整体的加工精度提高有着重要意义。

本文应用pro/E三维建模的方法对CM6150型车床的进给箱进行设计，主要是传动系统的设计。

通过本次设计以达到进一步提高其精度并掌握该机床进给箱设计流程的目的。

[关键词]CM6150车床；进给箱；传动系统The Feed Box Design Of CM6150 Horizontal Lathe “Abstract：”At present, the machine tool of the country's industrial development influence more and more big, and our country in such aspects as machine tool research and development and a large gap compared with developed countries. At the same time, it is mechanical processing machine tools, machine tool and feed box is an important part of it. So to improve the precision of machining accuracy of the whole machine has important significance. This paper applied pro/E 3 d modeling method of CM6150 type lathe feed box design, mainly is the transmission system design. Through this design to further improve the accuracy and grasp the purpose of the machine tool feed box design process.“Key words：”CM6150 lathe ,Feed box, The transmission system目录1.绪论 (1)1.1 选题的目的及研究意义 (1)1.2 相关领域的概况 (1)1.2.1 车床现状 (1)1.2.2 我国数控车床技术现状 (2)1.3设计思路及方法 (3)2.CM6150进给箱传动方案设计 (4)2.1 CM6150普通车床简介 (4)2.2 CM6150车床传动系统图 (5)2.3 转速图......................................................................................................... 错误！未定义书签。

CA6150车床主轴箱设计(有全套图纸)(可编辑)

CA6150车床主轴箱设计(有全套图纸)全套图纸或资料,联系q 174320523目录概述主运动的方案选择与主运动的设计确定齿轮齿数选择电动机皮带轮的设计计算传动装置的运动和运动参数的计算主轴调速系统的选择计算主轴刚度的校核一、概述主传动系统是用来实现机床主运动的传动系统,它应具有一定的转速(速度)和一定的变速范围,以便采用不同材料的刀具,加工不同的材料,不同尺寸,不同要求的工件,并能方便的实现运动的开停,变速,换向和制动等。

数控机床主传动系统主要包括电动机、传动系统和主轴部件,它与普通机床的主传动系统相比在结构上比较简单,这是因为变速功能全部或大部分由主轴电动机的无级调速来承担,剩去了复杂的齿轮变速机构,有些只有二级或三级齿轮变速系统用以扩大电动机无级调速的范围。

1.1数控机床主传动系统的特点与普通机床比较,数控机床主传动系统具有下列特点。

转速高、功率大。

它能使数控机床进行大功率切削和高速切削,实现高效率加工。

变速范围宽。

数控机床的主传动系统有较宽的调速范围,一般Ra100,以保证加工时能选用合理的切削用量,从而获得最佳的生产率、加工精度和表面质量。

主轴变速迅速可靠,数控机床的变速是按照控制指令自动进行的,因此变速机构必须适应自动操作的要求。

由于直流和交流主轴电动机的调速系统日趋完善,所以不仅能够方便地实现宽范围无级变速,而且减少了中间传递环节,提高了变速控制的可靠性。

主轴组件的耐磨性高,使传动系统具有良好的精度保持性。

凡有机械摩擦的部位,如轴承、锥孔等都有足够的硬度,轴承处还有良好的润滑。

1.2 主传动系统的设计要求①主轴具有一定的转速和足够的转速范围、转速级数,能够实现运动的开停、变速、换向和制动,以满足机床的运动要求。

②主电机具有足够的功率,全部机构和元件具有足够的强度和刚度,以满足机床的动力要求。

③主传动的有关结构,特别是主轴组件要有足够高的精度、抗震性,热变形和噪声要小,传动效率高,以满足机床的工作性能要求。

C6150车床主轴箱箱体加工工艺及工装夹具设计

C6150车床主轴箱箱体加工工艺及工装夹具设计1.C6150车床主轴箱箱体加工工艺主轴箱箱体一般由铸铁材料制成，其加工工艺主要包括以下几个步骤：(1)铸造准备：对铸铁材料进行熔炼、净化和浇铸前的处理，确保铸件质量。

(2)铸件浇铸：将熔化的铸铁材料倒入模具中，使其冷却、凝固成型。

(3)铸件脱模：待铸件冷却后，从模具中取出，进行清理和修整。

(4)精密加工：对铸件进行加工，包括切割、铣削、钻孔等工序，以使得箱体尺寸和形状精确到达要求。

(5)表面处理：对箱体表面进行打磨、抛光，以提高外观质量。

(6)检测和装配：对加工好的主轴箱箱体进行检测，确保质量达到要求，然后进行组装。

在主轴箱箱体的加工过程中，合理设计工装夹具可以提高加工效率和加工质量，减少劳动强度。

(1)定位夹具设计：主要用于确定箱体的位置和角度，以保证加工精度。

定位夹具可以根据箱体形状和尺寸设计，一般采用刚性夹具，如V型块。

(2)夹紧夹具设计：用于夹紧箱体，以防止其在加工过程中发生松动或位移。

夹紧夹具可以采用螺栓和垫圈进行固定，或者采用气动或液压夹紧装置。

(3)切削夹具设计：用于加工箱体的切削过程，包括刀具和刀架的选择和安装。

切削夹具要根据加工要求和箱体材料的切削特性来设计，以保证加工质量和效率。

(4)保护夹具设计：用于保护箱体的外表面和内孔。

保护夹具可以采用橡胶垫和保护套等材料进行设计，以确保箱体不被切削工具碰伤。

(5)检测夹具设计：用于检测箱体的尺寸和形状，以确保其符合加工要求。

检测夹具可以采用测量工具和传感器等设备进行设计，以确保检测的准确性和可靠性。

总之，C6150车床主轴箱箱体加工工艺和工装夹具设计是车床加工中的重要环节，可以通过合理的工艺和夹具设计来提高加工效率和加工质量。

CA6140型车床进给箱设计

摘要CA6140型卧式车床是普通精度级的万能机床，它的特有功能是车削一定范围内的各种螺纹，包括切削公制螺纹、英制螺纹、模数螺纹和径节螺纹的功能，要求进给传动链的变速机构能严格准确地按照标准螺距数列来变化。

CA6140型卧式车床进给箱固定在床身左前面，内有进给运动的变换装置及操纵机构，其功能是改变被加工螺纹的螺距或机动进给的进给量。

变换装置包括移换机构，用来实现倒数关系及特殊因子；基本螺距机构，用来实现车削出导程值按等差数列排列的螺纹；倍增机构，用来实现车削螺纹的导程值成倍数关系变化的螺纹。

当U倍=1时发现一条新的传动链，可以提高部分公制及模数螺纹的切削精度，并使传动路线大大缩短。

关键词：进给箱；变换装置；移换机构；基本螺距机构；倍增机构目录1 绪论-----------------------------------------------------------------12 CA6140进给箱传动方案设计----------------------------------4 2.1 CA6140普通车床简介-------------------------------------------------------------------------4 2.2 进给箱的传动机构-----------------------------------------------------------------------------5 2.3 进给箱切螺纹机构设计----------------------------------------------------------------------8 2.4 切螺纹系统及齿数比的确定---------------------------------------------------------------9 2.5 增倍机构设计以及移换机构设计--------------------------------------------------------102.6 车制螺纹的工作过程-------------------------------------------------------------------------123 主要零件设计-----------------------------------------------------21 3.1 齿式离合器的设计-----------------------------------------------------------------------------21 3.2 各轴及轴上组件的设计验算---------------------------------------------------------------213.2.1 中心距a的确定----------------------------------------------------------------------------223.2.2 XII轴上齿轮的设计验算-----------------------------------------------------------------223.2.3 XIV轴上齿轮的验算----------------------------------------------------------------------253.2.4 XIV轴的设计验算-------------------------------------------------------------------------303.2.5 XV轴上齿轮的设计验算-----------------------------------------------------------------353.2.6 XV轴的设计验算--------------------------------------------------------------------------383.2.7 XVI轴齿轮的设计验算-------------------------------------------------------------------404 双联滑移齿轮进给箱传动系统的研究-----------------------44 4.1 新传动链车公制螺纹-------------------------------------------------------------------------44 4.2 新传动链车模数螺纹-------------------------------------------------------------------------45 4.3 新传动链的特点及适用范围---------------------------------------------------------------46 结论---------------------------------------------------------------------------48致谢---------------------------------------------------------------------------49参考文献---------------------------------------------------------------------501 绪论1、毕业设计的目的及意义毕业设计是本科生教学活动中最后的一个重要环节。

CA6150型卧式车床进给箱设计

床身导轨硬度 RC 52
主轴转速范围（24） r/min 10-1400
进给量范围（标准） mm/r 0.08-1.59
进给量范围（细进给） mm/r 0.028-0.054
进给量范围（加大进给） mm/r 1.71-6.33
加工公制螺纹范围（44种） mm 1-192
加工英制螺纹范围（20种） tpi 24-2
所以研究C6150型车床具有经济，学术的现实意义。通过对C6150型车床的主轴箱的传动设计和制造的设计与分析可以使我们对大学四年所学的课程进行一次较好的巩固和提升。
1.6
C6150型卧式车床主要有主传动链和进给传动链两部分，电动机经主换向机构，主变速机构拖动主轴。主换向机构主要用于切削螺纹时换刀。进给链从主轴开始，经进给换向机构、挂轮和进给箱内的进给变换机构、转换机构——光杠（普通车床）、溜板箱内的转换机构传至刀架；或经丝杠（车螺纹）和溜板箱内的螺母传至刀架，如图1-4所示为传动系统框图。
加工模数螺纹范围（39种） mm 0.25-48
加工径节螺纹范围（37种） DP 96-1
主电机功率 kW 7.5
机床净重 kg 2220
机床轮廓尺寸（长×宽×高） mm 3168×1000×1267
机床包装尺寸（长×宽×高） mm 3300×1260×1760
1.5 主要研究内容
C6150型车床是我国设计制造的普通精度级卧式车床，在我国机械制造类工厂中使用非常广泛。此种卧式车床的工艺范围很广，它能完成多种多样的加工工序：加工各种轴类、套筒类和盘类零件上的回转表面，如车削内外圆柱面、圆锥面、环槽及成型回转面；车削端面及各种常用的螺纹(公制螺纹、英制螺纹、模数制螺纹和径节制螺纹)，还可以进行扩孔、钻孔、铰孔和滚花等工作。

CA6140型卧式车床进给箱设计

工业革命以后，蒸汽机出现，提供了新型巨大的能源，使生产技术发生了革命性的变化。车床也不断的演变，之前的皮带车床由于它的主轴转速低，变速级数少，刚度不高，抗振性差，加工精度低；并且车螺纹和进给使用同一根传动丝杠，丝杠易磨损，影响螺纹加工精度；用塔轮改变传动比，变速费时费力，生产率低。所以被齿轮传动车床所取代。
同时本课题作为毕业设计，可以有效的培养我们独立工作、发现问题和解决问题的能力；能根据设计课题查找有关的资料，了解本课题的前沿和发展方向；树立正确的设计思想，掌握设计的基本方法和步骤，为以后从事设计工作打下良好的基础。
研究本课题主要从其结构和传动原理上进一步了解车床的性能、功能、作用，从实物到装配图的绘制，逐步熟悉车床的加工工艺、结构和原理。如对进给箱中各齿轮相关参数有足够了解。比如着重讨论离合器M3所连接的轴上的一双联滑移齿轮，令此轴名为I轴其左侧齿数Z1=28,右侧齿数Z2=18,模数m=2mm，精度等级均为7级，不进行变位传动，为直齿轮，z1的公法线长度L1=21.449mm,上偏差为—0.09mm,下偏差为—0.13mm,Z2的公法线长度L2=15.265mm,其上偏差为—0.075mm,下偏差为—0.119mm。z1的一转度量距差=0.063mm，Z2的一转度量距差=0.055mm。Z1的齿向公差=0.015mm，Z2的齿向公差=0.005mm。经离合器M3传过的动力经I轴上四个滑移齿轮传至II轴上的八个固定齿轮，组成基本变速组。此齿轮为进给箱中的重要齿轮，故需保证其齿面接触强度和齿根弯曲强度，根据所传动力的大小对其进行校核和验算，从而保证丝杆和光杆的准确运动，以能进行切制螺纹和切削加工。
刀架上最大工作回转直径：210mm。
主轴中心到床身平面导轨距离（中心高）：205mm。
主轴转速：正转24级 10~1400转/分。

CA6140车床进给箱设计译文

译文学院：机械工程学院专业：机械设计制造及其自动化学号：0545501141姓名：周炜指导教师：李钦奉教授Failure Analysis，Dimensional Determination And Analysis，Applications Of CamsJack BaubleAbstract：It is absolutely essential that a design engineer know how and why parts fail so that reliable machines that require minimum maintenance can be designed；Cams are among the most versatile mechanisms available．A cam is a simple two-member device．The input member is the cam itself，while the output member is called the follower．Through the use of cams，a simple input motion can be modified into almost any conceivable output motion that is desired．Key words:failure high-speed cams design propertiesINTRODUCTIONIt is absolutely essential that a design engineer know how and why parts fail so that reliable machines that require minimum maintenance can be designed．Sometimes a failure can be serious，such as when a tire blows out on an automobile traveling at high speed．On the other hand，a failure may be no more than a nuisance．An example is the loosening of the radiator hose in an automobile cooling system．The consequence of this latter failure is usually the loss of some radiator coolant，a condition that is readily detected and corrected．The type of load a part absorbs is just as significant as the magnitude．Generally speaking，dynamic loads with direction reversals cause greater difficulty than static loads，and therefore，fatigue strength must be considered．Another concern is whether the material is ductile or brittle．For example，brittle materials are considered to be unacceptable where fatigue is involved．Many people mistakingly interpret the word failure to mean the actual breakage of a part．However，a design engineer must consider a broader understanding of what appreciable deformation occurs．A ductile material，however will deform a large amount prior to rupture．Excessive deformation，without fracture，may cause a machine to fail because the deformed part interferes with a moving second part．Therefore，a part fails(even if it has not physically broken)whenever it no longer fulfills its required function．Sometimes failure may be due to abnormal friction or vibration between two mating parts．Failure also may be due to a phenomenon called creep，which is the plastic flow of amaterial under load at elevated temperatures．In addition，the actual shape of a part may be responsible for failure．For example，stress concentrations due to sudden changes in contour must be taken into account．Evaluation of stress considerations is especially important when there are dynamic loads with direction reversals and the material is not very ductile．In general，the design engineer must consider all possible modes of failure，which include the following．——Stress——Deformation——Wear——Corrosion——Vibration——Environmental damage——Loosening of fastening devicesThe part sizes and shapes selected also must take into account many dimensional factors that produce external load effects，such as geometric discontinuities，residual stresses due to forming of desired contours，and the application of interference fit joints．Cams are among the most versatile mechanisms available．A cam is a simple two-member device．The input member is the cam itself，while the output member is called the follower．Through the use of cams，a simple input motion can be modified into almost any conceivable output motion that is desired．Some of the common applications of cams are——Camshaft and distributor shaft of automotive engine——Production machine tools——Automatic record players——Printing machines——Automatic washing machines——Automatic dishwashersThe contour of high-speed cams (cam speed in excess of 1000 rpm) must be determined mathematically．However，the vast majority of cams operate at low speeds(less than 500 rpm) or medium-speed cams can be determined graphically using a large-scale layout．In general，the greater the cam speed and output load，the greater must be the precision with which the cam contour is machined．DESIGN PROPERTIES OF MATERIALSThe following design properties of materials are defined as they relate to the tensile test．Static Strength． The strength of a part is the maximum stress that the part can sustain without losing its ability to perform its required function．Thus the static strength may be considered to be approximately equal to the proportional limit，since no plastic deformation takes place and no damage theoretically is done to the material．Stiffness．Stiffness is the deformation-resisting property of a material．The slope of the modulus line and，hence，the modulus of elasticity are measures of the stiffness of a material．Resilience． Resilience is the property of a material that permits it to absorb energy without permanent deformation．The amount of energy absorbed is represented by the area underneath the stress-strain diagram within the elastic region．Toughness． Resilience and toughness are similar properties．However，toughness is the ability to absorb energy without rupture．Thus toughness is represented by the total area underneath the stress-strain diagram， as depicted in Figure 2．8b．Obviously，the toughness and resilience of brittle materials are very low and are approximately equal．Brittleness． A brittle material is one that ruptures before any appreciable plastic deformation takes place．Brittle materials are generally considered undesirable for machine components because they are unable to yield locally at locations of high stress because of geometric stress raisers such as shoulders，holes，notches，or keyways．Ductility． A ductility material exhibits a large amount of plastic deformation prior to rupture．Ductility is measured by the percent of area and percent elongation of a part loaded to rupture．A 5%elongation at rupture is considered to be the dividing line between ductile and brittle materials．Malleability． Malleability is essentially a measure of the compressive ductility of a material and，as such，is an important characteristic of metals that are to be rolled into sheets．Hardness． The hardness of a material is its ability to resist indentation or scratching．Generally speaking，the harder a material，the more brittle itis and，hence，the less resilient．Also，the ultimate strength of a material is roughly proportional to its hardness．Machinability． Machinability is a measure of the relative ease with which a material can be machined．In general，the harder the material，the more difficult it is to machine．COMPRESSION AND SHEAR STATIC STRENGTHIn addition to the tensile tests，there are other types of static load testing that provide valuable information．Compression Testing． Most ductile materials have approximately the same properties in compression as in tension．The ultimate strength，however，can not be evaluated for compression．As a ductile specimen flows plastically in compression，the material bulges out，but there is no physical rupture as is the case in tension．Therefore，a ductile material fails in compression as a result of deformation，not stress．Shear Testing． Shafts，bolts，rivets，and welds are located in such a way that shear stresses are produced．A plot of the tensile test．The ultimate shearing strength is defined as the stress at which failure occurs．The ultimate strength in shear，however，does not equal the ultimate strength in tension．For example，in the case of steel，the ultimate shear strength is approximately 75% of the ultimate strength in tension．This difference must be taken into account when shear stresses are encountered in machine components．DYNAMIC LOADSAn applied force that does not vary in any manner is called a static or steady load．It is also common practice to consider applied forces that seldom vary to be static loads．The force that is gradually applied during a tensile test is therefore a static load．On the other hand，forces that vary frequently in magnitude and direction are called dynamic loads．Dynamic loads can be subdivided to the following three categories．Varying Load．With varying loads，the magnitude changes，but the direction does not．For example，the load may produce high and low tensile stresses but no compressive stresses．Reversing Load．In this case，both the magnitude and direction change．These load reversals produce alternately varying tensile and compressive stresses that are commonly referred to as stress reversals．Shock Load．This type of load is due to impact．One example is an elevator dropping on a nest of springs at the bottom of a chute．The resulting maximum spring force can be many times greater than the weight of the elevator，The same type of shock load occurs in automobile springs when a tire hits a bump or hole in the road．FATIGUE FAILURE-THE ENDURANCE LIMIT DIAGRAMThe test specimen in Figure 2.10a．，after a given number of stress reversals will experience a crack at the outer surface where the stress is greatest．The initial crack starts where the stress exceeds the strength of the grain on which it acts．This is usually where there is a small surface defect，such as a material flaw or a tiny scratch．As the number of cycles increases，the initial crack begins to propagate into a continuous series of cracks all around the periphery of the shaft．The conception of the initial crack is itself a stress concentration that accelerates the crack propagation phenomenon．Once the entire periphery becomes cracked，the cracks start to move toward the center of the shaft．Finally，when the remaining solid inner area becomes small enough，the stress exceeds the ultimate strength and the shaft suddenly breaks．Inspection of the break reveals a very interesting pattern，as shown in Figure 2.13．The outer annular area is relatively smooth because mating cracked surfaces had rubbed against each other．However，the center portion is rough，indicating a sudden rupture similar to that experienced with the fracture of brittle materials．This brings out an interesting fact．When actual machine parts fail as a result of static loads，they normally deform appreciably because of the ductility of the material.Thus many static failures can be avoided by making frequent visual observations and replacing all deformed parts．However，fatigue failures give to warning．Fatigue fail mated that over 90% of broken automobile parts have failed through fatigue．The fatigue strength of a material is its ability to resist the propagation of cracks under stress reversals．Endurance limit is a parameter used to measurethe fatigue strength of a material．By definition，the endurance limit is the stress value below which an infinite number of cycles will not cause failure．Let us return our attention to the fatigue testing machine in Figure 2.9．The test is run as follows：A small weight is inserted and the motor is turned on．At failure of the test specimen，the counter registers the number of cycles N，and the corresponding maximum bending stress is calculated from Equation 2.5．The broken specimen is then replaced by an identical one，and an additional weight is inserted to increase the load．A new value of stress is calculated，and the procedure is repeated until failure requires only one complete cycle．A plot is then made of stress versus number of cycles to failure．Figure 2.14a shows the plot，which is called the endurance limit or S-N curve．Since it would take forever to achieve an infinite number of cycles，1 million cycles is used as a reference．Hence the endurance limit can be found from Figure 2.14a by noting that it is the stress level below which the material can sustain 1 million cycles without failure．The relationship depicted in Figure 2.14 is typical for steel，because the curve becomes horizontal as N approaches a very large number．Thus the endurance limit equals the stress level where the curve approaches a horizontal tangent．Owing to the large number of cycles involved，N is usually plotted on a logarithmic scale，as shown in Figure 2.14b．When this is done，the endurance limit value can be readily detected by the horizontal straight line．For steel，the endurance limit equals approximately 50% of the ultimate strength．However，if the surface finish is not of polished equality，the value of the endurance limit will be lower．For example，for steel parts with a machined surface finish of 63 microinches ，the percentage drops to about 40%．For rough surfaces，the percentage may be as low as 25%．The most common type of fatigue is that due to bending．The next most frequent is torsion failure，whereas fatigue due to axial loads occurs very seldom．Spring materials are usually tested by applying variable shear stresses that alternate from zero to a maximum value，simulating the actual stress patterns．In the case of some nonferrous metals，the fatigue curve does not level off as the number of cycles becomes very large．This continuing toward zero stress means that a large number of stress reversals will cause failure regardless of how small the value of stress is．Such a material is said to have no endurancelimit．For most nonferrous metals having an endurance limit，the value is about 25% of the ultimate strength．EFFECTS OF TEMPERATURE ON YIELD STRENGTH AND MODULUS OF ELASTICITY Generally speaking，when stating that a material possesses specified values of properties such as modulus of elasticity and yield strength，it is implied that these values exist at room temperature．At low or elevated temperatures，the properties of materials may be drastically different．For example，many metals are more brittle at low temperatures．In addition，the modulus of elasticity and yield strength deteriorate as the temperature increases．Figure 2.23 shows that the yield strength for mild steel is reduced by about 70% in going from room temperature to 1000o F．Figure 2.24 shows the reduction in the modulus of elasticity E for mild steel as the temperature increases．As can be seen from the graph，a 30% reduction in modulus of elasticity occurs in going from room temperature to 1000o F．In this figure，we also can see that a part loaded below the proportional limit at room temperature can be permanently deformed under the same load at elevated temperatures．CREEP: A PLASTIC PHENOMENONTemperature effects bring us to a phenomenon called creep，which is the increasing plastic deformation of a part under constant load as a function of time．Creep also occurs at room temperature，but the process is so slow that it rarely becomes significant during the expected life of the temperature is raised to 300o C or more，the increasing plastic deformation can become significant within a relatively short period of time．The creep strength of a material is its ability to resist creep，and creep strength data can be obtained by conducting long-time creep tests simulating actual part operating conditions．During the test，the plastic strain is monitored for given material at specified temperatures．Since creep is a plastic deformation phenomenon，the dimensions of a part experiencing creep are permanently altered．Thus，if a part operates with tight clearances，the design engineer must accurately predict the amount of creep that will occur during the life of the machine．Otherwise，problems such binding or interference can occur．Creep also can be a problem in the case where bolts are used to clamp tow parts together at elevated temperatures．The bolts，under tension，will creep as a function of time．Since the deformation is plastic，loss of clamping force will result in an undesirable loosening of the bolted joint．The extent of this particular phenomenon，called relaxation，can be determined by running appropriate creep strength tests．Figure 2.25 shows typical creep curves for three samples of a mild steel part under a constant tensile load．Notice that for the high-temperature case the creep tends to accelerate until the part fails．The time line in the graph (the x-axis) may represent a period of 10 years，the anticipated life of the product．SUMMARYThe machine designer must understand the purpose of the static tensile strength test．This test determines a number of mechanical properties of metals that are used in design equations．Such terms as modulus of elasticity，proportional limit，yield strength，ultimate strength，resilience，and ductility define properties that can be determined from the tensile test．Dynamic loads are those which vary in magnitude and direction and may require an investigation of the machine part’s resistance to failure．Stress reversals may require that the allowable design stress be based on the endurance limit of the material rather than on the yield strength or ultimate strength．Stress concentration occurs at locations where a machine part changes size，such as a hole in a flat plate or a sudden change in width of a flat plate or a groove or fillet on a circular shaft．Note that for the case of a hole in a flat or bar，the value of the maximum stress becomes much larger in relation to the average stress as the size of the hole decreases．Methods of reducing the effect of stress concentration usually involve making the shape change more gradual．Machine parts are designed to operate at some allowable stress below the yield strength or ultimate strength．This approach is used to take care of such unknown factors as material property variations and residual stresses produced during manufacture and the fact that the equations used may be approximate rather that exact．The factor of safety is applied to the yield strength or the ultimate strength to determine the allowable stress．Temperature can affect the mechanical properties of metals．Increases in temperature may cause a metal to expand and creep and may reduce its yield strength and its modulus of elasticity．If most metals are not allowed to expand or contract with a change in temperature，then stresses are set up that may be added to the stresses from the load．This phenomenon is useful in assembling parts by means of interference fits．A hub or ring has an inside diameter slightly smaller than the mating shaft or post．The hub is then heated so that it expands enough to slip over the shaft．When it cools，it exerts a pressure on the shaft resulting in a strong frictional force that prevents loosening．故障的分析、尺寸的决定以及凸轮的分析和应用摘要：作为一名设计工程师有必要知道零件如何发生和为什么会发生故障，以便通过进行最低限度的维修以保证机器的可靠性；凸轮是被应用的最广泛的机械结构之一，是一种仅仅有两个组件构成的设备。

毕业设计(论文)-CA6140车床总体布局及主轴箱的设计

毕业设计说明书（论文）中文摘要金属切削机床在是人类改造自然的长期生产实践中，不断改进生产工具的基础上产生和发展起来的，它是用切削的方法将金属毛坯加工成机器零件的机器，是制造机器的机器。

CA6140车床可进行各种车削工作，并可加工公制、英制、模数和径节螺纹，所以在各个领域中应用越来越广泛。

本文首先介绍了金属切削机床的基本概念，以及在国内外的发展现状。

其次具体阐述CA6140车床主轴箱的功用，组成及各部分特点。

然后根据课题的要求及给定的设计参数，对CA6140车床主轴箱的主传动系统进行了方案设计。

最后文章分别对主轴箱中的各轴，以及轴上的齿轮和轴承进行了详细的计算和校核，并给出了各轴的装配图和主轴箱的总装配图。

关键词金属切削机床主轴箱设计传动系统装配图全套图纸加V信 sheji1120或扣 3346389411毕业设计说明书（论文）外文摘要目录1 绪论 (1)1.1 课题简介 (1)1.2 CA6140机床的说明 (2)1.3 CA6140主轴箱 (3)1.4 选题依据 (4)1.5 本设计的意义和应用价值 (4)1.6 研究内容及方法 (4)2 传动方案及传动系统图的拟定 (5)2.1 电动机的选择 (5)2.2 传动路线及转速图的拟定 (5)3 主轴箱主要零件的设计及校核 (10)3.1 主轴箱箱体尺寸的确定 (10)3.2 传动轴Ⅰ各主要零件的设计 (12)3.3 传动轴II各主要零件的设计 (25)3.4 传动轴III各主要零件的设计 (29)3.5 传动轴IV各主要零件的设计 (33)3.6 传动轴V各主要零件的设计 (38)3.7 传动轴VI各主要零件的设计 (42)4 结论与展望 (49)1 绪论1.1 课题简介1.1.1 金属切削机床国内外研究状况金属切削机床是用切削的方法将金属毛坯加工成机器零件的机器，它是制造机器的机器，所以又称“工作母机”或“工作机”，习惯上称“机床”[1]。

金属切削机床是人类在改造自然的长期生产实践中，不断改进生产工具的基础上产生很发展起来的。

CA6150普通车床说明书

CA6150普通车床说明书目录1 引言 (3)2普通车床介绍 (4)2.1 C650普通车床运行说明 (4)2.1.1 主运动 (4)2.1.2 进给运动 (4)2.1.3 冷却系统 (4)2.2普通车床电气控制线路的特点 (4)3 工作原理分析 (5)3.1 电气控制线路分析 (5)3.1.1 主电路分析 (5)3.1.2 控制电路分析 (6)3.1.3 辅助电路分析 (8)3.2 机械部分工作简介 (8)4 元器件选择 (9)4.1 隔离开关 (10)4.2 空气开关 (10)4.3 熔断器 (10)4.3.1 熔断器 (10)4.3.2 熔体 (10)5模拟机床操作使用说明 (10)5.1 面板操作说明： (11)5.2 使用注意事项： (11)5.3 维护注意事项 (12)6 大修报告 (12)6.1 检修前的设备使用记录 (12)6.1.1 常见故障 (14)6.1.2 维修配件清单................................. 错误!未定义书签。

6.1.3 维修后的技术参数................................ 错误!未定义书签。

6.2 大修总结.......................................... 错误!未定义书签。

致谢..................................................... 错误!未定义书签。

参考文献.................................................. 错误!未定义书签。

附录一系统实物图. (16)附录二普通车床原理图...................................... 错误!未定义书签。

附录三装接位置图. (19)附录四大修工艺卡片 (20)附录五机床元件清单 (21)1 引言在金属切削机床中，车床所占的比例最大，应用也最广泛，在实际生产中有着不可替代的作用。

CA6140车床主轴箱内部结构

a)传动路线两末端件：主电动机------主轴传动路线表达式:
56 39
电机（7.5kw ,1450r/min)
130 230
Ⅰ
M1左 3581 43
M1右
50 34
Ⅶ
34 30
Ⅱ
3401
50 22
Ⅲ
58
20
20
80 50
Ⅳ
80 50
当压块8处于中间位置时，左、右离合器都处于脱开状态主轴停止
离合器的接合与脱开由手柄18来操纵
制动器操纵
当离合器脱开时，齿条22处于中间位置，这时，齿条轴22上的凸起正处于与杠杆14下端相接触的位置，使杠杆14向逆时针方向摆动，将制动带拉紧，使轴凹和主轴迅速停止旋转。当齿条轴22移至左端或右端位置时，杠杆与齿条轴凸起的左侧或右侧的凹槽相接触，使制动带放松，这时摩擦离合器接合，使主轴旋转。
Ⅵ（主轴）
50
51
63 50
b)主轴转速级数和转速经低速传动路线时，主轴获得的实际转速是2×3×（2×2-1）
=18级转速，加上由高速传动路线获得的6级转速，
①带轮2与花键套1用螺钉连接,并支承在法兰3内的两个轴承上,当带轮转动时,带动花键套一起转动; ②法兰3固定在主轴箱体上。
Ⅴ
26 58
M2(合)
Ⅵ（主轴）
50
51
63 50
56
39
电机（7.5kw ,1450r/min)
130 230
Ⅰ
M1左 3581
43
M1右
50 34
Ⅶ
34 30
Ⅱ
3401
50 22
58
Ⅲ

CA6140主轴箱设计说明书

目录1.概述 (2)1.1机床课程设计的目的 (2)1.2机床的规格系列和用处 (2)1.3 操作性能要求 (2)2.参数的拟定 (2)2.1 公比选择 (2)2.2 求出转速系列 (2)2.3 主电机选择 (3)3.传动设计 (3)3.1 主传动方案拟定 (3)3.2 传动结构式、结构网的选择 (3)3.2.1 确定传动组及各传动组中传动副的数目 (3)3.2.2 传动式的拟定 (4)3.2.3 结构式、结构网的拟定 (4)3.2.4 转速图的拟定 (5)4. 传动件的估算 (5)4.1 V型带传动 (5)4.1.1 确定计算功率 (5)4.1.2 选择三角胶带的型号 (6)4.1.3 确定带轮直径 (6)4.1.4 计算V带速度V (6)4.1.5 初定中心距A0 (6)4.1.6 计算V带的长度 (6)4.1.7 计算实际中心距A (6)4.1.8 确定定小带轮的包角a (7)4.1.9 确定V型带的根数Z (7)4.1.10 计算单根V带的初拉力的最小值（F0）min (7)4.1.11 作用在支撑轴上的径向力 (7)4.2 传动轴的估算 (7)传动轴直径的估算 (8)4.2.2齿轮模数的计算 (9)4.2.3 齿宽的确定 (10)4.2.4 确定各轴的间距 (11)4.2.5 带轮结构设计 (11)5. 动力设计 (12)5.1主轴刚度验算 (12)5.2 齿轮校验 (13)6.主轴空间位置图 (16)7.主轴箱位置展开图 (17)8.结构设计及说明 (17)9.总结 (23)10.参考文献 (24)1.概述1.1机床课程设计的目的机床课程设计，是在金属切削机床课程之后进行的实践性教学环节。

其目的在于通过机床运动机械变速传动系统的结构设计，使学生在拟定传动和变速的结构的结构方案过程中，得到设计构思，方案分析，结构工艺性，机械制图，零件计算，编写技术文件和查阅技术资料等方面的综合训练，树立正确的设计思想，掌握基本的设计方法，并培养学生具有初步的结构分析，结构设计和计算能力。

CA6150型卧式车床进给箱设计

C6150车床进给箱设计1. 绪论1.1 研究的背景与现实意义1.1.1 此项研究背景本课题针是一种加工效率高，操作性能好，社会拥有量大的普通C6150型车床，对机械部分重新设计、装配，对电气部分在原有基础上进行较大规模的技术更新，较大幅度地提高水平和档次。

目的为重新恢复其使用，提高其精度、效率和自动化程度，提高性能或档次，更好的适应新工艺、新技术使用。

可见大多数制造行业和企业的生产、加工装备绝大数是传统的机床，而且半数以上是役龄在10 年以上的旧机床。

用这种装各加工出来的产品普遍存在质量差、品种少、档次低、成本高、供货期长，从而在国际、国内市场上缺乏竞争力，直接影响一个企业的产品、市场、效益，影响企业的生存和发展。

1.1.2 车床研究的现实意义通过对此型号车床的研究开发，随着科学技术水平和人类生活水平的提高，对机械产品的质量要求越来越高，产品品种越来越多，中大批量的产品需求越来越少，而单件小批量生产模式迅速增加，作为实现单件小批量加工自动化的数控机床，由于其突出的优点而得到广泛应用：(1)可以加工出传统机床加工不出来的曲线、曲面等复杂的零件。

这是由于计算机有高超的运算能力，可以瞬时准确地计算出每个坐标轴应该运动的运动量，这就可以加工复杂的曲线和曲面。

(2)可以实现加工的自动化，而且是柔性自动化，效率可比以往机床提高3 到7 倍。

(3)加工的零件精度高，尺寸分散度小，装配容易，不再需要”修配” 。

这是由于加工过程自动化，不受人的情绪和疲劳影响的结果。

计算机还可以自动进行刀具寿命管理，不会因刀具磨损而影响工件精度和其一致性。

最近，数控系统中增加了机床误差、加工误差修正补偿的功能，使加工精度得到进一步提高（4）可实现多工序的集中，减少零件在机床间的频繁搬运。

这是自动化带来的效果（可以自动更换刀具），如加工中心，在工件装夹好后，可实现钻、铣、攻丝、扩孔等多工序的加工。

这些多工序是在同一基面、同一次装夹下实现的，提高了相关的加工精度。

CA6140车床结构[1]

之用。主轴前端安装卡盘、拨盘或其它夹具。
CA6150型车床主轴结构 1-主轴 ; 2、9-锁紧螺母; 3-双列短圆柱滚子轴承; 4、 6-套筒; 5、10-锁紧盘; 7-推力球轴承; 8-角接触球轴承;
④双向摩擦式离合器
作用：①实现主轴正反转；②超载时摩擦片打滑起过载保护作用
双向片式摩擦离合器 1-双联齿轮；2-外摩擦片；3-内摩擦片； 4-调整销； 5-销；6-元宝销； 7-拉杆； 8-压套；9-螺母；10、11 –止推片
（2）丝杠用来车削螺纹。（3）光杠用来传动动力，带动床鞍、中滑板，使车刀作纵向或横向的进给运动。
4.溜板部分
刀架
用来装夹车刀
小滑板
作纵向移动
中滑板
作横向移动
床鞍
作纵向移动
溜箱
变换箱外手柄位置，在光杠或丝杠的传动下，可使车刀按要求方向作进给运动
5.尾座
用来安装顶尖、支顶较长工件，它还可以安装其它切削刀具，如钻头、绞刀等
三.车削加工的主要工艺类型
车削加工是机械加工方法中应用最为广泛的方法之一，是加工轴类、盘套类零件的主要方法。应用车削加工方法可以加工各种回转体内外表面，如内外圆柱面、圆锥面、成形回转表面等。
四.注意事项
1．要求每台机床都具有防护设施。 2．摇动滑板时要集中注意力，做模拟切削运动。 3．倒顺电气开关不准连接，确保安全。 4．变换车速时，应停车进行。 5．车床运转操作时，转速要慢，注意防止左右前后碰撞，以免发生事故。
一.CA6150车床基本结构
CA6150型卧式车床属通用的中型车床。其外型及组成部件如图所示。其主要组成部件可概括为“三箱刀架尾座床身”。
CA6150车床外形图 1-主轴箱；2-刀架；3-尾座；4-床身；5、9-床腿； 6-光杠；7-丝杠；8-溜板箱；10-进给箱；11-挂轮

CA6140机床进给箱设计指导书

目录第一部分总论 (1)一、毕业设计的目的与意义 (2)二、毕业设计的内容 (2)三、设计步骤 (2)(一)准备阶段 (2)(二)设计与计算 (2)(三)齿轮齿数优化设计 (2)四、设计时应注意事项 (3)第二部分CA6140进给箱传动方案设计 (4)一CA6140普通车床简介 (4)二进给箱的传动机构 (4)三进给箱切螺纹机构设计方法 (5)四切螺纹系统及齿数比的确定 (8)五增倍机构设计以及移换机构设计 (9)六车制螺纹的工作过程 (10)第三部分毕业设计说明书 (11)一、要求 (11)二、设计计算说明书的内容 (12)第四部分参考资料 (12)第一部分总论一、毕业设计的目的及意义毕业设计是本科生教学活动中最后的一个重要环节。

通过这个教学环节要求达到下列几个目的：1、通过毕业设计，把在本科阶段中所获得的知识在实际的设计工作中综合地加以运用。

使这些知识得到巩固，加强和发展，并使理论知识和生产实践密切地结合起来。

因此，毕业设计是大学学习阶段的总结性作业。

2、毕业设计是高等学校学生第一次进行的比较完整的设计过程。

通过毕业设计，培养学生独立工作、发现问题和解决问题的能力；能根据设计课题查找有关的资料，了解本课题的前沿和发展方向；树立正确的设计思想，掌握设计的基本方法和步骤，为以后从事设计工作打下良好的基础。

3、使学生能够熟练地应用有关参考资料，计算图表、手册，图集，规范，并熟悉有关国家标准和部颁标准(如GB，JB等)，以完成一个工程技术人员在机械工程设计方面所必须具备的基本训练。

二、毕业设计的内容1、学生在规定的时间内，要求完成CA6140车床进给箱总体设计，传统方法绘制总装配图一张，零件工作图一至两张(具体绘那几个零件工作图，由指导教师指定)：2、根据设计计算步骤对该机器的某一个零件进行CAD设计；3、在零件CAD设计的基础上，重新对箱内齿轮齿数进行优化选择；4、编写完整设计说明书一份。

说明：四个部分中，每个学生必须完成第1、4两项，2、3两项由指导教师指定其一。

机械毕业设计-CJK6150数控车床设计-主轴箱和尾座部件设计

(
CJK6150
)
CJK6150
Abstract
With the industrial equipment for precision degree of the increasingly high demand, the degree of precision machining processing equipment of machining equipment also to request more and more high. In the search, a lot of related data access research of machine tool automation technology, in-depth research and analysis, and describes the design of machine tool control system. The whole process is mainly carries on the design to the main drive lathe. CNC lathe main drive design, including the design, three aspects: according to the design of machine tool use, the given specifications, spindle speed limit, speed ratio determined sequence or series, other relevant motion parameters, selected at speed of the main shaft; through analysis and comparison, select the transmission scheme; develop structure or structure, develop speed diagram; to determine the number of gear teeth and belt pulley diameter; drawing drive system diagram. Secondly, based on the machine type and motor power, determining the spindle and the transmission of the computation speed, initial drive shaft diameter, the gear modulus, determine the transmission belt type and number of roots, friction plate size and number of assembly drawing; after checking transmission parts (gear, shaft, shaft, bearing stiffness,) strength or fatigue life. Finally, to complete the exercise design and dynamic design, to the main transmission scheme "structured", design of spindle gearbox assembly drawing and parts drawing, focuses on the transmission shaft assembly, spindle assembly, transmission mechanism, box, lubrication and seal, the transmission shaft and the sliding gear parts design.

CA6150车床主轴箱设计(有全套图纸)(可编辑)

1.1数控机床主传动系统的特点与普通机床比较,数控机床主传动系统具有下列特点。

转速高、功率大。

它能使数控机床进行大功率切削和高速切削,实现高效率加工。

变速范围宽。

数控机床的主传动系统有较宽的调速范围,一般Ra100,以保证加工时能选用合理的切削用量,从而获得最佳的生产率、加工精度和表面质量。

主轴变速迅速可靠,数控机床的变速是按照控制指令自动进行的,因此变速机构必须适应自动操作的要求。

由于直流和交流主轴电动机的调速系统日趋完善,所以不仅能够方便地实现宽范围无级变速,而且减少了中间传递环节,提高了变速控制的可靠性。

主轴组件的耐磨性高,使传动系统具有良好的精度保持性。

凡有机械摩擦的部位,如轴承、锥孔等都有足够的硬度,轴承处还有良好的润滑。

1.2 主传动系统的设计要求①主轴具有一定的转速和足够的转速范围、转速级数,能够实现运动的开停、变速、换向和制动,以满足机床的运动要求。

②主电机具有足够的功率,全部机构和元件具有足够的强度和刚度,以满足机床的动力要求。

③主传动的有关结构,特别是主轴组件要有足够高的精度、抗震性,热变形和噪声要小,传动效率高,以满足机床的工作性能要求。