机电专业毕业设计中英文翻译资料--圆柱凸轮的设计和加工
轴类毕业设计英文翻译、外文文献翻译
ShaftSolid shafts. As a machine component a shaft is commonly a cylindrical bar that supports and rotates with devices for receiving and delivering rotary motion and torque .The crankshaft of a reciprocating engine receive its rotary motion from each of the cranks, via the pistons and connecting roads (the slider-crank mechanisms), and delivers it by means of couplings, gears, chains or belts to the transmission, camshaft, pumps, and other devices. The camshafts, driven by a gear or chain from the crankshaft, has only one receiver or input, but each cam on the shaft delivers rotary motion to the valve-actuating mechanisms.An axle is usually defined as a stationary cylindrical member on which wheels and pulleys can rotate, but the rotating shafts that drive the rear wheels of an automobile are also called axles, no doubt a carryover from horse-and-buggy days. It is common practice to speak short shafts on machines as spindles, especially tool-carrying or work-carrying shafts on machine tools.In the days when all machines in a shop were driven by one large electric motor or prime mover, it was necessary to have long line shafts running length of the shop and supplying power, by belt, to shorter couter shafts, jack shafts, or head shafts. These lineshafts were assembled form separate lengths of shafting clampled together by rigid couplings. Although it is usually more convenient to drive each machine with a separate electric motor, and the present-day trend is in this direction, there are still some oil engine receives its rotary motion from each of the cranks, via the pistons and connecting roads (the slider-crank mechanisms) , and delivers it by means of couplings, gears, chains or belts to the transmission, camshaft, pumps, and other devices. The camshafts, driven by a gear or chain from the crankshaft, has only one receiver or input, but each cam on the shaft delivers rotary motion to the valve-actuating mechanisms.An axle is usually defined as a stationary cylindrical member on which wheels and pulleys can rotate, but the rotating shafts that drive the rear wheels of an automobile are also called axles, no doubt a carryover from horse-and-buggy days. It is common practice to speak short shafts on machines as spindles, especially tool-carrying or work-carrying shafts on machine tools.In the days when all machines in a shop were driven by one large electric motor or prime mover, it was necessary to have long line shafts running length of the shop and supplying power, by belt, to shorter coutershafts, jackshafts, or headshafts. These line shafts were assembled form separatelengths of shafting clampled together by rigid couplings. Although it is usually more convenient to drive each machine with a separate electric motor, and the present-day trend is in this direction, there are still some situation in which a group drive is more economical.A single-throw crankshaft that could be used in a single-cylinder reciprocating engine or pump is shown in Figure 21. The journals A andB rotate in the main bearings,C is the crankpin that fits in a bearing on the end of the connecting rod and moves on a circle of radius R about the main bearings, whileD andE are the cheeks or webs.The throw R is one half the stroks of the piston, which is connected, by the wrist pin, to the other end of the connecting rod and guided so as to move on a straight path passing throw the axis XX. On a multiple-cylinder engine the crankshaft has multiple throws---eight for a straight eight and for a V-8---arranged in a suitable angular relationship.Stress and strains. In operation, shafts are subjected to a shearing stress, whose magnitude depends on the torque and the dimensions of the cross section. This stress is a measure of resistance that the shaft material offers to the applied torque. All shafts that transmit a torque are subjected to torsional shearing stresses.In addition to the shearing stresses, twisted shafts are also subjected to shearing distortions. The distorted state is usually defined by the angle of twist per unit length; i.e., the retation of one cross section of a shaft relative to another cross section at a unit distance from it.Shafts that carry gears and pulleys are bent as well as twisted, and the magniude of the bending stresses, which are tensile on the convex side of the bend and compressive on the concave side, will depend on the load, the distance between the bearings of the shaft cross section.The combination of bending and twisting produces a state of stress in the shaft that is more complex than the state of pure shears produced by torsion alone or the state of tension-compression produced by bending alone.To the designer of shaft it is important to know if the shaft is likely to fail because of an excessive normal stress. If a piece of chalk is twisted, it will invariably rupture on a plane at about 45 degrees to the axis. This is because the maximum tensile stresses act on this plane, and chalk is weak in tension. Steel shafting is usually designed so that the maximum shearing stress produced by bending and torsion is less than a specified maximum.Shafts with circular cross sections are easier to produce in the steel mill, easier to machine, andeasier to support in bearings than shafts with other cross section; there is seldom any need for using noncircular shapes. In addition, the strength and stiffness, both in bending and torsion, are more easily calculated for circular shafts. Lastly, for a given amount of materials the circular shafts has the smallest maximum shearing stress for a given torque, and the highest torsional rigidity.The shearing in a circular shaft is highest at the surface and drops off to zero at the axis. This means that most of the torque is carried by the material on and near the surface.Critical speeds. In the same way that a violin string vibrates when stroked with a bow, a cylindrical shaft suspended between two bearings has a natural frequency of lateral vibration. If the speed of revolution of the shaft coincides with the natural frequency, the shaft experience a whirling critical speed and become noisy. These speeds are more likely to occur with long, flexible shafts than with short, stiff ones. The natural frequency of a shaft can be raised by increasing its stiffness.If a slender rod is fixed to the ceiling ta one end and supports a heavy disk at the other end, the disk will oscillate back and forth around the rod axis like a torsion pendulum if given an initial twist and let go. The frequency of the oscillations will depend on the torsional stiffness of the rod and the weight of the disk; the stiffer the rod and the lighter the disk the higher the frequency. Similar torsional oscillations can occur in the crankshafts of reciprocating engines, particularly those with many crank throws and a heavy flywheel. Each crank throw and part of the associated connecting rod acts like a small flywheel, and for the crankshaft as a whole, there are a number of ways or modes in which there small flywheels can oscillate back and forth around the shaft axis in opposition to one another and to the main flywheel. For each of these modes there corresponds a natural frequency of oscillation.When the engine is operating the torques delivered to the crankshaft by the connecting rods fluctuate, and if the crankshaft speed is such that these fluctuating impulses are delivered at a speed corresponding to one of the natural torsional frequencies of the shaft, torsional oscillations will be superimposed on the rotary motion of the shafts. Such speed are known as torsional critical speeds, and they can cause shaft failures. A number of devices to control the oscillations of crankshafts have been invented.Flexible shafts. A flexible shaft consists of a number of superimposed tightly wound right-and left-hand layers of helically wound wires wrapped about a single center wire or mandrel. The shaft is connected to source of power and the driven member by special fittings attached to the end of theshaft. Flexible easings of metallic or nonmetallic materials, which guide and protect the shaft and retain the lubricant, are also available. Compared with solid shafts, flexible shafts can be bent to much smaller radii without being overstressed.For transmitting power around corners and for considerable distances flexible shafts are usually cheaper and more convenient than belts, chains, or gears. Most speedometers on automobiles are driven by flexible shafts running from the transmission to the dashboard. When a valve, a switch, or other control devices is in a hard-to-reach location, it can be operated by a flexible shaft from a more convenient position. For portable tools such as sanders, grinders, and drilling machines, flexible shafts are practically indispensable.KEY, SPLINES AND PINSKeys, splines, and pins. When power is being transmitted from a machine member such as a coupling, a gear, a flywheel, or a pulley to the shaft on which it is mounted, means must be provided for preventing relative motion between the shaft and the member. On helical and bevel gears, relative movement along the shaft caused by the thrust(axial) loads is prevented by a step in the shaft or by having the gear contact the bearing directly or through a tubular spacer. When axial loads are incidental and of small magnitude, the members are kept from sliding along the shaft by means of a set screw. The primary purpose of keys, splines, and pins is to prevent relative rotary movement.A commonly used type of key has a square cross section and is sunk half in the shaft and half in the hub of the other member. If the key is made of steel(which is commonly the case)of the same strength as the shaft and has a width and depth equal to one fourth of the shaft diameter(this proportion is closely approximated in practice) then it will have the same torque capacity as the solid shaft if its length is 1.57 times that of the shaft diameter. Another common type of key has a rectangular cross section with a depth to width ratio of 0.75. Both of these keys may either be straight or tapered in depth. The straight keys fit snugly on the sides of the key ways only, the tapered keys on all sides. Gib-head keys are tapered keys with a projection on one end to facilitate removal.Woodruff keys are widely used on machine tools and motor vehicles. The key is a segment of adisk and fits in a keyway in the shaft that is with a special milling cutter. Though the extra depth of these keys weakens the shaft considerably, it prevents any tendency of the key to rotate or move axially. Woodruff keys are particularly suitable for tapering shaft ends.Because they weaken the shafts less, keys with straight or tapered circular cross sections are sometimes used in place of square and rectangular keys, but the keyways, half in the shaft and half in the shaft and half in the hub, must be cut with a drill after assembly,and interchangeability of parts is practically impossible. When a large gear blank is made by shrinking a high-strength rim on a cheaper cast center, circular keys, snugly fitted, are frequently used to ensure a permanent connection.Splines are permanent keys integral with the shaft, fitting in keyways cut in the hub. The dimensions of splined fittings are standardized for both permanent (press) fits and sliding fits. The teeth have either straight or involute profiles;the latter are stronger, more easily measured, and have a self-centring action when twisted.Tapered circular pins can be used to restrain shaft-mounted members from both axial and rotary movement. The pin fits snugly in a reamed tapered hole that is perpendicular to the shaft surface. A number of straight pins that grip by deforming elastically or plastically when driven into straight holes are commercially available.All the keys and pins that have been described are standard driving devices. In some cases they inadequate, and unorthodox means must be employed. For driving small gear in which there is no room between the bore and the roots of the teeth for a longitudinal keyway, a transverse radial slot on the end of the gear can be made to fit a radial protuberance on the shaft. For transmitting moderate loads, a cheaper and effective connection can be made by forming a series of longitudinal serrations on the shaft with a knurling tool and pressing the shaft into the hole in the driven member, it will cut grooves in the hole and provide, in effect, a press-fitted splined connection. Press and shrink fits are also used, and they can provide surprisingly firm connections, but the dimensions of the connected member must be closely controlled.轴实心轴轴作为机械零件通常是一根圆柱形杆，用来支撑部件并随部件一起转动以接受和传递转动和扭矩。
机电一体化中英文互译
机械专业中英文对照英语词汇陶瓷ceramics合成纤维synthetic fibre电化学腐蚀electrochemical corrosion车架automotive chassis悬架suspension转向器redirector变速器speed changer板料冲压sheet metal parts孔加工spot facing machining车间workshop工程技术人员engineer气动夹紧pneuma lock数学模型mathematical model画法几何descriptive geometry机械制图Mechanical drawing投影projection视图 view剖视图profile chart标准件standard component零件图part drawing装配图assembly drawing尺寸标注size marking技术要求technical requirements刚度rigidity内力internal force位移displacement截面section疲劳极限fatigue limit断裂fracture塑性变形plastic distortion脆性材料brittleness material刚度准则rigidity criterion垫圈washer垫片spacer直齿圆柱齿轮straight toothed spur gear斜齿圆柱齿轮helical-spur gear直齿锥齿轮straight bevel gear运动简图kinematic sketch齿轮齿条pinion and rack蜗杆蜗轮worm and worm gear虚约束passive constraint曲柄crank精品文档摇杆racker凸轮 cams共轭曲线conjugate curve范成法generation method定义域definitional domain值域 range导数微分differential coefficient求导 derivation定积分definite integral不定积分indefinite integral曲率curvature偏微分partial differential毛坯rough游标卡尺slide caliper千分尺micrometer calipers攻丝tap二阶行列式second order determinant逆矩阵inverse matrix线性方程组linear equations概率probability随机变量random variable排列组合permutation and combination气体状态方程equation of state of gas动能kinetic energy势能potential energy机械能守恒conservation of mechanical energy动量momentum桁架truss轴线axes余子式cofactor逻辑电路logic circuit触发器flip-flop脉冲波形pulse shape数模digital analogy液压传动机构fluid drive mechanism机械零件mechanical parts淬火冷却quench淬火hardening回火tempering调质hardening and tempering磨粒abrasive grain结合剂bonding agent砂轮grinding wheel后角 clearance angle龙门刨削planing主轴spindle主轴箱headstock卡盘chuck加工中心machining center车刀lathe tool车床lathe钻削镗削bore车削turning磨床grinder基准benchmark钳工locksmith锻 forge压模stamping焊 weld拉床broaching machine拉孔broaching装配assembling铸造found流体动力学fluid dynamics流体力学fluid mechanics加工machining液压hydraulic pressure切线tangent机电一体化mechanotronics mechanical-electrical integration 气压air pressure pneumatic pressure稳定性stability介质medium液压驱动泵fluid clutch液压泵hydraulic pump阀门valve失效invalidation强度intensity载荷load应力stress安全系数safty factor可靠性reliability螺纹thread螺旋helix键 spline精品文档滚动轴承rolling bearing滑动轴承sliding bearing弹簧 spring制动器 arrester brake十字结联轴节crosshead联轴器 coupling链 chain皮带 strap精加工 finish machining粗加工 rough machining变速箱体gearbox casing腐蚀 rust氧化 oxidation磨损 wear耐用度 durability随机信号random signal离散信号discrete signal超声传感器ultrasonic sensor集成电路integrate circuit挡板 orifice plate残余应力residual stress套筒 sleeve扭力 torsion冷加工 cold machining电动机 electromotor汽缸 cylinder过盈配合interference fit热加工 hotwork摄像头 CCD camera倒角 rounding chamfer优化设计optimal design工业造型设计industrial moulding design有限元 finite element滚齿 hobbing插齿 gear shaping伺服电机actuating motor铣床 milling machine钻床 drill machine镗床 boring machine步进电机stepper motor丝杠 screw rod导轨 lead rail组件 subassembly可编程序逻辑控制器Programmable Logic Controller PLC电火花加工electric spark machining电火花线切割加工electrical discharge wire - cutting 相图phase diagram热处理heat treatment固态相变solid state phase changes有色金属nonferrous metal陶瓷 ceramics合成纤维synthetic fibre电化学腐蚀electrochemical corrosion车架automotive chassis悬架suspension转向器redirector变速器speed changer板料冲压sheet metal parts孔加工spot facing machining车间workshop工程技术人员engineer气动夹紧pneuma lock数学模型mathematical model画法几何descriptive geometry机械制图Mechanical drawing投影projection视图view剖视图profile chart标准件standard component零件图part drawing装配图assembly drawing尺寸标注size marking技术要求technical requirements刚度rigidity内力internal force位移displacement截面section疲劳极限fatigue limit断裂fracture塑性变形plastic distortion脆性材料brittleness material刚度准则rigidity criterion垫圈washer垫片spacer直齿圆柱齿轮straight toothed spur gear斜齿圆柱齿轮helical-spur gear直齿锥齿轮straight bevel gear精品文档齿轮齿条pinion and rack蜗杆蜗轮worm and worm gear虚约束 passive constraint曲柄 crank摇杆 racker凸轮 cams共轭曲线conjugate curve范成法 generation method定义域 definitional domain值域 range导数微分differential coefficient求导 derivation定积分 definite integral不定积分indefinite integral曲率 curvature偏微分 partial differential毛坯 rough游标卡尺slide caliper千分尺 micrometer calipers攻丝 tap二阶行列式second order determinant逆矩阵 inverse matrix线性方程组linear equations概率 probability随机变量random variable排列组合permutation and combination气体状态方程equation of state of gas动能 kinetic energy势能 potential energy机械能守恒conservation of mechanical energy动量 momentum桁架 truss轴线 axes余子式 cofactor逻辑电路logic circuit触发器 flip-flop脉冲波形pulse shape数模 digital analogy液压传动机构fluid drive mechanism机械零件mechanical parts淬火冷却quench淬火 hardening回火 tempering调质 hardening and tempering磨粒abrasive grain结合剂bonding agent砂轮grinding wheelAssembly line组装线Layout 布置图Conveyer流水线物料板Rivet table拉钉机Rivet gun拉钉枪Screw driver起子Pneumatic screw driver气动起子worktable工作桌OOBA 开箱检查fit together组装在一起fasten 锁紧 ( 螺丝 )fixture 夹具 ( 治具 )pallet 栈板barcode 条码barcode scanner条码扫描器fuse together熔合fuse machine热熔机repair 修理operator 作业员QC 品管supervisor课长ME 制造工程师MT 制造生技cosmetic inspect外观检查inner parts inspect内部检查thumb screw大头螺丝lbs. inch 镑、英寸EMI gasket导电条front plate前板rear plate后板chassis 基座bezel panel面板power button电源按键reset button重置键Hi-pot test of SPS高源高压测试Voltage switch of SPS电源电压接拉键sheet metal parts冲件plastic parts塑胶件SOP 制造作业程序material check list物料检查表精品文档trolley台车carton纸箱sub-line支线left fork叉车personnel resource department人力资源部production department生产部门planning department企划部QC Section品管科stamping factory冲压厂painting factory烤漆厂molding factory成型厂common equipment常用设备uncoiler and straightener整平机punching machine冲床robot 机械手hydraulic machine油压机lathe 车床planer |plein|刨床miller 铣床grinder磨床linear cutting线切割electrical sparkle电火花welder 电焊机staker=reviting machine铆合机position职务president董事长general manager总经理special assistant manager特助factory director厂长department director部长deputy manager | =vice manager副理section supervisor课长deputy section supervisor =vice section superisor副课长group leader/supervisor组长line supervisor线长assistant manager助理to move, to carry, to handle搬运be put in storage入库pack packing包装to apply oil擦油to file burr锉毛刺final inspection终检to connect material接料to reverse material翻料wet station 沾湿台approved by / checked by / prepared by核准/ 审核 / 承办Tiana天那水PCE assembly production schedule sheet PCE组装厂生产排配表cleaning cloth抹布model机锺to load material上料work order工令to unload material卸料revision版次to return material/stock to退料remark备注scraped |\\'skr?pid|报废production control confirmation生产确认scrape ..v. 刮; 削checked by初审deficient purchase来料不良approved by核准manufacture procedure制程department部门deficient manufacturing procedure制程不良stock age analysis sheet库存货龄分析表oxidation |\\' ksi\\'dei?n|氧化on-hand inventory现有库存scratch刮伤available material良品可使用dents压痕obsolete material良品已呆滞defective upsiding down抽芽不良to be inspected or reworked待验或重工defective to staking铆合不良total 合计embedded lump镶块cause description原因说明feeding is not in place送料不到位part number/ P/N料号stamping-missing漏冲type 形态production capacity生产力item/group/class类别education and training教育与训练quality品质proposal improvement提案改善prepared by制表 notes说明spare parts=buffer备件year-end physical inventory difference analysis sheet年终盘点差异forklift叉车分析表trailer=long vehicle拖板车physical inventory盘点数量compound die合模physical count quantity帐面数量die locker 锁模器difference quantity差异量pressure plate=plate pinch压板cause analysis 原因分析bolt 螺栓raw materials原料administration/general affairs dept总务部materials 物料automatic screwdriver电动启子finished product成品thickness gauge厚薄规semi-finished product半成品gauge(or jig)治具packing materials包材power wire 电源线good product/accepted goods/ accepted parts/good parts良品buzzle蜂鸣器defective product/non-good parts不良品defective product label不良标签disposed goods处理品identifying sheet list标示单warehouse/hub仓库location 地点on way location在途仓present members出席人员oversea location海外仓subject主题spare parts physical inventory list备品盘点清单conclusion 结论spare molds location模具备品仓decision items决议事项skid/pallet栈板responsible department负责单位tox machine自铆机pre-fixed finishing date预定完成日wire EDM 线割EDM 放电机dejecting顶固模coil stock卷料demagnetization去磁; 消磁sheet stock片料high-speed transmission高速传递tolerance工差heat dissipation热传 rack上料score=groove压线degrease脱脂cam block滑块rinse 水洗pilot导正筒alkaline etch龄咬trim剪外边desmut 剥黑膜pierce 剪内边 D.I. rinse纯水次drag form压锻差Chromate铬酸处理pocket for the punch head挂钩槽Anodize阳性处理slug hole废料孔seal 封孔feature die公母模revision版次expansion dwg展开图part number/P/N料号radius 半径good products良品shim(wedge)楔子scraped products报放心品torch-flame cut火焰切割defective products不良品set screw止付螺丝finished products成品form block折刀disposed products处理品stop pin 定位销barcode条码round pierce punch=die button圆冲子flow chart流程表单shape punch=die insert异形子assembly组装stock locater block定位块stamping冲压under cut=scrap chopper清角molding成型active plate活动板spare parts=buffer备品baffle plate挡块coordinate 座标cover plate盖板dismantle the die折模male die 公模auxiliary fuction辅助功能female die母模poly-line多义线groove punch压线冲子heater band加热片air-cushion eject-rod气垫顶杆thermocouple热电偶spring-box eject-plate弹簧箱顶板sand blasting喷沙bushing block衬套grit 砂砾insert入块derusting machine除锈机club car 高尔夫球车degate打浇口capability能力dryer烘干机parameter参数induction感应factor系数induction light感应光phosphate皮膜化成response=reaction=interaction感应viscosity 涂料粘度ram 连杆alkalidipping脱脂edge finder巡边器main manifold主集流脉concave凸bezel斜视规convex 凹blanking 穿落模short射料不足nick 缺口speck 瑕 ??shine 亮班splay银纹gas mark焦痕delamination起鳞cold slug冷块blush导色gouge沟槽;凿槽satin texture段面咬花witness line证示线patent专利grit 沙砾granule=peuet=grain细粒grit maker抽粒机cushion缓冲magnalium镁铝合金magnesium镁金metal plate钣金lathe车 mill锉plane刨grind磨drill 铝boring镗blinster 气泡fillet 镶 ; 嵌边through-hole form通孔形式voller pin formality滚针形式cam driver 铡楔shank摸柄crank shaft曲柄轴augular offset角度偏差velocity 速度production tempo生产进度现状torque扭矩spline=the multiple keys花键quenching淬火tempering回火精品文档liaison联络单volatile挥发性resistance电阻ion 离子titrator滴定仪beacon警示灯coolant冷却液crusher破碎机阿基米德蜗杆Archimedes worm安全系数safety factor; factor ofsafety安全载荷safe load凹面、凹度concavity扳手wrench板簧flat leaf spring半圆键woodruff key变形deformation摆杆oscillating bar摆动从动件oscillating follower摆动从动件凸轮机构cam with oscillating follower摆动导杆机构oscillating guide-barmechanism摆线齿轮cycloidal gear摆线齿形cycloidal tooth profile摆线运动规律cycloidal motion摆线针轮cycloidal-pin wheel包角angle of contact保持架cage背对背安装back-to-backarrangement背锥back cone；normal cone背锥角back angle背锥距back cone distance比例尺scale比热容specific heat capacity闭式链closed kinematic chain闭链机构closed chain mechanism臂部arm变频器frequency converters变频调速frequency control ofmotor speed变速speed changeannealing 退火变速齿轮 change gear change wheel carbonization碳化变位齿轮 modified geartungsten high speed steel钨高速的变位系数 modification coefficient moly high speed steel钼高速的标准齿轮 standard gear.精品文档表面传热系数 surface coefficient of heat transfer齿轮变速箱 speed-changing gear boxes表面粗糙度 surface roughness齿轮齿条机构 pinion and rack并联式组合 combination in parallel齿轮插刀 pinion cutter; pinion-shaped shaper cutter并联机构 parallel mechanism齿轮滚刀 hob ,hobbing cutter并联组合机构 parallel combined mechanism齿轮机构 gear并行工程 concurrent engineering齿轮轮坯 blank并行设计 concurred design, CD齿轮传动系 pinion unit不平衡相位 phase angle of unbalance齿轮联轴器 gear coupling不平衡 imbalance (or unbalance)齿条传动 rack gear不平衡量 amount of unbalance齿数 tooth number不完全齿轮机构 intermittent gearing齿数比 gear ratio波发生器 wave generator齿条 rack波数 number of waves齿条插刀 rack cutter; rack-shaped shaper cutter补偿 compensation齿形链、无声链 silent chain参数化设计 parameterization design, PD齿形系数 form factor残余应力 residual stress齿式棘轮机构 tooth ratchet mechanism操纵及控制装置 operation control device插齿机 gear shaper槽轮 Geneva wheel重合点 coincident points槽轮机构 Geneva mechanism； Maltese cross重合度 contact ratio槽数 Geneva numerate冲床 punch槽凸轮 groove cam传动比 transmission ratio, speed ratio侧隙 backlash传动装置 gearing; transmission gear差动轮系 differential gear train传动系统 driven system差动螺旋机构 differential screw mechanism传动角 transmission angle差速器 differential传动轴 transmission shaft常用机构 conventional mechanism; mechanism in common use串联式组合 combination in series车床 lathe串联式组合机构 series combined mechanism承载量系数 bearing capacity factor串级调速 cascade speed control承载能力 bearing capacity创新 innovation creation成对安装 paired mounting创新设计 creation design尺寸系列 dimension series垂直载荷、法向载荷 normal load齿槽 tooth space唇形橡胶密封 lip rubber seal齿槽宽 spacewidth磁流体轴承 magnetic fluid bearing齿侧间隙 backlash从动带轮 driven pulley齿顶高 addendum从动件 driven link, follower齿顶圆 addendum circle从动件平底宽度 width of flat-face齿根高 dedendum从动件停歇 follower dwell齿根圆 dedendum circle从动件运动规律 follower motion齿厚 tooth thickness从动轮 driven gear齿距 circular pitch粗线 bold line齿宽 face width粗牙螺纹 coarse thread齿廓 tooth profile大齿轮 gear wheel齿廓曲线 tooth curve打包机 packer齿轮 gear打滑 slipping精品文档带传动belt driving动平衡机dynamic balancing machine带轮 belt pulley动态特性dynamic characteristics带式制动器band brake动态分析设计dynamic analysis design单列轴承single row bearing动压力dynamic reaction单向推力轴承single-direction thrust bearing动载荷dynamic load单万向联轴节single universal joint端面transverse plane单位矢量unit vector端面参数transverse parameters当量齿轮equivalent spur gear; virtual gear端面齿距transverse circular pitch当量齿数equivalent teeth number; virtual number of teeth端面齿廓transverse tooth profile当量摩擦系数equivalent coefficient of friction端面重合度transverse contact ratio当量载荷equivalent load端面模数transverse module刀具 cutter端面压力角transverse pressure angle导数 derivative锻造forge倒角 chamfer对称循环应力symmetry circulating stress导热性conduction of heat对心滚子从动件radial (or in-line ) roller follower导程 lead对心直动从动件radial (or in-line ) translating follower导程角lead angle对心移动从动件radial reciprocating follower等加等减速运动规律parabolic motion;constant acceleration and对心曲柄滑块机构in-line slider-crank (or crank-slider) mechanism deceleration motion多列轴承multi-row bearing等速运动规律uniform motion; constant velocity motion多楔带poly V-belt等径凸轮conjugate yoke radial cam多项式运动规律polynomial motion等宽凸轮constant-breadth cam多质量转子rotor with several masses等效构件equivalent link惰轮idle gear等效力equivalent force额定寿命rating life等效力矩equivalent moment of force额定载荷load rating等效量equivalent II级杆组dyad等效质量equivalent mass发生线generating line等效转动惯量equivalent moment of inertia发生面generating plane等效动力学模型dynamically equivalent model法面normal plane底座 chassis法面参数normal parameters低副 lower pair法面齿距normal circular pitch点划线chain dotted line法面模数normal module（疲劳）点蚀pitting法面压力角normal pressure angle垫圈 gasket法向齿距normal pitch垫片密封gasket seal法向齿廓normal tooth profile碟形弹簧belleville spring法向直廓蜗杆straight sided normal worm顶隙 bottom clearance法向力normal force定轴轮系ordinary gear train; gear train with fixed axes反馈式组合feedback combining动力学dynamics反向运动学inverse ( or backward) kinematics动密封kinematical seal反转法kinematic inversion动能 dynamic energy反正切Arctan动力粘度dynamic viscosity范成法generating cutting动力润滑dynamic lubrication仿形法form cutting动平衡dynamic balance方案设计、概念设计concept design, CD精品文档防振装置shockproof device工作循环图working cycle diagram飞轮 flywheel工作机构operation mechanism飞轮矩moment of flywheel工作载荷external loads非标准齿轮nonstandard gear工作空间working space非接触式密封non-contact seal工作应力working stress非周期性速度波动aperiodic speed fluctuation工作阻力effective resistance非圆齿轮non-circular gear工作阻力矩effective resistance moment粉末合金powder metallurgy公法线common normal line分度线reference line; standard pitch line公共约束general constraint分度圆reference circle; standard (cutting) pitch circle公制齿轮metric gears分度圆柱导程角lead angle at reference cylinder功率power分度圆柱螺旋角helix angle at reference cylinder功能分析设计function analyses design分母 denominator共轭齿廓conjugate profiles分子 numerator共轭凸轮conjugate cam分度圆锥reference cone; standard pitch cone构件link分析法analytical method鼓风机blower封闭差动轮系planetary differential固定构件fixed link; frame复合铰链compound hinge固体润滑剂solid lubricant复合式组合compound combining关节型操作器jointed manipulator复合轮系compound (or combined) gear train惯性力inertia force复合平带compound flat belt惯性力矩moment of inertia ,shaking moment复合应力combined stress惯性力平衡balance of shaking force复式螺旋机构Compound screw mechanism惯性力完全平衡full balance of shaking force复杂机构complex mechanism惯性力部分平衡partial balance of shaking force杆组 Assur group惯性主矩resultant moment of inertia干涉 interference惯性主失resultant vector of inertia刚度系数stiffness coefficient冠轮crown gear刚轮 rigid circular spline广义机构generation mechanism钢丝软轴wire soft shaft广义坐标generalized coordinate刚体导引机构body guidance mechanism轨迹生成path generation刚性冲击rigid impulse (shock)轨迹发生器path generator刚性转子rigid rotor滚刀hob刚性轴承rigid bearing滚道raceway刚性联轴器rigid coupling滚动体rolling element高度系列height series滚动轴承rolling bearing高速带high speed belt滚动轴承代号rolling bearing identification code高副 higher pair滚针needle roller格拉晓夫定理Grashoff`s law滚针轴承needle roller bearing根切 undercutting滚子roller公称直径nominal diameter滚子轴承roller bearing高度系列height series滚子半径radius of roller功 work滚子从动件roller follower工况系数application factor滚子链roller chain工艺设计technological design滚子链联轴器double roller chain coupling精品文档滚珠丝杆ball screw技术过程technique process滚柱式单向超越离合器roller clutch技术经济评价technical and economic evaluation过度切割undercutting技术系统technique system函数发生器function generator机械machinery函数生成function generation机械创新设计mechanical creation design, MCD含油轴承oil bearing机械系统设计mechanical system design, MSD耗油量oil consumption机械动力分析dynamic analysis of machinery耗油量系数oil consumption factor机械动力设计dynamic design of machinery赫兹公式H. Hertz equation机械动力学dynamics of machinery合成弯矩resultant bending moment机械的现代设计modern machine design合力 resultant force机械系统mechanical system合力矩resultant moment of force机械利益mechanical advantage黑箱 black box机械平衡balance of machinery横坐标abscissa机械手manipulator互换性齿轮interchangeable gears机械设计machine design; mechanical design花键 spline机械特性mechanical behavior滑键、导键feather key机械调速mechanical speed governors滑动轴承sliding bearing机械效率mechanical efficiency滑动率sliding ratio机械原理theory of machines and mechanisms滑块 slider机械运转不均匀系数coefficient of speed fluctuation环面蜗杆toroid helicoids worm机械无级变速mechanical stepless speed changes环形弹簧annular spring基础机构fundamental mechanism缓冲装置shocks; shock-absorber基本额定寿命basic rating life灰铸铁grey cast iron基于实例设计case-based design,CBD回程 return基圆base circle回转体平衡balance of rotors基圆半径radius of base circle混合轮系compound gear train基圆齿距base pitch积分 integrate基圆压力角pressure angle of base circle机电一体化系统设计mechanical-electrical integration system基圆柱base cylinderdesign基圆锥base cone机构 mechanism急回机构quick-return mechanism机构分析analysis of mechanism急回特性quick-return characteristics机构平衡balance of mechanism急回系数advance-to return-time ratio机构学mechanism急回运动quick-return motion机构运动设计kinematic design of mechanism棘轮ratchet机构运动简图kinematic sketch of mechanism棘轮机构ratchet mechanism机构综合synthesis of mechanism棘爪pawl机构组成constitution of mechanism极限位置extreme (or limiting) position机架 frame, fixed link极位夹角crank angle between extreme (or limiting) positions机架变换kinematic inversion计算机辅助设计computer aided design, CAD机器 machine计算机辅助制造computer aided manufacturing, CAM机器人robot计算机集成制造系统computer integrated manufacturing system,机器人操作器manipulator CIMS机器人学robotics计算力矩factored moment; calculation moment精品文档计算弯矩calculated bending moment结构设计structural design加权系数weighting efficient截面section加速度acceleration节点pitch point加速度分析acceleration analysis节距circular pitch; pitch of teeth加速度曲线acceleration diagram节线pitch line尖点 pointing; cusp节圆pitch circle尖底从动件knife-edge follower节圆齿厚thickness on pitch circle间隙 backlash节圆直径pitch diameter间歇运动机构intermittent motion mechanism节圆锥pitch cone减速比reduction ratio节圆锥角pitch cone angle减速齿轮、减速装置reduction gear解析设计analytical design减速器speed reducer紧边tight-side减摩性anti-friction quality紧固件fastener渐开螺旋面involute helicoid径节diametral pitch渐开线involute径向radial direction渐开线齿廓involute profile径向当量动载荷dynamic equivalent radial load渐开线齿轮involute gear径向当量静载荷static equivalent radial load渐开线发生线generating line of involute径向基本额定动载荷basic dynamic radial load rating渐开线方程involute equation径向基本额定静载荷basic static radial load tating渐开线函数involute function径向接触轴承radial contact bearing渐开线蜗杆involute worm径向平面radial plane渐开线压力角pressure angle of involute径向游隙radial internal clearance渐开线花键involute spline径向载荷radial load简谐运动simple harmonic motion径向载荷系数radial load factor键 key径向间隙clearance键槽 keyway静力static force交变应力repeated stress静平衡static balance交变载荷repeated fluctuating load静载荷static load交叉带传动cross-belt drive静密封static seal交错轴斜齿轮crossed helical gears局部自由度passive degree of freedom胶合 scoring矩阵matrix角加速度angular acceleration矩形螺纹square threaded form角速度angular velocity锯齿形螺纹buttress thread form角速比angular velocity ratio矩形牙嵌式离合器square-jaw positive-contact clutch角接触球轴承angular contact ball bearing绝对尺寸系数absolute dimensional factor角接触推力轴承angular contact thrust bearing绝对运动absolute motion角接触向心轴承angular contact radial bearing绝对速度absolute velocity角接触轴承angular contact bearing均衡装置load balancing mechanism铰链、枢纽hinge抗压强度compression strength校正平面correcting plane开口传动open-belt drive接触应力contact stress开式链open kinematic chain接触式密封contact seal开链机构open chain mechanism阶梯轴multi-diameter shaft可靠度degree of reliability结构 structure可靠性reliability精品文档可靠性设计reliability design, RD螺钉screws空气弹簧air spring螺栓bolts空间机构spatial mechanism螺纹导程lead空间连杆机构spatial linkage螺纹效率screw efficiency空间凸轮机构spatial cam螺旋传动power screw空间运动副spatial kinematic pair螺旋密封spiral seal空间运动链spatial kinematic chain螺纹thread (of a screw)空转 idle螺旋副helical pair宽度系列width series螺旋机构screw mechanism框图 block diagram螺旋角helix angle雷诺方程Reynolds‘s equ ation螺旋线helix ,helical line离心力centrifugal force绿色设计green design design for environment离心应力centrifugal stress马耳他机构Geneva wheel Geneva gear离合器clutch马耳他十字Maltese cross离心密封centrifugal seal脉动无级变速pulsating stepless speed changes理论廓线pitch curve脉动循环应力fluctuating circulating stress理论啮合线theoretical line of action脉动载荷fluctuating load隶属度membership铆钉rivet力 force迷宫密封labyrinth seal力多边形force polygon密封seal力封闭型凸轮机构force-drive (or force-closed) cam mechanism密封带seal belt力矩 moment密封胶seal gum力平衡equilibrium密封元件potted component力偶 couple密封装置sealing arrangement力偶矩moment of couple面对面安装face-to-face arrangement连杆 connecting rod, coupler面向产品生命周期设计design for product`s life cycle, DPLC连杆机构linkage名义应力、公称应力nominal stress连杆曲线coupler-curve模块化设计modular design, MD连心线line of centers模块式传动系统modular system链 chain模幅箱morphology box链传动装置chain gearing模糊集fuzzy set链轮 sprocket sprocket-wheel sprocket gear chain wheel模糊评价fuzzy evaluation联组 V 带 tight-up V belt模数module联轴器coupling shaft coupling摩擦friction两维凸轮two-dimensional cam摩擦角friction angle临界转速critical speed摩擦力friction force六杆机构six-bar linkage摩擦学设计tribology design, TD龙门刨床double Haas planer摩擦阻力frictional resistance轮坯 blank摩擦力矩friction moment轮系 gear train摩擦系数coefficient of friction螺杆 screw摩擦圆friction circle螺距 thread pitch磨损abrasion wear; scratching螺母 screw nut末端执行器end-effector螺旋锥齿轮helical bevel gear目标函数objective function精品文档耐腐蚀性corrosion resistance平底从动件flat-face follower耐磨性wear resistance平底宽度face width挠性机构mechanism with flexible elements平分线bisector挠性转子flexible rotor平均应力average stress内齿轮internal gear平均中径mean screw diameter内齿圈ring gear平均速度average velocity内力 internal force平衡balance内圈 inner ring平衡机balancing machine能量 energy平衡品质balancing quality能量指示图viscosity平衡平面correcting plane逆时针counterclockwise (or anticlockwise)平衡质量balancing mass啮出 engaging-out平衡重counterweight啮合 engagement, mesh, gearing平衡转速balancing speed啮合点contact points平面副planar pair , flat pair啮合角working pressure angle平面机构planar mechanism啮合线line of action平面运动副planar kinematic pair啮合线长度length of line of action平面连杆机构planar linkage啮入 engaging-in平面凸轮planar cam牛头刨床shaper平面凸轮机构planar cam mechanism凝固点freezing point; solidifying point平面轴斜齿轮parallel helical gears扭转应力torsion stress普通平键parallel key扭矩 moment of torque其他常用机构other mechanism in common use扭簧 helical torsion spring起动阶段starting period诺模图Nomogram启动力矩starting torqueO 形密封圈密封O ring seal气动机构pneumatic mechanism盘形凸轮disk cam奇异位置singular position盘形转子disk-like rotor起始啮合点initial contact , beginning of contact抛物线运动parabolic motion气体轴承gas bearing疲劳极限fatigue limit千斤顶jack疲劳强度fatigue strength嵌入键sunk key偏置式offset强迫振动forced vibration偏 (心)距offset distance切齿深度depth of cut偏心率eccentricity ratio曲柄crank偏心质量eccentric mass曲柄存在条件Grashoff`s law偏距圆offset circle曲柄导杆机构crank shaper (guide-bar) mechanism偏心盘eccentric曲柄滑块机构slider-crank (or crank-slider) mechanism偏置滚子从动件offset roller follower曲柄摇杆机构crank-rocker mechanism偏置尖底从动件offset knife-edge follower曲齿锥齿轮spiral bevel gear偏置曲柄滑块机构offset slider-crank mechanism曲率curvature拼接 matching曲率半径radius of curvature评价与决策evaluation and decision曲面从动件curved-shoe follower频率 frequency曲线拼接curve matching平带 flat belt曲线运动curvilinear motion平带传动flat belt driving曲轴crank shaft精品文档驱动力driving force输出力矩output torque驱动力矩driving moment (torque)输出轴output shaft全齿高whole depth输入构件input link权重集weight sets数学模型mathematic model球 ball实际啮合线actual line of action球面滚子convex roller双滑块机构double-slider mechanism, ellipsograph球轴承ball bearing双曲柄机构double crank mechanism球面副spheric pair双曲面齿轮hyperboloid gear球面渐开线spherical involute双头螺柱studs球面运动spherical motion双万向联轴节constant-velocity (or double) universal joint球销副sphere-pin pair双摇杆机构double rocker mechanism球坐标操作器polar coordinate manipulator双转块机构Oldham coupling燃点 spontaneous ignition双列轴承double row bearing热平衡heat balance; thermal equilibrium双向推力轴承double-direction thrust bearing人字齿轮herringbone gear松边slack-side冗余自由度redundant degree of freedom顺时针clockwise柔轮 flexspline瞬心instantaneous center柔性冲击flexible impulse; soft shock死点dead point柔性制造系统flexible manufacturing system; FMS四杆机构four-bar linkage柔性自动化flexible automation速度velocity润滑油膜lubricant film速度不均匀( 波动) 系数 coefficient of speed fluctuation润滑装置lubrication device速度波动speed fluctuation润滑 lubrication速度曲线velocity diagram润滑剂lubricant速度瞬心instantaneous center of velocity三角形花键serration spline塔轮step pulley三角形螺纹V thread screw踏板pedal三维凸轮three-dimensional cam台钳、虎钳vice三心定理Kennedy`s theorem太阳轮sun gear砂轮越程槽grinding wheel groove弹性滑动elasticity sliding motion砂漏 hour-glass弹性联轴器elastic coupling flexible coupling少齿差行星传动planetary drive with small teeth difference弹性套柱销联轴器rubber-cushioned sleeve bearing coupling设计方法学design methodology套筒sleeve设计变量design variable梯形螺纹acme thread form设计约束design constraints特殊运动链special kinematic chain深沟球轴承deep groove ball bearing特性characteristics生产阻力productive resistance替代机构equivalent mechanism升程 rise调节modulation, regulation升距 lift调心滚子轴承self-aligning roller bearing实际廓线cam profile调心球轴承self-aligning ball bearing十字滑块联轴器double slider coupling; Oldham‘s coupling调心轴承self-aligning bearing矢量 vector调速speed governing输出功output work调速电动机adjustable speed motors输出构件output link调速系统speed control system输出机构output mechanism调压调速variable voltage control。
机械类关于凸轮的中英文翻译
英文原文CamsV arious motions can be produced by the action of a cam against a follower.Mamy timing devices are operated by can action.The purpose of andy cam is to produce a displacement of its follower;a secondary follower is often .used to produce additional displacement in another location.The most popular type is the plate cam.The cylindrical type is used to transmit linear motion to a follower as the cam rotates.Three-dimensional cam are sometimes used;these provide some unusual follower motions,but also make follower design difficult.The camshaft in the automotive engine illustrates a simple but important application of a late cam.The cam assemblies in automatic record players illustrate a somewhat more complex application.Cam profiles are accurately constructed by either praphical or mathematical methods.The transitiom from development drawings to working (shop) drawing can be made in several ways:1.Make a full-scale template.This is desirable from the manufacturing standpoint,but it will not guarantee accurate cam profiles.e radial dimensions.This is fairly accurate,but sometimes produces layout problems in the shop.e coordinate dimensioning.This procedure will ensure accuracy.In selecring one of these methods,one should consider the function of the cam in terms of desired preciseness.Because the cam work outline already determined, therefore the cam structural design mainly was determines the curve outline axial thickness and the cam and the drive shaft connection way. When the work load compares the hour, curve outline axial thickness generally takes for the outline curve biggest radius of vector 1,/10 ～/5; Regarding a stress bigger important situation, must with carry on the design according to the cam contour surface from the contact intensity.When determination cam and drive shaft joint way, should synthesize theconsideration cam the assembling and dismantling, the adjustment and firmly grades the question. Regarding implementing agency more equipment, between its each execution component movement coordination usually determined by the cycle of motion chart, therefore in assembly cam gear time, the cam contour curve initial station (pushes regulation starts) the relative position to have according to the cycle of motion chart to carry on the adjustment, guarantees each execution component to be able according to the pre-set sequence synchronized action. Therefore, requests the cam in the structural design to be able to be opposite to the drive shaft carries on the rotation along the circumference direction, and reliably performs fixedly. The simplest method uses the clamping screw nail fixed cam, or with clamping screw nail pre- fixed, after treats adjusts uses the pin to be fixed again.From structural design: from structure: When design must consider from the guidance and prevented revolves. From movement rule design: Involves many aspects from the movement rule design the questions, besides consideration rigidity impact and flexible impact, but also should maximum speed vmax which has to each kind of movement rule, maximum acceleration amax and its the influence performs the comparison. 1) vmax bigger, then momentum mv is bigger. If from is suddenly prevented, the oversized momentum can cause the enormous impulse, endangers the equipment and the personal safety. Therefore, when is bigger from the quality, in order to reduce the momentum, should choose the vmax value smaller movement rule.2) amax bigger, is bigger. Function in high vice- contact place stress bigger, the organization intensity and the wear resistant request is also higher. Regarding high speed cam, in order to reduce the harm, should choose the amax value smaller movement rule. First states several kind of movements rules vmax, amax, the impact characteristic and the suitable situation following table regarding swings from the cam gear, its movement graph x-coordinate expression cam corner, y-coordinate then separately expresses from, angular speed and angle acceleration. This kind of movement graph has the state of motion and above is same.From structural design: from structure: When design must consider from the guidance and prevented revolves. From movement rule design: The cam gear design basic question 1. cam gears type choice, the definite cam shape, with from maintainsthe high vice- contact from the shape and the movement form and the cam the way 2. from the movement rule design, according to the application situation to from the travelling schedule and the state of motion request, determines from the movement rule. 3. cam gears basic parameter design, determines from the travelling schedule, various movements angle, the cam radius, , the roller radius, the center distance, from the length and so on. 4. cam contours curve design. 5. cam gears bearing capacity computation. 6. cam gears structural design, plan organization assembly drawing and various components shop drawingFromstructural design: from structure: When design must consider from the guidance and prevented revolves. From movement rule design: The cam gear design basic question 1. cam gears type choice, the definite cam shape, with from maintains the high vice- contact from the shape and the movement form and the cam the way 2. from the movement rule design, according to the application situation to fromthe travelling schedule and the movement 1, the cam gear application cam gear is includes the cam the high vice- organization, the cam gear has the structure to be simple, may accurately realize request merit and so on movement rule, thus obtains the widespread application in the industrial production, specially automatic device and in the automatic control device, obtains the widespread application. 2nd, the cam gear classification according to two moves the relative motion characteristic classification between the component (1) the plane cam gear 1) the disk cam; 2) translation cam. (2) space cam gear according to from movement vice- element shape classification (1) apex from; (2) roller from (3) flat base from. Note: Classifies this part of content when the introduction cam gear, should point out each kind of cam gear the good and bad points and its the adaption situation, showed each kind of cam gear the inner link, will build the foundation for the later translation cam and the column cam contour design.3rd, the throwout lever movement rule (1) the cam gear cycle of motion and the basic term terminology push the regulation movement angle: With from pushes the cam corner which the regulation corresponds; Far stops the angle: With from far rests the cam corner which the regulation corresponds; Return trip movement angle: With cam corner which corresponds from the return trip; Nearly stops the angle: With fromnearly rests the cam corner which the regulation corresponds; Cam: Take the cam axle center as the center of a circle, take its outline slightly to diameter r0 as the radius circle; From ravelling schedule: In pushes in the regulation or the return trip from the biggest displacement, indicated with h;: The cam center of rotation with from guides way the bias distance, indicated with e.Types of CamsPlate cams are simple to fabricate.The follower can be moved in various patterns with various rise /fall ratios.Motion should be controlled to avoid abrupt changes in force transmitted from the cam to the follower.One should carefully determine horizontal force components,since these present problems designing the follower assembly guide.Critical reactions occur at points A and B.These reaction values must be computed.The relative vertical position of point A with respect to B needs to be raised if the reaction value at Bis excessive.The position of B should be as close to cam as possible to minimize flexure in the roller-follower support.This type produces reciprocating motion in the follower.Again,dorces need to be determined and dimensions chosen so as to avoid excessive component sizes.A tapered roller follower is frequently employed ;the groove in the periphery of the cam should be shaped to accommodate the follower.This type of cam is expensive to produce.The cylindrical cam has two outstanding features.One is the fact that the cam is positive actiong.N outside forces (such as gravity or spring action ) are needed to hold the follower against the working surface of the cam.The second feature is the fact that the follower can move through a complete cycle in the course of several revolutions of the cam.For example,it is possible to design the cam so the follower could move from a starting position at the left end to the extreme right position in three revolutions( or more),then the starting position in two revolutions.Other variations are possible.A translation cam is illustrated.In the figure shown the cam reciprocates horizontally and the follower moves up and down.A pivoted follower can be used with this type .The translation cam can be made positive by providing a guided plate with an inclined slot for the cam;the slot cam then engage a pin or roller on a guided vertical reciprocated follower.With the latter type ,however,a complete force analysisis a critical phase of the design.In this type,the cam rotates and the follower (ususlly a roller or pin) is guided by a groove cut into the end face of a cylindrical section .Rotation of the cam provides translation of the follower.This type is also positive acting.Production costs for this type of cam are much higher than for a simple plate cam.A constant –diameter cam is illustrated .This is merely a circular plate with the camshaft hole eccentrically located.The amount of eccentricity determines the amount of follower displacement.As the cam rotates,the follower reciprocates.This arrangement is sometimes known as a Scotch yoke mechanism.Follower action is positive ;harmonic motion is produced by this type of arrangement.Types of FollowersIn neneral,the follower is considered to be the part that comes in contact with the cam profile .However,when a seconday follower is used, the motion of the secondary follower is dictated by that of the primary follower.For example ,a roller follower can be reciprocated by acting against the edge of a pivoted follower.The simplest type of follower is the reciprocationg type that merely moves up and down (or in and out ) with the rotation of the cam;the centerline can be either collinear with the cam centerline or offset from it .Contact with the cam can be via a point,a knife edge,a suface ,or a roller.A flat-afced reciprocating follower is shown If a point or surface is employed for contact the high normal force can result in abrasion and excessive wear.If the load being transmitted from the cam to the follower is small,the problem is not serious.For example ,the operation of a small snap-action switch does not produce cam surface wear.Miniature snap-action electrical switches have actuators with various configurations;some of these are in the form of rounded points or thin meta sections.Miniature three-way valves in air circuits have similar actuators.If cams are used to operate mechanical components directly,a roller is much more effective.Cam rollers are commercially available in roller sizes ranging from1/2 in .to 6 in Basic dynamic capacities range from 620 to 60000 ,based on 33.33 rpm and 500hr of minimum life .Correction factors must be used for any other speed or life values.It should be noted that the cam can be lubricated through and oil hole in the end of theshank.Rolling contact with the cam surface minimizes wear problems.Several mounting arrangements are possible with this type of followr .shows the roller follower mounted on a pivoted arm .A pivoted flat-faced follower is shown .As with any flat-faced follower,friction between the follower face and the cam profile must be controlled.Proper lubrication can reduce the effects of friction.汉语翻译:凸轮通过凸轮和从动件的作用，可得到不同的运动。
机械设计中英文词汇表(按英文排序)
Aa higher gear，top gear 高速档a low gear 低速档AGMA (American Gear Manufacturers Association) 美国齿轮制造业协会abrasion, wear, scratching, abrade 磨损abrasive 磨蚀剂abrasive wear 磨料磨损abscissa 横坐标absolute dimensional factor 绝对尺寸系数absolute motion 绝对运动absolute velocity 绝对速度acceleration 加速度acceleration analysis 加速度分析acceleration diagram 加速度曲线Access door 检修门accuracy 精密度acme thread form 梯形螺纹acme, acme thread 梯形螺纹；爱克米螺纹actual line of action 实际啮合线actual number of teeth 实际齿数actuations 传动机构addendum circle 齿顶圆addendum element 齿顶圆锥母线addendum line 齿顶线addendum thickness 齿顶厚addendum, addenda(plu) 齿顶高adhere 粘附adjacent angle 邻角adjustable speed motors 调速电动机advance-to return-time ratio 急回系数advance-to return-time ratio 行程速比系数air spring 空气弹簧allowable amount of unbalance 许用不平衡量allowable pressure angle 许用压力角allowable stress, permissible stress 许用应力allowance above nominal size, over allowrance 尺寸上偏差allowance below nominal size, under allowance 尺寸下偏差allowance for finish 精加工余量amount of unbalance 不平衡量amplitude of vibration 振幅analysis of mechanism 机构分析analytical design 解析设计analytical method 分析法angle of contact 包角angular acceleration 角加速度angular contact ball bearing 角接触球轴承angular contact bearing 角接触轴承angular contact radial bearing 角接触向心轴承angular contact thrust bearing 角接触推力轴承angular velocity 角速度angular velocity ratio 角速比anneal 退火annular spring 环形弹簧anti-friction quality 减摩性aperiodic speed fluctuation 非周期性速度波动application factor 工况系数application point；action spot ;applicationpoint ;point of action ;working point 作用点applied force 作用力arc of action 啮合弧Archimedes worm 阿基米德蜗杆Arctan 反正切arm 臂部assembly condition 装配条件Assur group 杆组atlas 图册、图谱automation 自动化average stress 平均应力average velocity 平均速度axial contact bearing 轴向接触轴承axial direction 轴向axial internal clearance 轴向游隙axial load 轴向载荷axial load factor 轴向载荷系数axial plane 轴向平面axial thrust load 轴向分力axial tooth profile 轴向齿廓Bback angle 背锥角back cone distance 背锥距back cone ；normal cone 背锥back-to-back arrangement 背对背安装backlash 侧隙backlash 齿侧间隙backlash 间隙balance 平衡balance of machinery 机械平衡balance of mechanism 机构平衡balance of rotor 转子平衡balance of rotors 回转体平衡balance of shaking force 惯性力平衡balancing machine 平衡机balancing mass 平衡质量—1—balancing quality 平衡品质balancing speed 平衡转速balata spring 橡胶弹簧ball 球ball bearing 球轴承ball screw 滚珠丝杆band brake 带式制动器barrel (cylindric) cam 圆柱式凸轮步进运动机构base circle 基圆base cone 基圆锥base cylinder 基圆柱base pitch 基圆齿距basic dynamic axial load rating 轴向基本额定动载荷basic dynamic radial load rating 径向基本额定动载荷basic rating life 基本额定寿命basic static axial load rating 轴向基本额定静载荷basic static radial load tating 径向基本额定静载荷beading stress 弯曲应力bearing alloy 轴承合金bearing block 轴承座bearing bore diameter 轴承内径bearing bush 轴瓦、轴承衬bearing capacity 承载能力bearing capacity factor 承载量系数bearing cup 轴承盖bearing height 轴承高度bearing life 轴承寿命bearing outside diameter 轴承外径bearing ring 轴承套圈bearing width 轴承宽度belleville spring 碟形弹簧belt driving 带传动belt pulley 带轮bending moment 弯矩bevel gear 锥齿轮bevel gears 圆锥齿轮机构bevel pulley, bevel wheel 锥轮bisector 平分线black box 黑箱blank 齿轮轮坯blank 轮坯block diagram 框图blower 鼓风机body guidance mechanism 刚体导引机构bold line 粗线bolts 螺栓bottom clearance 顶隙boundary dimension 外形尺寸brake 制动器buttress thread form 锯齿形螺纹Ccage 保持架calculated bending moment 计算弯矩cam 凸轮cam , cam mechanism 凸轮机构cam profile 实际廓线cam profile 凸轮廓线cam with oscillating follower 摆动从动件凸轮机构cantilever beam 悬臂梁cantilever structure 悬臂结构Cartesian coordinate manipulator 直角坐标操作器cascade speed control 串级调速case-based design,CBD 基于实例设计center distance 中心距center distance change 中心距变动center of mass 质心center of pressure 压力中心central gear 中心轮centrifugal force 离心力centrifugal force 向心力centrifugal seal 离心密封centrifugal stress 离心应力chain 链chain dotted line 点划线chain gearing 链传动装置chamfer 倒角change gear, change wheel 变速齿轮characteristics 特性chassis 底座circular gear 圆形齿轮circular pitch 齿距circular pitch, pitch of teeth 节距circular thickness 圆弧齿厚circulating power load 循环功率流clearance 径向间隙clockwise 顺时针closed chain mechanism 闭链机构closed kinematic chain 闭式链clutch 离合器coarse thread 粗牙螺纹coefficient of addendum 齿顶高系数coefficient of friction 摩擦系数coefficient of normal addendum 法面齿顶高系数coefficient of speed fluctuation 机械运转不均匀系数coefficient of speed fluctuation 速度不均匀coefficient of transverse addendum 端面—2—齿顶高系数coefficient of travel speed variation 行程速度变化系数coefficient of velocity fluctuation 运转不均匀系数coincident points 重合点combination in parallel 并联式组合combination in series 串联式组合combined efficiency, overall efficiency 总效率combined mechanism 组合机构combined mechanism 组合机构combined stress 复合应力common apex of cone 锥顶common normal line 公法线compensation 补偿complex mechanism 复杂机构composite tooth form 组合齿形compound (or combined) gear train 复合轮系compound combining 复合式组合compound flat belt 复合平带compound gear train 混合轮系compound hinge 复合铰链Compound screw mechanism 复式螺旋机构compression strength 抗压强度compressive stress 压应力compressor 压缩机computer aided design, CAD 计算机辅助设计computer aided manufacturing, CAM 计算机辅助制造computer integrated manufacturing system, CIMS 计算机集成制造系统concavity 凹面、凹度concept design, CD 方案设计、概念设计concurred design, CD 并行设计concurrent engineering 并行工程condition of self-locking 自锁条件conduction of heat 导热性cone angle 圆锥角cone distance 锥距conjugate cam 共轭凸轮conjugate profiles 共轭齿廓conjugate yoke radial cam 等径凸轮connecting rod, coupler 连杆conoid helical-coil compression spring 圆锥螺旋扭转弹簧constant-breadth cam 等宽凸轮constant-velocity (or double) universal joint 双万向联轴节constitution of mechanism 机构组成constraining force 约束反力constraint 约束constraint condition 约束条件consumption 消耗contact points 啮合点contact ratio 重合度contact seal 接触式密封contact stress 接触应力conventional mechanism, mechanism incommon use 常用机构convex 凸的，凸面体convex roller 球面滚子coordinate frame 坐标系correcting plane 平衡平面correcting plane 校正平面corrosion resistance 耐腐蚀性cosine acceleration (or simple harmonic)motion 余弦加速度运动counterclockwise (or anticlockwise) 逆时针counterweight 平衡重couple 力偶coupler-curve 连杆曲线coupling, shaft coupling 联轴器crank 曲柄crank angle between extreme (or limiting)positions 极位夹角crank arm, planet carrier 系杆crank shaft 曲轴crank shaper (guide-bar) mechanism 曲柄导杆机构crank-rocker mechanism 曲柄摇杆机构creation design 创新设计critical speed 临界转速cross-belt drive 交叉带传动crossed helical gears 交错轴斜齿轮crown gear 冠轮curvature 曲率curve matching 曲线拼接curved-shoe follower 曲面从动件curvilinear motion 曲线运动cutter 刀具cutting accuracy 切削精度cycle of motion 运动周期cycloidal gear 摆线齿轮cycloidal motion 摆线运动规律cycloidal tooth profile 摆线齿形cycloidal-pin wheel 摆线针轮cylindric pair 圆柱副cylindrical cam 圆柱凸轮cylindrical coordinate manipulator 圆柱坐标操作器cylindrical roller 圆柱滚子—3—cylindrical roller bearing 圆柱滚子轴承cylindrical worm 圆柱蜗杆cylindroid helical-coil compression spring 圆柱螺旋压缩弹簧cylindroid helical-coil extension spring 圆柱螺旋拉伸弹簧cylindroid helical-coil torsion spring 圆柱螺旋扭转弹簧Ddead point 死点dedendum 齿根高dedendum circle 齿根圆deep groove ball bearing 深沟球轴承deformation 变形degree of freedom, mobility 自由度degree of reliability 可靠度denominator 分母depth of cut 切齿深度derivative 导数design constraints 设计约束design for product`s life cycle, DPLC 面向产品生命周期设计design methodology 设计方法学design variable 设计变量detrimental resistance 有害阻力diameter of addendum 齿顶圆直径diameter series 直径系列diametral pitch 径节diametral quotient 蜗杆直径系数diametral quotient 直径系数differential 差速器differential gear train 差动轮系differential screw mechanism 差动螺旋机构differential screw mechanism 微动螺旋机构dimension series 尺寸系列direct (forward) kinematics 正向运动学disc brake 圆盘制动器disc friction clutch 圆盘摩擦离合器disk cam 盘形凸轮disk-like rotor 盘形转子displacement 位移displacement diagram 位移曲线double Haas planer 龙门刨床double crank mechanism 双曲柄机构double rocker mechanism 双摇杆机构double roller chain coupling 滚子链联轴器double row bearing 双列轴承double slider coupling, Oldham‘s coupling 十字滑块联轴器double-direction thrust bearing 双向推力轴承double-slider mechanism, ellipsograph双滑块机构driven gear 从动轮driven link, follower 从动件driven pulley 从动带轮driven system 传动系统driving force 驱动力driving gear 主动齿轮driving link 原动件driving link 主动件driving moment (torque) 驱动力矩driving pulley 主动带轮dwell 停歇dyad IIdynamic analysis design 动态分析设计dynamic analysis of machinery 机械动力分析dynamic balance 动平衡dynamic balancing machine 动平衡机dynamic characteristics 动态特性dynamic design of machinery 机械动力设计dynamic energy 动能dynamic equivalent axial load 轴向当量动载荷dynamic equivalent radial load 径向当量动载荷dynamic load 动载荷dynamic lubrication 动力润滑dynamic reaction 动压力dynamic viscosity 动力粘度dynamically equivalent model 等效动力学模型dynamics 动力学dynamics of machinery 机械动力学Eeccentric 偏心盘eccentric mass 偏心质量eccentricity ratio 偏心率effective circle force 有效圆周力effective length of line of action 实际啮合线段长度effective resistance 工作阻力effective resistance moment 工作阻力矩effective tension 有效拉力elastic coupling, flexible coupling 弹性联轴器elasticity sliding motion 弹性滑动end-effector 末端执行器energy 能量engagement, mesh, gearing, action 啮合—4—engaging-in 啮入engaging-out 啮出epicyclic gear train 周转轮系equilibrium 力平衡equivalent 等效量equivalent coefficient of friction 当量摩擦系数equivalent force 等效力equivalent link 等效构件equivalent load 当量载荷equivalent mass 等效质量equivalent mechanism 替代机构equivalent moment of force 等效力矩equivalent moment of inertia 等效转动惯量equivalent spur gear of the bevel gear 锥齿轮的当量直齿轮equivalent spur gear of the helical gear 斜齿轮的当量直齿轮equivalent spur gear, virtual gear 当量齿轮equivalent teeth number, virtual number of teeth 当量齿数evaluation and decision 评价与决策executive link, working link 执行构件external force 外力external gear 外齿轮external loads 工作载荷extreme (or limiting) position 极限位置Fface width 齿宽face width 平底宽度face-to-face arrangement 面对面安装factor of stress concentration 应力集中系数factored moment, calculation moment 计算力矩fastener 紧固件fatigue limit 疲劳极限fatigue strength 疲劳强度feather key 滑键、导键feedback combining 反馈式组合felt ring seal 毡圈密封ferrofluid seal 铁磁流体密封field balancing 现场平衡fillet radius 圆角半径final contact, end of contact 终止啮合点fine threads 细牙螺纹fixed link, frame 固定构件flange coupling 凸缘联轴器flat belt 平带flat belt driving 平带传动flat leaf spring 板簧flat-face follower 平底从动件flexible automation 柔性自动化flexible impulse, soft shock 柔性冲击flexible manufacturing system, FMS 柔性制造系统flexible rotor 挠性转子flexspline 柔轮fluctuating circulating stress 脉动循环应力fluctuating load 脉动载荷Fluctuating loads 变载荷flywheel 飞轮follower dwell 从动件停歇follower motion 从动件运动规律force 力force polygon 力多边形force-drive (or force-closed) cammechanism 力封闭型凸轮机构forced vibration 强迫振动forge 锻造form cutting 仿形法form factor 齿形系数four-bar linkage 四杆机构frame, fixed link 机架freezing point, solidifying point 凝固点frequency 频率frequency control of motor speed 变频调速frequency converters 变频器frequency of vibration 振动频率friction 摩擦friction angle 摩擦角friction circle 摩擦圆friction force 摩擦力friction moment 摩擦力矩frictional resistance 摩擦阻力full balance of shaking force 惯性力完全平衡function analyses design 功能分析设计function generation 函数生成function generator 函数发生器fundamental law of gearing, fundamentallaw of gear-tooth action 齿廓啮合基本定律fundamental mechanism 基础机构fuzzy evaluation 模糊评价fuzzy set 模糊集Ggas bearing 气体轴承gasket 垫圈gasket seal 垫片密封gear 齿轮gear 齿轮机构—5—gear coupling 齿轮联轴器gear ratio 齿数比gear shaper 插齿机gear train 轮系gear wheel 大齿轮gearing, transmission gear, Actuations 传动装置general constraint 公共约束generalized coordinate 广义坐标generalized kinematic chain 一般化运动链generating 展成法generating cutting 范成法generating line 发生线generating line of involute 渐开线发生线generating plane 发生面generation mechanism 广义机构Geneva mechanism ；Maltese cross 槽轮机构Geneva numerate 槽数Geneva wheel 槽轮Geneva wheel, Geneva gear 马耳他机构graphical method 图解法Grashoff`s law 格拉晓夫定理Grashoff`s law 曲柄存在条件green design, design for environment 绿色设计grey cast iron 灰铸铁grinding wheel groove 砂轮越程槽groove cam 槽凸轮gyroscope 陀螺仪HH. Hertz equation 赫兹公式hands of worm 蜗杆旋向harmonic driving 谐波传动harmonic gear 谐波齿轮harmonic generator 谐波发生器heat balance, thermal equilibrium 热平衡height series 高度系列height series 高度系列helical bevel gear 螺旋锥齿轮helical gear 斜齿圆柱齿轮helical pair 螺旋副helical torsion spring 扭簧helix ,helical line 螺旋线helix angle 螺旋角helix angle at reference cylinder 分度圆柱螺旋角herringbone gear 人字齿轮high speed belt 高速带higher pair 高副hindley worm 直廓环面蜗杆hinge 铰链、枢纽hob 滚刀hob ,hobbing cutter 齿轮滚刀hollow flank worm 圆弧圆柱蜗杆Hooks coupling, universal coupling 万向联轴器hour-glass 砂漏hydraulic couplers 液力耦合器hydraulic mechanism 液压机构hydraulic stepless speed changes 液压无级变速hydrodynamic drive 液力传动hyperboloid gear 双曲面齿轮hypoid gear 准双曲面齿轮Iidle 空转idle gear 惰轮imbalance (or unbalance) 不平衡in-line slider-crank (or crank-slider)mechanism 对心曲柄滑块机构increment or decrement work 盈亏功inertia force 惯性力infinite 无穷大initial contact , beginning of contact 起始啮合点inner ring 内圈innovation, creation 创新input link 输入构件instantaneous center 瞬心instantaneous center of velocity 速度瞬心integrate 积分intelligent design, ID 智能化设计interchangeable gears 互换性齿轮interference 干涉intermittent gearing 不完全齿轮机构intermittent motion mechanism 间歇运动机构internal force 内力internal gear 内齿轮inverse ( or backward) kinematics 反向运动学inverse cam mechanism 凸轮倒置机构involute 渐开线involute equation 渐开线方程involute function 渐开线函数involute gear 渐开线齿轮involute helicoid 渐开螺旋面involute profile 渐开线齿廓involute spline 渐开线花键involute worm 渐开线蜗杆—6—Jjack 千斤顶Jacobi matrix 雅可比矩阵jaw (teeth) positive-contact coupling 牙嵌式联轴器jerk 跃度jerk diagram 跃度曲线jointed manipulator 关节型操作器journal 轴颈Kkenematic viscosity 运动粘度Kennedy`s theorem 三心定理key 键keyway 键槽kinematic analysis 运动分析kinematic chain 运动链kinematic design 运动设计kinematic design of mechanism 机构运动设计kinematic inversion 反转法kinematic inversion 机架变换kinematic inversion 运动倒置kinematic pair 运动副kinematic precept design 运动方案设计kinematic sketch 运动简图kinematic sketch of mechanism 机构运动简图kinematic synthesis 运动综合kinematical seal 动密封knife-edge follower 尖底从动件Llabyrinth seal 迷宫密封lathe 车床layout of cam profile 凸轮廓线绘制lead 导程lead 螺纹导程lead angle 导程角lead angle at reference cylinder 分度圆柱导程角leakage 泄漏length of line of action 啮合线长度lift 升距limit of action 极限啮合点line of action 啮合线line of centers 连心线linear motion 直线运动link 构件linkage 连杆机构lip rubber seal 唇形橡胶密封liquid spring 液体弹簧load 载荷load balancing mechanism 均衡装置load rating 额定载荷load—deformation curve 载荷load—deformation diagram 载荷loom 织布机lower pair 低副lubricant 润滑剂lubricant film 润滑油膜lubrication 润滑lubrication device 润滑装置Mmachine 机器machine design, mechanical design 机械设计machinery 机械magnetic fluid bearing 磁流体轴承Maltese cross 马耳他十字manipulator 机器人操作器manipulator 机械手mass 质量mass-radius product 质径积matching 拼接mathematic model 数学模型matrix 矩阵maximum difference work between plusand minus work 最大盈亏功mean diameter 中径mean screw diameter 平均中径mechanical advantage 机械利益mechanical behavior 机械特性mechanical creation design, MCD 机械创新设计mechanical efficiency 机械效率mechanical speed governors 机械调速mechanical stepless speed changes 机械无级变速mechanical system 机械系统mechanical system design, MSD 机械系统设计mechanical-electrical integration systemdesign 机电一体化系统设计mechanism 机构mechanism 机构学mechanism with flexible elements 挠性机构membership 隶属度metric gears 公制齿轮mid-plane 中间平面milled helicoids worm 锥面包络圆柱蜗杆minimum radius 最小向径minimum teeth number 最少齿数minor diameter 小径—7—modern machine design 机械的现代设计modification coefficient 变位系数modified gear 变位齿轮modified sine acceleration motion 修正正弦加速度运动规律modified trapezoidal acceleration motion 修正梯形加速度运动规律modular design, MD 模块化设计modular system 模块式传动系统modulation, regulation 调节module 模数moment 力矩moment of couple 力偶矩moment of flywheel 飞轮矩moment of inertia ,shaking moment 惯性力矩moment of torque 扭矩morphology box 模幅箱moving link 运动构件multi-diameter shaft 阶梯轴multi-row bearing 多列轴承Nneedle roller 滚针needle roller bearing 滚针轴承negetive allowarance 负公差nominal diameter 公称直径nominal stress 名义应力、公称应力Nomogram 诺模图non-circular gear 非圆齿轮non-contact seal 非接触式密封nonstandard gear 非标准齿轮normal circular pitch 法面齿距normal force 法向力normal load 垂直载荷、法向载荷normal module 法面模数normal parameters 法面参数normal pitch 法向齿距normal plane 法面normal pressure angle 法面压力角normal stress 正应力、法向应力normal tooth profile 法向齿廓number of threads 蜗杆头数number of waves 波数numerator 分子OO ring seal O 形密封圈密封objective function 目标函数offset 偏置式offset circle 偏距圆offset distance 偏offset knife-edge follower 偏置尖底从动件offset roller follower 偏置滚子从动件offset slider-crank mechanism 偏置曲柄滑块机构oil bearing 含油轴承oil bottle 油杯oil can 油壶oil consumption 耗油量oil consumption factor 耗油量系数oily ditch seal 油沟密封Oldham coupling 双转块机构on-net design, OND 网上设计open chain mechanism 开链机构open kinematic chain 开式链open-belt drive 开口传动operation control device 操纵及控制装置operation mechanism 工作机构optimal design 优化设计ordinary gear train, gear train with fixedaxes 定轴轮系ordinate 纵坐标original mechanism 原始机构oscillating bar 摆杆oscillating follower 摆动从动件oscillating guide-bar mechanism 摆动导杆机构other mechanism in common use 其他常用机构outer ring 外圈output link 输出构件output mechanism 输出机构output shaft 输出轴output torque 输出力矩output work 输出功overlap contact ratio 纵向重合度Ppacker 打包机paired mounting 成对安装parabolic motion 抛物线运动parabolic motion, constant accelerationand deceleration motion 等加等减速运动规律parallel combined mechanism 并联组合机构parallel helical gears 平面轴斜齿轮parallel key 普通平键parallel mechanism 并联机构parameterization design, PD 参数化设计partial balance of shaking force 惯性力部分平衡passive degree of freedom 局部自由度—8—path generation 轨迹生成path generator 轨迹发生器path of action 啮合轨迹pawl 棘爪pedal 踏板periodic speed fluctuation 周期性速度波动phase angle of unbalance 不平衡相位pin 销pinion 小齿轮pinion and rack 齿轮齿条机构pinion cutter, pinion-shaped shaper cutter 齿轮插刀pinion unit 齿轮传动系pitch 周节pitch circle 节圆pitch cone 节圆锥pitch cone angle 节圆锥角pitch curve 理论廓线pitch curve 凸轮理论廓线pitch diameter 节圆直径pitch line 节线pitch point 节点pitting （疲劳）点蚀planar cam 平面凸轮planar cam mechanism 平面凸轮机构planar kinematic pair 平面运动副planar linkage 平面连杆机构planar mechanism 平面机构planar pair, flat pair 平面副planet gear 行星轮planetary differential 封闭差动轮系planetary drive with small teeth difference 少齿差行星传动planetary gear train 行星轮系planetary speed changing devices 行星轮变速装置planetary transmission 行星齿轮装置plasticine 橡皮泥pneumatic mechanism 气动机构pointing, cusp 尖点polar coordinate manipulator 球坐标操作器poly V-belt 多楔带polynomial motion 多项式运动规律pose , position and orientation 位姿positive allowrance 正公差positive-drive (or form-closed) cam mechanism 形封闭凸轮机构potted component 密封元件powder metallurgy 粉末合金power 功率power screw 螺旋传动power spring 涡圈形盘簧preload 预紧力pressure 压力pressure angle 压力角pressure angle of base circle 基圆压力角pressure angle of involute 渐开线压力角prime mover 原动机primer mover 原动机prismatic joint 移动关节prismatic pair, sliding pair 移动副productive resistance 生产阻力pulsating stepless speed changes 脉动无级变速punch 冲床Qquadrant 象限quick-return characteristics 急回特性quick-return mechanism 急回机构quick-return motion 急回运动Rraceway 滚道rack 齿条rack cutter, rack-shaped shaper cutter齿条插刀rack gear 齿条传动radial (or in-line ) roller follower 对心滚子从动件radial (or in-line ) translating follower对心直动从动件radial bearing 向心轴承radial contact bearing 径向接触轴承radial direction 径向radial internal clearance 径向游隙radial load 径向载荷radial load factor 径向载荷系数radial plane 径向平面radial reciprocating follower 对心移动从动件radius of addendum 齿顶圆半径radius of base circle 基圆半径radius of curvature 曲率半径radius of roller 滚子半径rating life 额定寿命reciprocating follower 移动从动件reciprocating motion 往复移动reciprocating seal 往复式密封reduction gear 减速齿轮、减速装置reduction ratio 减速比redundant (or passive) constraint 虚约束redundant degree of freedom 冗余自由—9—度reference circle, standard (cutting) pitch circle 分度圆reference cone, standard pitch cone 分度圆锥reference line, standard pitch line 分度线regulator, governor 调速器relative gap 相对间隙relative motion 相对运动relative velocity 相对速度reliability 可靠性reliability design, RD 可靠性设计repeated fluctuating load 交变载荷repeated stress 交变应力residual stress 残余应力resistance 阻抗力resultant bending moment 合成弯矩resultant force 合力resultant force 总反力resultant moment of force 合力矩resultant moment of inertia 惯性主矩resultant vector of inertia 惯性主失return 回程revolute (turning) pair 转动副revolute joint 转动关节revolving shaft 转轴Reynolds‘s equation 雷诺方程right triangle 直角三角形rigid bearing 刚性轴承rigid circular spline 刚轮rigid coupling 刚性联轴器rigid impulse (shock) 刚性冲击rigid rotor 刚性转子ring gear 内齿圈rise 升程rise 推程rivet 铆钉robot 机器人robotics 机器人学robust design 稳健设计rocker 摇杆roller 滚子roller bearing 滚子轴承roller chain 滚子链roller clutch 滚柱式单向超越离合器roller follower 滚子从动件rolling bearing 滚动轴承rolling bearing identification code 滚动轴承代号rolling element 滚动体rotary motion 旋转运动rotating seal 旋转式密封rotor 转子rotor with several masses 多质量转子round belt 圆带round belt drive 圆带传动rubber-cushioned sleeve bearing coupling 弹性套柱销联轴器running torque 旋转力矩Ssafe load 安全载荷safety factor, factor of safety 安全系数scale 比例尺scoring 胶合screw 螺杆screw efficiency 螺纹效率screw mechanism 螺旋机构screw nut 螺母screws 螺钉seal 密封seal belt 密封带seal gum 密封胶sealing arrangement 密封装置section 截面self-aligning ball bearing 调心球轴承self-aligning bearing 调心轴承self-aligning roller bearing 调心滚子轴承self-locking 自锁series combined mechanism 串联式组合机构serration spline 三角形花键shaft 轴shaft angle 轴角shaft collar 轴环shaft end ring 轴端挡圈shaft shoulder 轴肩shaking couple 振动力矩shaper 牛头刨床shockproof device 防振装置shocks, shock-absorber 缓冲装置shortening coefficient of addendum 齿顶高缩短系数silent chain 齿形链、无声链simple harmonic motion 简谐运动sine generator, scotch yoke 正弦机构single row bearing 单列轴承single universal joint 单万向联轴节single-direction thrust bearing 单向推力轴承singular position 奇异位置six-bar linkage 六杆机构slack-side 松边sleeve 套筒slider 滑块slider-crank (or crank-slider) mechanism—10—曲柄滑块机构sliding bearing 滑动轴承sliding ratio 滑动率slipping 打滑solid lubricant 固体润滑剂spacewidth 齿槽宽spatial cam 空间凸轮机构spatial kinematic chain 空间运动链spatial kinematic pair 空间运动副spatial linkage 空间连杆机构spatial mechanism 空间机构special kinematic chain 特殊运动链specific heat capacity 比热容speed change 变速speed control system 调速系统speed fluctuation 速度波动speed governing 调速speed reducer 减速器speed-changing gear boxes 齿轮变速箱sphere-pin pair 球销副spheric pair 球面副spherical involute 球面渐开线spherical motion 球面运动spindle 心轴spiral bevel gear 曲齿锥齿轮spiral seal 螺旋密封spline 花键spontaneous ignition 燃点spring constant 弹簧[刚度]系数sprocket, sprocket-wheel, sprocket gear, chain wheel 链轮spur gear 直齿圆柱齿轮square threaded form 矩形螺纹square-jaw positive-contact clutch 矩形牙嵌式离合器stack mounting 组合安装standard addendum 标准齿顶高standard gear 标准齿轮standard spur gear 标准直齿轮starting period 起动阶段starting torque 启动力矩static balance 静平衡static equivalent axial load 轴向当量静载荷static equivalent radial load 径向当量静载荷static force 静力static load 静载荷static seal 静密封steady motion period 稳定运转阶段step pulley 塔轮stepless speed changes devices 无级变速装置stiffiness; rigidity; severity; toughness 刚度stiffness coefficient 刚度系数stopping phase 停车阶段straight bevel gear 直齿锥齿轮straight shaft 直轴straight sided normal worm 法向直廓蜗杆stress amplitude 应力幅stress concentration 应力集中stress diagram 应力图stress-strain diagram 应力structural design 结构设计structure 结构studs 双头螺柱sub-mechanism 子机构subroutine 子程序sun gear 太阳轮sunk key 嵌入键superficial mass factor 表面质量系数surface coefficient of heat transfer 表面传热系数surface of action 啮合曲面surface roughness 表面粗糙度swiveling speed, rotating speed 转速symmetry circulating stress 对称循环应力synchronous belt 同步带synchronous belt drive 同步带传动synthesis of mechanism 机构综合system of normal addendum 正常齿高制Ttangent mechanism 正切机构taper key 斜键、钩头楔键tapered roller 圆锥滚子tapered roller bearing 圆锥滚子轴承technical and economic evaluation 技术经济评价technique process 技术过程technique system 技术系统technological design 工艺设计tension 张紧力tension pulley 张紧轮theoretical line of action 理论啮合线theory of constitution 组成原理theory of machines and mechanisms 机械原理thickness on pitch circle 节圆齿厚third gear 三档thread (of a screw) 螺纹thread pitch 螺距three-dimensional cam 三维凸轮thrust ball bearing 推力球轴承thrust bearing 推力轴承tight-side 紧边toggle mechanism 肘形机构tool withdrawal groove 退刀槽tooth curve 齿廓曲线tooth number 齿数tooth profile 齿廓tooth ratchet mechanism 齿式棘轮机构tooth space 齿槽tooth thickness 齿厚toroid helicoids worm 环面蜗杆torsion stress 扭转应力total contact ratio 总重合度transmission angle 传动角transmission ratio, speed ratio 传动比transmission shaft 传动轴transverse circular pitch 端面齿距transverse contact ratio 端面重合度transverse module 端面模数transverse parameters 端面参数transverse plane 端面transverse pressure angle 端面压力角transverse tooth profile 端面齿廓tribology design, TD 摩擦学设计two-dimensional cam 两维凸轮type selection 选型Uundercutting 根切undercutting 过度切割undercutting 运动失真uniform motion, constant velocity motion 等速运动规律unit vector 单位矢量useful resistance 有益阻力useless resistance 有害阻力VV belt V带V thread screw 三角形螺纹tight-up V belt 联组V 带narrow V belt 窄V 带variable voltage control 调压调速vector 矢量velocity 速度velocity diagram 速度曲线vibration 振动vice 台钳、虎钳virtual reality 虚拟现实virtual reality design, VRD 虚拟现实设计virtual reality technology, VRT 虚拟现实技术viscosity 能量指示图Wwave generator 波发生器wear resistance 耐磨性wedge cam 移动凸轮weight sets 权重集weighting efficient 加权系数whitworth mechanism 转动导杆机构whole depth 全齿高width of flat-face 从动件平底宽度width series 宽度系列wire soft shaft 钢丝软轴woodruff key 半圆键work 功working cycle diagram 工作循环图working pressure angle, angle of action 啮合角working space 工作空间working stress 工作应力worm 蜗杆worm and worm gear 蜗杆蜗轮机构worm cam interval mechanism 蜗杆形凸轮步进机构worm gear 蜗轮worm gearing 蜗杆传动机构wrench 扳手wrist 腕部Zzone of action 啮合区域。
机械制造及自动化专业外文翻译--运动的综合,凸轮和齿轮
外文原文：Kinematic Synthesis ，Cams and Gears Mechanisms form the basic geometrical elements of many mechanical devices including automatic packaging machinery, typewriters, mechanical toys, textile machinery, and others. A mechanism typically is designed to create a desired motion of a rigid body relative to a reference member. Kinematic design, or kinematic syntheses, of mechanisms often is the first step in the design of a complete machine. When forces are considered, the additional problems of dynamics, bearing loads, stresses, lubrication, and the like are introduced, and the larger problem becomes one of machine design.A kinematician defined kinematics as “the study of the motion of mechanisms and methods of creating them.” The first part of this definition deals with kinematic analysis. Given a certain mechanism, the motion characteristics of its components will be determined by kinematic analysis. The statement of the tasks of analysis contains all principal dimensions of the mechanism, the interconnections of its links, and the specification of the input motion or method of actuation. The objective is to find the displacements, velocities, accelerations, shock or jerk (second acceleration) , and perhaps higher accelerations of the various members, as well as the paths described and motions performed by certain elements. In short, in kinematic analysis we determine the performance of a given mechanism. The second part of definition may be paraphrased in two ways:1. The study of methods of creating a given motion by means of mechanisms.2. The study of methods of creating mechanisms having a given motion.In either version, the motion is given and the mechanism is to be found. This is the essence of kinematic synthesis. Thus kinematic synthesis deals with the systematic design of mechanisms for a given performance. The area of synthesis may be grouped into two categories.1. Type synthesis. Given the required performance, what type of mechanism will be suitable? (Gear trains? Linkages? Cam mechanisms? ) Also, how many links should the mechanism have? How many degrees of freedom are required? What configuration id desirable? And so on. Deliberations involving the number of links and degrees of freedom are often referred to as the province of a subcategory of type synthesis called number synthesis.2. Dimensional synthesis. The second major category of kinematic synthesis is best defined by way of its objective: Dimensional synthesis seeks to determine the significant dimensions and the starting position of a mechanism of preconceived type for a specified task and prescribed performance.Significant dimensions mean link lengths or distances on binary, ternary, and so on, links, angles between axis, cam-contour dimensions and cam-follower diameters, eccentricities, gear rations, and so forth. A mechanism of preconceived type may be a slider-crank linkage, a four-bar linkage, a cam with flat follower, or a more complex linkage of a certain configuration defined topologically but not dimensionally. Thereare three customary tasks for kinematic synthesis: function generation, path generation and motion generation.In function generation mechanisms rotation or sliding motions of input and output links must be correlated. For an arbitrary function )(x f y =, a kinematic synthesis task may be to design a linkage to correlate input and output such that the input moves by x , the output moves by )(x f y = for the range 10+<<n x x x . In the case of rotary input and output, the angles of rotation ϕ and ψ are the linear analogs of x and y respectively. When the input link is rotated to a value of the independent x , the mechanism in a “black box” causes the output link to turn to the corresponding value of the dependent variable )(x f y =. This may be regarded as a simple case of a mechanical analog computer. A variety of different mechanisms cou ld be contained within the “black box”. However, the four -bar linkage is not capable of error-free generation of an arbitrary function and can match the function at only a limited number of precision points. It is widely used in industry because the four-bar linkage id simple to construct and maintain.In path generation mechanism a point on a “floating link” is to trace a path defined with respect to a fixed frame of reference. If the path points are to be correlated with either time or input-link positions, the task is called path generation with prescribed timing. An example of path generation mechanisms id a four-bar linkage designed to pitch a baseball or tennis ball. In this case the trajectory of point p would be such as to pick up a ball at a prescribed location and to deliver the ball along a prescribed path with prescribed timing for reaching a suitable throw-velocity and direction.There are many situations in the design of mechanical devises in which it is necessary either to guide a rigid body through a series of specified, finitely separated positions or to impose constraints on the velocity and/or acceleration of the moving body at a reduced number of finitely separated positions. Motion-generation or rigid-body guidance mechanism requires that an entire body be guided through a prescribed motion sequence. The body to be guided usually is a part of a floating link, of which not only is the path of a point p prescribed, but also the rotation of a line passing through the point and embedded in the body,. For instance, the line might represent a carrier link in a automatic machinery where a point located on the carrier link has a prescribed path while the carrier has a prescribed angular orientation. Prescribing the movement of the bucket for a bucket loader id another example of motion generation mechanisms, the path of tip of the bucket is critical since the tip must perform a scooping trajectory followed by a lifting and a dumping trajectory. The angular orientation of the bucket are equally important to ensure that load is dumped from the correct position.A cam is a convenient device for transforming one motion into another. Thismachine element has a curved or grooved surface which mates with a follower and imparts motion to it. The motion of the cam (usually rotation) is transformed into follower oscillation, translation, or both. Because of the various cam geometries and the large number of cam and follower combinations, the cam is an extremely versatile mechanical element. Although a cam and follower may be designed for motion, path, or function generation, the majority of applications utilize the cam and follower for function generation.The most common cam types according to cam shapes are: disk or plate translating (two-dimensional or planar), and cylindrical (three-dimensional or spatial) cams. Followers can be classified in several ways: according to follower motion, such as translation or oscillation; according to whether the translational (straight-line) follower motion is radial of offset from the center of the cam shaft; and according to the shape of the follower contact surface (e. g. , flat-face, roller, point (knife-edge), spherical, planar curved, or spatial-curved surface).In the case of a disk cam with a radial (in-line) translating roller follower the smallest circle that can be drawn tangent to the cam surface and concentric with the camshaft is the base circle. The tracer point is a point at the center of the roller center and the normal to the pitch curve. The pressure angle is the angle between the direction of the path of the roller center and the normal to the pitch curve through the center of the roller and is the complement of the transmission angle. Neglecting friction, this normal is collinear with the contact force between the cam and follower. As in a linkage, the pressure angle varies during the cycle and is a measure of the ability of the cam to transfer motive effort to the follower. A large pressure angle will produce an appreciable lateral force exerted on the stem of the follower, which, in the presence of friction, would tend to bind the follower in the guide.Numerous applications in automatic machinery require intermittent motion. A typical example will call for a rise-dwell-return and perhaps another dwell period of a specified number of degrees each, together with a required follower displacement measured in centimeters or degrees. The designer’s job is to lay out the cam accordingly. The first decision to be made is to choose the cam follower type. The specified application may dictate the combination of the cam and follower. Some factors that should enter into the decision are: geometric considerations, dynamic considerations, environmental considerations and economic matters. Once a type of cam and follower pair has been selected, the follower motion must be chosen. Therefore, the velocity, acceleration, and in some cases further derivatives of the displacement of the follower are of great importance.Gears are machine elements that transmit motion by means of successively engaging teeth. Gears transmit motion from one rotating shaft to another, or to a rack that translates. Numerous applications exist in which a constant angular velocity ratio (or constant torque ratio) must be transmitted between shafts. Based on the variety of gear types available, there is no restriction that the input and the output shafts need be either in-line or parallel. Nonlinear angular velocity ratios are also available by using noncircular gears. In order to maintain a constant angular velocity, the individual tooth profile must obey the fundamental law of gearing: for a pair of gears to transmita constant angular velocity ratio, the shape of their contacting profiles must be such that the common normal passes through a fixed point on the line of the centers.Any two mating tooth profiles that satisfy the fundamental law of gearing are called conjugate profiles. Although there are many tooth shapes possible in which a mating tooth could be designed to satisfy the fundamental law, only two are in general use: the cycloidal and involute profiles. The involute has important advantages: it is easy to manufacture and the center distance between a pair of involute gears can be varied without changing the velocity ratio. Thus chose tolerances between shafts are not required when utilizing the involute profile.There are several standard gear types. For applications with parallel shafts, straight spur gear, parallel helical, or herringbone gears are usually used. In the case of intersecting shafts, straight bevel of spiral bevel gears are employed. For nonintersecting and nonparallel shafts, crossed helical, worm, face, skew bevel or hypoid gears would be acceptable choices. For spur gears, the pitch circles of mating gears are tangent to each other. They roll on one another without sliding. The addendum is the height by which a tooth projects beyond the pitch circle (also the radial distance between the pitch circle and the addendum circle). The clearance is the amount by which the addendum (tooth height below the pitch circle) in a given gears exceeds the addendum of its mating gear. The tooth thickness is the distance across the tooth along the arc of the pitch circle while the tooth space is the distance between adjacent teeth along the arc of the pitch circle. The backlash is the amount by which the width of the tooth space exceeds the thickness of the engaging tooth at the pitch circle.中文译文：运动的综合，凸轮和齿轮机构是形成许多机械装置的基本几何结构单元，这些机械装置包括自动包装机、打印机、机械玩具、纺织机械和其他机械等。
机械设计专业术语的英语翻译1
双滑块机构double-slidermechanism,ellipsograph
双曲柄机构doublecrankmechanism
双曲面齿轮hyperboloidgear
双头螺柱studs
双万向联轴节constant-velocityordoubleuniversaljoint
外齿轮externalgear
弯曲应力beadingstress
弯矩bendingmoment
腕部wrist
往复移动reciprocatingmotion
往复式密封reciprocatingseal
网上设计on-netdesign,OND
微动螺旋机构differentialscrewmechanism
双摇杆机构doublerockermechanism
双转块机构Oldhamcoupling
双列轴承doublerowbearing
双向推力轴承double-directionthrustbearing
松边slack-side
顺时针clockwise
瞬心instantaneouscenter
斜齿轮的当量直齿轮equivalentspurgearofthehelicalgear
心轴spindle
行程速度变化系数coefficientoftravelspeedvariation
行程速比系数advance-toreturn-timeratio
行星齿轮装置planetarytransmission
原始机构originalmechanism
圆形齿轮circulargear
圆柱滚子cylindricalroller
关于凸轮设计的外文翻译-其他专业
关于凸轮的外文资料ELEMENTS OF CAM DESIGNHow to plan and produce simple but efficient cams for petrol engines and other mechanismsCams 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．Cams in some form or other are essential to the operation of many kinds of mechanical devices. Their best-known application is in the valve-operating gear of internal combustion engines, but they play an equally important part in industrial machinery, from printing presses to reaping machines.In general, a cam can be defined as a projection on the face of a disc or the surface of a cylinder for the purpose of producing intermittent reciprocating motion of a contacting member or follower. Most cams operate by rotary motion, but this is not an essential condition and in special cases the motion may be semi-rotary，oscillatoryor swinging. Even straight-line motion of the operating member is possible, though the term cam may not be considered properly applicable in such circumstances.Most text books on mechanics give some information on the design of cams and show examples of cam forms plotted to produce various orders of motion. Where neither the operating speed nor the mechanical duty is very high, there is a good deal of latitude in the nermissible design of the cam and it is only necessary to avoid excessively steep contours or abrupt changes which would result in noise, impact shock, and side pressure on the follower. But, with increase of either speed or load, much more exacting demands are made on the cam, calling for the most careful design and, at very high speed, the effect of inertia on the moving parts is most pronounced, so that the further factors of acceleration and rate of lift have to be taken into account and these are rarely dealt with in any detail in the standard text books.The design of the cam follower is also of great importance and bears a definite relation to the shape of the cam itself. This is because the cam cannot make contact with the follower at a single fixed point. Surface contact is necessary to distribute load and avoid excess wear, thus the cam transmits its motion through various points of location on the follower, depending on the shape of the two complementary cams for operating . engine valves present specially difficult problems in design. In the case of racing engines, both the load and speed may be regarded as extreme, because in many engines the rate at which the valves can be effectively controlled is the limiting factor in engine performance. In some respects, cam design of miniature engines is simplified by reason of their lighter working parts (and consequent less inertia) but on the other hand, working friction is usually greater and rotational speeds are generally considerably higher than in full-size practice.In the many designs for small four-stroke engines which I have published, I have sought to simplify valve operation and to provide designs for cams which can be simply and accurately produced with the facilities of the amateur workshop. Numerous engine designs which have been submitted to me by readers have contained errors in the valve gear and particularly in the cams and in view of prevalent misconceptions in the fundamental principles of these items, I am givingsome advice on the matter which I trust will help individual designers to obtain the best results from their engines. There have been many engines built with cams of thoroughly bad design but which, in spite of this, have produced results more or less satisfactory to their constructors. It may be said that within certain limits of speed one can get away with murder but in no case can an engine perform efficiently with badly designed cams, or indeed errors in any of its working details. This article is concerned mainly with the design of cams for operating the valves of . engines and, in order to avoid any confusion of terms, Fig. 1 shows the various parts of a cam of this type and explains their functions. The circular, concentric portion of the cam, which has no operative effect, is known as the base circle: the humy of the cam (shown shaded) is known as the lobe, and the flanks on either side rise from the base circle to the nose, which is usually may be defined as the difference between the radius of the base circle and that of the nose. the anele enclosed between the points where the flanks join the base circle is termed the angular ‘period, representing the proportion of the full cycle during which the cam operates the valve gear. In Fig. 2, typical examples of cams used in . engines are illustrated. The tangent cam, A, has dead straightflanks-which as the name implies form tangents to the base circle. This type of cam is easy to design and produce, the simplest method of machining being by a circular milling process forming a concentric surface on the base circle and running straight out tangentially where the flanks start and finish. It can also be produced by filing and I have in the past described how to make it with the aid of a roller filing rest in the lathe, in conjunction with indexing gear to locate the flank angles.Tangent cams can only work efficiently in conjunction with a convex curved follower, as this is the only way in which the flank can be brought progressively and smoothly into action. Some time ago an engine was described having tangent cams in conjunction with flat followers. This was not intended for extremely high speed and very likely produced all the power required of it, but it is quite clear that the flat face of the tangent cam. On engaging the flat tappet-over the full length of the flank all at once, must produce an abrupt slapping action which is noisy, inefficient and destructive in the long run. Rollers are often used as followers with tangent cams andare satisfactory in respect of their shape, but the idea of introducing rolling motion at this point is not as good as it seems at first sight, because it merely transfers the sliding friction to a much smaller area--that of the pivot pin. It is possible in some cases, however, to use a ball or roller race for the follower and this, at any rate, has the merit of distributing and equalizing the wearing surface.Tangent cams have been used with a certain degree of success forhigh-performance-engines and were at one time popular on racing motorcycle engines, though usually with some slight modification of shape-often “ designed ” by the tuner with the aid of .a Carborundum slip! Their more common application, however, has been on gas and oil engines running at relatively slow speeds, where they work wellin contact with rollers attached to the ends of the valve rockers. Cams with convex flanks are extensively used in motor cars and other mass-produced engines. One important advantage in this respect is that they are suited to manufacture in quantity by a copying process from accurately formed master cams. The fact that hat-based tappets can be used also favours quantity production and they can be designed to work fairly silently. The contour of the flank can be plotted so that violent changes in the acceleration of the cam are avoided and, more important still, the tappet will follow the cam on the return motion without any tendency to bounce or float at quite high speeds. In such cases, it may be necessary to introduce compound curves which are extremely difficult to copy on a small scale, but cams made with flanks formmg true circular arcs will give reasonably efficient results, and are very easily produced in any scale: Concave-flanked cams.Comparatively few examples of concave-flanked cams (Fig. 2c) are to be seen nowadays, though they have been used extensively in the past with the idea of obtaining the most rapid opening and closing of the valves. Theoretically, they can be designed to produce constant-acceleration, but in practice they render valve control very difficult at high speed and their fierce angle of attack produces heavy side pressure on the tappet. The concave flank must always have a substantially greater radius than the follower, or a slapping action like that of a tangent cam on a flat follower is produced.The shape of the nose in most types of cams is dictated mainly by the need to decelerate the follower as smoothly as possible. It is one thing to design it in such a way that ideal conditions are obtained, and quite another to ensure in practice that the follower retains close contact with the cam. If the radius of the nose is too small, the follower will bounce and come down heavily on the return flank of the cam and,. if too great, valve opening efficiency will be reduced.Of the three types of cams, A, B and C, which all have identically equal lift and angular period, the lobe of B encloses the smallest area, and on first sight it might appear that it is the least efficient in producing adequate valve opening, or mean lift area, but owing to the use of a flat based tappet, its lift characteristics are not very different from those of a tangent cam with round-based tappet, and not necessarily inferior to those of a concave-flank cam.Unsymmetrical camsIt is not common to make the two flanks of a cam of different contours to produce some particular result which the designer may consider desirable. In some cases, the object is to produce rapid opening and gradual closing, but sometimes the opposite effect is preferred. When all things are considered, however, most attempts to monkey about with cam forms lead to complications which may actually defeat their own object, at least at really high speeds.In many engines, particularly those of motorcycles, the cams operate the valves through levers or rockers which move in an arc instead of in a straight line, as in the orthodox motor car tappet. This may be mechanically efficient, but it modifies the lift characteristic of the cam, as the point at which the latter transmits motion to the follower varies in relation to the radius of the lever arm, (Fig. 3).With the cam rotating in a clockwise direction, the effective length of the lever will be greater in the position.A during valve opening than in positionB during closing, as indicated by dimensions X and Y. This amounts to the same as using an unsymmetrical cam, and in the example shown, would result in slow opening and rapid closing of the valve, or vice versa if either the direction of r otation of the cam, or the relative “hand ” of thelever, is reversed. The shorter the lever, the greater the discrepancy in the rate of movement, Neither the unsymmetrical cam form nor the pivoted lever is condemned as bad design, but I have sought to avoid them in most of the engines I have designed because they are a complicating factor in what is already a very involved problem, and by keeping to fairly simple cams and straight-line tappets, one can be assured that there are not too many snags.The employment of cams with flanks of true circular arc has enabled me to devise means of producing them on the lathe without elaborate attachments and, what is more important still, to produce an entire set of cams for a multi-cylinder engine in correct angular relation to each other by equally simple means. There is no doubt whatever that these methods have enabled many engine constructors (some without previous experience) to tackle successfully a problem which would otherwise have been formidable, to say the least.Many designers have attempted to improve valve efficiency by designing cams which hold the valve at maximum opening for as long a period as possible. This is done by providing dwell or, in other words, making the top of the lobe concentric with the cam axis over a certain angular distance in the center of its lift. To do this, however, it is necessary to make the flanks excessively steep, thus producing heavy side thrust on the tappet, and making control at high speed more difficult, (Fig. 4A).A little consideration, however, will show that the same result can be achieved, with much less mechanical difficulty, by lifting the valve somewhat higher at an easier rate, as shown at B. This avoids the need for sudden acceleration and deceleration of the tappet and promotes flow efficiency of the valve. The shaded portions of the two cams show the differences in the area of the lobe, showing that nothing is really gained by the dwell. Factors in efficiency High valve lift is a desirable feature, but only if it can be obtained without making extra difficulties in controlling the valve. The maximum port area of a valve is obtained when the lift is equal to one-fourth of the seat diameter, but owing to the baffling effect on the valve head, a higher lift is better for flow efficiency-if it is practicable.中文翻译凸轮设计的基本内容如何为汽油发动机和其他机械设计和生产简单有效的凸轮凸轮是被应用的最广泛的机械结构之一。
机械设计专业英语
机械设计专业英语圆柱螺旋扭转弹簧cylindroid helical—coil torsion spring圆柱螺旋压缩弹簧cylindroid helical—coil compression spring圆柱凸轮cylindrical cam圆柱蜗杆cylindrical worm圆柱坐标操作器cylindrical coordinate manipulator圆锥螺旋扭转弹簧conoid helical—coil compression spring圆锥滚子tapered roller圆锥滚子轴承tapered roller bearing圆锥齿轮机构bevel gears圆锥角cone angle原动件driving link约束constraint约束条件constraint condition约束反力constraining force跃度jerk跃度曲线jerk diagram运动倒置kinematic inversion运动方案设计kinematic precept design运动分析kinematic analysis运动副kinematic pair运动构件moving link运动简图kinematic sketch运动链kinematic chain运动失真undercutting运动设计kinematic design运动周期cycle of motion运动综合kinematic synthesis运转不均匀系数coefficient of velocity fluctuation运动粘度kenematic viscosity载荷load载荷—变形曲线load—deformation curve 载荷—变形图load—deformation diagram 窄V 带narrow V belt毡圈密封felt ring seal展成法generating张紧力tension 张紧轮tension pulley振动vibration振动力矩shaking couple振动频率frequency of vibration振幅amplitude of vibration正切机构tangent mechanism正向运动学direct （forward）kinematics 正弦机构sine generator，scotch yoke织布机loom正应力、法向应力normal stress制动器brake直齿圆柱齿轮spur gear直齿锥齿轮straight bevel gear直角三角形right triangle直角坐标操作器Cartesian coordinate manipulator直径系数diametral quotient直径系列diameter series直廓环面蜗杆hindley worm直线运动linear motion直轴straight shaft质量mass质心center of mass执行构件executive link；working link质径积mass—radius product智能化设计intelligent design, ID中间平面mid-plane中心距center distance中心距变动center distance change中心轮central gear中径mean diameter终止啮合点final contact，end of contact 周节pitch周期性速度波动periodic speed fluctuation 周转轮系epicyclic gear train肘形机构toggle mechanism轴shaft轴承盖bearing cup轴承合金bearing alloy轴承座bearing block轴承高度bearing height轴承宽度bearing width轴承内径bearing bore diameter轴承寿命bearing life轴承套圈bearing ring轴承外径bearing outside diameter轴颈journal轴瓦、轴承衬bearing bush轴端挡圈shaft end ring轴环shaft collar轴肩shaft shoulder轴角shaft angle轴向axial direction轴向齿廓axial tooth profile轴向当量动载荷dynamic equivalent axial load轴向当量静载荷static equivalent axial load 轴向基本额定动载荷basic dynamic axial load rating轴向基本额定静载荷basic static axial load rating轴向接触轴承axial contact bearing轴向平面axial plane轴向游隙axial internal clearance轴向载荷axial load轴向载荷系数axial load factor轴向分力axial thrust load主动件driving link主动齿轮driving gear主动带轮driving pulley转动导杆机构whitworth mechanism转动副revolute (turning) pair转速swiveling speed ; rotating speed转动关节revolute joint转轴revolving shaft转子rotor转子平衡balance of rotor装配条件assembly condition锥齿轮bevel gear锥顶common apex of cone锥距cone distance锥轮bevel pulley; bevel wheel锥齿轮的当量直齿轮equivalent spur gear of the bevel gear锥面包络圆柱蜗杆milled helicoids worm准双曲面齿轮hypoid gear子程序subroutine 子机构sub-mechanism自动化automation自锁self-locking自锁条件condition of self—locking自由度degree of freedom, mobility总重合度total contact ratio总反力resultant force总效率combined efficiency; overall efficiency组成原理theory of constitution组合齿形composite tooth form组合安装stack mounting组合机构combined mechanism阻抗力resistance最大盈亏功maximum difference work between plus and minus work纵向重合度overlap contact ratio纵坐标ordinate组合机构combined mechanism最少齿数minimum teeth number最小向径minimum radius作用力applied force坐标系coordinate frame行星轮变速装置planetary speed changing devices行星轮系planetary gear train形封闭凸轮机构positive-drive (or form-closed) cam mechanism虚拟现实virtual reality虚拟现实技术virtual reality technology，VRT虚拟现实设计virtual reality design, VRD虚约束redundant （or passive）constraint 许用不平衡量allowable amount of unbalance许用压力角allowable pressure angle许用应力allowable stress; permissible stress 悬臂结构cantilever structure悬臂梁cantilever beam循环功率流circulating power load旋转力矩running torque旋转式密封rotating seal旋转运动rotary motion选型type selection压力pressure压力中心center of pressure压缩机compressor压应力compressive stress压力角pressure angle牙嵌式联轴器jaw (teeth）positive—contact coupling雅可比矩阵Jacobi matrix摇杆rocker液力传动hydrodynamic drive液力耦合器hydraulic couplers液体弹簧liquid spring液压无级变速hydraulic stepless speed changes液压机构hydraulic mechanism一般化运动链generalized kinematic chain 移动从动件reciprocating follower移动副prismatic pair, sliding pair移动关节prismatic joint移动凸轮wedge cam盈亏功increment or decrement work应力幅stress amplitude应力集中stress concentration应力集中系数factor of stress concentration 应力图stress diagram应力—应变图stress-strain diagram优化设计optimal design油杯oil bottle油壶oil can油沟密封oily ditch seal有害阻力useless resistance有益阻力useful resistance有效拉力effective tension有效圆周力effective circle force有害阻力detrimental resistance余弦加速度运动cosine acceleration （or simple harmonic) motion预紧力preload原动机primer mover圆带round belt圆带传动round belt drive圆弧齿厚circular thickness 圆弧圆柱蜗杆hollow flank worm圆角半径fillet radius圆盘摩擦离合器disc friction clutch圆盘制动器disc brake原动机prime mover原始机构original mechanism圆形齿轮circular gear圆柱滚子cylindrical roller圆柱滚子轴承cylindrical roller bearing圆柱副cylindric pair圆柱式凸轮步进运动机构barrel （cylindric) cam圆柱螺旋拉伸弹簧cylindroid helical-coil extension spring凸轮cam凸轮倒置机构inverse cam mechanism凸轮机构cam ，cam mechanism凸轮廓线cam profile凸轮廓线绘制layout of cam profile凸轮理论廓线pitch curve凸缘联轴器flange coupling图册、图谱atlas图解法graphical method推程rise推力球轴承thrust ball bearing推力轴承thrust bearing退刀槽tool withdrawal groove退火anneal陀螺仪gyroscopeV 带V belt外力external force外圈outer ring外形尺寸boundary dimension万向联轴器Hooks coupling ; universal coupling外齿轮external gear弯曲应力beading stress弯矩bending moment腕部wrist往复移动reciprocating motion往复式密封reciprocating seal网上设计on-net design，OND微动螺旋机构differential screw mechanism 位移displacement位移曲线displacement diagram位姿pose , position and orientation稳定运转阶段steady motion period稳健设计robust design蜗杆worm蜗杆传动机构worm gearing蜗杆头数number of threads蜗杆直径系数diametral quotient蜗杆蜗轮机构worm and worm gear蜗杆形凸轮步进机构worm cam interval mechanism蜗杆旋向hands of worm蜗轮worm gear涡圈形盘簧power spring无级变速装置stepless speed changes devices无穷大infinite系杆crank arm, planet carrier现场平衡field balancing向心轴承radial bearing向心力centrifugal force相对速度relative velocity相对运动relative motion相对间隙relative gap象限quadrant橡皮泥plasticine细牙螺纹fine threads销pin消耗consumption小齿轮pinion小径minor diameter橡胶弹簧balata spring修正梯形加速度运动规律modified trapezoidal acceleration motion修正正弦加速度运动规律modified sine acceleration motion斜齿圆柱齿轮helical gear斜键、钩头楔键taper key泄漏leakage谐波齿轮harmonic gear谐波传动harmonic driving谐波发生器harmonic generator 斜齿轮的当量直齿轮equivalent spur gear of the helical gear心轴spindle行程速度变化系数coefficient of travel speed variation行程速比系数advance—to return-time ratio 行星齿轮装置planetary transmission行星轮planet gear平衡机balancing machine平衡品质balancing quality平衡平面correcting plane平衡质量balancing mass平衡重counterweight平衡转速balancing speed平面副planar pair，flat pair平面机构planar mechanism平面运动副planar kinematic pair平面连杆机构planar linkage平面凸轮planar cam平面凸轮机构planar cam mechanism平面轴斜齿轮parallel helical gears普通平键parallel key其他常用机构other mechanism in common use起动阶段starting period启动力矩starting torque气动机构pneumatic mechanism奇异位置singular position起始啮合点initial contact ，beginning of contact气体轴承gas bearing千斤顶jack嵌入键sunk key强迫振动forced vibration切齿深度depth of cut曲柄crank曲柄存在条件Grashoff`s law曲柄导杆机构crank shaper （guide—bar) mechanism曲柄滑块机构slider—crank (or crank-slider) mechanism曲柄摇杆机构crank—rocker mechanism曲齿锥齿轮spiral bevel gear曲率curvature曲率半径radius of curvature曲面从动件curved-shoe follower曲线拼接curve matching曲线运动curvilinear motion曲轴crank shaft驱动力driving force驱动力矩driving moment （torque）全齿高whole depth权重集weight sets球ball球面滚子convex roller球轴承ball bearing球面副spheric pair球面渐开线spherical involute球面运动spherical motion球销副sphere-pin pair球坐标操作器polar coordinate manipulator 燃点spontaneous ignition热平衡heat balance; thermal equilibrium人字齿轮herringbone gear冗余自由度redundant degree of freedom柔轮flexspline柔性冲击flexible impulse；soft shock柔性制造系统flexible manufacturing system; FMS柔性自动化flexible automation润滑油膜lubricant film润滑装置lubrication device润滑lubrication润滑剂lubricant三角形花键serration spline三角形螺纹V thread screw三维凸轮three—dimensional cam三心定理Kennedy`s theorem砂轮越程槽grinding wheel groove砂漏hour—glass少齿差行星传动planetary drive with small teeth difference设计方法学design methodology设计变量design variable设计约束design constraints深沟球轴承deep groove ball bearing生产阻力productive resistance 升程rise升距lift螺旋角helix angle螺旋线helix ,helical line绿色设计green design ；design for environment马耳他机构Geneva wheel ; Geneva gear马耳他十字Maltese cross脉动无级变速pulsating stepless speed changes脉动循环应力fluctuating circulating stress 脉动载荷fluctuating load铆钉rivet迷宫密封labyrinth seal密封seal密封带seal belt密封胶seal gum密封元件potted component密封装置sealing arrangement面对面安装face—to-face arrangement面向产品生命周期设计design for product`s life cycle，DPLC名义应力、公称应力nominal stress模块化设计modular design, MD模块式传动系统modular system模幅箱morphology box模糊集fuzzy set模糊评价fuzzy evaluation模数module摩擦friction摩擦角friction angle摩擦力friction force摩擦学设计tribology design, TD摩擦阻力frictional resistance摩擦力矩friction moment摩擦系数coefficient of friction摩擦圆friction circle磨损abrasion ;wear；scratching末端执行器end-effector目标函数objective function耐腐蚀性corrosion resistance耐磨性wear resistance挠性机构mechanism with flexible elements挠性转子flexible rotor内齿轮internal gear内齿圈ring gear内力internal force内圈inner ring能量energy能量指示图viscosity逆时针counterclockwise (or anticlockwise）啮出engaging-out啮合engagement，mesh, gearing啮合点contact points啮合角working pressure angle啮合线line of action啮合线长度length of line of action啮入engaging-in牛头刨床shaper凝固点freezing point; solidifying point扭转应力torsion stress扭矩moment of torque扭簧helical torsion spring诺模图NomogramO 形密封圈密封O ring seal盘形凸轮disk cam盘形转子disk-like rotor抛物线运动parabolic motion疲劳极限fatigue limit疲劳强度fatigue strength偏置式offset偏（心) 距offset distance偏心率eccentricity ratio偏心质量eccentric mass偏距圆offset circle偏心盘eccentric偏置滚子从动件offset roller follower偏置尖底从动件offset knife—edge follower 偏置曲柄滑块机构offset slider—crank mechanism拼接matching评价与决策evaluation and decision频率frequency平带flat belt平带传动flat belt driving平底从动件flat—face follower平底宽度face width 平分线bisector平均应力average stress平均中径mean screw diameter平均速度average velocity平衡balance可靠度degree of reliability可靠性reliability可靠性设计reliability design, RD空气弹簧air spring空间机构spatial mechanism空间连杆机构spatial linkage空间凸轮机构spatial cam空间运动副spatial kinematic pair空间运动链spatial kinematic chain空转idle宽度系列width series框图block diagram雷诺方程Reynolds‘s equation离心力centrifugal force离心应力centrifugal stress离合器clutch离心密封centrifugal seal理论廓线pitch curve理论啮合线theoretical line of action隶属度membership力force力多边形force polygon力封闭型凸轮机构force—drive (or force—closed）cam mechanism力矩moment力平衡equilibrium力偶couple力偶矩moment of couple连杆connecting rod，coupler连杆机构linkage连杆曲线coupler-curve连心线line of centers链chain链传动装置chain gearing链轮sprocket ；sprocket-wheel ；sprocket gear ；chain wheel联组V 带tight-up V belt联轴器coupling ; shaft coupling两维凸轮two—dimensional cam临界转速critical speed六杆机构six—bar linkage龙门刨床double Haas planer轮坯blank轮系gear train螺杆screw螺距thread pitch螺母screw nut螺旋锥齿轮helical bevel gear螺钉screws螺栓bolts螺纹导程lead螺纹效率screw efficiency螺旋传动power screw螺旋密封spiral seal螺纹thread （of a screw）螺旋副helical pair螺旋机构screw mechanism基本额定寿命basic rating life基于实例设计case—based design，CBD基圆base circle基圆半径radius of base circle基圆齿距base pitch基圆压力角pressure angle of base circle基圆柱base cylinder基圆锥base cone急回机构quick—return mechanism急回特性quick-return characteristics急回系数advance—to return—time ratio急回运动quick-return motion棘轮ratchet棘轮机构ratchet mechanism棘爪pawl极限位置extreme (or limiting）position极位夹角crank angle between extreme (or limiting）positions计算机辅助设计computer aided design, CAD计算机辅助制造computer aided manufacturing，CAM计算机集成制造系统computer integrated manufacturing system，CIMS计算力矩factored moment；calculation moment 计算弯矩calculated bending moment加权系数weighting efficient加速度acceleration加速度分析acceleration analysis加速度曲线acceleration diagram尖点pointing; cusp尖底从动件knife-edge follower间隙backlash间歇运动机构intermittent motion mechanism减速比reduction ratio减速齿轮、减速装置reduction gear减速器speed reducer减摩性anti-friction quality渐开螺旋面involute helicoid渐开线involute渐开线齿廓involute profile渐开线齿轮involute gear渐开线发生线generating line of involute渐开线方程involute equation渐开线函数involute function渐开线蜗杆involute worm渐开线压力角pressure angle of involute渐开线花键involute spline简谐运动simple harmonic motion键key键槽keyway交变应力repeated stress交变载荷repeated fluctuating load交叉带传动cross—belt drive交错轴斜齿轮crossed helical gears胶合scoring角加速度angular acceleration角速度angular velocity角速比angular velocity ratio角接触球轴承angular contact ball bearing 角接触推力轴承angular contact thrust bearing角接触向心轴承angular contact radial bearing角接触轴承angular contact bearing铰链、枢纽hinge校正平面correcting plane接触应力contact stress接触式密封contact seal阶梯轴multi—diameter shaft结构structure结构设计structural design截面section节点pitch point节距circular pitch；pitch of teeth节线pitch line节圆pitch circle节圆齿厚thickness on pitch circle节圆直径pitch diameter节圆锥pitch cone节圆锥角pitch cone angle解析设计analytical design紧边tight-side紧固件fastener径节diametral pitch径向radial direction径向当量动载荷dynamic equivalent radial load径向当量静载荷static equivalent radial load 径向基本额定动载荷basic dynamic radial load rating径向基本额定静载荷basic static radial load tating径向接触轴承radial contact bearing径向平面radial plane径向游隙radial internal clearance径向载荷radial load径向载荷系数radial load factor径向间隙clearance静力static force静平衡static balance静载荷static load静密封static seal局部自由度passive degree of freedom矩阵matrix矩形螺纹square threaded form锯齿形螺纹buttress thread form矩形牙嵌式离合器square—jaw positive—contact clutch绝对尺寸系数absolute dimensional factor绝对运动absolute motion绝对速度absolute velocity 均衡装置load balancing mechanism抗压强度compression strength开口传动open-belt drive开式链open kinematic chain开链机构open chain mechanism高度系列height series功work工况系数application factor工艺设计technological design工作循环图working cycle diagram工作机构operation mechanism工作载荷external loads工作空间working space工作应力working stress工作阻力effective resistance工作阻力矩effective resistance moment公法线common normal line公共约束general constraint公制齿轮metric gears功率power功能分析设计function analyses design共轭齿廓conjugate profiles共轭凸轮conjugate cam构件link鼓风机blower固定构件fixed link；frame固体润滑剂solid lubricant关节型操作器jointed manipulator惯性力inertia force惯性力矩moment of inertia ，shaking moment惯性力平衡balance of shaking force惯性力完全平衡full balance of shaking force惯性力部分平衡partial balance of shaking force惯性主矩resultant moment of inertia惯性主失resultant vector of inertia冠轮crown gear广义机构generation mechanism广义坐标generalized coordinate轨迹生成path generation轨迹发生器path generator滚刀hob滚道raceway滚动体rolling element滚动轴承rolling bearing滚动轴承代号rolling bearing identification code滚针needle roller滚针轴承needle roller bearing滚子roller滚子轴承roller bearing滚子半径radius of roller滚子从动件roller follower滚子链roller chain滚子链联轴器double roller chain coupling 滚珠丝杆ball screw滚柱式单向超越离合器roller clutch过度切割undercutting函数发生器function generator函数生成function generation含油轴承oil bearing耗油量oil consumption耗油量系数oil consumption factor赫兹公式H. Hertz equation合成弯矩resultant bending moment合力resultant force合力矩resultant moment of force黑箱black box横坐标abscissa互换性齿轮interchangeable gears花键spline滑键、导键feather key滑动轴承sliding bearing滑动率sliding ratio滑块slider环面蜗杆toroid helicoids worm环形弹簧annular spring缓冲装置shocks; shock—absorber灰铸铁grey cast iron回程return回转体平衡balance of rotors混合轮系compound gear train积分integrate机电一体化系统设计mechanical—electrical integration system design机构mechanism 机构分析analysis of mechanism机构平衡balance of mechanism机构学mechanism机构运动设计kinematic design of mechanism机构运动简图kinematic sketch of mechanism机构综合synthesis of mechanism机构组成constitution of mechanism机架frame，fixed link机架变换kinematic inversion机器machine机器人robot机器人操作器manipulator机器人学robotics技术过程technique process技术经济评价technical and economic evaluation技术系统technique system机械machinery机械创新设计mechanical creation design，MCD机械系统设计mechanical system design, MSD机械动力分析dynamic analysis of machinery机械动力设计dynamic design of machinery 机械动力学dynamics of machinery机械的现代设计modern machine design机械系统mechanical system机械利益mechanical advantage机械平衡balance of machinery机械手manipulator机械设计machine design; mechanical design 机械特性mechanical behavior机械调速mechanical speed governors机械效率mechanical efficiency机械原理theory of machines and mechanisms机械运转不均匀系数coefficient of speed fluctuation机械无级变速mechanical stepless speed changes基础机构fundamental mechanism端面transverse plane端面参数transverse parameters端面齿距transverse circular pitch端面齿廓transverse tooth profile端面重合度transverse contact ratio端面模数transverse module端面压力角transverse pressure angle锻造forge对称循环应力symmetry circulating stress对心滚子从动件radial (or in-line ) roller follower对心直动从动件radial （or in—line ）translating follower对心移动从动件radial reciprocating follower对心曲柄滑块机构in-line slider—crank (or crank-slider）mechanism多列轴承multi—row bearing多楔带poly V-belt多项式运动规律polynomial motion多质量转子rotor with several masses惰轮idle gear额定寿命rating life额定载荷load ratingII 级杆组dyad发生线generating line发生面generating plane法面normal plane法面参数normal parameters法面齿距normal circular pitch法面模数normal module法面压力角normal pressure angle法向齿距normal pitch法向齿廓normal tooth profile法向直廓蜗杆straight sided normal worm法向力normal force反馈式组合feedback combining反向运动学inverse （or backward）kinematics反转法kinematic inversion反正切Arctan范成法generating cutting仿形法form cutting方案设计、概念设计concept design, CD 防振装置shockproof device飞轮flywheel飞轮矩moment of flywheel非标准齿轮nonstandard gear非接触式密封non-contact seal非周期性速度波动aperiodic speed fluctuation非圆齿轮non-circular gear粉末合金powder metallurgy分度线reference line；standard pitch line分度圆reference circle；standard （cutting）pitch circle分度圆柱导程角lead angle at reference cylinder分度圆柱螺旋角helix angle at reference cylinder分母denominator分子numerator分度圆锥reference cone；standard pitch cone分析法analytical method封闭差动轮系planetary differential复合铰链compound hinge复合式组合compound combining复合轮系compound （or combined）gear train复合平带compound flat belt复合应力combined stress复式螺旋机构Compound screw mechanism 复杂机构complex mechanism杆组Assur group干涉interference刚度系数stiffness coefficient刚轮rigid circular spline钢丝软轴wire soft shaft刚体导引机构body guidance mechanism刚性冲击rigid impulse (shock)刚性转子rigid rotor刚性轴承rigid bearing刚性联轴器rigid coupling高度系列height series高速带high speed belt高副higher pair格拉晓夫定理Grashoff`s law根切undercutting公称直径nominal diameter阿基米德蜗杆Archimedes worm安全系数safety factor; factor of safety安全载荷safe load凹面、凹度concavity扳手wrench板簧flat leaf spring半圆键woodruff key变形deformation摆杆oscillating bar摆动从动件oscillating follower摆动从动件凸轮机构cam with oscillating follower摆动导杆机构oscillating guide-bar mechanism摆线齿轮cycloidal gear摆线齿形cycloidal tooth profile摆线运动规律cycloidal motion摆线针轮cycloidal-pin wheel包角angle of contact保持架cage背对背安装back—to—back arrangement背锥back cone ；normal cone背锥角back angle背锥距back cone distance比例尺scale比热容specific heat capacity闭式链closed kinematic chain闭链机构closed chain mechanism臂部arm变频器frequency converters变频调速frequency control of motor speed 变速speed change变速齿轮change gear ；change wheel变位齿轮modified gear变位系数modification coefficient标准齿轮standard gear标准直齿轮standard spur gear表面质量系数superficial mass factor表面传热系数surface coefficient of heat transfer表面粗糙度surface roughness并联式组合combination in parallel 并联机构parallel mechanism并联组合机构parallel combined mechanism 并行工程concurrent engineering并行设计concurred design, CD不平衡相位phase angle of unbalance不平衡imbalance （or unbalance)不平衡量amount of unbalance不完全齿轮机构intermittent gearing波发生器wave generator波数number of waves补偿compensation参数化设计parameterization design，PD 残余应力residual stress操纵及控制装置operation control device槽轮Geneva wheel槽轮机构Geneva mechanism ; Maltese cross 槽数Geneva numerate槽凸轮groove cam侧隙backlash差动轮系differential gear train差动螺旋机构differential screw mechanism 差速器differential常用机构conventional mechanism；mechanism in common use车床lathe承载量系数bearing capacity factor承载能力bearing capacity成对安装paired mounting尺寸系列dimension series齿槽tooth space齿槽宽spacewidth齿侧间隙backlash齿顶高addendum齿顶圆addendum circle齿根高dedendum齿根圆dedendum circle齿厚tooth thickness齿距circular pitch齿宽face width齿廓tooth profile齿廓曲线tooth curve齿轮gear齿轮变速箱speed—changing gear boxes齿轮齿条机构pinion and rack齿轮插刀pinion cutter; pinion—shaped shaper cutter齿轮滚刀hob ，hobbing cutter齿轮机构gear齿轮轮坯blank齿轮传动系pinion unit齿轮联轴器gear coupling齿条传动rack gear齿数tooth number齿数比gear ratio齿条rack齿条插刀rack cutter；rack—shaped shaper cutter齿形链、无声链silent chain齿形系数form factor齿式棘轮机构tooth ratchet mechanism插齿机gear shaper重合点coincident points重合度contact ratio冲床punch传动比transmission ratio, speed ratio传动装置gearing；transmission gear传动系统driven system传动角transmission angle传动轴transmission shaft串联式组合combination in series串联式组合机构series combined mechanism串级调速cascade speed control创新innovation ; creation创新设计creation design垂直载荷、法向载荷normal load唇形橡胶密封lip rubber seal磁流体轴承magnetic fluid bearing从动带轮driven pulley从动件driven link, follower从动件平底宽度width of flat-face从动件停歇follower dwell从动件运动规律follower motion从动轮driven gear粗线bold line粗牙螺纹coarse thread大齿轮gear wheel打包机packer 打滑slipping带传动belt driving带轮belt pulley带式制动器band brake单列轴承single row bearing单向推力轴承single—direction thrust bearing单万向联轴节single universal joint单位矢量unit vector当量齿轮equivalent spur gear; virtual gear 当量齿数equivalent teeth number; virtual number of teeth当量摩擦系数equivalent coefficient of friction当量载荷equivalent load刀具cutter导数derivative倒角chamfer导热性conduction of heat导程lead导程角lead angle等加等减速运动规律parabolic motion; constant acceleration and deceleration motion 等速运动规律uniform motion；constant velocity motion等径凸轮conjugate yoke radial cam等宽凸轮constant—breadth cam等效构件equivalent link等效力equivalent force等效力矩equivalent moment of force等效量equivalent等效质量equivalent mass等效转动惯量equivalent moment of inertia 等效动力学模型dynamically equivalent model底座chassis低副lower pair点划线chain dotted line（疲劳）点蚀pitting垫圈gasket垫片密封gasket seal碟形弹簧belleville spring顶隙bottom clearance定轴轮系ordinary gear train; gear train withfixed axes动力学dynamics动密封kinematical seal动能dynamic energy动力粘度dynamic viscosity动力润滑dynamic lubrication动平衡dynamic balance动平衡机dynamic balancing machine 动态特性dynamic characteristics动态分析设计dynamic analysis design 动压力dynamic reaction动载荷dynamic load。
凸轮设计外文翻译参考文献
外文文献翻译(含：英文原文及中文译文)英文原文Failure Analysis, Dimensional Determination And Analysis , ApplicationsOf CamsINTRODUCTIONIt 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 abroader 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 a material 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 . R esilience 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 yieldlocally 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 it is and, hence , the less resilient. Also , the ultimate strength of a material is roughly proportional to its hardness .Machinability . M achinability 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.Figure 2.8COMPRESSION 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 thesame 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 loadmay 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 avery 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 measure the 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. Anew 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 ( μin. ) , the percentage drops to about 40%. For rough surfaces (300μin. or greater), 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 occursvery 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 endurance limit. 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 ELASTICITYGenerally 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 roomtemperature 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 forcewill 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.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.中文译文失效分析，尺寸确定与分析，凸轮的应用引言设计工程师知道如何以及为什么部件出现故障是绝对必要的，这样可以设计出需要最少维护的可靠机器。
机电专业毕业设计中英文翻译资料--圆柱凸轮的设计和加工
机电专业毕业设计中英文翻译资料--圆柱凸轮的设计和加工英文资料翻译英文原文：Design and machining of cylindrical cams with translating conical followersBy DerMin Tsay and Hsien Min WeiA simple approach to the profile determination and machining ofcylindrical cams with translating conical followers is presented .On thebasis of the theory of envelopes for a 1-parameter family of surfaces,acam profile with a translating conical follower can be easily designedonce the follower-motion program has been given .In the investigation ofgeometric characteristics ,it enables the contact line and the pressureangle to be analysed using the obtained analytical profile expressions .Inthe process of machining ,the required cutter path is provided for atapered endmill cutter ,whose size may be identical to or smaller thanthat of the conical follower .A numerical example is given to illustrate theapplication of the procedure .Keywords : cylindrical cams, envelopes , CAD/CAMA cylindrical cam is a 3D cam which drives its follower in a groove cut onthe periphery of a cylinder .The follower, which is either cylindrical orconical, may translate or oscillate. The cam rotates about its longitudinalaxis, and transmits a transmits a translation or oscillation displacementto the follower at the same time. Mechanisms of this type have long beenused in many devices, such as elevators, knitting machines, packingmachines, and indexing rotary tables.In deriving the profile of a 3Dcam, various methods have used.Dhande et al.1 and Chakraborty and dhande2 developed a method tofind the profiles of planar and spatial cams. The method used is based onthe concept that the common normal vector and the relative velocityvector are orthogonal to each other at the point of contact between thecam and the follower surfaces. Borisov3 proposed an approach to theproblem of designing cylindrical-cam mechanisms by a computeralgorithm. By this method, the contour of a cylindrical cam can beconsidered as a developed linear surface, and therefore the designproblem reduces to one of finding the centre and side profiles of the camtrack on a development of the effective cylinder. Instantaneousscrew-motion theory4 has been applied to the design of cam mechanisms.Gonzalez-Palacios et al.4 used the theory to generate surfaces of planar,spherical, and spatial indexing cam mechanisms in a unified framework.Gonzalez-Palacios and Angeles5 again used the theory to determine thesurface geometry of spherical cam-oscillating roller-follower mechanisms.Considering machining for cylindrical cams by cylindrical cutters whosesizes are identical to those of the followers, Papaioannou and Kiritsis6proposed a procedure for selecting the cutter step by solving aconstrained optimization problem.The research presented in this paper shows q new, easy procedure fordetermining the cylindrical-cam profile equations and providing thecutter path required in the machining process. This is accomplished bythe sue of the theory of envelopes for a 1-parameter family of surfacesdescribed in parametric form7 to define the cam profiles. Hanson andChurchill8 introduced the theory of envelopes for a 1-parameter familyof plane curves in implicit form to determine the equations of plate-camprofiles Chan and Pisano9 extended the envelope theory for the geometryof plate cams to irregular-surface follower systems. They derived ananalytical description of cam profiles for general cam-follower systems,and gave an example to demonstrate the method in numerical form.Using the theory of envelopes for a 2-parameter family of surfaces inimplicit form, Tsay and Hwang10 obtained the profile equations ofcamoids. According to the method, the profile of a cam is regarded as anenvelope for the family of the follower shapes in different cam-followerpositions when the cam rotates for a complete cycle.THEORY OF ENVELPOES FOR 1-PARAMETER FAMILY OFSURFACES IN PARAMETRIC FORMIn 3D xyz Cartesian space , a 1-parameter family of surfaces can be givenin parametric form as()12,,r r μμζ= (1)w here ζ is the parameter of the family, and u1, u 2, are theparameters for a particular surface of the family. Then, the envelope forthe family described in Equation 1 satisfies equation 1 and the followingEquation:0211=∂∂⨯∂∂⨯∂∂ςμμr r r (2) where the right-hand side is a constant zero7. Litvin showed the provingprocess of the theorem in detail.If we can solve Equation2 and substitute into equation1to eliminateone of the three parameters u1, u 2, and ζ , we may obtain the envelope inparametric form. However, one important thing should be pointed outhere. Equations 1 and 2 can also be satisfied by the singular points ofsurfaces described below I the family, even if they do not belong to theenvelope. Points which are regular points of surfaces of the family andsatisfy Equation 2 lie on the envelope.The condition for the singular points of a surface is discussed here.. aparametric representation of a surface is()12,r r μμ= (3)where u1 and u 2 are the parameters of the surface. A point of thesurface that corresponds to120r r μμ∂∂⨯=∂∂ in a given parameterization is called a singular point of theparameterization. A point of a surface is called singular if it is singularfor every parameterization of the surface7. A point that is singular in oneparameterization of a surface may not be singular in otherparameterizations.For a fixed value of ζ, equations 1 and 2 represent, in general, a curveon the surface which corresponds to this value of the parameter. If this isnot a line of singular points, the curve slso lies on the envelope. Thesurface and the envelope are tangent to each other along this curve. Suchcurves are called characteristic lines of the family7. they can be used tofind the contact lines between the surfaces of the cylindrical cam and thefollower.THEORY OF ENVELOPES FOR DETERMINATION OFCYLINDRICAL-CAM PROFILESOn the basis of the theory of envelopes, the profile of a cylindrical camcan be regarded as the envelope of the family of follower surfaces inrelative positions between the cylindrical cam and the follower while themotion of cam proceeds. In such a condition, the input parameters of thecylindrical cam serve as the family parameters. Because the cylindricalor conical follower surface can be expressed in parametric form withoutdifficulty, the theory of envelopes for a 1-parameter of surfacesrepresented in parametric form (see equations 1 and 2) is used indetermining the analytical equations of cylindrical-cam profiles. Asstated in the last section, a check for singular points on the followersurface is always needed.Figure 1a shows a cylindrical-cam mechanism with a translatingconical follower. The axis which the follower translates along is parallelto the axis of rotation of the cylindrical cam. a is the offset, that is, thenormal distance between the longitudinal axis of the cam and that of thefollower. R and L are the radius and the axial length of the cam,respectively.The rotation angle of the cylindrical cam is Ф2 about its axis. Thedistance traveled by the follower is s1 , which is a function of parameterФ2 ,as follows:()112S S φ= (4)The displacement relationship (see equation 4 ) for the translatingfollower is assumed to be given.In figure 1b, the relative position of the follower when the follower movesis shown. The follower is in the form of a frustum of a cone. Thesemicone angle is α, and the smallest radius is r. δ1 is the height, and μ isthe normal distance from the xz plane to the base of the cone. The fixedcoordinate system Oxyz is located in such a way that the z axis is alongthe rotation axis of the cam, and the y axis is parallel to the longitudinalaxis of the conical follower. the unit vectors of the x axis, y axis and z axisare i , j and k, respectively.By the use of the envelope technique to generate the cylindrical-camprofile, the cam is assumed to be stationary. The follower rotates aboutthe dam axis in the opposite direction. It is assumed that the followerrotates through an angle Ф2 about the axis. At the same time, thefollower is transmitted a linear displacement s1 by the cam, as shown inFigure 1b. Consequently using the technique, if we introduce θ and δ astwo parameters for the follower surface, the family of the followersurfaces can be described as()()()()()()2222222,,cos sin tan cos cos sin cos tan cos sin 1tan sin r r a r ia r js r kθδφφμδφδαθφφμδφδαθφδαθ==++-+⎡⎤⎣⎦+-++++⎡⎤⎣⎦+--+⎡⎤⎣⎦ (5)where0≤θ＜2piAnd ф2 is the independent parameter of the cam motion.Referring to theory of envelopes for surfaces represented inparametric form (see equations 1and 2), we proceed with the solvingprocess by finding()()()()2222tan cos cos sin tan cos sin cos tan sin r r r i j kδαθφδαθδθφφαθ∂∂⨯=++⎡⎤⎣⎦∂∂+-++⎡⎤⎣⎦ (6)There are no singular points on the family of surfaces, since(r +δtanα) ＞0 in actual applications. The profile equation satisfies equation 5 and the following equation:()()(){}2'1sec tan cos sin tan sin cos cos sin 0r r r r s r a αδαθδφαθδααμδαθα∂∂∂⨯=-+⨯∂∂∂+-+-++⎡⎤⎣⎦=(7)Where 1'12ds s d φ=or()22212tan E E F G θ--±+-= ⎪⎝⎭ (8) Where ()()'1cos tan sin cos sin E s F r G a αδααμδαα==-+--+=Substituting equation 8 in to equation 5, and eliminating θ, we obtain theprofile equation of the cylindrical cam with a translating conical follower,and denote it as()2,c c r r δφ= (9)As shown in equation 8,θ is a function of the selected follower -motionprogram and the dimensional parameters. As a consequence, thecylindrical-com profile can be controlled by the chosen follower-motioncurves and the dimensional parameters. Two values of θ correspond tothe two groove walls of the cylindrical cam.Now the profile of the cylindrical cam with a translating conicalfollower is derived by the new proposed method. As stated above,Dhande et al.1 and Chakraborty and Dhande2 have derived the profileequation of the same type of cam by the method of contact points. Acomparison of the result is carried out here. Since the same fixedcoordinate system and symbols are used, one can easily see that theprofile equation is identical although the methods used are different.Moreover, we find that the process of finding the cam profile issignificantly reduced by this method.CONTACT LINEAt every moment, the cylindrical cam touches the follower along spacelines. The contact lines between the cylindrical cam and its follower arediscussed in this section.The concept of characteristic lines in the theory of envelopes for a1-parameter family of surfaces mentioned above could be applied tofinding the contact lines in a cylindrical com. The profile of a cylindricalcam with a translating conical follower is given by Equation9. Then, thecontact line at a specific value of ф2, say ф20, is()()20,cl cl c r r r δδφ== (10)Where, in Equation 10, the value of θ is a function of δ defined byEquation 8.The contact lines between the surfaces of the cam and the follower ateach moment is determined by Equation 10. we see that the relationshipbetween the two parameters θ and δ of the follower surface is given byEquation 8, a nonlinear function. Thus, one can easily find that thecontact line is not always a straight line on the conical follower surface.PRESSURE ANGLEThe angle that the common normal vector of the cam and the followermakes with the path of the follower is called the pressure angle12. thepressure angle must be considered when designing a cam, and it is ameasure of the instantaneous force-transmission properties of themechanism13. The magnitude of the pressure angle in such acam-follower system affects the efficiency of the cam. The smaller thepressure angle is, the higher its efficiency because14.In figure2, the unit normal vector which passes through the point ofcontact between the cylindrical cam and the translating conical followerin the inversion position, i.e. point C, is denoted by n. The path of thefollower labeled as the unit vector p is parallel to the axis of the follower.from the definition, the pressure angle Ψ is the angle between the unitvectors n and p.Since, at the point of contact, the envelope and the surface of thefamily possesses the same tangent plane, the unit normal of thecylindrical-cam surface is the same as that of the follower surface.Referring to the family equation Equation5 and Figure2, we can obtainthe unit vector as()()()2222cos cos cos sin tan cos sin cos tan sin r r n i j k θδαθφφαθφφαθ∂∂=⨯∂∂=++-++⎡⎤⎣⎦(11)where the value of θ is given by equation 8, and the unit vector of thefollower path isp k = (12)By the use of their inner product, the pressure angle Ψ can be obtainedby the following equation:cos cos sin n p ψαθ=•= (13)The pressure angle derived here is identical to that used in the earlywork carried out by Chakraborty and Dhande2.CUTTER PATHIn this section, the cutter path required for machining the cylindricalcam with a translating conical follower is found by applying theprocedure described below.Usually, with the considerations of dimensional accuracy and surfacefinish, the most convenient way to machine a cylindrical cam is to use acutter whose size is identical to that of the conical roller. In the process ofmachining, the cylindrical blank is held on a rotary table of a 4-axismilling machine. As the table rotates, the cutter, simulating the givenfollower-motion program, moves parallel to the axis of the cylindricalblank. Thus the cutter moves along the ruled surface generated by thefollower axis, and the cam surface is then machined along the contactlines step by step. If we have no cutter of the same shape, an availablecutter of a smaller size could also be sued to generate the cam surface.Under the circumstances, the cutter path must be found for a generalendmill cutter. Figure 3 shows a tapered endmill cutter machining acurved surface. The front portion of the tool is in the form of a cone. Thesmallest radius is R, and the semicone angle is β.If the cutter moves along a curve δ =δ0 on the surface X=X （δ，ф2），the angle σ between the unit vector of the cutter axis ax and the unitcommon normal vector n at contact point C is determined bycos x n a δ=• (14)Thus the path of the point ό on the cutter axis that the vector n passesthrough is()()''000202,,sin X X R X δφδφδ==+ (15) and the tip centre T follows the path()()0202,11,sin tan T T x X X X R n a δφδφδδ=⎛⎫+- ⎪⎝⎭ (16) Figure 4 shows a tapered endmill cutter machining the groove wall of acylindrical cam. The axis of the tapered endmill is parallel to the y axis.Note that the two conditionsαβ≥ （17）r R ≥ (18)for the geometric parameters of the cutter and the roller follower musthold, or otherwise the cutter would not fit the groove. The unit vector ofthe cutter axis is()()22sin cos ax i j φφ=+ (19)For the profile of the cylindrical cam with a translating conical followergiven by equation 9, the angle σ is determined by the inner product:()()()()()222222cos cos cos sin tan cos sin cos tan cos sin sin cos xn a i j x ki j δθφφαθφφαθφφ=•++-+⎡⎤=⎢⎥+⎢⎥⎣⎦•+⎡⎤⎣⎦ (20)Thus, by using the results obtained earlier, the position of the tip centreof the cutter can be derived as()2,11sin tan T T x r r rc r n a Ai Bj Ckδφδδ=⎛⎫=+- ⎪⎝⎭=++ (21) where22sin cos cos 2sin tan cos cos sin tan sin R R R A a r ααφμδφδαθφδδδ⎛⎫⎛⎫=+++--+- ⎪ ⎪⎝⎭⎝⎭22sin cos cos 2cos tan cos s sin tan sin R R R B a r in ααφμδφδαθφδδδ⎛⎫⎛⎫=-+++-++- ⎪ ⎪⎝⎭⎝⎭cos 1tan sin sin r C s r αδαθδ⎛⎫=--+- ⎪⎝⎭NUMERICAL EXAMPLEThe procedures developed are applied in this section to determine thecylindrical-cam profile, and to analyse its characteristics. The motionprogram of the follower for the cylindrical cam with a translatingcylindrical cam is given as()()112022122sin 22220222221sin 2h s h h φλφπφλφπλπλδφλφλπφλφλλπλ≤≤⎛⎫⎛⎫- ⎪ ⎪≤≤⎝⎭ ⎪ ⎪== ⎪≤≤-⎡⎤- ⎪--⎢⎥ ⎪⎣⎦⎝⎭(22) where h and λ are two constants. And h=20 units and λ=60℃. Themotion program is a dwell-rise-dwell-return-dwell curve, and the riseand return portions are cycloidal curves 15. Figure 5 shows the motionprogram. The dimensional parameters used for the cylindrical cam andthe follower are as follows:semicone angle of follower α = 0℃height of follower δ1 =15 unitsdistance from bottom of follower to xz plane μ =55 unitssmallest radius of follower r =7.5 unitsoffset a = 20 unitsradius of cam R = 73 unitsaxial length of cam L = 100 unitsThe profile of the cylindrical cam obtained by applying Equation 9 isshown in Figure 6. In Figure 6, the groove wall with the smaller z coordinates is side Ⅰ, and the other is side Ⅱ. The variations of the pressure angles for the rise and return portions are shown in Figures 7 and 8 for side Ⅰand Ⅱ, respectively. It can be seen that the pressure angles for both sides happen to be identical.CONCLUSIONSAs has been shown above , the application of the theory of envelopes affords a convenient and versatile tool for determining the cylinder-cam profiles with translating conical followers. By means of the analytical cam profile equations, it can be easily extended to accomplish the task for the analysis of the contact line and the pressure angle. Further , the cutter path required in the process of machining is generated for tapered endmill cutters.Since the same fixed coordinate system and symbols are used in this study, one can see that the results for cam profiles and pressure angles are identical to those obtained in previous research1,2. Only one coordinate system is used in this approach. As a result, the process of derivation is simple.Work is currently under way to facilitate the implementation of the tool path for the machining of the cylindrical cam on a numerically controlled milling machine.翻译：圆柱凸轮的设计和加工有人提出了具有平移圆锥传动件的圆柱凸轮的轮廓确定及其机加工的简单方法.在单参数曲面族的包络线理论的基础上,给定从动件运动规律的具有平移圆锥传动件的圆柱凸轮的轮廓的设计是很简单的.通过这种设计方法得到的轮廓曲线可以进行凸轮切线和压力角等几何特征的分析研究.在机加工过程中,可以使用锥形端铣刀,它的尺寸小于等于圆锥传动件的尺寸.很多实例证明该方法的实用性.关键词:圆柱凸轮,包络线,计算机辅助设计和计算机辅助制造.圆柱凸轮是利用其圆周上的沟槽来驱动传动件的空间凸轮.传动件是圆柱或者圆锥形状的,可以做平行移动也可以做摆动.凸轮绕着它的纵向轴线旋转,同时将平移或摆动运动传递给传动件.这种机械原理长期广泛应用在各种设备中,比如,运输机,纺织机,包装机,旋转分度盘等等.为获得三维凸轮的轮廓曲线,曾用过各种方法.DHANDE 和CHAKRABORTY 和 DHANDE 发明了确定平面和立体凸轮轮廓的一种方法.这种方法是在一个前提下使用的,即认为在主动轮和从动件交点处,凸轮的径向矢量和速度矢量二者相互垂直.BROISOV提出了借助计算机辅助计算的方法来解决圆柱凸轮机构设计上的问题.通过这种方法,可以把圆柱凸轮的轮廓考虑成为展开的线性曲面.这样,设计时就只需在实际圆柱上找到凸轮轨迹的中心和轮廓边缘.瞬间螺旋运动理论已经应用到凸轮机构的设计中.GONZALEZ-PALACIOS在统一标准下应用这种理论得到了平面,球面和柱面凸轮机构. GONZALEZ-PALACIOS 和ANGLES 又应用这个理论确定了球面摆动辊子凸轮机构的几何形状.考虑到用与传动件同样尺寸的圆柱刀具加工圆柱凸轮,PAPAIOANNOU 和KIRITSIS 提出了通过解决最优化受限问题来选择刀具步距的程序.在这份研究报告提出了一个新的简单的程序来确定圆柱凸轮的轮廓方程并提供机加工过程中所要求的刀具路径.它是通过应用以参数形式描述的单参数曲面族的包络线理论来完成的.Hanson 和Churchill 引用隐函数形式的单参数平面曲线族包络线理论确定盘形凸轮的轮廓曲线方程。
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英文资料翻译英文原文：Design and machining of cylindrical cams with translating conical followers By DerMin Tsay and Hsien Min WeiA simple approach to the profile determination and machining of cylindricalcams with translating conical followers is presented .On the basis of the theory of envelopes for a 1-parameter family of surfaces,a cam profile with a translating conical follower can be easily designed once the follower-motion program has been given .In the investigation of geometric characteristics ,it enables the contact line and the pressure angle to be analysed using the obtained analytical profile expressions .In the process of machining ,the required cutter path is provided fora tapered endmill cutter ,whose size may be identical to or smaller than that of theconical follower .A numerical example is given to illustrate the application of the procedure .Keywords : cylindrical cams, envelopes , CAD/CAMA cylindrical cam is a 3D cam which drives its follower in a groove cut on theperiphery of a cylinder .The follower, which is either cylindrical or conical, may translate or oscillate. The cam rotates about its longitudinal axis, and transmits a transmits a translation or oscillation displacement to the follower at the same time.Mechanisms of this type have long been used in many devices, such as elevators, knitting machines, packing machines, and indexing rotary tables.In deriving the profile of a 3Dcam, various methods have used. Dhande et al.1 and Chakraborty and dhande2 developed a method to find the profiles of planar and spatial cams. The method used is based on the concept that the common normal vector and the relative velocity vector are orthogonal to each other at the point of contact between the cam and the follower surfaces. Borisov3 proposed an approach to the problem of designing cylindrical-cam mechanisms by a computer algorithm. By this method, the contour of a cylindrical cam can be considered asa developed linear surface, and therefore the design problem reduces to one offinding the centre and side profiles of the cam track on a development of the effective cylinder. Instantaneous screw-motion theory4 has been applied to the design of cam mechanisms. Gonzalez-Palacios et al.4 used the theory to generate surfaces of planar, spherical, and spatial indexing cam mechanisms in a unified framework. Gonzalez-Palacios and Angeles5 again used the theory to determine the surface geometry of spherical cam-oscillating roller-follower mechanisms.Considering machining for cylindrical cams by cylindrical cutters whose sizes are identical to those of the followers, Papaioannou and Kiritsis6 proposed a procedure for selecting the cutter step by solving a constrained optimization problem.The research presented in this paper shows q new, easy procedure for determining the cylindrical-cam profile equations and providing the cutter path required in the machining process. This is accomplished by the sue of the theory of envelopes for a 1-parameter family of surfaces described in parametric form7 to define the cam profiles. Hanson and Churchill8 introduced the theory ofenvelopes for a 1-parameter family of plane curves in implicit form to determinethe equations of plate-cam profiles Chan and Pisano9 extended the envelopetheory for the geometry of plate cams to irregular-surface follower systems. Theyderived an analytical description of cam profiles for general cam-followersystems, and gave an example to demonstrate the method in numerical form.Using the theory of envelopes for a 2-parameter family of surfaces in implicitform, Tsay and Hwang10 obtained the profile equations of camoids. According tothe method, the profile of a cam is regarded as an envelope for the family of thefollower shapes in different cam-follower positions when the cam rotates for acomplete cycle.THEORY OF ENVELPOES FOR 1-PARAMETER FAMILY OF SURFACES INPARAMETRIC FORMIn 3D xyz Cartesian space , a 1-parameter family of surfaces can be given inparametric form as()12,,r r μμζ= (1)where ζ is the parameter of th e family, and u1, u 2, are the parameters for aparticular surface of the family. Then, the envelope for the family described inEquation 1 satisfies equation 1 and the following Equation:0211=∂∂⨯∂∂⨯∂∂ςμμr r r (2) where the right-hand side is a constant zero7. Litvin showed the proving processof the theorem in detail.If we can solve Equation2 and substitute into equation1to eliminate one of thethree parameters u1, u 2, and ζ , we may obtain the envelope in parametric form.However, one important thing should be pointed out here. Equations 1 and 2 canalso be satisfied by the singular points of surfaces described below I the family,even if they do not belong to the envelope. Points which are regular points ofsurfaces of the family and satisfy Equation 2 lie on the envelope.The condition for the singular points of a surface is discussed here.. aparametric representation of a surface is()12,r r μμ= (3)where u1 and u 2 are the parameters of the surface. A point of the surface thatcorresponds to120r r μμ∂∂⨯=∂∂ in a given parameterization is called a singular point of the parameterization. Apoint of a surface is called singular if it is singular for every parameterization ofthe surface7. A point that is singular in one parameterization of a surface may notbe singular in other parameterizations.For a fixed value of ζ, equations 1 and 2 represent, in general, a curve on thesurface which corresponds to this value of the parameter. If this is not a line ofsingular points, the curve slso lies on the envelope. The surface and the envelopeare tangent to each other along this curve. Such curves are called characteristiclines of the family7. they can be used to find the contact lines between thesurfaces of the cylindrical cam and the follower.THEORY OF ENVELOPES FOR DETERMINATION OFCYLINDRICAL-CAM PROFILESOn the basis of the theory of envelopes, the profile of a cylindrical cam can beregarded as the envelope of the family of follower surfaces in relative positionsbetween the cylindrical cam and the follower while the motion of cam proceeds.In such a condition, the input parameters of the cylindrical cam serve as thefamily parameters. Because the cylindrical or conical follower surface can beexpressed in parametric form without difficulty, the theory of envelopes for a1-parameter of surfaces represented in parametric form (see equations 1 and 2) isused in determining the analytical equations of cylindrical-cam profiles. As statedin the last section, a check for singular points on the follower surface is alwaysneeded.Figure 1a shows a cylindrical-cam mechanism with a translating conicalfollower. The axis which the follower translates along is parallel to the axis ofrotation of the cylindrical cam. a is the offset, that is, the normal distance betweenthe longitudinal axis of the cam and that of the follower. R and L are the radiusand the axial length of the cam, respectively.The rotation angle of the cylindrical cam is Ф2 about its axis. The dist ancetraveled by the follower is s1 , which is a function of parameter Ф2 ,as follows:()112S S φ= (4)The displacement relationship (see equation 4 ) for the translating follower isassumed to be given.In figure 1b, the relative position of the follower when the follower moves isshown. The follower is in the form of a frustum of a cone. The semicone angle isα, and the smallest radius is r. δ1 is the height, and μ is the normal distance fromthe xz plane to the base of the cone. The fixed coordinate system Oxyz is locatedin such a way that the z axis is along the rotation axis of the cam, and the y axis isparallel to the longitudinal axis of the conical follower. the unit vectors of the xaxis, y axis and z axis are i , j and k, respectively.By the use of the envelope technique to generate the cylindrical-cam profile,the cam is assumed to be stationary. The follower rotates about the dam axis inthe opposite direction. It is assumed that the follower rotates through an angle Ф2about the axis. At the same time, the follower is transmitted a linear displacements1 by the cam, as shown in Figure 1b. Consequently using the technique, if weintroduce θ and δ as two parameters for the follower surface, the family of thefollower surfaces can be described as()()()()()()2222222,,cos sin tan cos cos sin cos tan cos sin 1tan sin r r a r ia r js r kθδφφμδφδαθφφμδφδαθφδαθ==++-+⎡⎤⎣⎦+-++++⎡⎤⎣⎦+--+⎡⎤⎣⎦ (5)where0≤θ＜2piAnd ф2 is the independent parameter of the cam motion.Referring to theory of envelopes for surfaces represented in parametric form(see equations 1and 2), we proceed with the solving process by finding()()()()2222tan cos cos sin tan cos sin cos tan sin r r r i j kδαθφδαθδθφφαθ∂∂⨯=++⎡⎤⎣⎦∂∂+-++⎡⎤⎣⎦ (6)There are no singular points on the family of surfaces, since(r +δtanα) ＞0 inactual applications. The profile equation satisfies equation 5 and the following equation:()()(){}2'1sec tan cos sin tan sin cos cos sin 0r r r r s r a αδαθδφαθδααμδαθα∂∂∂⨯=-+⨯∂∂∂+-+-++⎡⎤⎣⎦=(7)Where 1'12ds s d φ=or ()22212tan E E F G G F θ-⎛⎫-±+- ⎪= ⎪- ⎪⎝⎭ (8) Where ()()'1cos tan sin cos sin E s F r G a αδααμδαα==-+--+=Substituting equation 8 into equation 5, and eliminati ng θ, we obtain the profileequation of the cylindrical cam with a translating conical follower, and denote itas()2,c c r r δφ= (9)As shown in equation 8,θ is a function of the selected follower -motion programand the dimensional parameters. As a consequence, the cylindrical-com profilecan be controlled by the chosen follower-motion curves and the dimensionalparameters. Two values of θ correspond to the two groove walls of the cylindricalcam.Now the profile of the cylindrical cam with a translating conical follower isderived by the new proposed method. As stated above, Dhande et al.1 andChakraborty and Dhande2 have derived the profile equation of the same type ofcam by the method of contact points. A comparison of the result is carried outhere. Since the same fixed coordinate system and symbols are used, one caneasily see that the profile equation is identical although the methods used aredifferent. Moreover, we find that the process of finding the cam profile issignificantly reduced by this method.CONTACT LINEAt every moment, the cylindrical cam touches the follower along space lines. Thecontact lines between the cylindrical cam and its follower are discussed in thissection.The concept of characteristic lines in the theory of envelopes for a 1-parameterfamily of surfaces mentioned above could be applied to finding the contact linesin a cylindrical com. The profile of a cylindrical cam with a translating conicalfollower is given by Equation9. Then, the contact line at a specific value of ф2,say ф20, is()()20,cl cl c r r r δδφ== (10)Where, in Equation 10, the value of θ is a function of δ defined by Equation8.The contact lines between the surfaces of the cam and the follower at eachmoment is determined by Equation 10. we see that the relationship between thetwo parameters θ and δ of the follower surface is given by Equation 8, a nonlinearfunction. Thus, one can easily find that the contact line is not always a straightline on the conical follower surface.PRESSURE ANGLEThe angle that the common normal vector of the cam and the follower makeswith the path of the follower is called the pressure angle12. the pressure anglemust be considered when designing a cam, and it is a measure of theinstantaneous force-transmission properties of the mechanism13. Themagnitude of the pressure angle in such a cam-follower system affects theefficiency of the cam. The smaller the pressure angle is, the higher its efficiencybecause14.In figure2, the unit normal vector which passes through the point of contactbetween the cylindrical cam and the translating conical follower in the inversionposition, i.e. point C, is denoted by n. The path of the follower labeled as the unitvector p is parallel to the axis of the follower. from the definition, the pressureangle Ψ is the angle between the unit vectors n and p.Since, at the point of contact, the envelope and the surface of the familypossesses the same tangent plane, the unit normal of the cylindrical-cam surfaceis the same as that of the follower surface. Referring to the family equationEquation5 and Figure2, we can obtain the unit vector as()()()2222cos cos cos sin tan cos sin cos tan sin r r n i j k θδαθφφαθφφαθ∂∂=⨯∂∂=++-++⎡⎤⎣⎦(11)where the value of θ is given by equa tion 8, and the unit vector of the followerpath isp k = (12)By the use of their inner product, the pressure angle Ψ can be obtained by thefollowing equation:cos cos sin n p ψαθ=∙= (13)The pressure angle derived here is identical to that used in the early work carriedout by Chakraborty and Dhande2.CUTTER PATHIn this section, the cutter path required for machining the cylindrical cam with atranslating conical follower is found by applying the procedure described below.Usually, with the considerations of dimensional accuracy and surface finish,the most convenient way to machine a cylindrical cam is to use a cutter whosesize is identical to that of the conical roller. In the process of machining, thecylindrical blank is held on a rotary table of a 4-axis milling machine. As thetable rotates, the cutter, simulating the given follower-motion program, movesparallel to the axis of the cylindrical blank. Thus the cutter moves along the ruledsurface generated by the follower axis, and the cam surface is then machinedalong the contact lines step by step. If we have no cutter of the same shape, anavailable cutter of a smaller size could also be sued to generate the cam surface.Under the circumstances, the cutter path must be found for a general endmillcutter. Figure 3 shows a tapered endmill cutter machining a curved surface. Thefront portion of the tool is in the form of a cone. The smallest radius is R, and thesemicone angle is β.If the cutter moves along a curve δ =δ0 on the surface X=X （δ，ф2），the angleσ between the unit vector of the cutter axis ax and the unit common normal vectorn at contact point C is determined bycos x n a δ=∙ (14)Thus the path of the point ό on the cutter axis that the vector n passes through is()()''000202,,sin X X R X δφδφδ==+ (15) and the tip centre T follows the path()()0202,11,sin tan T T x X X X R n a δφδφδδ=⎛⎫+- ⎪⎝⎭ (16) Figure 4 shows a tapered endmill cutter machining the groove wall of acylindrical cam. The axis of the tapered endmill is parallel to the y axis. Note thatthe two conditionsαβ≥ （17）r R ≥ (18)for the geometric parameters of the cutter and the roller follower must hold, orotherwise the cutter would not fit the groove. The unit vector of the cutter axis is()()22sin cos ax i j φφ=+ (19)For the profile of the cylindrical cam with a translating conical follower given byequation 9, the angle σ is determined by the inner product:()()()()()222222cos cos cos sin tan cos sin cos tan cos sin sin cos xn a i j x ki j δθφφαθφφαθφφ=∙++-+⎡⎤=⎢⎥+⎢⎥⎣⎦∙+⎡⎤⎣⎦ (20)Thus, by using the results obtained earlier, the position of the tip centre of thecutter can be derived as()2,11sin tan T T x r r rc r n a Ai Bj Ckδφδδ=⎛⎫=+- ⎪⎝⎭=++ (21) where22sin cos cos 2sin tan cos cos sin tan sin R R R A a r ααφμδφδαθφδδδ⎛⎫⎛⎫=+++--+- ⎪ ⎪⎝⎭⎝⎭ 22sin cos cos 2cos tan cos s sin tan sin R R R B a r in ααφμδφδαθφδδδ⎛⎫⎛⎫=-+++-++- ⎪ ⎪⎝⎭⎝⎭cos 1tan sin sin r C s r αδαθδ⎛⎫=--+- ⎪⎝⎭NUMERICAL EXAMPLEThe procedures developed are applied in this section to determine thecylindrical-cam profile, and to analyse its characteristics. The motion program ofthe follower for the cylindrical cam with a translating cylindrical cam is given as()()112022122sin 22220222221sin 2h s h h φλφπφλφπλπλδφλφλπφλφλλπλ≤≤⎛⎫⎛⎫- ⎪ ⎪≤≤⎝⎭ ⎪ ⎪== ⎪≤≤-⎡⎤- ⎪--⎢⎥ ⎪⎣⎦⎝⎭(22) where h and λ are two constants. And h=20 units and λ=60℃. The motionprogram is a dwell-rise-dwell-return-dwell curve, and the rise and return portionsare cycloidal curves 15. Figure 5 shows the motion program. The dimensionalparameters used for the cylindrical cam and the follower are as follows:semicone angle of follower α = 0℃height of follower δ1 =15 unitsdistance from bottom of follower to xz plane μ =55 unitssmallest radius of follower r =7.5 unitsoffset a = 20 unitsradius of cam R = 73 unitsaxial length of cam L = 100 unitsThe profile of the cylindrical cam obtained by applying Equation 9 is shown inFigure 6. In Figure 6, the groove wall with the smaller z coordinates is side Ⅰ,and the other is side Ⅱ. The variations of the pressure angles for the rise andreturn portions are shown in Figures 7 and 8 for side Ⅰand Ⅱ, respectively. Itcan be seen that the pressure angles for both sides happen to be identical.CONCLUSIONSAs has been shown above , the application of the theory of envelopes affords aconvenient and versatile tool for determining the cylinder-cam profiles withtranslating conical followers. By means of the analytical cam profile equations, itcan be easily extended to accomplish the task for the analysis of the contact lineand the pressure angle. Further , the cutter path required in the process ofmachining is generated for tapered endmill cutters.Since the same fixed coordinate system and symbols are used in this study, onecan see that the results for cam profiles and pressure angles are identical to thoseobtained in previous research1,2. Only one coordinate system is used in thisapproach. As a result, the process of derivation is simple.Work is currently under way to facilitate the implementation of the tool pathfor the machining of the cylindrical cam on a numerically controlled millingmachine.翻译：错误！未找到引用源。