下载文档原格式
带式输送机英文文献翻译原文Transporting machine to press the operation way can is divided into:1:The leather belt type transports machine 2:Is spiral to transport machine 3:The Dou type promotes machine 4:The roller transports machine 5:Calculate to transport machine 6:The plank chain transports machine 7:The net takes to transport machine 8:The chain transports machine.1.ParameterIs general according to various condition of request, material shipping point that the material transports system, relevant of the production craft process and material of characteristic etc. to make sure each main parameter.①Transport ability:The ability oftransporting the transporting of machine means unit for time inside transport of material quantity.While transporting to spread a form material, with the quality or physical volume calculation that the per hour transports a material;At transport into a piece product, with the number of items calculation that the per hour transports.②Transport speed:The exaltation transports speed to improve the ability of transporting.When being making to lead a piece by belt conveyer and transporting length was more big, transport speed to gradually enlarge.But the take type of high-speed operation transports machine to need to notice vibration, Zao voice and start and make etc. problem.For use chain as lead a piece of transport machine,transporting the speed should not lead greatly, in order to prevent the aggrandizement power carry alotus.Carry on transporting of craft operation machine at the same time, transporting the speed should press to produce a craft to request an assurance.③Reach a size:Transport reaching of machine a size to include belt conveyer width, lath width and anticipate Dou capacity, piping diameter and container all of etc.s.These reach a sizes to all directly influence to transport machine of transport ability.④Transport length and QingCape:Transport circuit length and Qing Cape size to directly influence the total resistance of transporting the machine and need of power.2.Transport a machine the spot application wayConstitute to carry on explaining in detail from the take type machine system first:Leather belt's transporting machine is to spread a form material to transport and pack to unload an equipments most importantly, can extensively used for the mineral mountain, metallurgy, building materials, chemical engineering, electric power, industrial realms like food processing,etc, in the coal mine, metal mineral, the steel business enterprise, port, grounds like cement works,etc a great deal of application that can see skin machine, transporting the machine can not only complete to spread a transporting of form material, but also can transport into a piece material, butbasis use location, work environment, transport the dissimilarity of material category, will also have bigger difference in its design and the application;Modernization of transport the machine system has higher request to the dust palliative, is this, in each the device that transfer place and establish and sprinkle water and gather a dust, transport machine and follow line in the tape will establish and defend a breeze cover or block an aerofoil, system from list the machine constitute of, to work in the whole machine system of operate and fix to say, want and have a foothold and divide the single machine of the tube at oneself, and want to understand mutual contact between systems, list machine again is constitute to°from many partses,only work well the daily maintenance of each parts maintains and makes it is placed in good work status so as to ensure the safe movement of equipments;We generally will transport the use place, work environment of machine according to the take type, technique function and transport material category to wait various dissimilarity with satisfy various forms of homework work condition, in addition to in addition to transporting machine, the in general use leather belt of more adoption also various special kind tapes of new structure transport machine and have a mainly having of the representative among them:Big Qing Cape take type machine, deep slot take type machine and press take type machine, take care of the formtake type, the air cushion take type, the flat surface turn take type, the line friction type, wave-like in shape the belt conveyer type blocking a side transport machine etc. and carry on a thin method for turning and canning exist various classifications and make following introduction now:Press the use classification, there is in general use ambulation type, under the well choice type, the strip mine is used a fixed type, special kind structure type, can move a place type and transport machine, load machine appropriation redistribution function type, the big Qing Cape type transports machine etc., generally speaking transport machine inside the short distance factory can complete level, up the luck or bottomcarries, canning go against the wood grain type leather belt machine can be used for double to transport a material, hang arm machine usually install anticipate on board in the heap, and can turn round, line up the function of soil or cloth by realization, but Gao Jia Ji propped up by in the door usually match with other spread and anticipate and handle an equipments common use, for example give or get an electric shock and constuct a medium application in water, can install standard in the center frame, the machine's mounting places on the track Zhen, easy to move and place;Press the category of transporting the material to categorize, have the generally lax material is used of, the strong and tough material is used of and list piece theleather belt used in material transport machine etc. and press the rubber conveyance takes a loading segment of position to categorize, include a leather belt loading segment at top of and loading segment at underneath of and at the same time loading segment at up underneath of double to transport machine three, the use double can distinguish to transporting machine at up branch and bottom branch transport a material, but for keeping material contact noodles don't produce a change and need to bring in to go to the rubber to be periodically inside out.3.CategorizeTransporting machine generally and pressing already didn't lead piece to carry on a classification and had to lead a transporting of piece machine to generallyinclude to lead a piece, loading to reach a piece, drive device, bring to the stretch device and change to accept an etc. to the device and.Lead a piece to in order to deliver to lead dint, can adopt belt conveyer and lead chain or steel wire rope;The loading reaches a piece to in order to accept to put a material and has already anticipated Dou and bracket or mourns to have...etc.;Drive device to transport machine with the power, generally from electric motor, decelerate a machine and make machine(stop a machine) etc. to constitute;Bring to the stretch to equip to generally have the Luo pole the type and heavy hammer type 2 kind, can make to lead a piece to keep certain tension and hang a degree, transport machine by assurance normaloperation;Pay to accept a piece to in order to accept to give to lead piece or loading to reach a piece, can adopt to give Gun and roll an etc..Having the structure characteristics that lead the transporting of piece machine is:Be delivered a material and pack reaching with the loading leading a link together inside the piece, or directly pack in leading a piece(is like belt conveyer), led a piece to once round each roller or the chain round beginning and end and connect with each other, formation include and deliver a having of material carry branch and don't deliver a material of have never carried shutting of branch and match wreath road, make use of lead continuous sport of piece and transport a material.This type ofly transporting model is numerous,there is mainly a take type transporting a machine, plank type and transporting a machine, small car type and transporting machine, escalator, automatic sidewalk, paring off plank and transporting machine, covering up and paring off plank and transporting a machine, Dou type and transporting a machine, Dou type and promoting machine and hanging and transporting machine and build on stilts a cableway...etc..The structure that didn't lead transporting of piece machine constitutes each not same, use to the work of transporting the material to reach a piece as well not same.Their structure characteristicses are:Make use of a work to reach a revolving of piece to exercise or the back and forth exercise, or make useof lie quality to make the material transport forward in the fluxion in the piping.For example, the Gun son transports the work of machine to reach the piece as a series of Gun son, the Gun son makes to revolve sport to transport a material;Is spiral to transport the work of machine to reach a piece for spiral, helix at anticipate and make to revolve sport in the slot with follow anticipate slot to push to send a material;The vibration transports the work of machine to reach piece in order to anticipate slot, anticipate slot to make back and forth sport with transport Be placed to among them of material etc..Install(1)The fixed type transports machine should by rule gearing method gearing atfix of foundation up.The ambulation type transports machine formally before circulating and should live wheel with the wedge Xie or uses to make a machine to stop.So as not to take place to take a stroll in the work, there is the passage that many sets , between machine and machine, there shoulded be one meter between wall and machine while transporting a parallel homework of machine.(2)The beard checks an each operation part, tape to take to button up to equip with loading before using whether normal, whether protection equipments iswell-found.The tape rises a tight degree beard before starting the adjustment is to suitable extent.(3)Leather belt's transporting machine should get empty to carry a start.Waitingto revolve normal rear can go into to anticipate.Drive after forbiding to go into first to anticipate.(4)There are few set that when transport machine to establish to circulate should from unload to anticipate to carry a beginning, the sequence starts.After revolving as usual all, the square can go into to anticipate.(5)Appear in the movement when the tape runs to be partial to a phenomenon should park the car adjustment, can not force an use, so as not to wear away edge and increment burden.(6)Work environment and be sent material temperature not to must be higher than 50 ℃ and be lowerthan-10 ℃ .Can not transport the material of having sour alkaline oil andorganic melting agent composition.(7)Forbid pedestrian or multiply by a person on the belt conveyer.(8)Have to stop going into first to anticipate before parking the car, wait leather belt up save to anticipate to unload to the utmost a square can park the car.(9)Transporting the machine electric motor has to insulate good.The ambulation type transports machine electric cable to pull and drag along indiscriminately.The dynamoelectric confidential credibility connects ground.(10)The leather belt beats slippery strictly forbid to by hand pull leather belt, so as not to take place trouble.5.Adjust to try(1) Each equipments with meticulouscare adjusts to try to transport machine after installing and satisfies a drawing request.(2) Each deceleration machine exercises parts to add to note to correspond lubricant.(3) The gearing after transporting machine to attain to request each single set equipments carries on beginning to work to make run-in, and knot to put together to adjust to try to transport machine to satisfy an operative request. (4) Adjust to try the electricity part of transporting the machine.Include to connect adjusting of line and action to try to the normal regulations electricity, make the equipments have good function, attain the function and status of design.6.Transport machine to block knothole 2kinds of boring crafts(1)Blow up boring:The material after the irradiation of continuous laser and centrally forms one cave pit, then from and laser beam the coaxial oxygen flow to clean meltdown material and form one bore very quickly.The size of general bore is as thick relevant as plank, blow up to bore hole the average diameter as thick plank half, therefore blow up to bore hole bore path bigger to thicker plank, and not circle, should not in requesting higher spare parts use(if the petroleum Shai sews a tube), can be used for a waste up.In addition because of bore hole use of oxygen pressure with incise homology, splash a little bit greatly.(2)Pulse boring:The pulse laser that adopts high peak value power makes alittle amount material melt or vaporizes, in common use air or nitrogen spirit are to lend support to air and oxidize to make bore expand because of putting heat by decrease, the air pressure more incises of the oxygen pressure is small.The particle jet with small creation of each pulse laser gradually goes deep into, therefore slab boring time takes several seconds.Once bore hole completion, immediately change assistance air into oxygen to carry on incising.Boring hole diameter like this is smaller, its boring quality is better than to blow up boring.Not only should have higher exportation power for the laser machine used by this;The time and space characteristic that more important time ties, therefore the general crosscurrent carbon dioxide laser machine can notadapt to the request that the laser incises.In addition the pulse bores hole to also have the more dependable spirit road the control system to carry out cutting over of air category, air pressure and bore hole a horary control.译文：输送机按运作方式可以分为：1：皮带式输送机2：螺旋输送机3：斗式提升机4：滚筒输送机5：计量输送机6：板链输送机7：网带输送机8：链条输送机。
附件A高速带式输送机的设计G. Lodewijks，荷兰摘要本文主要探讨高速带式输送机设计方面的问题。
带式输送机的输送量取决于输送带的速度、传送带宽度和托辊槽形角。
然而输送带速度的选择又受到各种实际条件的限制，在本文有这方面的讨论。
输送带速度也影响传送带的性能，例如它的能源消耗和它连续运行的稳定性。
一种计算输送带的能源消耗的方法就是通过考虑运输过程中的各种能量损耗来进行估算的。
输送带速度的不同使得安全系数的要求也各不相同，这也影响输送带所要求的强度。
一种新的计算输送带速度对安全系数的影响的方法在本文中被介绍。
最后，输送带速度的冲击对各组成部分的选择和对中转站设计的影响也在本文中被讨论。
1 概述过去的研究已经证实使用窄带输送机的经济可行性，输送带的速度变快要求输送带的宽度随之变宽，低速输送机适于长距离输送。
例如图[1] - [5]。
现在，传送带以8 m/s 的速度运行是没有问题的。
无论怎样，输送带速度在10m/s到20 m/s在技术上是(动态地)可行的，并且也许在经济上也是可行的。
本文将输送带速度在10和20 m/s之间的定义为高速。
输送带速度在10m/s之下的定义为低速。
使用高速输送带的目的并不在于它本身。
如果使用高速输送带不是经济上有利，或则，如果安全和可靠的操作没有保证的，那么就应该选择低速输送带。
输送带速度的选择是总的设计过程的一部分。
静态或稳定的设计方法决定了带式输送机的优化设计。
在这些设计方法中输送带被认为是刚性的，静止的。
这增加了输送机稳定运行的质量和也决定了带式输送机各零部件的尺寸。
稳定操作包括传送带稳定运行时的张力、相对各种物料载荷的能量消耗和相关的工作环境情况。
应该体会到找到最优的设计不是一次性的努力，而是一个反复的过程[6]。
优化设计，开始于优化的决心，终于符合要求的确定的控制算法和组成输送机的各零部件确定的位置和尺寸的大小，例如驱动，闸和飞轮，可由动态设计方法确定。
在这些设计方法中，也涉及动态分析，输送带可看作是一个三维的弹性体。
翻译部分英文原文Belt Conveying Systems Development of driving system Among the methods of material conveying employed，belt conveyors play a very important part in the reliable carrying of material over long distances at competitive cost．Conveyor systems have become larger and more complex and drive systems have also been going through a process of evolution and will continue to doso．Nowadays，bigger belts require more power and have brought the need for larger individual drives as well as multiple drives such as 3 drives of 750 kW for one belt(this is the case for the conveyor drives in Chengzhuang Mine)．The ability to control driveacceleration torque is critical to belt conveyors’ performance．An efficient drive system should be able to provide smooth，soft starts while maintaining belt tensions within the specified safe limits．For load sharing on multiple drives．torque and speed control are also important considerations in the drive system’s design. Due to the advances in conveyor drive control technology，at present many more reliable．Cost-effective and performance-driven conveyor drivesystems covering a wide range of power are available for customers’choices[1].1 Analysis on conveyor drive technologies1．1 Direct drivesFull-voltage starters．With a full-voltage starter design，the conveyor head shaft is direct-coupled to the motor through the gear drive．Direct full-voltage starters are adequate for relatively low-power,simple-profile conveyors．With direct fu11-voltage starters．no control is provided for various conveyor loads and．depending on the ratio between fu11-and no-1oad power requirements，empty starting times can be threeor four times faster than full load．The maintenance-free starting system is simple，low-cost and very reliable．However, they cannot control starting torque and maximum stall torque；therefore．they are limited to the low-power, simple-profile conveyor belt drives．Reduced-voltage starters．As conveyor power requirements increase，controlling the applied motor torque during the acceleration period becomes increasingly important．Because motor torque 1s a function of voltage，motor voltage must be controlled．This can be achieved through reduced-voltage starters by employing a silicon controlledrectifier(SCR)．A common starting method with SCR reduced-voltage starters is to apply low voltage initially to take up conveyor belt slack．and then to apply a timed linear ramp up to full voltage and belt speed．However, this starting method will not produce constant conveyor belt acceleration．When acceleration is complete．the SCRs,which control the applied voltage to the electric motor． are locked in full conduction, providing fu11-line voltage to the motor．Motors with higher torque and pull—up torque，can provide better starting torque when combined with the SCR starters, which are available in sizes up to 750 KW．Wound rotor induction motors．Wound rotor induction motors are connected directly to the drive system reducer and are a modified configuration of a standard AC induction motor．By inserting resistance in series with the motor’s rotor windings．the modified motor control system controls motor torque．For conveyor starting，resistance is placed in series with the rotor for low initial torque．As the conveyor accelerates，the resistance is reduced slowly to maintain a constant acceleration torque．On multiple-drive systems．an external slip resistor may be left in series with the rotor windings to aid in load sharing．The motor systems have a relatively simple design．However, the control systems for these can be highly complex，because they are based on computercontrol of the resistance switching．Today，the majority of control systems are custom designed to meet a conveyor system’s particular specifications．Wound rotor motors are appropriate for systems requiring more than 400 kW ．DC motor．DC motors．available from a fraction of thousands of kW ，are designed to deliver constant torque below base speed and constant kW above base speed to the maximum allowable revolutions perminute(r/min)．with the majority of conveyor drives, a DC shunt wound motor is used．Wherein the motor’s rotating armature is connected externally．The most common technology for controlling DC drives is a SCR device． which allows for continual variable-speed operation．The DC drive system is mechanically simple, but can include complex custom-designed electronics to monitor and control the complete system．This system option is expensive in comparison to other soft-start systems．but it is a reliable,cost-effective drive in applications in which torque,1oad sharing and variable speed are primary considerations．DC motors generally are used with higher-power conveyors，including complex profile conveyors with multiple-drive systems，booster tripper systems needing belt tension control and conveyors requiring a wide variable-speed range．1．2 Hydrokinetic couplingHydrokinetic couplings，commonly referred to as fluid couplings．are composed of three basic elements; the driven impeller, which acts as a centrifugal pump；the driving hydraulic turbine known as the runner and a casing that encloses the two power components．Hydraulic fluid is pumped from the driven impeller to the driving runner, producing torque at the driven shaft．Because circulating hydraulic fluid produces the torque and speed，no mechanical connection is required between the driving and driven shafts．The power produced by this coupling is based on the circulated fluid’s amount and density and the torque in proportion to inputspeed．Because the pumping action within the fluid coupling depends on centrifugal forces．the output speed is less than the input speed．Referred to as slip．this normally is between l% and 3%．Basic hydrokinetic couplings are available in configurations from fractional to several thousand kW ．Fixed-fill fluid couplings．Fixed-fill fluid couplings are the most commonly used soft-start devices for conveyors with simpler belt profiles and limited convex/concave sections．They are relativelysimple,1ow-cost,reliable,maintenance free devices that provide excellent soft starting results to the majority of belt conveyors in use today．Variable-fill drain couplings．Drainable-fluid couplings work on the same principle as fixed-fill couplings．The coupling’s impellers are mounted on the AC motor and the runners on the driven reducer high-speed shaft．Housing mounted to the drive base encloses the working circuit．The coupling’s rotating casing contains bleed-off orifices that continually allow fluid to exit the working circuit into a separate hydraulic reservoir．Oil from the reservoir is pumped through a heat exchanger to a solenoid-operated hydraulic valve that controls the filling of the fluid coupling．To control the starting torque of a single-drive conveyor system，the AC motor current must be monitored to provide feedback to the solenoid control valve．Variable fill drain couplings are used in medium to high-kW conveyor systems and are available in sizes up to thousands of kW ．The drives can be mechanically complex and depending on the control parameters．the system can be electronically intricate．The drive system cost is medium to high, depending upon size specified．Hydrokinetic scoop control drive．The scoop control fluid coupling consists of the three standard fluid coupling components：a driven impeller, a driving runner and a casing that encloses the working circuit．The casing is fitted with fixed orifices that bleed apredetermined amount of fluid into a reservoir．When the scoop tube is fully extended into the reservoir, the coupling is l00 percent filled．The scoop tube, extending outside the fluid coupling，is positioned using an electric actuator to engage the tube from the fully retracted to the fully engaged position．This control provides reasonably smooth acceleration rates．to but the computer-based control system is very complex．Scoop control couplings are applied on conveyors requiring single or multiple drives from l50 kW to 750 kW.1．3 Variable-frequency control(VFC)Variable frequency control is also one of the direct drive methods．The emphasizing discussion about it here is because that it has so unique characteristic and so good performance compared with other driving methods for belt conveyor． VFC devices Provide variable frequency and voltage to the induction motor, resulting in an excellent starting torque and acceleration rate for belt conveyor drives．VFC drives．available from fractional to several thousand(kW ), are electronic controllers that rectify AC line power to DC and，through an inverter, convert DC back to AC with frequency and voltage contro1．VFC drives adopt vector control or direct torque control(DTC)technology，and can adopt different operating speeds according to different loads．VFC drives can make starting or stalling according to any given S-curves．realizing the automatic track for starting or stalling curves．VFC drives provide excellent speed and torque control for starting conveyor belts．and can also be designed to provide load sharing for multiple drives．easily VFC controllers are frequently installed on lower-powered conveyor drives，but when used at the range of medium-high voltage in the past．the structure of VFC controllers becomes very complicated due to the limitation of voltage rating of power semiconductor devices，the combination of medium-high voltage drives and variable speed is often solved withlow-voltage inverters using step-up transformer at the output，or with multiple low-voltage inverters connected in series．Three-level voltage-fed PWM converter systems are recently showing increasing popularity for multi-megawatt industrial drive applications because of easy voltage sharing between the series devices and improved harmonic quality at the output compared to two-level converter systems With simple series connection of devices．This kind of VFC system with three 750 kW /2．3kV inverters has been successfully installed in ChengZhuang Mine for one 2．7-km long belt conveyor driving system in following the principle of three-level inverter will be discussed in detail．2 Neutral point clamped(NPC)three-level inverter using IGBTsThree-level voltage-fed inverters have recently become more and more popular for higher power drive applications because of their easy voltage sharing features．1ower dv/dt per switching for each of the devices，and superior harmonic quality at the output．The availability of HV-IGBTs has led to the design of a new range of medium-high voltage inverter using three-level NPC topology．This kind of inverter can realize a whole range with a voltage rating from 2．3 kV to 4．1 6 kV Series connection of HV-IGBT modules is used in the 3．3 kV and 4．1 6 kV devices．The 2．3 kV inverters need only one HV-IGBT per switch[2,3].2．1 Power sectionTo meet the demands for medium voltage applications．a three-level neutral point clamped inverter realizes the power section．In comparison to a two-level inverter．the NPC inverter offers the benefit that three voltage levels can be supplied to the output terminals，so for the same output current quality，only 1/4 of the switching frequency is necessary．Moreover the voltage ratings of the switches in NPC inverter topology will be reduced to 1/2．and the additional transient voltage stress on the motor can also be reduced to 1/2 compared to that of atwo-level inverter．The switching states of a three-level inverter are summarized in Table 1．U．V and W denote each of the three phases respectively；P N and O are the dc bus points．The phase U，for example，is in state P(positive busvoltage)when the switches S1u and S2uare closed，whereas it is in stateN (negative bus voltage) when the switches S3u and S4uare closed．Atneutral point clamping，the phase is in O state when either S2u or S3uconducts depending on positive or negative phase current polarity，respectively．For neutral point voltage balancing，the average current injected at O should be zero．2．2 Line side converterFor standard applications．a l2-pulse diode rectifier feeds the divided DC-link capacitor．This topology introduces low harmonics on the line side．For even higher requirements a 24-pulse diode rectifier can be used as an input converter．For more advanced applications where regeneration capability is necessary, an active front．end converter can replace the diode rectifier, using the same structure as the inverter．2．3 Inverter controlMotor Contro1．Motor control of induction machines is realized by using a rotor flux．oriented vector controller．Fig．2 shows the block diagram of indirect vector controlled drive that incorporates both constant torque and high speed field-weakening regions where the PW M modulator was used．In this figure，the commandflux is generated as function of speed．The feedback speed is addedwith the feed forward slip command signal . the resulting frequencysignal is integrated and then the unit vector signals(cos and sin )aregenerated．The vector rotator generates the voltage and anglecommands for the PW M as shown．PWM Modulator．The demanded voltage vector is generated using anelaborate PWM modulator．The modulator extends the concepts ofspace-vector modulation to the three-level inverter．The operation can be explained by starting from a regularly sampled sine-triangle comparison from two-level inverter．Instead of using one set of reference waveforms and one triangle defining the switching frequency， thethree-level modulator uses two sets of reference waveforms Ur1and Ur2andjust one triangle．Thus, each switching transition is used in an optimal way so that several objectives are reached at the same time．Very low harmonics are generated．The switching frequency is low and thus switching losses are minimized．As in a two-level inverter, a zero-sequence component can be added to each set of reference waveform s in order to maximize the fundamental voltage component．As an additional degree of freedom，the position of the reference waveform s within the triangle can be changed．This can be used for current balance in the two halves of the DC-1ink．3 Testing resultsAfter Successful installation of three 750 kW /2．3 kV three-level inverters for one 2．7 km long belt conveyor driving system in Chengzhuang Mine．The performance of the whole VFC system was tested．Fig．3 is taken from the test，which shows the excellent characteristic of the belt conveyor driving system with VFC controller．Fig．3 includes four curves．The curve 1 shows the belt tension．From the curve it can be find that the fluctuation range of the belt tension is very smal1．Curve 2 and curve 3 indicate current and torque separately．Curve 4 shows the velocity of the controlled belt．The belt velocity have the“s”shape characteristic．A1l the results of the test show a very satisfied characteristic for belt driving system．4 ConclusionsAdvances in conveyor drive control technology in recent years haveresulted in many more reliable．Cost-effective and performance-driven conveyor drive system choices for users．Among these choices，the Variable frequency control (VFC) method shows promising use in the future for long distance belt conveyor drives due to its excellent performances．The NPC three-level inverter using high voltage IGBTs make the Variable frequency control in medium voltage applications become much more simple because the inverter itself can provide the medium voltage needed at the motor terminals，thus eliminating the step-up transformer in most applications in the past．The testing results taken from the VFC control system with NPC three．1evel inverters used in a 2．7 km long belt conveyor drives in Chengzhuang Mine indicates that the performance of NPC three-level inverter using HV-IGBTs together with the control strategy of rotor field-oriented vector control for induction motor drive is excellent for belt conveyor driving system．中文译文：带式输送机及其牵引系统在运送大量的物料时，带式输送机在长距离的运输中起到了非常重要的竞争作用。
附录A带式输送机技术的最新发展M. A. AlspaughOverland Conveyor Co., Inc.MINExpo 2004拉斯维加斯, 内华达州，美国，9，27, 2004摘要粒状材料运输要求带式输送机具有更远的输送距离、更复杂的输送路线和更大的输送量。
为了适应社会的发展，输送机需要在系统设计、系统分析、数值仿真领域向更高层次发展。
传统水平曲线和现代中间驱动的应用改变和扩大了带式输送机发展的可能性。
本文回顾了为保证输送机的可靠性和可用性而运用数字工具的一些复杂带式输送机。
前言虽然这篇文章的标题表明在皮带输送机技术中将提出“新”发展，但是提到的大多思想和方法都已存在很长时间了。
我们不怀疑被提出一些部件或想法将是“新”的对你们大部分人来说。
所谓的“新”就是利用成熟的技术和部件组成特别的、复杂的系统；“新”就是利用系统设计工具和方法，汇集一些部件组成独特的输送机系统，并解决大量粒状原料的装卸问题；“新”就是在第一次系统试验(委任)之前利用日益成熟的计算机技术进行准确节能计算机模拟。
同样，本文的重点是特定复杂系统设计及满足长距离输送的要求。
这四个具体课题将覆盖：●托辊阻力●节能●动力分散●分析与仿真节能减小设备整体电力消费是所有项目的一个重要方面，皮带输送机是也不例外。
虽然与其他运输方法比较皮带输送机总是运输大吨位高效率的手段，但是减少带式输送机的功率消耗的方法还是很多的。
皮带输送机的主要阻力组成部分有：●托辊阻力●托辊与皮带的摩擦力●材料或输送带弯曲下垂引起的阻力●重力这些阻力加上一些混杂阻力组成输送材料所需的力。
1在一台输送长度400米的典型短距离输送机中,力可以分为如图1所示的几个部分，图中可以看出提升力所占比例最大，而阻力还是占绝大部分。
图1在高倾斜输送带中如矿用露天倾斜输送带，所受力可分解为图2所示的几个部分，其中提升力仍占巨大比例。
由于重力是无法避免的，因此没有好的方法减少倾斜式输送机所受力。
中英文翻译Development of belt conveyor driving systemAbstract A short review for the existing various driving methods for belt conveyor was given, which include the analysis and comparison about the advantages, disadvantages and suitable application range of these methods. Based on this the variable-frequency-control(VFC} method for belt conveyor drive was fully discussed with focus on its application in medium-high voltage range. The principle of Neutral Point Clamped (NPC) Three一Level Inverter using high-voltage IGBTs together with the control strategy of rotor field-oriented vector control for induction motor drive were illustrated.Key words belt conveyor driving system, variable-frequency-control, three-level inverter Among the methods of material conveying employed，belt conveyors play a very important part in the reliable carrying of material over long distances at competitive cost．Conveyor systems have become larger and more complex and drive systems have also been going through a process of evolution and will continue to do so．Nowadays，bigger belts require more power and have brought the need for larger individual drives as well as multiple drives such as 3 drives of 750 kW for one belt(this is the case for the conveyor drives in Chengzhuang Mine)．The ability to control drive acceleration torque is critical to belt conveyors’ performance．An efficient drive system should be able to provide smooth，soft starts while maintaining belt tensions within the specified safe limits．For load sharing on multiple drives．torque and speed control are also important considerations in the drive system’s design. Due to the advances in conveyor drive control technology，at present many more reliable．Cost-effective and performance-driven conveyor driv e systems covering a wide range of power are available for customers’choices[1].1 Analysis on conveyor drive technologies1．1 Direct drivesFull-voltage starters．With a full-voltage starter design，the conveyor head shaft is direct-coupled to the motor through the gear drive．Direct full-voltage starters are adequate for relativelylow-power, simple-profile conveyors．With direct fu11-voltage starters．no control is provided for various conveyor loads and．depending on the ratio between fu11- and no-1oad power requirements，empty starting times can be three or four times faster than full load．The maintenance-free starting system is simple，low-cost and very reliable．However, they cannot control starting torque and maximum stall torque；therefore．they are limited to the low-power,simple-profile conveyor belt drives．Reduced-voltage starters．As conveyor power requirements increase，controlling the applied motor torque during the acceleration period becomes increasingly important．Because motor torque 1s a function of voltage，motor voltage must be controlled．This can be achieved through reduced-voltage starters by employing a silicon controlled rectifier(SCR)．A common starting method with SCR reduced-voltage starters is to apply low voltage initially to take up conveyor belt slack．and then to apply a timed linear ramp up to full voltage and belt speed．However, this starting method will not produce constant conveyor belt acceleration．When acceleration is complete．the SCRs, which control the applied voltage to the electric motor．are locked in full conduction, providing fu11-line voltage to the motor．Motors with higher torque and pull—up torque，can provide better starting torque when combined with the SCR starters, which are available in sizes up to 750 KW．Wound rotor induction motors．Wound rotor induction motors are connected directly to the drive system reducer and are a modified configuration of a standard AC induction motor．By inserting resistance in series with the motor’s rotor windings．the modified motor control system controls motor torque．For conveyor starting，resistance is placed in series with the rotor for low initial torque．As the conveyor accelerates，the resistance is reduced slowly to maintain a constant acceleration torque．On multiple-drive systems．an external slip resistor may be left in series with the rotor windings to aid in load sharing．The motor systems have a relatively simple design．However, the control systems for these can be highly complex，because they are based on computer control of the resistance switching．Today，the majority of control systems are custom designed to meet a conveyor system’s particular specifications．Wound rotor motors are appropriate for systems requiring more than 400 kW ．DC motor．DC motors．available from a fraction of thousands of kW ，are designed to deliver constant torque below base speed and constant kW above base speed to the maximum allowable revolutions per minute(r/min)．with the majority of conveyor drives, a DC shunt wound motor is used．Wherein the motor’s rotating arma ture is connected externally．The most common technology for controlling DC drives is a SCR device．which allows for continual variable-speed operation．The DC drive system is mechanically simple, but can include complex custom-designed electronics to monitor and control the complete system．This system option is expensive in comparison to other soft-start systems．but it is a reliable, cost-effective drive inapplications in which torque,1oad sharing and variable speed are primary considerations．DC motors generally are used with higher-power conveyors，including complex profile conveyors with multiple-drive systems，booster tripper systems needing belt tension control and conveyors requiring a wide variable-speed range．1．2 Hydrokinetic couplingHydrokinetic couplings，commonly referred to as fluid couplings．are composed of three basic elements; the driven impeller, which acts as a centrifugal pump；the driving hydraulic turbine known as the runner and a casing that encloses the two power components．Hydraulic fluid is pumped from the driven impeller to the driving runner, producing torque at the driven shaft．Because circulating hydraulic fluid produces the torque and speed，no mechanical connection is required between the driving and driven shafts．The power produced by this coupling is based on the circulated fluid’s amount and density and the torque in proportion to input speed．Because the pumping action within the fluid coupling depends on centrifugal forces．the output speed is less than the input speed．Referred to as slip．this normally is between l% and 3%．Basic hydrokinetic couplings are available in configurations from fractional to several thousand kW ．Fixed-fill fluid couplings．Fixed-fill fluid couplings are the most commonly used soft-start devices for conveyors with simpler belt profiles and limited convex/concave sections．They are relatively simple,1ow-cost,reliable,maintenance free devices that provide excellent soft starting results to the majority of belt conveyors in use today．Variable-fill drain couplings．Drainable-fluid couplings work on the same principle as fixed-fill couplings．The coupling’s impellers are mounted on the AC motor and the runners on the driven reducer high-speed shaft．Housing mounted to the drive base encloses the working circuit．The c oupling’s rotating casing contains bleed-off orifices that continually allow fluid to exit the working circuit into a separate hydraulic reservoir．Oil from the reservoir is pumped through a heat exchanger to a solenoid-operated hydraulic valve that controls the filling of the fluid coupling．To control the starting torque of a single-drive conveyor system，the AC motor current must be monitored to provide feedback to the solenoid control valve．Variable fill drain couplings are used in medium to high-kW conveyor systems and are available in sizes up to thousands of kW ．The drives can be mechanically complex and depending on the control parameters．the system can be electronically intricate．The drive system cost is medium to high,depending upon size specified．Hydrokinetic scoop control drive．The scoop control fluid coupling consists of the three standard fluid coupling components：a driven impeller, a driving runner and a casing that encloses the working circuit．The casing is fitted with fixed orifices that bleed a predetermined amount of fluid into a reservoir．When the scoop tube is fully extended into the reservoir, the coupling is l00 percent filled．The scoop tube, extending outside the fluid coupling，is positioned using an electric actuator to engage the tube from the fully retracted to the fully engaged position．This control provides reasonably smooth acceleration rates．to but the computer-based control system is very complex．Scoop control couplings are applied on conveyors requiring single or multiple drives from l50 kW to 750 kW.1．3 Variable-frequency control(VFC)Variable frequency control is also one of the direct drive methods．The emphasizing discussion about it here is because that it has so unique characteristic and so good performance compared with other driving methods for belt conveyor．VFC devices Provide variable frequency and voltage to the induction motor, resulting in an excellent starting torque and acceleration rate for belt conveyor drives．VFC drives．available from fractional to several thousand(kW ), are electronic controllers that rectify AC line power to DC and，through an inverter, convert DC back to AC with frequency and voltage contro1．VFC drives adopt vector control or direct torque control(DTC)technology，and can adopt different operating speeds according to different loads．VFC drives can make starting or stalling according to any givenS-curves．realizing the automatic track for starting or stalling curves．VFC drives provide excellent speed and torque control for starting conveyor belts．and can also be designed to provide load sharing for multiple drives．easily VFC controllers are frequently installed on lower-powered conveyor drives，but when used at the range of medium-high voltage in the past．the structure of VFC controllers becomes very complicated due to the limitation of voltage rating of power semiconductor devices，the combination of medium-high voltage drives and variable speed is often solved with low-voltage inverters using step-up transformer at the output，or with multiple low-voltage inverters connected in series．Three-level voltage-fed PWM converter systems are recently showing increasing popularity for multi-megawatt industrial drive applications because of easy voltage sharing between the series devices and improved harmonic quality at the output compared to two-level converter systems With simple series connection ofdevices．This kind of VFC system with three 750 kW /2．3kV inverters has been successfully installed in ChengZhuang Mine for one 2．7-km long belt conveyor driving system in following the principle of three-level inverter will be discussed in detail．2 Neutral point clamped(NPC)three-level inverter using IGBTsThree-level voltage-fed inverters have recently become more and more popular for higher power drive applications because of their easy voltage sharing features．1ower dv/dt per switching for each of the devices，and superior harmonic quality at the output．The availability of HV-IGBTs has led to the design of a new range of medium-high voltage inverter usingthree-level NPC topology．This kind of inverter can realize a whole range with a voltage rating from 2．3 kV to 4．1 6 kV Series connection of HV-IGBT modules is used in the 3．3 kV and 4．1 6 kV devices．The 2．3 kV inverters need only one HV-IGBT per switch[2,3].2．1 Power sectionTo meet the demands for medium voltage applications．a three-level neutral point clamped inverter realizes the power section．In comparison to a two-level inverter．the NPC inverter offers the benefit that three voltage levels can be supplied to the output terminals，so for the same output current quality，only 1/4 of the switching frequency is necessary．Moreover the voltage ratings of the switches in NPC inverter topology will be reduced to 1/2．and the additional transient voltage stress on the motor can also be reduced to 1/2 compared to that of a two-level inverter．The switching states of a three-level inverter are summarized in Table 1．U．V and W denote each of the three phases respectively；P N and O are the dc bus points．The phase U，for example，is in state P(positive bus voltage)when the switches S1u and S2u are closed，whereas it is in state N (negative bus voltage) when the switches S3u and S4u are closed．At neutral point clamping，the phase is in O state when either S2u or S3u conducts depending on positive or negative phase current polarity，respectively．For neutral point voltage balancing，the average current injected at O should be zero．2．2 Line side converterFor standard applications．a l2-pulse diode rectifier feeds the divided DC-link capacitor．This topology introduces low harmonics on the line side．For even higher requirements a 24-pulse diode rectifier can be used as an input converter．For more advanced applications where regeneration capability is necessary, an active front．end converter can replace the dioderectifier, using the same structure as the inverter．2．3 Inverter controlMotor Contro1．Motor control of induction machines is realized by using a rotor flux．oriented vector controller．Fig．2 shows the block diagram of indirect vector controlled drive that incorporates both constant torque and high speed field-weakening regions where the PW M modulator was used．Inthis figure，the command flux is generated as function of speed．The feedback speed isadded with the feed forward slip command signal . the resulting frequency signal isintegrated and then the unit vector signals(cos and sin)are generated．The vector rotatorgenerates the voltage and angle commands for the PW M as shown．PWM Modulator．The demanded voltage vector is generated using an elaborate PWM modulator．The modulator extends the concepts of space-vector modulation to the three-level inverter．The operation can be explained by starting from a regularly sampled sine-triangle comparison from two-level inverter．Instead of using one set of reference waveforms and one triangle defining the switching frequency，the three-level modulator uses two sets of reference waveforms U r1 and U r2 and just one triangle．Thus, each switching transition is used in an optimal way so that several objectives are reached at the same time．Very low harmonics are generated．The switching frequency is low and thus switching losses are minimized．As in a two-level inverter, a zero-sequence component can be added to each set of reference waveform s in order to maximize the fundamental voltage component．As an additional degree of freedom，the position of the reference waveform s within the triangle can be changed．This can be used for current balance in the two halves of the DC-1ink．3 Testing resultsAfter Successful installation of three 750 kW /2．3 kV three-level inverters for one 2．7 km long belt conveyor driving system in Chengzhuang Mine．The performance of the whole VFC system was tested．Fig．3 is taken from the test，which shows the excellent characteristic of the belt conveyor driving system with VFC controller．Fig．3 includes four curves．The curve 1 shows the belt tension．From the curve it can be find that the fluctuation range of the belt tension is very smal1．Curve 2 and curve 3 indicate current and torque separately．Curve 4 shows the velocity of the controlled belt．The belt velocityhave the“s”shape characteristic．A1l the results of the test show a very satisfied characteristic for belt driving system．4 ConclusionsAdvances in conveyor drive control technology in recent years have resulted in many more reliable．Cost-effective and performance-driven conveyor drive system choices for users．Among these choices，the Variable frequency control (VFC) method shows promising use in the future for long distance belt conveyor drives due to its excellent performances．The NPC three-level inverter using high voltage IGBTs make the Variable frequency control in medium voltage applications become much more simple because the inverter itself can provide the medium voltage needed at the motor terminals，thus eliminating the step-up transformer in most applications in the past．The testing results taken from the VFC control system with NPC three．1evel inverters used in a 2．7 km long belt conveyor drives in Chengzhuang Mine indicates that the performance of NPC three-level inverter using HV-IGBTs together with the control strategy of rotor field-oriented vector control for induction motor drive is excellent for belt conveyor driving system．References[l] Jim Ehler. Conveyor drive technologies offer smooth, soft starts[J]. Motors& Drives, 2001(4): 28-35.[2] Sommer R, Mertens A. Medium voltage drive system with three-level NPC inverter using IGBTs[A]. IEE Colloquium on PWM Medium V oltage Drives[C]. Birmingham,2000[3] Mertens A, Sommer R, Brunotte C. Applications of medium voltage drives with IGBT three-level inverter[A]. IEE colloquium on PWM medium voltage drives[C]. Birmingham,2000中文译文：带式输送机及其牵引系统在运送大量的物料时，带式输送机在长距离的运输中起到了非常重要的竞争作用。
附录英文文献A Comparison of Soft Start Mechanisms for Mining Belt ConveyorsMichael L. Nave, P.E.CONSOL Inc.1800 Washington Road Pittsburgh, PA 15241Belt Conveyors are an important method for transportation of bulk materials in the mining industry. The control of the application of the starting torque from the belt drive system to the belt fabric affects the performance, life cost, and reliability of the conveyor. This paper examines applications of each starting method within the coal mining industry.INTRODUCTIONThe drive pulley via friction between the drive pulley and the belt fabric must transmit the force required to move a belt conveyor. In order to transmit power there must be a difference in the belt tension as it approaches and leaves the drive pulley. These conditions are true for steady state running, starting, and stopping. Traditionally, belt designs are based on static calculations of running forces. Since starting and stopping are not examined in detail, safety factors are applied to static loadings (Harrison, 1987). This paper will primarily address the starting or acceleration duty of the conveyor. The belt designer must control starting acceleration to prevent excessive tension in the belt fabric and forces in the belt drive system (Surtees, 1986). High acceleration forces can adversely affect the belt fabric, belt splices, drive pulleys, idler pulleys, shafts, bearings, speed reducers, and couplings. Uncontrolled acceleration forces can cause belt conveyor system performance problems with vertical curves, excessive belt take-up movement, loss of drive pulley friction, spillage of materials, and festooning of the belt fabric. The belt designer Is confronted with two problems, The belt drive system must produce a minimum torque powerful enough to start the conveyor, and controlled such that the acceleration forces are within safe limits. Smooth starting of the conveyor can be accomplished by the use of drive torque control equipment, eithermechanical or electrical, or a combination of the two (CEM, 1979).SOFT START MECHANISM EV ALUATION CRITERIONWhat is the best belt conveyor drive system? The answer depends on many variables. The best system is one that provides acceptable control for starting, running, and stopping at a reasonable cost and with high reliability (Llewellyn and Sudarshan, 1978).Belt Drive SystemFor the purposes of this paper we will assume that belt conveyors are almost always driven by electrical prime movers (Goodyear Tire and Rubber, 1982). The belt "drive system" shall consist of multiple components including the electrical prime mover, the electrical motor starter with control system, the motor coupling, the speed reducer, the low speed coupling, the belt drive pulley, and the pulley brake or hold back (Zur, 1986). It is important that the belt designer examine the applicability of each system component to the particular application. For the purpose of this paper, we will assume that all drive system components are located in the fresh air, non-permissible, areas of the mine, or in non-hazardous, National Electrical Code, Article 500 explosion-proof, areas of the surface of the mine.Belt Drive Component AttributesSize.Certain drive components are available and practical in different size ranges. For this discussion, we will assume that belt drive systems range from fractional horsepower to multiples of thousands of horsepower. Small drive systems are often below 50 horsepower. Medium systems range from 50 to 1000 horsepower. Large systems can be considered above 1000 horsepower. Division of sizes into these groups is entirely arbitrary. Care must be taken to resist the temptation to over motor or under motor a belt flight to enhance standardization. An over motored drive results in poor efficiency and the potential for high torques, while an under motored drive could result in destructive over speeding on regeneration, or overheating with shortened motor life (Lodi, etal., 1978).Torque Control.Belt designers try to limit the starting torque to no more than 150% of the running torque (Cema, 1979; Goodyear, 1982). The limit on the applied starting torque is often the limit of rating of the belt carcass, belt splice, pulley lagging, or shaft deflections. On larger belts and belts withoptimized sized components, torque limits of 110% through 125% are common (Elberton, 1986). In addition to a torque limit, the belt starter may be required to limit torque increments that would stretch belting and cause traveling waves. An ideal starting control system would apply a pretension torque to the belt at rest up to the point of breakaway, or movement of the entire belt, then a torque equal to the movement requirements of the belt with load plus a constant torque to accelerate the inertia of the system components from rest to final running speed. This would minimize system transient forces and belt stretch (Shultz, 1992). Different drive systems exhibit varying ability to control the application of torques to the belt at rest and at different speeds. Also, the conveyor itself exhibits two extremes of loading. An empty belt normally presents the smallest required torque for breakaway and acceleration, while a fully loaded belt presents the highest required torque. A mining drive system must be capable of scaling the applied torque from a 2/1 ratio for a horizontal simple belt arrangement, to a 10/1 range for an inclined or complex belt profile.Thermal Rating.During starting and running, each drive system may dissipate waste heat. The waste heat may be liberated in the electrical motor, the electrical controls,, the couplings, the speed reducer, or the belt braking system. The thermal load of each start Is dependent on the amount of belt load and the duration of the start. The designer must fulfill the application requirements for repeated starts after running the conveyor at full load. Typical mining belt starting duties vary from 3 to 10 starts per hour equally spaced, or 2 to 4 starts in succession. Repeated starting may require the debating or over sizing of system components. There is a direct relationship between thermal rating for repeated starts and costs.Variable Speed.Some belt drive systems are suitable for controlling the starting torque and speed, but only run at constant speed. Some belt applications would require a drive system capable of running for extended periods at less than full speed. This is useful when the drive load must be shared with other drives, the belt is used as a process feeder for rate control of the conveyed material, the belt speed is optimized for the haulage rate, the belt is used at slower speeds to transport men or materials, or the belt is run a slow inspection or inching speed for maintenance purposes (Hager, 1991). The variable speed belt drive will require a control system based on some algorithm toregulate operating speed.Regeneration or Overhauling Load.Some belt profiles present the potential for overhauling loads where the belt system supplies energy to the drive system. Not all drive systems have the ability to accept regenerated energy from the load. Some drives can accept energy from the load and return it to the power line for use by other loads. Other drives accept energy from the load and dissipate it into designated dynamic or mechanical braking elements. Some belt profiles switch from motoring to regeneration during operation. Can the drive system accept regenerated energy of a certain magnitude for the application? Does the drive system have to control or modulate the amount of retarding force during overhauling? Does the overhauling occur when running and starting?Maintenance and Supporting Systems.Each drive system will require periodic preventative maintenance. Replaceable items would include motor brushes, bearings, brake pads, dissipation resistors, oils, and cooling water. If the drive system is conservatively engineered and operated, the lower stress on consumables will result in lower maintenance costs. Some drives require supporting systems such as circulating oil for lubrication, cooling air or water, environmental dust filtering, or computer instrumentation. The maintenance of the supporting systems can affect the reliability of the drive system.Cost.The drive designer will examine the cost of each drive system. The total cost is the sum of the first capital cost to acquire the drive, the cost to install and commission the drive, the cost to operate the drive, and the cost to maintain the drive. The cost for power to operate the drive may vary widely with different locations. The designer strives to meet all system performance requirements at lowest total cost. Often more than one drive system may satisfy all system performance criterions at competitive costs.Complexity.The preferred drive arrangement is the simplest, such as a single motor driving through a single head pulley. However, mechanical, economic, and functional requirements often necessitate the use of complex drives. The belt designer must balance the need for sophistication against the problems that accompany complex systems. Complex systems require additional design engineering for successful deployment. An often-overlooked cost in a complex system is the costof training onsite personnel, or the cost of downtime as a result of insufficient training.Multiple Drives.A simple belt is often driven by one drive pulley. Multiple, independent pulleys drive some more complex belts. These pulleys may be near each other, or at different belt locations. Multiple drives allow the belt designer to increase the driven horsepower, while maintaining or reducing belt fabric tensions. Multiple drives require a drive starting and running system that allows for coordination between drives. Multiple drives of different sizes or different belt wrap angles may require a load proportion scheme (load sharing). Load sharing requires one of the drives to operate at a lower torque rating during starting, or also during running conditions. Will the multiple drive belt system operate with one or more prime movers out of service? Multiple drives at different locations will require a distributed control system (Gallina, 1991; Sur, 1987).Conveyor Jam.It is possible for a running belt conveyor to encounter a mechanical jam of the belt fabric. The drive system will continue to impart torque to the fabric up to the slip of the fabric on the drive pulley. Different drives vary in the application of breakdown torque to the stalled machine. It is important for the drive designer to examine the rotating inertia in the drive system. The prime mover motor rotor and all other rotating parts may contribute significant kinetic energy to the stalled belt. The drive response to the stall and the application of the torque limit may vary.Control System.Each drive system will require a base case permissive control system for starting and running supervision. Most belt drive systems today use some form of computer control. The computer control systems all depend on field sensors for measurement and reporting of drive parameters. The belt drive designer must determine the minimum required number and location of the field devices for adequate control. The drive control system will require power switchgear and control switchgear with provisions for "lockout" for conveyor maintenance and service. Lockout applies to sources of electrical, hydraulic, pneumatic, and gravity energy.SOFT START METHODS OVERVIEWThe system approach will group the electrical prime mover with control, the high and low speed couplings, the speed reducer, and the drive pulley for examination. The belt conveyor will require a force to initiate movement, termed breakaway torque. In movement, the conveyor willrequire torque to support existing motion and torque to support acceleration to running speed within the time and thermal limits imposed by the system. The resultant acceleration is proportional to the applied force divided by the mass in the system according to Newton's second law, where the mass is the system equivalent weight, or external inertia, divided by the force of gravity. More commonly, the belt designer will calculate the Wk, or the weight of the system times the square of the radius of gyration. It is important that the designer add the drive system external inertia to the belt system inertia in order to view total system inertia. System inertias are modeled at the rotating speed of the electrical prime mover, or at the linear speed of the belt fabric. All system external inertias must be referred to a common base (Harper, 1960).中文翻译煤矿输送带软启动机制的比较Michael L. Nave, P.E.CONSOL Inc.1800 Washington Road Pittsburgh, PA 15241在采矿业，带式输送机是运送散装材料方面的一个重要方法。
绳架吊挂式带式输送机设计ABSTRACTA machine is a combination of mechanisms and other components which transforms, transmits. Examples are engines, turbines, vehicles, hoists, printing presses, washing machines, and movie cameras. Many of the principles and methods of design that apply to machines also apply to manufactured articles that are not true machines. The term "mechanical design" is used in a broader sense than "machine design" to include their design. the motion and structural aspects and the provisions for retention and enclosure are considerations in mechanical design. Applications occur in the field of mechanical engineering, and in other engineering fields as well, all of which require mechanical devices, such as switches, cams, valves, vessels, and mixers.KEY WORDS Mechanical, Design mechanisms,Design Process1 The Design ProcessDesigning starts with a need real.Existing apparatus may need improvements in durability, efficiency, weight, speed, or cost. New apparatus may be needed to perform a function previously done by men, such as computation, assembly, or servicing. With the objective wholly or partly.In the design preliminary stage, should allow to design the personnel fully to display the creativity, not each kind of restraint. Even if has had many impractical ideas, also can in the design early time, namely in front of the plan blueprint is corrected. Only then, only then does not send to stops up the innovation the mentality. Usually, must propose several sets of design proposals, then perform the comparison. Has the possibility very much in the plan which finally designated, has used certain not in plan some ideas which accepts.When the general shape and a few dimensions of the several components become apparent, analysis can begin in earnest. The analysis will have as its objective satisfactory or superior performance, plus safety and durability with minimum weight, and a competitive cost. Optimum proportions and dimensions will be sought for each critically loaded section, together with a balance between the strengths of the several components. Materials and their treatment will be chosen. These important objectives can be attained only by analysis based upon the principles of mechanics, such as those of static for reaction forces and for the optimum utilization of friction; of dynamics for inertia, acceleration, and energy; of elasticity and strength of materials for stress and deflection; of physical behavior of materials; and of fluid mechanics for lubrication and hydrodynamic drives. The analyses may be made by the same engineer who conceived the arrangement of mechanisms, or, in a large company, they may be made by a separate analysis division or research group. Design is a reiterative and cooperative process, whether done formally or informally, and the analyst can contribute to phases other than his own. Product design requires much research and development. Many Concepts of anidea must be studied, tried, and then either used or discarded. Although the content of each engineering problem is unique, the designers follow the similar process to solve the problems.Product liability suits designers and forced in material selection, using the best program. In the process of material, the most common problems for five (a) don't understand or not use about the latest application materials to the best information, (b) failed to foresee and consider the reasonable use material may (such as possible, designers should further forecast and consider due to improper use products. In recent years, many products liability in litigation, the use of products and hurt the plaintiff accused manufacturer, and won the decision), (c) of the materials used all or some of the data, data, especially when the uncertainty long-term performance data is so, (d) quality control method is not suitable and unproven, (e) by some completely incompetent persons choose materials.Through to the above five questions analysis, may obtain these questions is does not have the sufficient reason existence the conclusion. May for avoid these questions to these questions research analyses the appearance indicating the direction. Although uses the best choice of material method not to be able to avoid having the product responsibility lawsuit, designs the personnel and the industry carries on the choice of material according to the suitable procedure, may greatly reduce the lawsuit the quantity.May see from the above discussion, the choice material people should to the material nature, the characteristic and the processing method have comprehensive and the basic understanding.Finally, a design based upon function, and a prototype may be built. If its tests are satisfactory, the initial design will undergo certain modifications that enable it to be manufactured in quantity at a lower cost. During subsequent years of manufacture and service, the design is likely to undergo changes as new ideas are conceived or as further analyses based upon tests and experience indicate alterations. Sales appeal.2 Some Rules for DesignIn this section it is suggested that, applied with a creative attitude, analyses can lead to important improvements and to the conception and perfection of alternate, perhaps more functional, economical, and durable products.To stimulate creative thought, the following rules are suggested for the designer and analyst. The first six rules are particularly applicable for the analyst.1. A creative use of need of physical properties and control process.2. Recognize functional loads and their significance.3. Anticipate unintentional loads.4. Devise more favorable loading conditions.5. Provide for favorable stress distribution and stiffness with minimum weight.6. Use basic equations to proportion and optimize dimensions.7. Choose materials for a combination of properties.8. Select carefully, stock and integral components.9. Modify a functional design to fit the manufacturing process and reduce cost.10. Provide for accurate location and noninterference of parts in assembly.Machinery design covers the following contents.1. Provides an introduction to the design process , problem formulation ,safety factors.2. Reviews the material properties and static and dynamic loading analysis ,Including beam , vibration and impact loading.3. Reviews the fundamentals of stress and defection analysis.4. Introduces fatigue-failure theory with the emphasis on stress-life approaches to high-cycle fatigue design, which is commonly used in the design of rotation machinery.5. Discusses thoroughly the phenomena of wear mechanisms, surface contact stresses ,and surface fatigue.6. Investigates shaft design using the fatigue-analysis techniques.7. Discusses fluid-film and rolling-element bearing theory and application8. Gives a thorough introduction to the kinematics, design and stress analysis of spur gears , and a simple introduction to helical ,bevel ,and worm gearing.9. Discusses spring design including compression ,extension and torsion springs.10. Deals with screws and fasteners including power screw and preload fasteners.11. Introduces the design and specification of disk and drum clutches and brakes.3 Machine DesignThe complete design of a machine is a complex process. The machine design is a creative work. Project engineer not only must have the creativity in the work, but also must in aspect and so on mechanical drawing, kinematics, engineerig material, materials mechanics and machine manufacture technology has the deep elementary knowledge.One of the first steps in the design of any product is to select the material from which each part is to be made. Numerous materials are available to today's designers. The function of the product, its appearance, the cost of the material, and the cost of fabrication are important in making a selection. A careful evaluation of the properties of a. material must be made prior to any calculations.Careful calculations are necessary to ensure the validity of a design. In case of any part failures, it is desirable to know what was done in originally designing the defective components. The checking of calculations (and drawing dimensions) is of utmost importance. The misplacement of one decimal point can ruin an otherwise acceptable project. All aspects of design work should be checked and rechecked.The computer is a tool helpful to mechanical designers to lighten tedious calculations, and provide extended analysis of available data. Interactive systems, based on computer capabilities, have made possible the concepts of computer aideddesign (CAD) and computer-aided manufacturing (CAM). How does the psychologist frequently discuss causes the machine which the people adapts them to operate. Designs personnel''s basic responsibility is diligently causes the machine to adapt the people. This certainly is not an easy work, because certainly does not have to all people to say in fact all is the most superior operating area and the operating process. Another important question, project engineer must be able to carry on the exchange and the consultation with other concerned personnel. In the initial stage, designs the personnel to have to carry on the exchange and the consultation on the preliminary design with the administrative personnel, and is approved. This generally is through the oral discussion, the schematic diagram and the writing material carries on.If front sues, the machine design goal is the production can meet the human need the product. The invention, the discovery and technical knowledge itself certainly not necessarily can bring the advantage to the humanity, only has when they are applied can produce on the product the benefit. Thus, should realize to carries on before the design in a specific product, must first determine whether the people do need this kind of productMust regard as the machine design is the machine design personnel carries on using creative ability the product design, the system analysis and a formulation product manufacture technology good opportunity. Grasps the project elementary knowledge to have to memorize some data and the formula is more important than. The merely service data and the formula is insufficient to the completely decision which makes in a good design needs. On the other hand, should be earnest precisely carries on all operations. For example, even if places wrong a decimal point position, also can cause the correct design to turn wrongly.A good design personnel should dare to propose the new idea, moreover is willing to undertake the certain risk, when new method is not suitable, use original method. Therefore, designs the personnel to have to have to have the patience,because spends the time and the endeavor certainly cannot guarantee brings successfully. A brand-new design, the request screen abandons obsoletely many, knows very well the method for people. Because many person of conservativeness, does this certainly is not an easy matter. A mechanical designer should unceasingly explore the improvement existing product the method, should earnestly choose originally, the process confirmation principle of design in this process, with has not unified it after confirmation new idea.摘要机器是由机械装置和其它组件组成的。
外文原文：A Comparison of Soft Start Mechanisms for Mining Belt Conveyors1800 Washington Road Pittsburgh, PA 15241 Belt Conveyors are an important method for transportation of bulk materials in the mining industry. The control of the application of the starting torque from the belt drive system to the belt fabric affects the performance, life cost, and reliability of the conveyor. This paper examines applications of each starting method within the coal mining industry.INTRODUCTIONThe force required to move a belt conveyor must be transmitted by the drive pulley via friction between the drive pulley and the belt fabric. In order to transmit power there must be a difference in the belt tension as it approaches and leaves the drive pulley. These conditions are true for steady state running, starting, and stopping. Traditionally, belt designs are based on static calculations of running forces. Since starting and stopping are not examined in detail, safety factors are applied to static loadings (Harrison, 1987). This paper will primarily address the starting or acceleration duty of the conveyor. The belt designer must control starting acceleration to prevent excessive tension in the belt fabric and forces in the belt drive system (Suttees, 1986). High acceleration forces can adversely affect the belt fabric, belt splices, drive pulleys, idler pulleys, shafts, bearings, speed reducers, and couplings. Uncontrolled acceleration forces can cause belt conveyor system performance problems with vertical curves, excessive belt take-up movement, loss of drive pulley friction, spillage of materials, and festooning of the belt fabric. The belt designer is confronted with two problems, The belt drive system must produce a minimum torque powerful enough to start the conveyor, and controlled such that the acceleration forces are within safe limits. Smooth starting of the conveyor can be accomplished by the use of drive torque control equipment, either mechanical or electrical, or acombination of the two (CEM, 1979).SOFT START MECHANISM EV ALUATION CRITERIONWhat is the best belt conveyor drive system? The answer depends on many variables. The best system is one that provides acceptable control for starting, running, and stopping at a reasonable cost and with high reliability (Lewdly and Sugarcane, 1978). Belt Drive System For the purposes of this paper we will assume that belt conveyors are almost always driven by electrical prime movers (Goodyear Tire and Rubber, 1982). The belt "drive system" shall consist of multiple components including the electrical prime mover, the electrical motor starter with control system, the motor coupling, the speed reducer, the low speed coupling, the belt drive pulley, and the pulley brake or hold back (Cur, 1986). It is important that the belt designer examine the applicability of each system component to the particular application. For the purpose of this paper, we will assume that all drive system components are located in the fresh air, non-permissible, areas of the mine, or in non-hazardous, National Electrical Code, Article 500 explosion-proof, areas of the surface of the mine.Belt Drive Component Attributes Size.Certain drive components are available and practical in different size ranges. For this discussion, we will assume that belt drive systems range from fractional horsepower to multiples of thousands of horsepower. Small drive systems are often below 50 horsepower. Medium systems range from 50 to 1000 horsepower. Large systems can be considered above 1000 horsepower. Division of sizes into these groups is entirely arbitrary. Care must be taken to resist the temptation to over motor or under motor a belt flight to enhance standardization. An over motored drive results in poor efficiency and the potential for high torques, while an under motored drive could result in destructive overspending on regeneration, or overheating with shortened motor life (Lords, et al., 1978).Torque Control.Belt designers try to limit the starting torque to no more than 150% of the running torque (CEMA, 1979; Goodyear, 1982). The limit on the applied starting torque is often the limit of rating of the belt carcass, belt splice, pulley lagging, or shaft deflections. On larger belts and belts with optimized sized components, torque limits of 110% through 125% are common (Elberton, 1986). In addition to a torque limit, the belt starter may be required to limit torque increments that would stretch belting and cause traveling waves. An ideal starting control system would apply a pretension torque to the belt at rest up to the point of breakaway, or movement of the entire belt, then a torque equal to the movement requirements of the belt with load plus a constant torque to accelerate the inertia of the system components from rest to final running speed. This would minimize system transient forces and belt stretch (Shultz, 1992). Different drive systems exhibit varying ability to control the application of torques to the belt at rest and at different speeds. Also, the conveyor itself exhibits two extremes of loading. An empty belt normally presents the smallest required torque for breakaway and acceleration, while a fully loaded belt presents the highest required torque. A mining drive system must be capable of scaling the applied torque from a 2/1 ratio for a horizontal simple belt arrangement, to a 10/1 ranges for an inclined or complex belt profile.Thermal Rating.During starting and running, each drive system may dissipate waste heat. The waste heat may be liberated in the electrical motor, the electrical controls,, the couplings, the speed reducer, or the belt braking system. The thermal load of each start Is dependent on the amount of belt load and the duration of the start. The designer must fulfill the application requirements for repeated starts after running the conveyor at full load. Typical mining belt starting duties vary from 3 to 10 starts perhour equally spaced, or 2 to 4 starts in succession. Repeated starting may require the dreading or over sizing of system components. There is a direct relationship between thermal rating for repeated starts and costs. Variable Speed. Some belt drive systems are suitable for controlling the starting torque and speed, but only run at constant speed. Some belt applications would require a drive system capable of running for extended periods at less than full speed. This is useful when the drive load must be shared with other drives, the belt is used as a process feeder for rate control of the conveyed material, the belt speed is optimized for the haulage rate, the belt is used at slower speeds to transport men or materials, or the belt is run a slow inspection or inching speed for maintenance purposes (Hager, 1991). The variable speed belt drive will require a control system based on some algorithm to regulate operating speed. Regeneration or Overhauling Load. Some belt profiles present the potential for overhauling loads where the belt system supplies energy to the drive system. Not all drive systems have the ability to accept regenerated energy from the load. Some drives can accept energy from the load and return it to the power line for use by other loads. Other drives accept energy from the load and dissipate it into designated dynamic or mechanical braking elements. Some belt profiles switch from motoring to regeneration during operation. Can the drive system accept regenerated energy of a certain magnitude for the application? Does the drive system have to control or modulate the amount of retarding force during overhauling? Does the overhauling occur when running and starting? Maintenance and Supporting Systems. Each drive system will require periodic preventative maintenance. Replaceable items would include motor brushes, bearings, brake pads, dissipation resistors, oils, and cooling water. If the drive system is conservatively engineered and operated, the lower stress on consumables will result in lower maintenance costs. Some drives require supporting systems such as circulating oil for lubrication, cooling air or water, environmental dust filtering, or computer instrumentation. The maintenance of the supporting systems can affect the reliability of the drive system.Cost.The drive designer will examine the cost of each drive system. The total cost is the sum of the first capital cost to acquire the drive, the cost to install and commission the drive, the cost to operate the drive, and the cost to maintain the drive. The cost for power to operate the drive may vary widely with different locations. The designer strives to meet all system performance requirements at lowest total cost. Often more than one drive system may satisfy all system performance criterions at competitive costs.Complexity.The preferred drive arrangement is the simplest, such as a single motor driving through a single head pulley. However, mechanical, economic, and functional requirements often necessitate the use of complex drives. The belt designer must balance the need for sophistication against the problems that accompany complex systems. Complex systems require additional design engineering for successful deployment. An often-overlooked cost in a complex system is the cost of training onsite personnel, or the cost of downtime as a result of insufficient training.SOFT START DRIVE CONTROL LOGICEach drive system will require a control system to regulate the starting mechanism. The most common type of control used on smaller to medium sized drives with simple profiles is termed "Open Loop Acceleration Control". In open loop, the control system is previously configured to sequence the starting mechanism in a prescribed manner, usually based on time. In open loop control, drive-operating parameters such as current, torque, or speed do not influence sequence operation. This method presumes that the control designer has adequately modeled drive system performance on the conveyor. For larger or more complex belts, "Closed Loop" or "Feedback" control may he utilized. In closed loop control, during starting, the controlsystem monitors via sensors drive operating parameters such as current level of the motor, speed of the belt, or force on the belt, and modifies the starting sequence to control, limit, or optimize one or wore parameters. Closed loop control systems modify the starting applied force between an empty and fully loaded conveyor. The constants in the mathematical model related to the measured variable versus the system drive response are termed the tuning constants. These constants must be properly adjusted for successful application to each conveyor. The most common schemes for closed loop control of conveyor starts are tachometer feedback for speed control and load cell force or drive force feedback for torque control. On some complex systems, It is desirable to have the closed loop control system adjust itself for various encountered conveyor conditions. This is termed "Adaptive Control". These extremes can involve vast variations in loadings, temperature of the belting, location of the loading on the profile, or multiple drive options on the conveyor. There are three common adaptive methods. The first involves decisions made before the start, or ''Restart Conditioning''. If the control system could know that the belt is empty, it would reduce initial force and lengthen the application of acceleration force to full speed. If the belt is loaded, the control system would apply pretension forces under stall for less time and supply sufficient torque to adequately accelerate the belt in a timely manner. Since the belt only became loaded during previous running by loading the drive, the average drive current can be sampled when running and retained in a first-in-first-out buffer memory that reflects the belt conveyance time. Then at shutdothe FIFO average may be use4 to precondition some open loop and closed loop set points for the next start. The second method involves decisions that are based on drive observations that occur during initial starting or "Motion Proving''. This usually involves a comparison In time of the drive current or force versus the belt speed. if the drive current or force required early in the sequence is low and motion is initiated, the belt must be unloaded. If the drive current or force required is high and motion is slow in starting, the conveyor must be loaded. This decision can be divided in zones and used to modify the middle and finish of the start sequence control. The third methodinvolves a comparison of the belt speed versus time for this start against historical limits of belt acceleration, or ''Acceleration Envelope Monitoring''. At start, the belt speed is measured versus time. This is compared with two limiting belt speed curves that are retained in control system memory. The first curve profiles the empty belt when accelerated, and the second one the fully loaded belt. Thus, if the current speed versus time is lower than the loaded profile, it may indicate that the belt is overloaded, impeded, or drive malfunction. If the current speed versus time is higher than the empty profile, it may indicate a broken belt, coupling, or drive malfunction.In either case, the current start is aborted and an alarm issued.CONCLUSIONThe best belt starting system is one that provides acceptable performance under all belt load Conditions at a reasonable cost with high reliability. No one starting system meets all needs. The belt designer must define the starting system attributes that are required for each belt. In general, the AC induction motor with full voltage starting is confined to small belts with simple profiles. The AC induction motor with reduced voltage SCR starting is the base case mining starter for underground belts from small to medium sizes. With recent improvements, the AC motor with fixed fill fluid couplings is the base case for medium to large conveyors with simple profiles. The Wound Rotor Induction Motor drive is the traditional choice for medium to large belts with repeated starting duty or complex profiles that require precise torque control. The DC motor drive, Variable Fill Hydrokinetic drive, and the Variable Mechanical Transmission drive compete for application on belts with extreme profiles or variable speed at running requirements. The choice is dependent on location environment, competitive price, operating energy losses, speed response, and user familiarity. AC Variable Frequency drive and Brush less DC applications are limited to small to medium sized belts that require precise speed control due to higher present costs and complexity. However, with continuing competitive and technical improvements, theuse of synthesized waveform electronic drives will expand.译文：煤矿业带式输送机几种软起动方式的比较统一公司1800 年华盛顿路匹兹堡, PA 15241带式运送机是采矿工业运输大批原料的重要方法。
Design Of Belt Conveyor Transporting machine to press the operation way can is divided into:1:The leather belt type transports machine 2:Is spiral to transport machine 3:The Dou type promotes machine 4:The roller transports machine 5:Calculate to transport machine 6:The plank chain transports machine 7:The net takes to transport machine 8:The chain transports machine.1.ParameterIs general according to various condition of request, material shipping point that the material transports system, relevant of the production craft process and material of characteristic etc. to make sure each main parameter.①Transport ability:The ability of transporting the transporting of machine means unit for time inside transport of material quantity.While transporting to spread a form material, with the quality or physical volume calculation that the per hour transports a material;At transport into a piece product, with the number of items calculation that the per hour transports.②Transport speed:The exaltation transports speed to improve the ability of transporting.When being making to lead a piece by belt conveyer and transporting length was more big, transport speed to gradually enlarge.But the take type of high-speed operation transports machine to need to notice vibration, Zao voice and start and make etc. problem.For use chain as lead a piece of transport machine, transporting the speed should not lead greatly, in order to prevent the aggrandizement power carry a lotus.Carry on transporting of craft operation machine at the same time, transporting the speed should press to produce a craft to request an assurance.③Reach a size:Transport reaching of machine a size to include belt conveyer width, lath width and anticipate Dou capacity, piping diameter and container all of etc.s.These reach a sizes to all directly influence to transport machine of transport ability.④Transport length and Qing Cape:Transport circuit length and Qing Cape size to directly influence the total resistance of transporting the machine and need of power.2.Transport a machine the spot application wayConstitute to carry on explaining in detail from the take type machine system first:Leather belt's transporting machine is to spread a form material to transport and pack to unload an equipments most importantly, can extensively used for the mineral mountain, metallurgy, building materials, chemical engineering, electric power, industrial realms like food processing,etc, in the coal mine, metal mineral, the steel business enterprise, port, grounds like cement works,etc a great deal of application that can see skin machine, transporting the machine can not only complete to spread a transporting of form material, but also can transport into a piece material, but basis use location, work environment, transport the dissimilarity of material category, will also have bigger difference in its design and the application;Modernization of transport the machine system has higher request to the dust palliative, is this, in each the device that transfer place and establish and sprinkle water and gather a dust, transport machine and follow line in the tape will establish and defend a breeze cover or block an aerofoil, system from list the machine constitute of, to work in the whole machine system of operate and fix to say, want and have a foothold and divide the single machine of the tube at oneself, and want to understand mutual contact between systems, list machine again is constitute to°from many partses, only work well the daily maintenance of each parts maintains and makes it is placed in good work status so as to ensure the safe movement of equipments;We generally will transport the use place, work environment of machine according to the take type, technique function and transport material category to wait various dissimilarity with satisfy various forms of homework work condition, in addition to in addition to transporting machine, the in general use leather belt of more adoption also various special kind tapes of new structure transport machine and have a mainly having of the representative among them:Big Qing Cape take type machine, deep slot take type machine and press take type machine, take care of the form take type, the air cushion take type, the flat surface turn take type, the line friction type, wave-like in shape the belt conveyer type blocking a side transport machine etc. andcarry on a thin method for turning and canning exist various classifications and make following introduction now:Press the use classification, there is in general use ambulation type, under the well choice type, the strip mine is used a fixed type, special kind structure type, can move a place type and transport machine, load machine appropriation redistribution function type, the big Qing Cape type transports machine etc., generally speaking transport machine inside the short distance factory can complete level, up the luck or bottom carries, canning go against the wood grain type leather belt machine can be used for double to transport a material, hang arm machine usually install anticipate on board in the heap, and can turn round, line up the function of soil or cloth by realization, but Gao Jia Ji propped up by in the door usually match with other spread and anticipate and handle an equipments common use, for example give or get an electric shock and constuct a medium application in water, can install standard in the center frame, the machine's mounting places on the track Zhen, easy to move and place;Press the category of transporting the material to categorize, have the generally lax material is used of, the strong and tough material is used of and list piece the leather belt used in material transport machine etc. and press the rubber conveyance takes a loading segment of position to categorize, include a leather belt loading segment at top of and loading segment at underneath of and at the same time loading segment at up underneath of double to transport machine three, the use double can distinguish to transporting machine at up branch and bottom branch transport a material, but for keeping material contact noodles don't produce a change and need to bring in to go to the rubber to be periodically inside out.3.CategorizeTransporting machine generally and pressing already didn't lead piece to carry on a classification and had to lead a transporting of piece machine to generally include to lead a piece, loading to reach a piece, drive device, bring to the stretch device and change to accept an etc. to the device and.Lead a piece to in order to deliver to lead dint, can adopt belt conveyer and lead chain or steel wire rope;The loading reaches apiece to in order to accept to put a material and has already anticipated Dou and bracket or mourns to have...etc.;Drive device to transport machine with the power, generally from electric motor, decelerate a machine and make machine(stop a machine) etc. to constitute;Bring to the stretch to equip to generally have the Luo pole the type and heavy hammer type 2 kind, can make to lead a piece to keep certain tension and hang a degree, transport machine by assurance normal operation;Pay to accept a piece to in order to accept to give to lead piece or loading to reach a piece, can adopt to give Gun and roll an etc..Having the structure characteristics that lead the transporting of piece machine is:Be delivered a material and pack reaching with the loading leading a link together inside the piece, or directly pack in leading a piece(is like belt conveyer), led a piece to once round each roller or the chain round beginning and end and connect with each other, formation include and deliver a having of material carry branch and don't deliver a material of have never carried shutting of branch and match wreath road, make use of lead continuous sport of piece and transport a material.This type ofly transporting model is numerous, there is mainly a take type transporting a machine, plank type and transporting a machine, small car type and transporting machine, escalator, automatic sidewalk, paring off plank and transporting machine, covering up and paring off plank and transporting a machine, Dou type and transporting a machine, Dou type and promoting machine and hanging and transporting machine and build on stilts a cableway...etc..The structure that didn't lead transporting of piece machine constitutes each not same, use to the work of transporting the material to reach a piece as well not same.Their structure characteristicses are:Make use of a work to reach a revolving of piece to exercise or the back and forth exercise, or make use of lie quality to make the material transport forward in the fluxion in the piping.For example, the Gun son transports the work of machine to reach the piece as a series of Gun son, the Gun son makes to revolve sport to transport a material;Is spiral to transport the work of machine to reach a piece for spiral, helix at anticipate and make to revolve sport in the slot with follow anticipate slot to push to send a material;The vibration transports the work of machine to reach piece in order to anticipate slot, anticipate slot to make backand forth sport with transport Be placed to among them of material etc..Install(1)The fixed type transports machine should by rule gearing method gearing at fix of foundation up.The ambulation type transports machine formally before circulating and should live wheel with the wedge Xie or uses to make a machine to stop.So as not to take place to take a stroll in the work, there is the passage that many sets , between machine and machine, there shoulded be one meter between wall and machine while transporting a parallel homework of machine.(2)The beard checks an each operation part, tape to take to button up to equip with loading before using whether normal, whether protection equipments is well-found.The tape rises a tight degree beard before starting the adjustment is to suitable extent.(3)Leather belt's transporting machine should get empty to carry a start.Waiting to revolve normal rear can go into to anticipate.Drive after forbiding to go into first to anticipate.(4)There are few set that when transport machine to establish to circulate should from unload to anticipate to carry a beginning, the sequence starts.After revolving as usual all, the square can go into to anticipate.(5)Appear in the movement when the tape runs to be partial to a phenomenon should park the car adjustment, can not force an use, so as not to wear away edge and increment burden.(6)Work environment and be sent material temperature not to must be higher than 50 ℃ and be lower than-10 ℃ .Can not transport the material of having sour alkaline oil and organic melting agent composition.(7)Forbid pedestrian or multiply by a person on the belt conveyer.(8)Have to stop going into first to anticipate before parking the car, wait leather belt up save to anticipate to unload to the utmost a square can park the car.(9)Transporting the machine electric motor has to insulate good.The ambulation type transports machine electric cable to pull and drag along indiscriminately.The dynamoelectric confidential credibility connects ground.(10)The leather belt beats slippery strictly forbid to by hand pull leather belt, so as not to take place trouble.5.Adjust to try(1) Each equipments with meticulous care adjusts to try to transport machine after installing and satisfies a drawing request.(2) Each deceleration machine exercises parts to add to note to correspond lubricant.(3) The gearing after transporting machine to attain to request each single set equipments carries on beginning to work to make run-in, and knot to put together to adjust to try to transport machine to satisfy an operative request.(4) Adjust to try the electricity part of transporting the machine.Include to connect adjusting of line and action to try to the normal regulations electricity, make the equipments have good function, attain the function and status of design.6.Transport machine to block knothole 2 kinds of boring crafts(1)Blow up boring:The material after the irradiation of continuous laser and centrally forms one cave pit, then from and laser beam the coaxial oxygen flow to clean meltdown material and form one bore very quickly.The size of general bore is as thick relevant as plank, blow up to bore hole the average diameter as thick plank half, therefore blow up to bore hole bore path bigger to thicker plank, and not circle, should not in requesting higher spare parts use(if the petroleum Shai sews a tube), can be used for a waste up.In addition because of bore hole use of oxygen pressure with incise homology, splash a little bit greatly.(2)Pulse boring:The pulse laser that adopts high peak value power makes a little amount material melt or vaporizes, in common use air or nitrogen spirit are to lend support to air and oxidize to make bore expand because of putting heat by decrease, the air pressure more incises of the oxygen pressure is small.The particle jet with small creation of each pulse laser gradually goes deep into, therefore slab boring time takes several seconds.Once bore hole completion, immediately change assistance air into oxygen to carry on incising.Boring hole diameter like this is smaller, its boring quality is better than to blow up boring.Not only should have higher exportationpower for the laser machine used by this;The time and space characteristic that more important time ties, therefore the general crosscurrent carbon dioxide laser machine can not adapt to the request that the laser incises.In addition the pulse bores hole to also have the more dependable spirit road the control system to carry out cutting over of air category, air pressure and bore hole a horary control.皮带输送机输送机械按运作方式可以分为：1：皮带式传输机2：螺旋输送机3：斗式提升机4：滚筒运送机5：计量运输机6：板链式运送机7：网带输送机8：链条运输机。
皮带机输送机中英文对照外文翻译文献中英文资料翻译中文:带式输送机及其牵引系统在运送大量的物料时，带式输送机在长距离的运输中起到了非常重要的竞争作用。
输送系统将会变得更大、更复杂，而驱动系统也己经历了一个演变过程，并将继续这样下去。
如今，较大的输送带和多驱动系统需耍更大的功率，比如3驱动系统需耍给输送带750KW(成庄煤矿输送机驱动系统的要求)。
控制驱动力和加速度扭矩是输送机的关键。
一个高效的驱动系统应该能顺利的运行，同时保持输送带张紧力在指定的安全极限负荷内。
为了负载分配在多个驱动上，扭矩和速度控制在驱动系统的设计中也是很重要的因素。
由于输送机驱动系统控制技术的进步，目前更多可靠的低成本和高效驱动的驱动系统可供顾客选择[1]1带式输送机驱动1. 1带式输送机驱动方式全电压启动在全电压启动设计中，带式输送机驱动轴通过齿轮传动直接连接到电机。
直接全压驱动没有为变化的传送负载提供任何控制，根据满载和空载功率需求的比率，空载启动时比满载可能快3-4倍。
此种方式的优点是:免维护，启动系统简单，低成本，可靠性高。
但是，不能控制启动扭矩和最大停止扭矩。
因此，这种方式只用于低功率，结构简单的传送驱动中。
降压启动随着传送驱动功率的增加，在加速期间控制使用的电机扭矩变得越来越重要。
由于电机扭矩是电压的函数，电机电压必须得到控制，一般用可控硅整流器(SCR}构成的降压启动装置，先施加低电压拉紧输送带，然后线性的增加供电电压直到全电压和最大带速。
但是，这种启动方式不会产生稳定的加速度，当加速完成时，控制电机电压的SCR 锁定在全导通，为电机提供全压。
此种控制方式功率可达到750kW。
绕线转子感应电机绕线转子感应电机直接连接到驱动系统减速机上，通过在电机转子绕组中串联电阻控制电机转矩。
在传送装置启动时，把电阻串联进转子产生较低的转矩，当传送带加速时，电阻逐渐减少保持稳定增加转矩。
在多驱动系统中，一个外加的滑差电阻可能将总是串联在转子绕组回路中以帮助均分负载。
英文原文：Commissioning of the belt conveyor and automatically tighten its hydraulic device ofHydraulic belt conveyor automatically tensioning device is based on tape and in normal operation at the start of the strain of the different needs of the tape, after reasonable analysis of tension model designed. Hydraulic automatically tensioning device is the traditional way tighten the upgrading products can be widely used in coal, metallurgical, power plants, cement plants, terminals and other bulk material conveyor belt of the take-up equipment. Belt conveyor after two centuries of development. Has become from the initial prototype development with a high-speed, long distance, high-power, the capacity of modern means of transport, belt conveyor widely used in metallurgy, mining, chemical industry, ports, power plants, light industry, building materials and food And many other enterprises on the field. Because of their steady and reliable work belt conveyor, the noise of small, simple structure and operation of low-cost, anywhere in feeding or unloading. Has become a major granular material transport equipment one. As the conveyor belt of the viscoelastic properties, in order to ensure belt conveyor running the necessary friction, we must provide a suitable strain of. Tension belt conveyor device is an important and indispensable component of its properties have a direct impact on the overall performance of belt conveyorsConveyor belt by the nose, tail, drive, drag roller, roller, asked planes, belts, consisting of cleaning, etc.. Conveyor belt installed in the end, officially put into use, the equipment needed to debug.1. A conveyor belt of the debugging process1.1 belt conveyor belt conveyor belt deviation running belt deviation is the most common fault. Failure to resolve the focus of attention should be paid to such installation of dimensional accuracy and day-to-day maintenance. Deviation due to a combination, depending on the need to address the reasons for differences. Such as:1.1.1 adjustment drag roller bearing GroupThe belt-belt in the central belt of the transport plane deviation, they can drag roll by adjusting the group to adjust the location of deviation. Specific method is biased belt which side of the trailer roll group which side of the direction of advancement in the belt, or the other side after the shift.1.1.2 adjustment bend drum-driven drum and the location of drum-driven drum and bend the adjustment deviation adjustment of the belt is an important link. Because a belt transport planes at least 2-5 drum, drum all the installationlocation must be perpendicular to the length of the belt transports the centerline, if skewed too much inevitable deviation.1.2 unusual noiseRunning its transport belt drive, drive pulley and bend drum roll and drag Group, is not normal in abnormal noise will be issued, according to the abnormal noise judgement of equipment failure.1.2.1 serious drag roll eccentricity when the noise. Conveying belt running tractors will happen very often roll noise and vibration mix is cyclical. In particular, is a return drag roll, because of their greater length, its own weight, and also more noise. Noise in the two main reasons: First, manufacturing tractors roll of seamless steel pipe wall thickness uneven, the greater the centrifugal force and the other is in the processing of bearings at either end of the round hole with the heart of bias, so that was too large centrifugal force . Bearing in not allowing the noise and damage to the existence of too large. Bearing in not allowing the noise and damage to the circumstances may continue to use.1.2.2 shaft coupling the two different heart when the noise. In the high-speed drive motor-reducer and asked the coupling of the band or brake coupling Department issued a round of the unusual noise, the noise and also with the same frequency of rotating motor vibration. This should be a noise reducer in time to motor to adjust the location, in order to avoid reducer input shaft fracture.1.2.3 bend and rolling Chien Chien-driven roller abnormal noise. Bend and drum-driven drum normal working hours noise is very small, unusual noise in general is damaged bearings, housings Department issued Kaka beep, at this time to replace bearings1.3 belt skid.Tensioning device using a heavy hammer of the belt when the plane skid in the belt to add weight to resolve, added to the belt so far not slippery. But should not add too much, so as to keep the belt too much to bear unnecessary tension and reduce belt life.2.tensioning device research2.1 tensioning device featuresIn the course of running belt conveyors, should be able to solve the start-up, parking at the tape skid, and the impact of the loss of tension and other issues, with the use of the belt conveyor continuous expansion and the constant development of science and technology, and rational design tensioning device It is particularly important. Tensioning device functions in the following points:2.1.1 ensure that the tape drive from the point of roller Ben sufficient tension, thus ensuring drive must rely on the friction drive transmission friction traction, driven conveyor to the normal operation , The conveyor system to preventskidding.2.1.2 ensure that the smallest branch of carrying the tension point must be tension, restrictions on the conveyor belt in the roller asked the sag, and ensure normal operation of belt conveyors, not because of the conveyor system down through the vertical jump impact caused the coal roller Losses caused by the electrical energy and the materials, such as flesh littered the phenomenon.2.1.3 compensation tape and plastic deformation transition condition elongation qualitative change. As load will cause changes in the length of the conveyor system changes, creep phenomenon may cause conveyor belt extension, the tension there is a change in the trend of small, to absorb the need tensioning device by the creep of the SIN, to maintain normal operation of the conveyor The minimum required tension, thus ensuring the normal operation of belt conveyors.2.1.4 for the conveyor belt to make the necessary joint trip preparations. Each has a number of joint belt conveyor, when asked in a possible joint will have problems, we must first cut redo, tensioning device for belt conveyor prepared a load other than the transport belt, this can be through joint failure Relaxation of tension joints to solve the re-installation.2.2 PrincipleHydraulic-tensioning device is the automatic use of the conveyor belt sensors Rally Rally, and given after the rally to compare. Tightly control the hydraulic cylinder movement. Prior to the commencement of the belt conveyor, hydraulic tensioning device first launched by hydraulic cylinder moves to tighten T1 value of the conveyor system to activate Rally value (the value of the normal operation of about 1.5 times). Conveyor and then start the motor, so that the T2 =: e remain constant this relationship, so as to achieve the objective to prevent slipping. After the launch, after the conveyor belt to the rated speed, T2 are automatically converted to the stable functioning of value. In the stable operation of state, the conveyor belt Rally almost unchanged, tensioning device fixed. When the load changes or because of other causes Rally distribution changes, so that larger value of T2, hydraulic cylinders will be automatically moves, so that the elastic deformation of the conveyor system in order to reduce the T2 lower. When the 112 hours of change, sensing vigorous rally will send a signal to promote the hydraulic cylinder hydraulic pump oil supply tension. T2 to achieve this ratio to a constant value.3.Main features and functions.Belt conveyor hydraulic winch dynamic tensioning device with the characteristics of the following areas:3.1 Taking into account current in direct response to load on the conveyor belt of change, drum-driven motor current use as a feedback signal, and then underthe conveyor belt, load on the direct regulation of changes in the conveyor belt tension, This will fundamentally overcome the traditional design of the problems so that the conveyor belt at the turn of tension and relaxation of the state, to extend the life of a conveyor belt to meet the conveyor belt on the slippery, Droop of the conditions is not overrun, belt conveyor to maintain normal operation of the required minimum take-up of dynamic tension, you can achieve the best effect of dynamic tension, the tensioning device can also is studying the conveyor The dynamic design of the match, conveyor to the current situation of the potential.3.2 According to the conveyor belt on the condition and the tension.Different requirements, simply modify procedures in the corresponding SCM conditions of parameters, you can make the conveyor belt tensioning devices adapt to the needs of all kinds, can be arbitrary regulation conveyor start and stable operation of the tension, to meet the full commencement of Tension over the stable operation of the tension on the 1.4 to 1.5 times the request.3.3 system response speed, high stability.Commencement of belt conveyors, hydraulic station can immediately move to the electromagnetic valve brake-by reducing the fuel tank pressure to increase metres from the clutch asked, tensioning device released tape, timely compensation tape elongation , Reducing the tape-edge-to-bear-impact, not only stable and reliable transmission is activated, it is better to protect the tape, broken belt can reduce accidents. Hydraulic belt conveyor dynamic tensioning device can automatically achieve dynamic tension, and fundamentally resolve the tension regulating the issue of lack of coordination, fast response, the take-up better-performing, have a good economic value, has a broad Application, to conveyor current trend of development.中文译文：带式输送机的调试及对其液压自动拉紧装置的研究带式输送机液压自动拉紧装置是根据胶带在起动和正常运转时对拉紧力的不同需要，经合理的胶带张力模型分析研究而设计的。
附件Aesign of High Speed Belt ConveyorsG. Lodewijks, The Netherlands.SUMMARYThis paper discusses aspects of high-speed belt conveyor design. The capacity of a belt conveyor is determined by the belt speed given a belt width and troughing angle. Belt speed selection however is limited by practical considerations, which are discussed in this paper. The belt speed also affects the performance of the conveyor belt, as for example its energy consumption and the stability of it's running behavior.A method is discussed to evaluate the energy consumption of conveyor belts by using the loss factor of transport. With variation of the belt speed the safety factor requirements vary, which will affect the required belt strength. A new method to account for the effect of the belt speed on the safety factor is presented. Finally, the impact of the belt speed on component selection and on the design of transfer stations is discussed.1 INTRODUCTIONPast research has shown the economical feasibility of using narrower, faster running conveyor belts versus wider, slower running belts for long overland belt conveyor systems. See for example [I]-[5]. Today, conveyor belts running at speeds around 8 m/s are no exceptions. However, velocities over 10 m/s up to 20 m/s are technically (dynamically) feasible and may also be economically feasible. In this paper belt speeds between the 10 and 20 m/s are classified as high. Belt speeds below the 10 m/s are classified as low.Using high belt speeds should never be a goal in itself. If using high belt speeds is not economically beneficial or if a safe and reliable operation is not ensured at a high belt speed then a lower belt speed should be selected.Selection of the belt speed is part of the total design process. The optimum belt conveyor design is determined by static or steady state design methods. In these methods the belt is assumed to be a rigid, inelastic body. This enables quantification of the steady-state operation of the belt conveyor and determination of the size of conveyor components. The specification of the steady-state operation includes a quantification of the steady-state running belt tensions and power consumption for all material loading and relevant ambient conditions. It should be realized that finding the optimum design is not a one-time effort but an iterative process [6].Design fine-tuning, determination of the optimum starting and stopping procedures, including determination of the required control algorithms, and determination of the settings and sizes of conveyor components such as drives, brakes and flywheels, are determined by dynamic design methods. In these design methods, also referred to as dynamic analyses, the belt is assumed to be a three-dimensional (visco-) elastic body. A three dimensional wave theory should be used to study time dependent transmission of large local force and displacement disturbances along the belt [7]. In this theory the belt is divided into a series of finite elements. The finite elements incorporate (visco-) elastic springs and masses. The constitutive characteristics of the finite elements must represent the rheological characteristics of the belt. Dynamic analysis produces the belt tension and power consumption during non-stationary operation, like starting and stopping, of the belt conveyor.This paper discusses the design of high belt-speed conveyors, in particular the impact of using high belt speeds on the performance of the conveyor belt in terms of energy consumption and safety factor requirements. Using high belt speeds also requires high reliability of conveyor components such as idlers to achieve an acceptable component life. Another important aspect of high-speed belt conveyor design is the design of efficient feeding and discharge arrangements. These aspects will be discussed briefly.2 BELTSPEED2.1 BELT SPEED SELECTIONThe lowest overall belt conveyor cost occur in the range of belt widths of 0.6 to 1.0 m [2]. The required conveying capacity can be reached by selection of a belt width in this range and selecting whatever belt speed is required to achieve the required flow rate. Figure 1 shows an example of combinations of belt speed and belt width to achieve Specific conveyor capacities. In this example it is assumed that the bulk density is 850 kg/m3 (coal) and that the trough angle and the surcharge angle are 35' and 20' respectively.Figure 1: Belt width versus belt speed for different capacities.Belt speed selection is however limited by practical considerations. A first aspect is the troughability of the belt. In Figure 1 there is no relation with the required belt strength (rating), which partly depends on the conveyor length and elevation. The combination of belt width and strength must be chosen such that good troughabilityof the belt is ensured. If the troughability is not sufficient then the belt will not track properly. This will result in unstable running behavior of the belt, in particular at high belt speeds, which is not acceptable. Normally, belt manufacturers expect a sufficiently straight run if approximately 40% of the belt width when running empty, makes contact with the carrying idlers. Approximately 10% should make tangential contact with the center idler roll.A second aspect is the speed of the air relative to the speed of the bulk solid material on the belt (relative airspeed). If the relative airspeed exceeds certain limits then dust will develop. This is in particular a potential problem in mine shafts where a downward airflow is maintained for ventilation purposes. The limit in relative airspeed depends on ambient conditions and bulk material characteristics.A third aspect is the noise generated by the belt conveyor system. Noise levels generally increase with increasing belt speed. In residential areas noise levels are restricted to for example 65 dB. Although noise levels are greatly affected by the design of the conveyor support structure and conveyor covers, this may be a limiting factor in selecting the belt speed.2.2 BELT SPEED VARIATIONThe energy consumption of belt conveyor systems varies with variation of the belt speed, as will be shown in Section 3. The belt velocity can be adjusted with bulk material flow supplied at the loading point to save energy. If the belt is operating at full tonnage then it should run at the high (design) belt speed. The belt speed can be adjusted (decreased) to the actual material (volume) flow supplied at the loading point. This will maintain a constant filling of the belt trough and a constant bulk material load on the belt. A constant filling of the belt trough yields an optimum loading-ratio, and lower energy consumption per unit of conveyed material may be expected. The reduction in energy consumption will be at least 10% for systems where the belt speed is varied compared to systems where the belt speed is kept constant [8].Varying the belt speed with supplied bulk material flow has the following advantages:•Less belt wear at the loading areas•Lower noise emission•Improved operating behavior as a result of better belt alignment and the avoidance of belt lifting in concave curve by reducing belt tensionsDrawbacks include:•Investment cost for controllability of the drive and brake systems•Variation of discharge parabola with belt speed variation•Control system required for controlling individual conveyors in a conveyor system•Constant high belt pre-tension•Constant high bulk material load on the idler rollsAn analysis should be made of the expected energy savings to determine whether it is worth the effort of installing a more expensive, more complex conveyor system.3 ENERGY CONSUMPTIONClients may request a specification of the energy consumption of a conveyor system, for example quantified in terms of maximum kW-hr/ton/km, to transport the bulk solid material at the design specifications over the projected route. For long overland systems, the energy consumption is mainly determined by the work done to overcome the indentation rolling resistance [9]. This is the resistance that the belt experiences due to the visco-elastic (time delayed) response of the rubber belt cover to the indentation of the idler roll. For in-plant belt conveyors, work done to overcome side resistances that occur mainly in the loading area also affects the energy consumption. Side resistances include the resistance due to friction on the side walls of the chute and resistance that occurs due to acceleration of the material at the loading point.The required drive power of a belt conveyor is determined by the sum of the total frictional resistances and the total material lift. The frictional resistances include hysteresis losses, which can be considered as viscous (velocity dependent) friction components. It does not suffice to look just at the maximum required drive power to evaluate whether or not the energy consumption of a conveyor system is reasonable. The best method to compare the energy consumption of different transport systems is to compare their transport efficiencies.3.1 TRANSPORT EFFICIENCYThere are a number of methods to compare transport efficiencies. The first and most widely applied method is to compare equivalent friction factors such as the DIN f factor. An advantage of using an equivalent friction factor is that it can also be determined for an empty belt. A drawback of using an equivalent friction factor is that it is not a 'pure' efficiency number. It takes into account the mass of the belt, reduced mass of the rollers and the mass of the transported material. In a pure efficiency number, only the mass of the transported material is taken into account.The second method is to compare transportation cost, either in kW-hr/ton/km or in $/ton/km. The advantage of using the transportation cost is that this number is widely used for management purposes. The disadvantage of using the transportation cost is that it does not directly reflect the efficiency of a system.The third and most "pure" method is to compare the loss factor of transport [10]. The loss factor of transport is the ratio between the drive power required to overcome frictional losses (neglecting drive efficiency and power loss/gain required to raise/lower the bulk material) and the transport work. The transport work is defined as the multiplication of the total transported quantity of bulk material and the average transport velocity. The advantage of using loss factors of transport is that they can be compared to loss factors of transport of other means of transport, like trucks and trains. The disadvantage is that the loss factor of transport depends on the transported quantity of material, which implies that it can not be determined for an empty belt conveyor.The following are loss factors of transport for a number of transport systems to illustrate the concept:Continuous transport:•Slurry transport around 0.01•Belt conveyors between 0.01 and 0.1•Vibratory feeders between 0.1 and 1•Pneumatic conveyors around 1 0Discontinuous transport:•Ship between 0.001 and 0.01•Train around 0.01•Truck between 0.05 and 0.13.2 INDENTATION ROLLING RESISTANCEFor long overland systems, the energy consumption is mainly determined by the work done to overcome the indentation rolling resistance. Idler rolls are made of a relatively hard material like steel or aluminum whereas conveyor belt covers are made of much softer materials like rubber or PVC. The rolls therefore indent the belt's bottom-cover when the belt moves over the idler rolls, due to the weight of the belt and bulk material on the belt. The recovery of the compressed parts of the belt's bottom cover will take some time due to its visco-elastic (time dependent) properties. The time delay in the recovery of the belt's bottom cover results in an asymmetrical stress distribution between the belt and the rolls, see Figure 2. This yields a resultant resistance force called the indentation rolling resistance force. The magnitude of this force depends on the visco-elastic properties of the cover material, the radius of the idler roll, the vertical force due to the weight of the belt and the bulk solid material, and the radius of curvature of the belt in curves in the vertical plane.Figure 2: Asymmetric stress distribution between belt and roll [7].It is important to know how the indentation rolling resistance depends on the belt velocity to enable selection of a proper belt velocity, [11].Figure 3: Loss factor (tanb) of typical cover rubber [7]Firstly, the indentation rolling resistance depends on the vertical load on the belt, which is the sum of the belt and the bulk material weight. If the vertical load on the belt decreases with a factor 2 then the indentation rolling resistance decreases with a factor 2.52 (2 ^4/3). The bulk load decreases with increasing belt speed assuming a constant capacity. Therefore, the indentation rolling resistance decreases more than proportionally with increasing belt speed.Secondly, the indentation rolling resistance depends on the size of the idler rolls. If the roll diameter increases with a factor 2 then the indentation rolling resistance decreases with a factor 1.58 (2 ^2/3). In general the idler roll diameter increases with increasing belt speed to limit the bearing rpm's to maintain acceptable idler life. In that case the indentation rolling resistance decreases with increasing belt speed.Thirdly, the indentation rolling resistance depends on the visco-elastic properties of the belt's cover material. These properties depend on the deformation rate, see Figure 3. The deformation rate in its turn depends on the size of the deformation area in the belt's bottom cover (depending on belt and bulk load) and on the belt speed. In general the indentation rolling resistance increases with increasing deformation rate (and thus belt speed), but only to a relatively small account.Fourthly, the indentation rolling resistance depends on the belt's bottom cover thickness. If the bottom cover thickness increases with a factor 2 then the indentation rolling resistance increases with a factor 1.26 (2 ^1/3). if a bottom cover is increased to account for an increase in belt wear with increasing belt speed, then the indentation rolling resistance increases as well.It should be realized that the indentation rolling resistance, although important, is not the only velocity dependent resistance. The rolling resistance of the idler rolls for example depends on the vertical load as well as on their rotational speed. The effect of the vertical load, which directly depends on the belt speed, is large. The effect of the rotational speed is much smaller. Another resistance occurs due to acceleration of the bulk solid material at the loading point. This resistance increases quadratically with an increase in belt speed assuming that the bulk material falls straight onto the belt. This will affect smaller, in plant belt conveyors in particular.EXAMPLETo illustrate the concept discussed above lets consider a 6 km long conveyor belt with a capacity of 5000 TPH. The trough angle, the surcharge angle and the bulk density are again taken 35', 20' and 850 kg/m^3 respectively. Figure 4 shows the required belt speed as a function of the belt width to achieve the required capacity of 5000 TPH. This figure is somewhat similar to Figure 1.Figure 4The figures 5 and 6 show the required belt strength and the required drive power as a function of the belt speed. The required belt strength decreases and the required drive power slowly increases with increasing belt speed as can be seen in those figures. Figure 7 shows the loss factor of transport and the DIN f factor versus belt speed. The loss factor of transport is always higher than the DIN f factor because the DIN f factor takes the mass of the belt into account (in the denominator) whereas the loss factor of transport only accounts for the mass of the bulk solid material. Intuitively, it may be expected that there will be an economically optimum belt speed in the high belt speed range. The determination of the optimum belt speed however, requires more information and is beyond the scope of this paper.Figure 5 Figure 6Figure 73.3 RUBBER COMPOUNDSThe indentation rolling resistance depends on the visco-elastic properties of the belt's bottom cover as discussed in the preceding section. This implies that the rolling resistance can be decreased by selecting a special low indentation rolling resistance (rubber) compound that is available on the market today. A small premium has to be paid for this special compound, but costs can be limited by applying it for the bottom cover only and using a normal wear-resistant compound for the carrying top cover. In that case turnovers are required to fully use the energy saving function of the bottom compound.A Quantitative indication of the level of indentation rolling resistance is the indentation rolling resistance indicator tan/E ^1/3, where tan is the loss angle and E' the storage modulus of the compound. Compounds with a reasonable indentation rolling resistance performance have indicators below 0.1. Figure 8 shows these indicators for typical medium to good performing rubbers. As can be seen in that figure, the choice for a specific rubber compound affects the energy consumption of the belt conveyor, in particular as a function of the ambient temperature.One comment (warning) must be made. A special belt with low indentation rolling resistance compound should never be selected if only one conveyor belt manufacturer offers it. In that case the conveyor system can only perform in accordance with its design specifications when that specific belt is used. It is much better, also cost wise, to specify the upper limit of the resistance indicator as given above that can be met by more than one conveyor belt manufacturer.Figure 8: Indentation rolling resistance indicators for four differentrubbers as a function of temperature.4. SAFETY FACTOR REQUIREMENTSFor design purposes, standards like DIN 22101, ISO 5048 and CEMA provide safety factors (SF) that limit the permissible belt loads. Two types of safety factors can be distinguished: safety factors on the steady-state running tensions and safety factors on the non-stationary tensions. In general the safety factor on the steady-state running tension is based on:(1) Stationary (full and empty, summer and winter) and non-stationary belt tensions(2) Belt tensions from extra resistances and deformations in horizontal and vertical curves, troughing transitions, belt turnovers, on pulleys etc.(3) Belt conveyor system maintenance(4) Belt conveyor system operational data including hours per day, days per year and years of service(5) Belt splice design and fatigue characteristics including those of the belt tensile carrying member (steel cords or fabric) and the rubber(6) Splice kit storage and handling.All these six items should be taken into account when determining the safety factor.standards like the DIN standard base the recommended safety factor on reduction factors. DIN 22101 uses three reduction factors. The first (r0) generally accounts for the reduction of the strength of the belt (splices) due to fatigue. The second (r1) accounts for the extra forces that act on the belt in transition zones and on pulleys etc. The third (r2) accounts for the extra dynamic stresses in the belt during starting and stopping. The required minimum safety factor can be calculated as follows:SF=1/(1-(r0+r1+r2)) (1)The DIN standard also gives values for the three reduction factors. For example, for a steel cord conveyor belt under "normal" operational conditions the values are as follows: r0>0.665, r1>0.15, r2>0.06, which yields a safety factor SF>8.Although much can be said about the applicability of the safety factor determined with the DIN standard for the design of long belt conveyor systems, the major drawback, keeping the belt speed selection in mind, is that the conveyor system's operational data and the real fatigue properties of the belt are not taken into account.It is possible to account for these factors and to achieve a tailor-made safety factor by taking the belt's operational data into account. The reduction factors r1 and r2 are independent of the fatigue properties of the belt and thus constant with increasing number of load cycles. Let's assume that the reduction factor r0 varies linearly with the log1O of the number of load cycles (revolution of the belt through the total belt conveyor) from 0 to 0.665 at 10,000 load cycles (approximation of DIN standard):r0= 0.166 log10(N) (N<10.000) (2)where N is the number of load cycles. After 10,000 load cycles r0 hardly increases. Now let's assume that the conveyor under design has a length of 10,000 m, a life expectation of 5 years at 5000 operational hours per year. The total number of load cycles can be calculated with the following equation:N=[(3600 V)/(2L)]HY (3)where V is the belt speed, L the conveyor length, H the number of operational hours per year and Y the number of expected years of operation. Equation (3) is visualized in Figure 9.Figure 9: Number of load cycles versus belt speed for given example.The value of the reduction factor ro can be determined with equation (2) and the number of load cycles as given in Figure 9. The result is shown in Figure 10.Figure 10: DIN 22101 reduction factor r0 for given exampleThe safety factor as a function of the belt speed then can be determined with equation (1) and Figure 10. The result is shown in Figure 11.Figure 11: Minimum required safety factor for given exampleFrom Figure 11 it can be learned that for the belt under design the required minimum safety factor on the steady-state running tensions is about 7.5 if the belt is running at 2 m/s, and about 10 in case the belt is running at 20 m/s. Taking thebelt speed into account during safety factor determination thus prevents overrating of the belt at low speeds and underrating at high speeds (also depends on the length of the conveyor system).The above given figures and numbers are to illustrate the procedure only. This procedure can be fine tuned by taking measured fatigue properties of the belt tensile-carrying member (steel cords or fabric) and the rubber into account, as well as the actual load cycle of the belt (empty, fully loaded, steady state running, starting and stopping, summer, and winter conditions etc.).5 BELT CONVEYOR DYNAMICSIn essence the dynamics of a belt conveyor does not change with the belt speed. However, with increasing belt speed the rate of changes increases, which will result in a decreasing running stability of the belt. This paper is not intended to fully discuss belt conveyor dynamics. It is referred to [7] where this topic is extensively discussed. However, a number of notes on the dynamics of high belt speed conveyors can be made.When a belt between two idlers is exited by an idler roll in or near a natural frequency of transverse vibration of the belt span, resonance phenomena occur. The amplitude of transverse vibration increases considerably when resonance occurs yielding increased roll/ bearing wear and an increased power consumption of the belt. This increase in vibration amplitude, also referred to as belt flap, must be avoided. In high-speed belt systems the effect of resonance on the structure is very destructive, as observed with lower speed belts that resonate and destroy idler bearings. Care should therefore be taken to design a belt conveyor so that the possibility of resonance in the belt is avoided and at the same time best use is made of current static design methods so that the economics of the design are saved.Belt tracking must be excellent at high speeds. If the belt does not track properly then run off may be expected since, with increasing belt speed, side displacements and the rate of side displacement increase. The combination of belt width and strength must be chosen such that good troughability is ensured, see Section 2.1. Also maximum effort must be made by the belt manufacturer to make straight belts and to construct true belt splices. In addition, longer manufactured belt lengths reduce the number of splices and thus increase the chance of straightness.A similar comment can be made for the design of horizontal belt curves. The position of the belt on the idlers changes with a change in belt tension mainly due to a change in loading degree. The belt will move sideward in particular during large tension variations as occur during (aborted) starting and (emergency) stopping. The change in belt tension during starting and stopping will increase with increasing belt speed. For low belt speed conveyors static design methods may be sufficient to determine the maximum side displacement. For high belt speed conveyors however,dynamic design methods are required to predict the side displacement to a sufficient level of accuracy.Normal operational starting and stopping procedures will not change for high belt speed conveyors, except that starting and stopping will take more time. The nature of emergency stop procedures however will change. In general emergency stop procedures are designed to stop the belt in a short period of time without the use of the drive system and so that the belt conveyor is not damaged. A typical emergency stop time for a long overland conveyor is 30 seconds, which may be short enough to prevent casualties. However at high belt speeds the amount of energy (which increases quadratically with increasing belt speed) that has to be transferred from the conveyor belt into a braking system is much higher, which will result in considerably longer emergency stopping times. Therefore the chance of casualties is much higher in case an emergency happens. For high belt speed conveyors it is therefore even more important to be equipped with appropriate safety guards.6 IDLER SELECTIONThe most important selection criterion of idlers for high-speed belt conveyors is the idler diameter. In general it can be said that the diameter of idlers will need to be increased for high speed belts compared to the diameter of idlers used in low-speed belts for a number of reasons including:•with low rotational speed idler bearings can be used with L10 ratings that are currently available and used in low speed belt conveyors. This implies thatcurrently used maintenance schedules can be followed. The diameter of anidler has a considerable effect on the idler performance. Together with thebelt speed, it fixes the speed at which the idler, and thus the roller bearing,rotates. The permissible operating temperature limits the speed at whichroller bearings can operate. Bearing types with low friction andcorrespondingly low heat generation in the bearing itself are therefore themost suitable for high-speed operation. The highest speed can be achievedwith deep groove ball bearings when loads are purely radial, and withangular contact bearings for combined loads.•if there is any slippage between the belt and the idler shell then the diameter governs the belt cover wear. Slippage may occur if the axis of the idler isnot in line with the direction of the belt.•the resistance to rolling friction offered by an idler and the break-away torque decrease with increasing idler diameter.The only adverse factors of increasing idler diameters are the higher idler price and greater inertia.The life of idler bearings decreases as rotational speed (and thus the belt speed) increases. The bearing life is inversely proportional to the belt speed, and is raised。
高速带式输送机的设计_外文翻译（可编辑）附件Aesign of High Speed Belt ConveyorsG. Lodewijks, The Netherlands.SUMMARYThis paper discusses aspects of high-speed belt conveyor design. The capacity of a belt conveyor is determined by the belt speed given a belt width and troughing angle. Belt speed selection however is limited by practical considerations, which are discussed in this paper. The belt speed also affects the performance of the conveyor belt, as for exampleits energy consumption and the stability of it's running behavior. A method is discussed to evaluate the energy consumption of conveyor belts by using the loss factor of transport. With variation of the belt speed the safety factor requirements vary, which will affect the required belt strength. A new method to account for the effect of the belt speed onthe safety factor is presented. Finally, the impact of the belt speed on component selection and on the design of transfer stations is discussed.1 INTRODUCTIONPast research has shown the economical feasibility of using narrower, faster running conveyor belts versus wider, slower running belts forlong overland belt conveyor systems. See for example [I]-[5]. Today, conveyor belts running at speeds around 8 m/s are no exceptions. However,velocities over 10 m/s up to 20 m/s are technically dynamically feasible and may also be economically feasible. In this paper belt speeds between the 10 and 20 m/s are classified as high. Belt speeds below the 10 m/s are classified as low.Using high belt speeds should never be a goal in itself. If using high belt speeds is not economically beneficial or if a safe andreliable operation is not ensured at a high belt speed then a lower belt speed should be selected.Selection of the belt speed is part of the total design process. The optimum belt conveyor design is determined by static or steady state design methods. In these methods the belt is assumed to be a rigid, inelastic body. This enables quantification of the steady-state operation of the belt conveyor and determination of the size of conveyor components. The specification of the steady-state operation includes a quantification of the steady-state running belt tensions and power consumption for all material loading and relevant ambient conditions. It should be realized that finding the optimum design is not a one-time effort but an iterative process [6].Design fine-tuning, determination of the optimum starting and stopping procedures, including determination of the required control algorithms, and determination of the settings and sizes of conveyor components such as drives, brakes and flywheels, are determined by dynamicdesign methods. In these design methods, also referred to as dynamic analyses, the belt is assumed to be a three-dimensional visco- elastic body. A three dimensional wave theory should be used to study time dependent transmission of large local force and displacement disturbances along the belt [7]. In this theory the belt is divided into a series of finite elements. The finite elements incorporate visco- elastic springs and masses. The constitutive characteristics of thefinite elements must represent the rheological characteristics of the belt. Dynamic analysis produces the belt tension and power consumption during non-stationary operation, like starting and stopping, of the belt conveyor.This paper discusses the design of high belt-speed conveyors, in particular the impact of using high belt speeds on the performance of the conveyor belt in terms of energy consumption and safety factor requirements. Using high belt speeds also requires high reliability of conveyor components such as idlers to achieve an acceptable component life. Another important aspect of high-speed belt conveyor design is the design of efficient feeding and discharge arrangements. These aspects will be discussed briefly.2 BELTSPEED2.1 BELT SPEED SELECTIONThe lowest overall belt conveyor cost occur in the range of belt widthsof 0.6 to 1.0 m [2]. The required conveying capacity can be reached by selection of a belt width in this range and selecting whatever belt speed is required to achieve the required flow rate. Figure 1 shows an example of combinations of belt speed and belt width to achieve Specific conveyor capacities. In this example it is assumed that the bulk density is 850 kg/m3 coal and that the trough angle and the surcharge angle are 35' and 20' respectively.Figure 1: Belt width versus belt speed for different capacities.Belt speed selection is however limited by practical considerations.A first aspect is the troughability of the belt. In Figure 1 there is no relation with the required belt strength rating , which partly depends on the conveyor length and elevation. The combination of belt width and strength must be chosen such that good troughability of the belt is ensured. If the troughability is not sufficient then the belt will not track properly. This will result in unstable running behavior of the belt, in particular at high belt speeds, which is not acceptable. Normally, belt manufacturers expect a sufficiently straight run if approximately 40% of the belt width when running empty, makes contact with the carrying idlers. Approximately 10% should make tangential contact with the center idler roll.A second aspect is the speed of the air relative to the speed of the bulk solid material on the belt relative airspeed . If the relative airspeed exceeds certain limits then dust will develop. This is in particular a potential problem in mine shafts where a downward airflowis maintained for ventilation purposes. The limit in relative airspeed depends on ambient conditions and bulk material characteristics.A third aspect is the noise generated by the belt conveyor system. Noise levels generally increase with increasing belt speed. In residential areas noise levels are restricted to for example 65 dB. Although noise levels are greatly affected by the design of the conveyor support structure and conveyor covers, this may be a limiting factor in selecting the belt speed.2.2 BELT SPEED VARIATIONThe energy consumption of belt conveyor systems varies withvariation of the belt speed, as will be shown in Section 3. The belt velocity can be adjusted with bulk material flow supplied at the loading point to save energy. If the belt is operating at full tonnage then it should run at the high design belt speed. The belt speed can be adjusted decreased to the actual material volume flow supplied at the loading point. This will maintain a constant filling of the belt trough and a constant bulk material load on the belt. A constant filling of the belt trough yields an optimum loading-ratio, and lower energy consumption per unit of conveyed material may be expected. The reduction in energy consumption will be at least 10% for systems where the belt speed is varied comparedto systems where the belt speed is kept constant [8].Varying the belt speed with supplied bulk material flow has the following advantages:Less belt wear at the loading areasLower noise emissionImproved operating behavior as a result of better belt alignment and the avoidance of belt lifting in concave curve by reducing belt tensions Drawbacks include:Investment cost for controllability of the drive and brake systems Variation of discharge parabola with belt speed variationControl system required for controlling individual conveyors in a conveyor systemConstant high belt pre-tensionConstant high bulk material load on the idler rollsAn analysis should be made of the expected energy savings to determine whether it is worth the effort of installing a more expensive, more complex conveyor system.3 ENERGY CONSUMPTIONClients may request a specification of the energy consumption of a conveyor system, for example quantified in terms of imum kW-hr/ton/km,to transport the bulk solid material at the design specifications over the projected route. For long overland systems, the energy consumption is mainly determined by the work done to overcome the indentation rolling resistance [9]. This is the resistance that the belt experiences due to the visco-elastic time delayed response of the rubber belt cover to the indentation of the idler roll. For in-plant belt conveyors, work done to overcome side resistances that occur mainly in the loading areaalso affects the energy consumption. Side resistances include the resistance due to friction on the side walls of the chute and resistance that occurs due to acceleration of the material at the loading point.The required drive power of a belt conveyor is determined by the sum of the total frictional resistances and the total material lift. The frictional resistances include hysteresis losses, which can be considered as viscous velocity dependent friction components. It doesnot suffice to look just at the imum required drive power to evaluate whether or not the energy consumption of a conveyor system is reasonable. The best method to compare the energy consumption of different transport systems is to compare their transport efficiencies.3.1 TRANSPORT EFFICIENCYThere are a number of methods to compare transport efficiencies. The first and most widely applied method is to compare equivalent friction factors such as the DIN f factor. An advantage of using an equivalent friction factor is that it can also be determined for an empty belt. A drawback of using an equivalent friction factor is that it is not a'pure'efficiency number. It takes into account the mass of the belt, reduced mass of the rollers and the mass of the transported material. In a pure efficiency number, only the mass of the transported material is taken into account.The second method is to compare transportation cost, either in kW-hr/ton/km or in $/ton/km. The advantage of using the transportation costis that this number is widely used for management purposes. The disadvantage of using the transportation cost is that it does not directly reflect the efficiency of a system.The third and most "pure" method is to compare the loss factor of transport [10]. The loss factor of transport is the ratio between the drive power required to overcome frictional losses neglecting drive efficiency and power loss/gain required to raise/lower the bulk material and the transport work. The transport work is defined as the multiplication of the total transported quantity of bulk material and the average transport velocity. The advantage of using loss factors of transport is that they can be compared to loss factors of transport of other means of transport, like trucks and trains. The disadvantage is that the loss factor of transport depends on the transported quantity of material, which implies that it can not be determined for an empty belt conveyor.The following are loss factors of transport for a number oftransportsystems to illustrate the concept:Continuous transport:Slurry transport around 0.01Belt conveyors between 0.01 and 0.1Vibratory feeders between 0.1 and 1Pneumatic conveyors around 1 0Discontinuous transport:Ship between 0.001 and 0.01Train around 0.01Truck between 0.05 and 0.13.2 INDENTATION ROLLING RESISTANCEFor long overland systems, the energy consumption is mainly determined by the work done to overcome the indentation rolling resistance. Idler rolls are made of a relatively hard material likesteel or aluminum whereas conveyor belt covers are made of much softer materials like rubber or PVC. The rolls therefore indent the belt's bottom-cover when the belt moves over the idler rolls, due to the weight of the belt and bulk material on the belt. The recovery of the compressed parts of the belt's bottom cover will take some time due to its visco-elastic time dependent properties. The time delay in the recovery of the belt's bottom cover results in an asymmetrical stress distribution between the belt and the rolls, see Figure 2. This yields a resultant resistance force called theindentation rolling resistance force. The magnitude of this force depends on the visco-elastic properties of the cover material, the radius of the idler roll, the vertical force due to the weight of the belt and the bulk solid material, and the radius of curvature of thebelt in curves in the vertical plane.Figure 2: Asymmetric stress distribution between belt and roll [7].It is important to know how the indentation rolling resistance depends on the belt velocity to enable selection of a proper belt velocity, [11].Figure 3: Loss factor tanb of typical cover rubber [7]Firstly, the indentation rolling resistance depends on the vertical load on the belt, which is the sum of the belt and the bulk material weight. If the vertical load on the belt decreases with a factor 2 then the indentation rolling resistance decreases with a factor 2.52 2 ^4/3 . The bulk load decreases with increasing belt speed assuming a constant capacity. Therefore, the indentation rolling resistance decreases more than proportionally with increasing belt speed.Secondly, the indentation rolling resistance depends on the size of the idler rolls. If the roll diameter increases with a factor 2 then the indentation rolling resistance decreases with a factor 1.58 2 ^2/3 . In general the idler roll diameter increases with increasing belt speed to limit the bearing rpm's to maintain acceptable idler life. In that case the indentation rolling resistance decreases with increasing belt speed.Thirdly, the indentation rolling resistance depends on the visco-elastic properties of the belt's cover material. These properties depend on the deformation rate, see Figure 3. The deformation rate in its turn depends on the size of the deformation area in the belt's bottom cover depending on belt and bulk load and on the belt speed. In general the indentation rolling resistance increases with increasing deformationrate and thus belt speed , but only to a relatively small account.Fourthly, the indentation rolling resistance depends on the belt's bottom cover thickness. If the bottom cover thickness increases with a factor 2 then the indentation rolling resistance increases with a factor 1.26 2 ^1/3 . if a bottom cover is increased to account for an increase in belt wear with increasing belt speed, then the indentation rolling resistance increases as well.It should be realized that the indentation rolling resistance, although important, is not the only velocity dependent resistance. The rolling resistance of the idler rolls for example depends on thevertical load as well as on their rotational speed. The effect of the vertical load, which directly depends on the belt speed, is large. The effect of the rotational speed is much smaller. Another resistance occurs due to acceleration of the bulk solid material at the loading point. This resistance increases quadratically with an increase in belt speed assuming that the bulk material falls straight onto the belt. This willaffect smaller, in plant belt conveyors in particular.EXAMPLETo illustrate the concept discussed above lets consider a 6 km long conveyor belt with a capacity of 5000 TPH. The trough angle, the surcharge angle and the bulk density are again taken 35', 20' and 850kg/m^3 respectively. Figure 4 shows the required belt speed as afunction of the belt width to achieve the required capacity of 5000 TPH. This figure is somewhat similar to Figure 1.Figure 4The figures 5 and 6 show the required belt strength and the required drive power as a function of the belt speed. The required belt strength decreases and the required drive power slowly increases with increasing belt speed as can be seen in those figures. Figure 7 shows the loss factor of transport and the DIN f factor versus belt speed. The loss factor of transport is always higher than the DIN f factor because the DIN f factor takes the mass of the belt into account in the denominator whereas the loss factor of transport only accounts for the mass of the bulk solid material. Intuitively, it may be expected that there will be an economically optimum belt speed in the high belt speed range. The determination of the optimum belt speed however, requires more information and is beyond the scope of this paper.Figure 5Figure 6Figure 7 3.3 RUBBER COMPOUNDSThe indentation rolling resistance depends on the visco-elastic properties of the belt's bottom cover as discussed in the preceding section. This implies that the rolling resistance can be decreased by selecting a special low indentation rolling resistance rubber compound that is available on the market today. A small premium has to be paidfor this special compound, but costs can be limited by applying it for the bottom cover only and using a normal wear-resistant compound for thecarrying top cover. In that case turnovers are required to fully use the energy saving function of the bottom compound.A Quantitative indication of the level of indentation rolling resistance is the indentation rolling resistance indicator tan/E ^1/3, where tan is the loss angle and E' the storage modulus of the compound. Compounds with a reasonable indentation rolling resistance performance have indicators below 0.1. Figure 8 shows these indicators for typical medium to good performing rubbers. As can be seen in that figure, the choice for a specific rubber compound affects the energy consumption of the belt conveyor, in particular as a function of the ambient temperature.One comment warning must be made. A special belt with lowindentation rolling resistance compound should never be selected if only one conveyor belt manufacturer offers it. In that case the conveyor systemcan only perform in accordance with its design specifications when that specific belt is used. It is much better, also cost wise, to specify the upper limit of the resistance indicator as given above that can be met by more than one conveyor belt manufacturer.Figure 8: Indentation rolling resistance indicators forfour?different rubbers as a function of temperature.4. SAFETY FACTOR REQUIREMENTSFor design purposes, standards like DIN 22101, ISO 5048 and CEMA provide safety factors SF that limit the permissible belt loads. Twotypes of safety factors can be distinguished: safety factors on the steady-state running tensions and safety factors on the non-stationary tensions. In general the safety factor on the steady-state running tension is based on:1 Stationary full and empty, summer and winter andnon-stationary belt tensions2 Belt tensions from extra resistances and deformations inhorizontal and vertical curves, troughing transitions, belt turnovers, on pulleys etc.3 Belt conveyor system maintenance4 Belt conveyor system operational data including hours per day, days per year and years of service5 Belt splice design and fatigue characteristics including those of thebelt tensile carrying member steel cords or fabric and the rubber6 Splice kit storage and handling.All these six items should be taken into account when determiningthe safety factor.standards like the DIN standard base the recommended safety factoron reduction factors. DIN 22101 uses three reduction factors. The first r0 generally accounts for the reduction of the strength of the belt splices due to fatigue. The second r1 accounts for the extra forces that act on the belt in transition zones and on pulleys etc. The third r2 accounts for the extra dynamic stresses in the belt during starting andstopping. The required minimum safety factor can be calculated as follows:SF 1/ 1- r0+r1+r2 1The DIN standard also gives values for the three reduction factors. For example, for a steel cord conveyor belt under "normal" operational conditions the values are as follows: r0 0.665, r1 0.15, r2 0.06, which yields a safety factor SF 8.Although much can be said about the applicability of the safety factor determined with the DIN standard for the design of long belt conveyor systems, the major drawback, keeping the belt speed selection in mind, is that the conveyor system's operational data and the real fatigue properties of the belt are not taken into account.It is possible to account for these factors and to achieve a tailor-made safety factor by taking the belt's operational data into account. The reduction factors r1 and r2 are independent of the fatigue properties of the belt and thus constant with increasing number of load cycles. Let's assume that the reduction factor r0 varies linearly with the log1O of the number of load cycles revolution of the belt through the total belt conveyor from 0 to 0.665 at 10,000 load cycles approximation of DIN standard :r0 0.166 log10 N N 10.000 2where N is the number of load cycles. After 10,000 load cycles r0 hardly increases. Now let's assume that the conveyor under design has a length of 10,000 m, a life expectation of 5 years at 5000 operationalhours per year. The total number of load cycles can be calculated with the following equation:N [ 3600 V / 2L ]HY 3where V is the belt speed, L the conveyor length, H the number of operational hours per year and Y the number of expected years of operation. Equation 3 is visualized in Figure 9.Figure 9: Number of load cycles versus belt speed for given example.The value of the reduction factor ro can be determined with equation 2 and the number of load cycles as given in Figure 9. The result is shown in Figure 10.Figure 10: DIN 22101 reduction factor r0 for given exampleThe safety factor as a function of the belt speed then can be determined with equation 1 and Figure 10. The result is shown in Figure 11.Figure 11: Minimum required safety factor for given exampleFrom Figure 11 it can be learned that for the belt under design the required minimum safety factor on the steady-state running tensions is about 7.5 if the belt is running at 2 m/s, and about 10 in case the belt is running at 20 m/s. Taking the belt speed into account during safety factor determination thus prevents overrating of the belt at low speeds and underrating at high speeds also depends on the length of the conveyor system .The above given figures and numbers are to illustrate the procedure only. This procedure can be fine tuned by taking measured fatigueproperties of the belt tensile-carrying member steel cords or fabric and the rubber into account, as well as the actual load cycle of the belt empty, fully loaded, steady state running, starting and stopping, summer, and winter conditions etc. .5 BELT CONVEYOR DYNAMICSIn essence the dynamics of a belt conveyor does not change with the belt speed. However, with increasing belt speed the rate of changes increases, which will result in a decreasing running stability of the belt.This paper is not intended to fully discuss belt conveyor dynamics.It is referred to [7] where this topic is extensively discussed. However, a number of notes on the dynamics of high belt speed conveyors can be made.When a belt between two idlers is exited by an idler roll in or near a natural frequency of transverse vibration of the belt span, resonance phenomena occur. The amplitude of transverse vibration increases considerably when resonance occurs yielding increased roll/ bearing wear and an increased power consumption of the belt. This increase invibration amplitude, also referred to as belt flap, must be avoided. In high-speed belt systems the effect of resonance on the structure is very destructive, as observed with lower speed belts that resonate anddestroy idler bearings. Care should therefore be taken to design a belt conveyor so that the possibility of resonance in the belt is avoided andat the same time best use is made of current static design methods so that the economics of the design are saved.Belt tracking must be excellent at high speeds. If the belt does not track properly then run off may be expected since, with increasing belt speed, side displacements and the rate of side displacement increase. The combination of belt width and strength must be chosen such that good troughability is ensured, see Section 2.1. Also imum effort must be made by the belt manufacturer to make straight belts and to construct true belt splices. In addition, longer manufactured belt lengths reduce the numberof splices and thus increase the chance of straightness.A similar comment can be made for the design of horizontal belt curves. The position of the belt on the idlers changes with a change in belt tension mainly due to a change in loading degree. The belt will move sideward in particular during large tension variations as occur during aborted starting and emergency stopping. The change in belt tension during starting and stopping will increase with increasing belt speed. For low belt speed conveyors static design methods may be sufficient to determine the imum side displacement. For high belt speed conveyors however, dynamic design methods are required to predict the side displacement to a sufficient level of accuracy.Normal operational starting and stopping procedures will not change for high belt speed conveyors, except that starting and stopping will take more time. The nature of emergency stop procedures however willchange. In general emergency stop procedures are designed to stop the belt in a short period of time without the use of the drive system and so that the belt conveyor is not damaged. A typical emergency stop time f。
出自: The South African Institute of Materials Handling有关带式输送机驱动装置设计的一些研究J.H. Rall 理工学硕士,汉森变速器（控股）有限公司董事P. Staples 理工学硕士,输送机知识与信息科技（控股）有限公司（CKIT）董事、总经理摘要：这是是一篇关于探讨运送大量颗粒物质的动力和平板橡胶输送带之间的驱动装置的综述。
它关注的是大批量的物料输送，而不是像喂料或计量输送带，大倾角式输送机等特殊情况。
它主要研究电机联轴器和驱动滚筒之间的减速器，带速，轴承寿命，使用因数，制动器和逆止器等。
1.概述地球原材料的消耗越来越多，那就需要很快地将这些材料从一个地方转移到使用它的地方，而且要通过一定的工艺来运输这些物料并且要在最短的时间内处置废物。
许多物料输送的方法是从轮手推车送到自卸卡车或接送的车辆上，或是依靠一定的空气流在空气导管中进行散料输送。
这种输送方式中，在限制成本的前提下，在可靠的长距离的物料输送中带式输送机发挥了非常重要的作用。
每一种物料输送都有其优点和缺点。
带式输送机的问题之一是，输送带柔软易降解，特别是在装货和卸货的时候。
如果维持整体尺寸是很重要的话，那么照目前的技术来说这在复杂的输送系统中是很困难。
输送系统已变得越来越大，越来越复杂，驱动系统也已经历一个演进过程而且会继续演进下去。
大带要求很大的驱动力。
不仅需要更大的独立驱动装置，同时也需要多驱动装置比如一个带需要4个各1000KW功率的驱动器。
完整驱动装置中轴的安装是另一个变化，它要求更紧凑重量更轻的驱动装置。
这往往倾向于在输送带和硬齿面齿轮旁边配置一个直角驱动器来减小驱动器的尺寸和质量。
2. 传动比与带速根据待输送物料的数量，规模，输送距离和其特点的不同决定了带的吸收功率，宽度，拉伸要求和厚度等。
大部分的传送带带速范围在2～6m/s，并且由带允许的弯曲半径决定了托辊的直径。
大型传送带的托辊直径在0.8～1.5m之间，托辊速度在50～125rpm之间。
外文文献Belt conveyor is a machinery for conveying goods without end conveyer belt moving continuously . It has simple structure , low cost , long transportation distance and high productivity . With the development of modern industrial science and technology , belt conveyor has become more and more important in industrial production . With the development of belt joint technology, belt conveyor has developed to a high level. In the 17th century, the prototype of modern bucket hoists and scraper conveyors began to use aerial ropeway to transport loose materials. In the middle of 19th century, conveyors of various modern structures appeared one after another. In 1868, Belt conveyor appeared in England, screw conveyor in America in 1887, steel belt conveyor in Switzerland in 1905, inertial conveyor in England and Germany in 1906. After that, the conveyor receives The impact of technological progress in the mechanical manufacturing, electrical machinery, chemical and metallurgical industries has been continuously improved, gradually from the completion of the internal transportation of the workshop to the completion of material handling within the enterprise, between enterprises and even between cities, Become an indispensable part of material handling system mechanization and automation.1.Belt conveyor having a circulating conveying belt, comprising: carrying rollers ar ranged between a top strand and a bottom strand of the circulating conveying belt; up per and lower guide rollers acting on upper and lower beads on the circulating convey ing belt and forcing the circulating conveying belt radially outward, the upper and low er beads being formed opposite to each other on the circulating conveying belt; at leas t one toothed ring interacting with at least one toothed belt arranged on the circulating conveying belt, whereby the upper bead is neighbored to the toothed belt; and a drive device for moving the circulating conveying belt.2. Belt conveyor according to claim 1, wherein the toothed belt is arranged on the u nderside of the circulating conveying belt, in the running direction of the circulating c onveying belt.3. Belt conveyor according to claim 2, wherein the toothed ring is arranged at the e nd of the carrying rollers, and wherein projecting from the end of a first carrying rolle r is a journal for the connection of the drive device.4. Belt conveyor according to claim 3, wherein the toothed belt extends in the regio n of the side border of the circulating conveying belt.5. Belt conveyor according to claim 1, wherein the toothed belt and the toothed ring have multisplining.6. Belt conveyor according to claim 1, wherein Kevlar filaments are incorporated i n the toothed belt.7. Belt conveyor according to claim 1, wherein the toothed belt is attached on the c irculating conveying belt via one of welding, vulcanizing, and adhesively bonding the reto.8. Belt conveyor having a circulating conveying belt, comprising: carrying rollers a rranged between a top strand and a bottom strand of the circulating conveying belt; an d a drive device and a force-transmission device for moving the conveying belt, where in a pair of elements which interact with one another with a form fit is provided for fo rce-transmission purposes, one of said elements being assigned to the force-transmissi on device and the other of said elements being assigned to the conveying belt, wherei n the force-transmission device comprises at least one toothed ring, and wherein the ci rculating conveying belt has at least one toothed belt, the toothed ring and toothed belt interacting with a form fit, wherein the toothed belt is a constituent part of a toothed-belt component which is of essentially U-shaped design in the transverse direction of t he toothed belt and engages around the side-border region of the conveying belt.9. Belt conveyor according to claim 8, wherein the toothed ring is assigned at least t o a first belt-conveyor carrying roller, which is operatively connected to the drive devi ce.10. Belt conveyor according to claim 8, further comprising a counterpressure devic e, which acts on that region of the toothed-belt component which extends on the top si de of the circulating conveying belt.11. Belt conveyor according to claim 8, wherein the free ends of the essentially U-shaped toothed-belt component are designed as a bead.12. Belt conveyor according to claim 8, further comprising guide rollers, which act on one of the toothed belt and the toothed-belt component.13. Belt conveyor having a circulating conveying belt, comprising: carrying rollers arranged between a top strand and a bottom strand of the circulating conveying belt; u pper and lower guide rollers acting on upper and lower beads on the circulating conve ying belt and forcing the circulating conveying belt radially outward, the upper and lo wer beads being formed opposite to each other on the circulating conveying belt; at le ast one toothed ring interacting with at least one toothed belt formed on the circulating conveying belt, whereby the upper bead is neighbored to the toothed belt; and a drive device for moving the circulating conveying belt, wherein a pair of said guide rollers are arranged on angled retaining arms such that the guide rollers act on one of the toot hed belt and the upper and lower beads, by way of inclined running surfaces.14. Belt conveyor according to claim 12, wherein in each case one pair of guide rol lers on the top strand and on the bottom strand of the circulating conveying belt act on one of the toothed belt and the toothed-belt component, extending over the entire bor der region of the circulating conveying belt.15. Belt conveyor according to claim 1, wherein the carrying rollers are of conical configuration and form a belt curve, and wherein the toothed ring undergoes a form-fi tting connection in relation to the circulating conveying belt at the larger-diameter end of the respective carrying roller on the outer radius of the belt curve.16. The belt driving device of claim 1, wherein one of said toothed ring and said to othed belt is releasably fixed to the carrying rollers.Belt conveyor according to claim 16, wherein one of said toothed ring and said toot hed belt is releasably fixed to the force-transmission device by one of.The present invention relates to a belt conveyor having a circulating conveying belt , having carrying rollers, which are arranged between the top strand and the bottom str and of the conveying belt, and having a drive device and a force-transmission device f or moving the conveying belt.BACKGROUND OF THE INVENTIONIt is known from practice for force to be transmitted from the drive device to the co nveying belt of a belt conveyor via friction fitting. The friction between a driven carry ing roller and the conveying belt, for example, may even be sufficient for this purpose . The rest of the carrying rollers are mounted in a movable manner and rotate along. DE 42 44 170 C2Discloses a belt conveyor having an endless conveying belt, the latter being driven by means of a force-transmission device which is present in the form of a friction whe el. A drive shaft extends beneath the bottom strand of the conveying belt. On the inner radius of the belt curve, a motor is connected as a drive device to the drive shaft and, in the region of the outer radius, a friction wheel is seated on the drive shaft and is in c ontact with the outer surface of the conveying belt. In this case, the friction wheel inte racts with a carrying roller functioning as counterpressure roller. The drive shaft is mo unted such that it can be moved at an angle both in the region of the outer radius and i n the region of the inner radius of the belt curve.Theangle mounting of the drive shaft allows adaptation of the exent towhich the friction movablewheel is pressed against the conveying belt in proportion t o the actual load. In this way, the wear is reduced if, in part-load operation, the conve ying belt is only subjected to the contact-pressure force which is necessary for this pur pose.Although the belt conveyor known from DE 42 44 170 C2 reduces the wear of the c onveying belt, it cannot rule it out altogether. The task of conveying foodstuffs or othe r goods which are to be kept clean involves, in addition to the mechanical damage to t he conveying belt, the aspect of hygiene and of keeping goods clean. The abraded surf ace particles of the conveying belt could have a considerable adverse effect on the qua lity of the goods which are to be conveyed. Moreover, the known belt conveyor requir es an extremely high level of structural outlay as far as the movable mounting of the s eparate drive shaft is concerned.Taking as departure point the belt conveyor known from DE 42 44 170 C2, the obje ct of the invention is to specify a belt conveyor of the type in question which largely r ules out any adverse effect to the surface of the coconveying belt of the belt conveyorby the force-transmission device. According to a particularly preferred configuration, the belt conveyor is intended to require just a low level of structural outlay.The above object is achieved by the features of Patent claim 1. According to the latt er, a belt conveyor of the type in question is configured such that a pair of elements w hich interact with one another with a form fit is provided for force-transmission purpo ses, and that one element is assigned to the force-transmission device and the other ele ment is assigned to the conveying belt. According to the invention, it has been found t hat the surface of the conveying belt is not adversely affected as a result of the action of the force-transmission device if a separate pair of elements is provided in order to r ealize force transmission. It has also been found that the use of a pair of movement-co nverting elements which are known per se and interact with one another with a form fi t largely eliminates the disadvantages which are known in the case of friction-fitting movement conversion, in particular wear and abrasion.According to a preferred exemplary embodiment of the belt conveyor according to t he invention, the pair of elements could be present as toothed ring and toothed belt, th e tooth flanks of the toothed ring and of the toothed belt interacting with one another. It would be possible for the toothed ring to be assigned to the force-transmission devic e and for the toothed belt to be assigned to the conveying belt.As far as a particularly low level of structural outlay is concerned, a preferred confi guration of the abovementioned exemplary embodiment provides that the toothed ring is assigned to a carrying roller, and the latter thus simultaneously assumes the role of the force-transmission device. Via a journal projecting from the carrying roller, the dri ve takes place by means of a motor. The toothed ring could be plugged onto the carryi ng roller and fixed releasably—for example via a shaft/hubconnection or a feather key —to the same.In the case of a plugged-on toothed ring, it isadvantageous that it is possible to use carrying rollers which are already present. It is particularly advantageous for each carr ying roller to be assigned at least one toothed ring. Over the entire running path of the conveying belt, it would then be the case that the toothed belt and the toothed rings int erengage and move the conveying belt in a dimensionally stable manner. Corresponding to the toothed ring or rings which is/are arranged between the top and bottom stran ds and belongs/belong to the preferred configuration mentioned above, the toothed bel t is arranged on the underside of the conveying belt, and extends in the running directi on of the same. Arranging the toothed belt on the underside of the conveying belt onc e again ensures that the top side of the conveying belt, which is charged if appropriate with goods which are to be kept clean, is not subject to any force transmission, mecha nical damage or production of abrasion particles or other contaminants.An expedient development of the preferred configuration of the belt conveyor acco rding to the invention makes provision for the toothed ring to be arranged at the end o f the carrying roller. As a result, on the one hand, straightforward maintenance of the f orce-transmission device is made possible and, on the other hand, this arrangement is also more cost-effective than a, for example, central arrangement. Direct force transmi ssion over a short distance is achieved by a journal for the connection of the drive dev ice projecting from that end of the carrying roller which is provided with the toothed r ing.It is particularly advantageous if the toothed belt extends in the region of the side b order of the conveying belt. As a result, on the one hand, straightforward production o f the conveying belt with the toothed belt is made possible by the direct relationship to the border region and, on the other hand, a role is also played here by the accessibilit y to the pair of elements for maintenance purposes and, of course, by the coordination between the toothed belt and the arrangement of the toothed ring.In addition to toothed belts and toothed rings with normal toothing, it would also b e possible to realize multisplining. This further reduces undesired sliding and thus we ar, heating and noise development. In order to absorb high tensile forces, it would be possible for Kevlar filaments to be incorporated in the toothed belt, which usually con sists of plastic. It would be possible for the conveying belt to be produced with the too thed belt by welding, vulcanizing or adhesive bonding. According to a particularly pre ferred configuration, it would be possible for the toothed belt to be a constituent part o f a toothed- belt component which is of essentially U-shaped design in the transverse direction of the toothed belt.The U-shape makes it possible for the toothed- belt component simply to be plugge d onto the border of the conveying belt until the border region has come into contact with the base part between the U-legs. The inner surface of the toothed- belt compone nt may have been provided with adhesive beforehand. As a result of its shaping and of being produced in this way, the toothed- belt component engages around the side-bor der region of the conveying belt.While the toothed belt of the conveying belt is subjected to compressive force by th e toothed ring, and this largely rules out detachment of the toothed- belt component o n the underside of the conveying belt, a counterpressure device could be provided in o rder to secure that region of the toothed- belt component which extends on the top sid e of the conveying belt. In design terms, the leg of the counterpressure device could b e present in the form of an arm which acts on the U-toothed- belt component on the to p side and thus constantly presses the same onto the top side of the conveying belt. As far as reliable guidance is concerned, it would be possible for the toothed belt or the toothed- belt component containing the toothed belt to form a bead. A bead ridge is thus produced over the length of the conveying belt. In the case of a U-shaped tooth ed- belt component, the bead ridge extends in each case at the free ends of the U-legs, at a distance from the border of the conveying belt, the distance depending essentially on the width of the toothed belt. As an alternative to a bead ridge, it would be possible for the toothed- belt component or for the straightforward toothed belt also to have at least one beveled free end. The guidance measure taken on the toothed belt or on the s pecific toothed- belt component is provided in order that a guide roller or a pair of gui de rollers acts on the beveled surface or on the bead or bead ridge. The guidance meas ure explained above could be taken equally well in the case of belt curves and straight belt lines and of belt S-shapes bridging different heights.In the case of belt curves, the force acting on the conveying belt is directed toward the inner radius of the belt curve, with the result that the guide rollers, in an advantage ous manner which is known per se, could have inclined running surfaces. Correspondi ngly angled retaining arms as a constituent part of retaining structures for the guide ro llers could be arranged in each case in the region of a carrying roller. The guide rollers could be arranged in pairs on the top strand and on the bottom strand of the conveyi ng belt.It should be emphasized at this point that, with the abovementioned configuration o f the belt conveyor according to the invention having the bead or beveled free ends, t wo functions are combined in the pair of form-fitting elements. Not only the force tra nsmission, but also the guidance of the conveying belt, takes place. The dimensional s tability of the conveying belt isadvantageously increased by the pair of form-fitting el ements with the specific configuration of the toothed belt or of the toothed- belt comp onent for action of the guide rollers thereon.In the case of the already cited design of the belt conveyor in the form of a belt curv e, the carrying rollers are of conical design and the toothed ring is arranged at the larg er-diameter end of the respective carrying roller, that is to say on the outer radius of th e belt curve. The drive device is present as a motor and is assigned to the first carrying roller of the belt curve. The form-fitting interengagement of the toothed wheel and to othed belt takes place in the region of each carrying roller, the form fit, in relation to t he first, motor-driven carrying roller, serving for force-transmission purposes and, in r elation to the rest of the rollers, serving for guiding the conveying belt.The previously explained principle of force transmission via a pair of elements w hich interact with one another with a form fit could also be used in the case of a straig ht belt line or in the case of a height-changing belt S-shape. Here, the carrying rollers are of a cylindrical design and the force transmission takes place—as with the belt cur ve—at a first carrying roller, while the followingcarrying rollers, likewise equipped w ith the pair of form-fitting elements, serve for guiding the conveying belt. In contrast t o the belt curve, however, it would be possible, in the case of the straight belt line or i n the case of the belt S-shape, for the pair of elements to be arranged at the two free e nds of the respective carrying roller and on the two border regions of the conveying b elt. It would thus be possible specifically for the two border regions of the conveying belt to have a toothed belt or a toothed- belt component which interacts with the tooth ed rings at the two free ends ofeac carrying roller. Furthermore, it would also be possible, with these types of construction of the belt conveyor according to the invention, to provide guide rollers.A further advantage of the preferred embodiment of the belt conveyor according to th e invention, the toothed ring and toothed belt interacting, consists in the improved cap acity for controlling the belt speed in accordance with the current loading. It would be possible to provide a control device which senses a change in the speed by correspon ding measuring sensors and adjusts the power of the drive device in line with the safet y regulations.In comparison with the force transmission realized by friction fitting, the belt con veyor according to the invention not only has the advantage of better capacity for cont rol, but also has the advantage that the conveying belt has a high level of dimensional stability as a result of the guidance by means of the pair of form-fitting elements and b y means of the pairs of guide rollers and can be subjected to higher torques. Overall, it is possible to achieve an increased level of drive power during start-up. In the case of the belt conveyor according to the invention being designed in the form of a belt curv e with an inner radius of 400 mm, the carrying rollers rotate at 230 rpm at a maximum speed of 1.5 m/sec.There are various possibilities then, of advantageously configuring and developin g the teaching of the present invention. For this purpose, reference is made, on the one hand, to the claims subordinate to Patent claim 1 and, on the other hand, to the follow ing explanation of an exemplary embodiment of the invention with reference to the dr awing. In conjunction with the explanation of the cited exemplary embodiment of the invention, generally preferred configurations anddevelopments of the teaching are also explained.中文译文带式输送机是连续运动的无端输送带输送货物的机械。
带式输送机论文中英文资料外文翻译文献中英文资料外文翻译文献A Comparison of Drive Starting Mechanisms forAggregate Belt ConveyorsAbstractThe purpose of this paper is to describe the torque/speed characteristics，during starting conditions，of the most common drives used on belt conveyors today. Requirements of a Belt Conveyor DriveA belt conveyor is considered to be a constant torque device. In other words，the required driving torque is approximately constant at varying speeds (see figure l).other applications，such as a pump drive，have variable torque requirements(see figure2).However，to increase the speed of a conveyor additional torque must be added until the desired speed is obtained. Newton’s Second Law of Motion governs this relationship.∑=F m aThe most straightforward example would be a constant acceleration torque(see figure3).In reality the acceleration torque is rarely constant. However，static calculation models as outlined in the Conveyor Equipment Manufacturers Association handbook (CEMA) make this assumption. When using static models the average acceleration torque is estimated over the entire acceleration time and assumed to be linear. Dynamic models，which are beyond the scope of this paper，allow acceleration torque values to vary in magnitude during the acceleration(or deceleration)Period.It should be noted that，given a constant load，a larger acceleration torque results in a faster acceleration time and also higher Peak belt tensions. Conversely，a smalleracceleration torque results in a longer start time and smaller Peak belt tensions. Across-The-Line AC Motor StartTechnically this is the simplest type of drive used on a belt conveyor. In this drive type an AC squirrel cage induction motor is started by simply throwing the contactor and energizing the motor. The resulting output torque，assuming that rated voltage is maintained，is strictly a function of the motor design. NEMA has Provided design standards that define the output torque characteristics of the most commonly used 3 Phase motors up to approximately 250 hp(figure4).In sizes larger than 250 hp manufacturers generally use the NEMA design codes in a relative manner(i.e.，NEMA C has a greater locked rotor torque than a NEMA B motor).The most critical locations on the AC motor speed/torque curve have been named for definition purposes. These common names are provided in figure 5.The most rigorous method of determining average acceleration torque，for staticcalculations，is to break the curve into several verticalsections，then sum the individual areas under the curve and finally divide by the number of sections.The more common way is to apply the following simplified equation:These static approximation methods work for most belt conveyors but can get the designer into trouble from time to time，especially on long and/or steep and/or fast conveyors. One item that needs to be examined is breakaway torque. Just because the drive provides enough average torque to accelerate the load doesn’t mean that it provides enough torque to break it away from zero speed and get it moving.CEMA defines breakaway torque as twice the torque required to overcome the total friction plus the torque required to lift the load vertically. Locked rotor torque (LRT) needs to be greater than breakaway torque! A good static Program makes this check.In addition to examining the effect that average torque has on the conveyor components the belt designer needs to determine the effect of peak torque. It is not uncommon for the breakdown torque (BDT) of a NEMA C motor to be greater than2.5 times full load torque (FLT).Generally the belting and Pulley manufacturers allowa transient overload of 1.5 times full load operating load. An across-the-line start can easily cause tensions to exceed these maximums. These higher than normal loads can be designed into the conveyor if they are known up front.Considering only average starting torque can cause the conveyor designer to undersize the take-up weight. It is notuncommon for conveyors with across-the-line starters to experience intermittent drive slip. This generally happens when Peak torque (BDT) is input by the drive and the take-up has been sized for average torque but not peak torque. The result can be devastating. When the drive pulley slips during thiscondition，the tension on the Tl and T2 sides (high and low)of the drive Pulley tries to equalize. This can subject a low tension bend or take-up pulley，just behind the drive pulley，to tensions that approach Tl tension. These Pulleys are rarely，if ever，designed for this load condition and the result is low tension Pulley failure. This condition is easily demonstrated with dynamic analysis.Another common Problem with across-the-line starts is caused by voltage dips during starting. If the power distribution system is not stiff enough to handle the huge inrush currents of an across-the-1ine start，the starting torque of the motors can be reduced to a Point that the conveyor will not start. This is due to the fact that the output torque of an AC squirrel cage induction motor is reduced by the square of the applied voltage. In other words，a voltage drop of 10%would equate to a torque reduction of 19%. Reduced Voltage StartingThe reduced voltage starting of an AC squirrel cage induction motor is done for two basic reasons:1 .To reduce the inrush current that naturally occurs when a motor is Startedacross-the-1ine. A typical current/speed graph is shown in figure 6.It is not uncommon for the inrush current to be 6 times or more than it is at full load torque. As stated above high inrush currents cause the voltage in a power distribution system to sag. The cost of electrical power distribution equipment can becomevery high if it needs to be designed to handle the high inrush currents.2 . To reduce Peak motor torque during starting conditions，which subsequentlyincreases acceleration time. By reducing the Peak torques the conveyor components can be designed for lower tension loads. This primarily includes belting，Pulleys and external support structure. This can result in significant cost savings.Two common types of reduced voltage starters are the Current Limiting and the Constant Torque devices.Graphs are included above(figures 7 through 8) that depict the same motor/conveyorapplication with an Across-The-Line，a limitd Curren, and a constant Torque start. After studying the graphs it becomes apparent that the best use of the limited torque start is to protect the power distribution system from high inrush currents. The constant torque start reduces the high torque Peaks and Protects the conveyor’s mechanical components. In both cases the Start time is increased because the over all magnitude of acceleratingtorque is reduced. However，neither method will make it easier to start a“hard-to-start conveyor.”Correcting a hard starting conveyor is not a reason to use a reduced voltage starter!翻译带式输送机驱动方式比较摘要本文的目的是描述最常见的机用输送皮带起动时的扭矩/转速特性。
JINGGANGSHAN UNIVERSITY外文翻译题目调整送料量输送装置设计学院机电工程学院专业机械制造及其自动化班级机制11本（1）班学号110611014姓名蓝善龙指导教师康志成教授起讫时间2014.12.1—2015.4教务处印制AbstractBulk material transportation requirements have continued to press the belt conveyor indu stry to carry higher tonnages over longer distances and more diverse routes. In order keep up, si gnificant technology advances have been required in the field of system design, analysis and nu merical simulation. The application of traditional components in non-traditional applications re quiring horizontal curves and intermediate drives have changed and expanded belt conveyor po ssibilities. Examples of complex conveying applications along with the numerical tools require d to insure reliability and availability will be reviewed.Belt Conveying Systems Development of driving system Among the methods of material conveying emploved, belt conveyors play a very imporient part in the reliable carrying of material over long distances at competitive cost. Conveyor systems have become larger and more complex and drive systems have a l so been going through a process of evolution and will continue to do so. Nowadays, bigger belts require more power and have brought the need for larger individual drives as well as multiple drives such as 3 drives of 750 kW for one belt(this is the case for the conveyor drives in Chengzhuang Mine). The ability to control drive acceleration torque is critical to belt conveyors' performance. A efficient drive system should be able to provide smooth, soft starts while maintaining belt tensions within the specified safe limits. For load sharing on multiple drives. torque and speed control are also considerations in the drive system's design. Due to the advances in conveyor drive control technology, at present many more reliable. Cost-effective and performance- driven conveyor drive systems covering a wide range of power are available for customers' choices[1]. 1 Analysis on conveyor drive technologies1. 1 Direct drives Full-voltage starters.With a full-voltage starter design, the conveyor head shaft is direct-coupled to the motor through the gear drive. Direct 8 full-voltage starters are adequate for relatively low-power, simple- Profile conveyors. With direct full-voltage starters. no control is provided for various conveyor loads and. depending on the ratio between full- and no-load power requirements, empty starting times can be three or our times faster than full load. The maintenance-free starting system is simple, low-cost and very reliable. However, they cannot control starting torque and maximum stall torque; therefore. they are limited to the low-power, simple-profile conveyor belt drives.Reduced-voltage starters. As conveyor power requirements increase,controlling theapplied motor torque during the acceleration period becomes increasingly important. Because motor torque is a function of voltage, motor voltage must be controlled. This can be achieved throughreduced-voltage starters by employing a silicon controlled rectifier (SCR). A common starting method with SCR reduced-voltage starters is to apply low voltage initially to take up conveyor belt slack. and then to apply a timed linear ramp up to full voltage and belt speed. However, this starting method will not produce constant conveyor belt acceleration. When acceleration is complete. the SCRs, which control the applied voltage to the electric motor. are locked in full conduction, providing full-line voltage to the motor. Motors with higher torque and pull -vp torque, can providebetterstarting torque when combined with the SCR starters, which are available in sizesup to 750 KW.Wound rotor induction motors. Wound rotor induction motors are 9 connected directly to the drive system reducer and are a modified onfiguration of a standard AC induction motor. By inserting resistance in series with the motor's rotor windings. the modified motor control System controls motor torque. For conveyor starting, resistance is placed in series with the rotor for low initial torque. As the conveyor accelerates,the resistance is reduced slowly to maintain a constant acceleration torque. On multiple-drive systems. an external slip resistor may be left in series with the rotor windings to aid in load sharing .the motor systems have a relatively simple a design.However,the control systems for these can be highly complex, because they are based on computer control of the resistance switching. Today, the majority of control systems are custom designed to meet a conveyor system's particular specifications. Wound rotor motors are appropriate for systems requiring more than 400KW.DC motor. DC motors. available from a fraction of thousands of KW，are designed to deliver constant torque below base speed and constant KW above base speed to themaximum allowable revolutions per minute (r/min). with the majority of conveyor drives, a .DC shunt wound motor is used. Wherein the motor's rotating armature is connected externally. The most common technology for controlling DC drives is a SCR device. which allows for continual variable-speed operation. The DC drive system is mechanically simple, but can include complex custom-designed electronics to monitor and control the complete system. this system option is expensive in comparison to othersoft-start systems. but it is a reliable, cost-effective drive in applications in which torque,load sharing and variable speed are primary considerations. DC motors generally are used with higher-power conveyors, 10 including complex profile conveyors with multiple-drive systems, booster tripper systems needing belt tension control and conveyors requiring a wide variable-speed range.1. 2 Hydrokinetic coupling2.Hydrokinetic couplings, commonly referred to as fluid couplings. are composed of threebasic elements; the driven impeller, which acts as a centrifugal pump; the driving hydraulic turbine known as the runner and a casing that encloses the two power components.Hydraulic fluid is pumped from the driven impeller to the driving runner, producing torqueat the driven shaft. Because circulating hydraulic fluid produces the torque and speed, no mechanical connection is required between the driving and driver shafts.The power produced by this coupling is based on the circulated fluid's amount and density and the torque in proportion to input speed. Because the pumping action within the fluid coupling depends on centrifugal forces. the output speed is less than the input speed. Referred to as slip. this normally is between 1% and 3%. Basic hydrokinetic couplings are available in configurations from fractional to several thousand KW.Fixed-fill fluid couplings. Fixed-fill fluid couplings are the most commonly usedsoft-start devices for conveyors with simpler belt profiles and limited convex/concave sections. They are relatively simple,low-cost,reliable,maintenance free devices that provide excellent soft starting results to the majority of belt conveyors in use today.Variable-fill drain couplings. Drainable-fluidcouplings work on the same principle as fixed-fill couplings. The coupling's 11 impellersare mounted on the AC motor and therunners on the driven reducer high-speed shaft. Housing mounted to the drive base encloses the working circuit. The coupling's rotating casing contains bleed-off orifices that continually allow fluid to exit the working circuit into a separate hydraulic reservoir. Oil from the reservoir is pumped through a heat exchanger to a solenoid-operated hydraulic valve that controls the filling of the fluid coupling. To control the starting torque of a single-drive conveyor system, the AC motor current must be monitored to provide feedback to the solenoid control valve. Variable fill drain couplings are used in medium to high-kw conveyor systems and are available in sizes up to thousands of kw.The drives can be mechanically complex and depending on the control parameters. the system can be electronically intricate. The drive system cost is medium to high,depending upon size specified.Hydrokinetic scoop control drive. The scoop control fluid coupling consists of the three standard fluid coupling cmponents: a driven impeller, a driving runner and a casing that encloses the working circuit. The casing is fitted with fixed orifices that bleed a predetermined amount of fluid into a reservoir. When the scoop tube is fully extended into the reservoir, the coupling is 100 percent filled. The scoop tube, extending outside the fluid coupling, is positioned using an electric actuator to engage the tube from the fully retracted to the fully engaged position. This control provides reasonably smooth acceleration rates. to but the computer-based control system is very complex. Scoop control couplings areVariable-frequency control(VFC) Variable frequency control is also one of the direct drive methods. the emphasizing discussion about it here is because that it has so unique characteristic and so good performance compared with other driving methods for belt conveyor. VFC devices Provide variable frequency and voltage to the induction motor, resulting in anexcellent starting torque and acceleration rate for belt conveyor drives. VFC drives. available from fractional to several thousand (kW)，are electronic controllers that rectify AC line power to DC and, through an inverter, convert DC back to AC with frequency and voltage control. VFC drives adopt vector control or direct torquecontrol(DTC)technology, and can adopt different operating speeds according to different loads. VFC drives can make starting or stalling according to any given S-curves realizing the automatic track for starting or stalling curves. VFC drives provide excellent speed and torque control for starting conveyor belts. and can also be designed to provide load sharing for multiple drives. easily VFC controllers are frequently installed on lower-powered convey- or drives, but when used at the range of medium-high voltage in the past. the structure of VFC controllers becomes very complicated due to the limitation of voltage rating of power semiconductor devices, the combination of medium-high voltage drives and variable speed is often solved with low-voltage inverters using step-up transformer at the output, or with multiple low-voltage inverters connected in series. Three-level voltage-fed PWM converter systems are recently showing increasing popularity for multi-megawatt industrial drive applications because of easy voltage sharing between the series devices and iroved 13 harmonic quality at the outputcompared to two-level converter systems With simple series connection of devices. This kind of VFC system with three 750 kW /2. A V inverters has been successfully installed in ChengZhuang Mine for one 2. 7-km long belt conveyor driving system in following the principle of three-level inverter will be discussed in detail. 2 Neutral point clamped(NPC)three-level inverter using IGBTs Three-level voltage-fed inverters have recently become more and more popular for higher power drive applications because of their easy voltage sharing features. lower dv/dt per switching for each of the devices, and superiorharmonic quality at the output. The availability of NV-IGBTs has led to the design of a new range of medium-high voltage inverter using three-level NPC topology. This kind of inverter can realize a whole range with a voltage rating from 2. 3 kV to 4. 16kV Series connection of IIV-IGBT modules is used in the 3. 3 kV and 4. 1 6kV devices. The 2. 3 kV inverters need only one HV-IGBT per switch[2,3].2. 1 Power section To meet the demands for medium voltage applications. a three-level neutral point clamped inverter realizes the power section. In comparison to a two-level inverter. the NPC inverter offers the benefit that three voltage levels can be supplied to the output terminals, so for the same output current quality, only 1/4 of the switching frequency is necessary. Moreover the voltage ratings of the switches in NPC inverter topology will be reduced to 1/2. and the additional transient voltage stress on themotor 14 can also be reduced to 1/2 compared to that of a two-level inverter.The switching states of a three-level inverter are summarized in Table 1. U. V and W denote each of the three phases respectively; P N and 0 are the do bus points. The phase U, for example, is in state P (positive bus voltage)when theswitches S1uand S2u are closed, whereas it is in state N (negative bus voltage) when the switches S3u and S4u, are closed. At neutral point clamping, the phase is in 0 state when either S2u.or S3u, conducts depending on positive or negative phase current polarity, respectively. For neutral point voltage balancing, the average current injected at 0 should be zero.2. 2 Line side converter For standard applications. a 12-pulse diode rectifier feeds the divided DC-link capacitor. This topology introduces low harmonics on. the line side. For even higher requirements a 24-pulse diode rectifier can be used as an input converter. For more advanced applications where regeneration. capability is necessary, an active front. end converter can replace the diode rectifier, using the same structure as the inverter.2. 3 Inverter control Motor Control. Motor control of induction machinesis realized by using a rotor flux. oriented vector controller. Fig. 2 shows the block diagram of indirect vector controlled drive that incorporates both constant torque and high speed field-weakening regions where the PW M modulator was used. In this figure, the command fluxψ.is generated as function of speed. The feedback speed is added with the feed 15 forward slip command signalψ,the resulting frequency signal is integrated and then the unit vector signals(cosθe and sinθ e)are generated. The vector rotator generates the voltage Vs and Angle θe commands for the PW M as shown.PWM Modulator. The demanded voltage vector is generated using an elaborate PWM modulator. The modulator extends the concepts of space-vector modulation to the three-level inverter. The operation can be explained by starting from a regularly sampled sine-triangle comparison from two-level inverter. Instead of using one set of reference waveforms and one triangle defining the switching frequency, three-level Modulator uses two sets of reference waveforms Uand U and just one triangle. Thus, each switching transition is used in an optimal way so that several objectives are reached at the same time. Very low harmonics are generated. The switching frequency is low and thusswitching losses are minimized. A in a two-level inverter, a zero-sequencecomponent can be added to each set of reference waveform s in order to maximize the fundamental voltage component. As an additional degree of freedom, the position of the reference waveform s within the triangle can be changed. This can be used for current balance in the two halves of the DC-link. 3 Testing results After Successful installation of three 750 kW /2. 3 kV three-level inverters for one 2. 7 km long belt conveyor driving system in Cheng zhuang Mine. The performance of the whole VFC system was tested. Fig. 3 is 16 taken from the test, which shows the excellent characteristic of the belt conveyor driving system with VFC controller. Fig. 3 includes four curves. The curve 1 shows the belt tension . From the curve it can be find that the fluctuation range of the belt tension is very small. Curve 2 and curve 3 indicate current and torque separately. Curve 4 shows the velocity of the controlled belt. The belt velocity have the "s" shape characteristic. All the results of the test show a very satisfied characteristic for belt driving system. 4 Conclusions Advances in conveyor drive control technology in recent years have resulted in many morereliable. Cost-effective and performance-driven conveyor drive system choices forusers.Among these choices,theVariable frequency control (VFC) method shows promising use in the future for long distance belt conveyor drives due to its excellent performances. The NPC three-level inverter using high voltage TGBTs make the Variable frequency control in medium voltage applications become much more simple because the inverter itself can provide the medium voltage needed at the motor terminals, thus eliminating the step-up transformer in most applications in the past. The testing results taken from the VFC control system with NTC three. level inverters used in a 2. 7 km long belt conveyor drives in Chengzhuang Mine indicates that the performance of NPC three-level inverter usingHV-TGBTs together with the control strategy of rotor field-oriented vector control for induction motor drive is excellent for belt conveyor driving system.References:[1]Kung, Walter, “The Henderson Coarse Ore Conveying System-A Review of Commissioning, Start-up, and Operation”, Bulk Material Handling by Belt Conveyor 5, Society for Mining, Metallurgy and Exploration , Inc., 2004 ；[2]Alspaugh, Mark, “The Evolution of Intermediate Driven Belt Conveyor Technology”, Bulk Solids Handli ng”, Vol. 23 (2003) No.3;[3]Goodnough, Ryne, “In-Pit Conveying at the Wyodak Mine- Gillette, Wyoming” , Bulk Material Handling by Belt Conveyor 5, Society for Mining, Metallurgy and Exploration, Inc., 2004 ;[4]Dewicki, Grzegorz, “Bulk Material Handling and Processing- Numerical Techniques and Simulation of G ranular Material”, Bulk Solids Handling”, V ol. 23 (2003) No.2.摘要粒状材料运输要求带式输送机具有更远的输送距离、更复杂的输送路线和更大的输送量。
出自: The South African Institute of Materials Handling有关带式输送机驱动装置设计的一些研究J.H. Rall 理工学硕士,汉森变速器（控股）有限公司董事P. Staples 理工学硕士,输送机知识与信息科技（控股）有限公司（CKIT）董事、总经理摘要：这是是一篇关于探讨运送大量颗粒物质的动力和平板橡胶输送带之间的驱动装置的综述。
它关注的是大批量的物料输送，而不是像喂料或计量输送带，大倾角式输送机等特殊情况。
它主要研究电机联轴器和驱动滚筒之间的减速器，带速，轴承寿命，使用因数，制动器和逆止器等。
1.概述地球原材料的消耗越来越多，那就需要很快地将这些材料从一个地方转移到使用它的地方，而且要通过一定的工艺来运输这些物料并且要在最短的时间内处置废物。
许多物料输送的方法是从轮手推车送到自卸卡车或接送的车辆上，或是依靠一定的空气流在空气导管中进行散料输送。
这种输送方式中，在限制成本的前提下，在可靠的长距离的物料输送中带式输送机发挥了非常重要的作用。
每一种物料输送都有其优点和缺点。
带式输送机的问题之一是，输送带柔软易降解，特别是在装货和卸货的时候。
如果维持整体尺寸是很重要的话，那么照目前的技术来说这在复杂的输送系统中是很困难。
输送系统已变得越来越大，越来越复杂，驱动系统也已经历一个演进过程而且会继续演进下去。
大带要求很大的驱动力。
不仅需要更大的独立驱动装置，同时也需要多驱动装置比如一个带需要4个各1000KW功率的驱动器。
完整驱动装置中轴的安装是另一个变化，它要求更紧凑重量更轻的驱动装置。
这往往倾向于在输送带和硬齿面齿轮旁边配置一个直角驱动器来减小驱动器的尺寸和质量。
2. 传动比与带速根据待输送物料的数量，规模，输送距离和其特点的不同决定了带的吸收功率，宽度，拉伸要求和厚度等。
大部分的传送带带速范围在2～6m/s，并且由带允许的弯曲半径决定了托辊的直径。
大型传送带的托辊直径在0.8～1.5m之间，托辊速度在50～125rpm之间。
假设使用4极电机，这能提供12:1～30:1之间需要的减速比。
大部分的齿轮制造商不会采用过高的传动比，每级传动比不超过5:1，这意味着将会是2～3级减速。
（除小功率的蜗杆减速器或是扭矩臂和V带驱动器可能会使用）。
有一种误解以为减速器使用6或8极电机可以降低成本，但即使是8极电极能有更高的速度，且每级减速比超过6:1，这样仍然需要2级传动。
大部分变速器的成本与低速轴的扭矩有关系。
因此，只要确定了这一点，除了使用了4极电机以外使用其他任何电机相比之下都是没有任何经济优势可言的。
由于受到规模和数量的限制，一般对电机制造商来说提供的4极电机的价格最低。
因此作为选择电机的一条原则，为了达到要求的传动轴速度，4极电机是最佳选择了。
电动机使用球轴承和滚子轴承的一些制造商喜欢6极甚至8极的转速，能给电机提供超过1000千瓦的功率。
3.1 选择单个或多个驱动器在计算出驱动皮带所需功率和皮带张力和包角之后就可决定就带是否应装有一个或多个驱动器。
这一决定往往受安装在工厂的数倍于经常使用的小驱动器等设备的影响。
驱动器的大小也可能由最近可用的标准电动机决定。
如果一个驱动器离主要动力源有相当的距离，那么就要用一根长的电缆来连接电机和驱动器。
这样一来，在选择我们使用的电机的数量和尺寸时电缆尺寸和变压器的成本就可能发挥一个很重要的作用。
随着电机的启动，电动机的峰值电流可能是6相满载电流。
一个电机或一组电机的运行电流与最后一个电机启动时的启动电流之间的联系对驱动器的选择会有很强的影响。
3.2 低速轴的连接从减速器到皮带轮轴的传动一种是通过与安装在构架旁边的基础部件上的驱动装置的“弹性”耦合来实现，一种是通过挂在带轮轴上的驱动装置的轴来实现。
驱动装置可以安装空心轴，通过摩擦锁合原理来驱动或是安装实心轴用一个刚性联轴器将其与输送机轴连接起来以实现驱动。
附件中给出了一些典型的附属装置草图。
（见附录A ）。
4.1 起动方法﹑驱动器的大小和保护装置的选择在启动传送带时，通常涉及到一个需要加速的相当大的质量。
为了缩短电机达到启动电流的时间，需要在减速器和驱动电机之间安装一个“滑动联轴器”。
另外，滑环电动机的使用，实现了通过控制电机的峰值电流以实现快速且柔性启动。
功率10kW以下的小带直接在线器启动采用直接耦合是很正常的，但对于100千瓦以下的带来说采用“滑动联轴器”是最常见的，而且可能是最简单和成本效益最大的。
采用较大的驱动器来获得需要的功率会持续的增加成本，在这种情况下滑环电机就可能引起了人们的注意，因为它能预防用电高峰期，特别是在最高电力需求需要支出大量电费的时候。
市场上有很多种与D.O.L.启动机配套使用的滑动联轴器，但对于较大的输送带来说多数使用液体耦合器，无论是连续牵引或是延迟填补牵引或是可控填补填补牵引（杓子式）。
流力耦合器总是会做少量的“滑动”以帮助多个驱动器共担负载，并且提供了精确调整过的耦合“填补”。
一般来说，每个耦合器都略有各自不同的特点，如果正确调整分担载荷，在满载条件下将有可能比轻载条件下不适当的分担载荷更好。
电机的特点也各不相同，这有助于多个驱动器分担负荷。
驱动系统通常都是每带最多4个电机，但只用很少的会用更多的电机。
4.2 电动机起动（D.O.L.与液力偶合器）多个驱动器启动的一般做法是先启动次级驱动器电机3～5秒钟后在启动另一个主级电机，持续5～10秒钟后启动下一个主级电机。
然而，在实践中观察到启动开始后和理想状态有一个时间延迟。
一个非常常见的现象是观察到次级驱动电机由于保守耦合的选择，启动电流有所下降，但很快又开始上升，由于延迟填补耦合增加了它的滑动力矩，而带依然平稳。
如果主级驱动器是在耦合扭矩大幅度增加之前的正确时间启动的，带就会在过低电流状态下带速增加。
联轴器的相对滑移影响到它的扭矩和电机电流，而且很快带就可以启动了，峰值电流很快也将下降。
在杓子式液力偶合器中所有电机都很快成功的启动然后所有联轴器开始缓慢填补。
滑环电动机也采用类似的的方式启动。
这两种方法无疑对皮带，皮带轮是有利的方式。
采用杓子式液力偶合器或滑环电机有可能使较小型电机的使用更安全和开关装置维修成本的节省。
4.3 其他驱动器方法如果要求输送率变化的，那么直流驱动器可以当作鼠笼电动机来实现变频控制。
另一种方法是用水文静态驱动器，但大功率驱动器的运行和维护费用上很可能会高于采用SC电机液力偶合驱动器和或滑环电动机。
4.4 带保护带保护是为了防止超载和失控。
其做法通常是通过皮带下方的托辊驱动的离心开关来实现的。
然而，这并不是现在使用的非常灵敏和最尖端的方法。
一种恰当的方法是在驱动变速箱低速轴上安装一个脉冲发生器，皮带驱动的托辊上装上类似的脉冲发生器。
监测器能不断的检测脉冲频率，如果输送带跑偏的话它就会给出警报或直接使带停下来。
通过使用监测器来控制滑环电动机的启动能将带的跑偏滑动控制在最低限度内。
监测器可控制转子电阻继而控制起动转矩。
5. 带式输送机制动5.1 正向制动一般说来，摩擦会降低皮带正常前进的速度并增加负载使其在相对较短的时间内停止。
停车时间的长短主要取决于卸料结束条件。
如果一个带给另一个带送料是，平稳的条件，转载仓的大小和带的布局可能会需要一个制动带的其他方法而不是靠正常的摩擦。
一般来说向下卸料或是向上输送的带都需要制动。
如果一个输送带输送部分比输送机其它部分长很多的话，输送斜槽就可会超载甚至可能是遭到破坏，但这种情况很少出现。
先初步根据输送带的布局（见附录B ）在变速箱高速轴上装制动器，可以看到，当又载荷的情况下停止的时候载荷的惯性往往会依靠重力拉紧和释放驱动器和前部带轮之间带的张紧力，甚至带还可能会松弛。
反转时驱动器因制动器作用而不动，但负载会在重力的作用下使带加速。
而当驱动器和头部滚筒张紧时，就会使因负载而加速的带由于长距离输送之间的摩擦力而减缓下来。
在这种根据负载突然停止的时候驱动器会受到剧烈冲击。
在这种情况下，制动不仅是不必要的，而且是极不可取的。
安装在卸料带的制动器将再次释放驱动器和头部滚筒之间的张紧力，但这往往会释放正在运行（或停止）的带轮的张力，并使得带有滑动。
这对皮带和带轮有害，而且也是很危险的。
制动带正确的方法像是这样的：在带尾部滚筒或反转时的其它滚筒上采取行动。
另一个制动器有时会用到的方法有时用一个移动堆垛机来制动皮带，以减少带的刮伤；带固定的时候堆垛机应能够移动。
但在尾部滚筒上仍然要装一个制动器，在驱动器或输送机头部安装一个钳制器。
附件：FROM : The South African Institute of Materials Handling BELT CONVEYOR DRIVES - A CONSIDERATION OFSOME DESIGN ASPECTSJ.H. Rall Pr.Eng., BSc Eng., MSAIME Hansen Transmissions(Pty) ltdP. Staples Pr.Eng BSc, MSAIMEManaging Director Conveyor Knowledge and InformationTechnology (Pty)Ltd (CKIT)Summary:This is a short review of part of the link between the electric power grid and flat rubber covered belts used for transporting large volumes of granular material. It is concerned with high volume material conveying and not with special cases such as feed or metering conveyors, steep inclined conveyors etc. It considers mainly the speed reducer between motor coupling and drive pulley, ratings, bearing life, service factors, stopping and anti-runback devices1.GeneralThe ever increasing rate of consumption of earth's raw materials has brought with it a need for faster movement of these material from the point of extractionto the point of process or usage and transporting these materials through the process plant and disposing of the waste in the shortest possible time. Many methods of material handling are employed from wheel barrows to dump trucksor shuttle cars, to pneumatic ducts carrying pulverised particles in an air stream.In this line of movement, belt conveyors play a very important part in the reliable carrying of material over long distances at a competitive cost.Each method of material conveying has its advantages and disadvantages. Oneof the problems with belt conveyors is that soft friable material can be degraded, particularly in loading and unloading. If the maintenance of lump size is important, this can present difficulties on a complicated conveyor system.Conveyor systems have become larger and more complex and drive systems have also been going through a process of evolution and will continue to do so.Bigger belts require more power and has brought the need for larger individual drives as well as multiple drives such as 4 drives of 1000 kW each on one belt. Shaft mounting of the complete drive unit is another change which has brought with it the requirement for more compact and lighter drive units. This tends to favor a right angle drive configuration with the motor next to the belt and hardened gears to reduce the dimensions and mass of the drive.2. Drive Ratio and Belt speedsDepending on the quantity, size, distance and characteristics of the material to be conveyed, the absorbed power, width, tensile requirements and top cover thickness of the belt will be decided.Large volume conveyor belts run in the range of 2 to 6 metre/second and the allowable bend radius of the belt determines pulley diameters which for large belts is of the order of 0,8 to 1,5 m giving pulley speeds between 50 and 125 rpm. Assuming that 4 pole motors are used, this gives a reduction ratio required between 12:1 and 30:1.Most modern gear manufacturers do not use a higher ratio per stage than 5:1, which means that speed reducers will be either 2 or 3 stage reduction. (Except for small powers where worm reducers, or torque arms and V belt drives may be used).There is a misconception that one can reduce the cost of the gear-speed reducer byusing a 6 or 8 pole motor, but even an 8 pole motor on the higher speeds would require a reduction above 6:1and a 2 stage unit would still be required. The bulk of the cost of a gearbox is related to the low speed shaft torque and therefore having determined this, there is generally no economic advantage at all in using anything but a 4 pole motor. The motor manufacturers, because of size and volume, generally supply 4 pole motors at the lowest price, and as a rule therefore, a 4 pole motor is the best choice with a gearbox of the appropriate ratio to arrive at the desired conveyor shaft speed.Where ball and roller bearings are used in the electric motors some manufacturers prefer 6 pole or even 8 pole speeds for motors over 1000 kW.3.1. Choice of Single or Multiple DriveHaving calculated the power required to drive the belt and having considered the belt tension and angle of contact, a decision can be taken on whether the belt should be fitted with single or multiple drive.This decision is often influenced by other equipment installed in a plant and multiples of other smaller drives are often used. Drive size may also be determined by the nearest standard motor available. Where a drive point is situated some considerable distance from the main power source, a long cable may be involved to supply electric power to the drive. In this case, the cable size and cost of transformers may play an important part in the selection of number and size of motors used. With direct on line starting, the peak current the motor will draw is likely to be of the order of 6 x full load current and the combination of running current of a motor or group of motors with the starting current of the last motor to start will have a strong influence on the drive choice.3.2. Method of Low Speed Shaft ConnectionsDrive from the reducer to the belt pulley shaft is either by "flexible" coupling from adrive pack mounted on a foundation next to the structure or by shaft mounted drive unit hanging on the pulley shaft. When shaft mounted, the drive unit can be either hollow shaft, driving through a friction locking element or solid shaft attached by a rigid coupling to the conveyor shaft. Some typical attachments are shown in the sketches. (See appendix A).4.1. Choice of Starting method, drive size and ProtectionDuring start up of conveyor belts, a considerable mass is usually involved which requires acceleration, and to reduce the length of time that the motor draws starting current, a "slip coupling" is fitted between the drive motor and speed reducer. Alternatively,slip ring motors are used to achieve a quick but gentle start up with control of the peak current. On small belts below 10kW direct on line starting directly coupled is quite normal and on belts, say below 100 kW D.O.L. starting with "slip" couplings is most common, and probably the simplest and most cost effective. On larger drives with power at its present continuously increasing cost, slip ring motors may be attractive, due to the prevention of the peak, particularly where maximum demand plays a part in the electricity tariff.There is a multitude of slip couplings on the market for use with D.O.L. start motors, but for larger belts the majority in use are liquid type couplings, either straight traction or traction with delayed fill or controllable fill (scoop type). A fluid coupling will always "slip" a small amount and will help multiple drives to share load, provided the coupling "fill" has been carefully adjusted. As a rule, each coupling has a slightly different characteristic and if adjusted to share load correctly under full load conditions will more than likely not share properly under light load conditions. Motor characteristics also vary a little and can also contribute to poor load sharing on multiple drives. Drive systems commonly go up to 4 motors per belt, but rarely more.4.2. Motor Starting: (D.O.L. with fluid coupling)On multiple drives accepted practice is to start the motor on the secondary drive firstand say 3-5 seconds later one of the primary drive motors and then the next primary motor say 5-10 seconds later.In practice, however, the observed starting procedures and delay times vary a great deal. A very common sight is to see the secondary drive motor running and due to conservative coupling selection, the starting current drops somewhat, but starts rising quickly again due to the delayed fill coupling increasing it's slip torque, while the belt remains stationary. If a primary drive is started at the correct time before the coupling torque has increased too far, the belt is brought into motion much quicker with a lower overall current. The relative slip of the coupling affects it's torque and so the motor current, and the sooner the belt can be moved, the sooner the current peaks will drop.In the case of scoop controlled fluid couplings all motors are started in quick succession and then all couplings filled slowly. A similar procedure is followed with slip ring motors and these two methods are undoubtedly the kindest to the belt, pulley and lagging etc.The choice of scoop type fluid couplings or slip ring motors is likely to lead to the use of smaller motors with safety and possible savings on switch gear maintenance.4.3. Other Drive MethodsWhere a variable conveying rate is required, D.C. drives can be used as well as squirrel cage motors with frequency control. Another method is by hydro-static drive; again ideal for variable speed, but overall running and maintenance costson big powers are likely to be higher than a fluid coupling drive, with S.C. motoror slip ring motor.4.4. Belt ProtectionBelt protection against overload and stalling is commonly done by a centrifugal switch driven by a roller on the underside of the belt. This, however, is not very sensitive and more sophisticated methods are now used.One method consists of fitting a pulse generator to the drive gearbox low speed shaft and similar pulse generator to a roller driven by the belt. A monitoring unit compares the pulse frequencies continuously and if they go outside set limits, an alarm is given or the belt stopped. On start up, belt slip can be kept to a minimum by using the monitoring unit to control the start up on slipring motors. The monitoring unit can control the rotor resistance and so the starting torque. Alternatively, the "fill" of a variable fill fluid coupling can be controlled by the comparitor.5. Stopping a Belt Conveyor5.1. Forward stoppingAs a general rule, friction will reduce the normal forward speed of the belt and load and bring it to rest in a relatively short time. The allowable time for stopping depends mainly on the discharge end conditions. Where one belt feeds onto another, tripping conditions, transfer bunker size and belt layout may indicate a need for a belt to be slowed down by other methods than normal friction.On a downhill section of a conveyor discharging onto a level or uphill belt is generally the place where braking is required. If one belt runs on longer than the rest of a system of conveyors, bunkers or transfer chutes can be overloaded and may even be a hazard, but this is generally a very rare condition.Considering a conveyor layout as per sketch (see appendix B) fitted with a brake on the gearbox high speed shaft, it can be seen that when stopped under load the inertiaof the load would tend to pick up the gravity tensioner and release the tension in the belt between drive and head pulley and may even go slack by the time the load comes to rest. The load assisted by the gravity take up would then accelerate the belt in the return direction while the drives are stationery with brakes on. When the belt between drive and head pulley becomes tight it has to retard the load in a fraction of the distance in which it had been accelerated. Under this sudden stopping of the load the drive is subjected to heavy shock. In this case, a brake is not only unnecessary, but highly undesirable.A brake fitted on a downhill belt drive would again release tension between drive and head pulley and pick up the take up, but this would tend to release tension on the driving (or stopping) pulleys and allow the belt to slip. This can damage the belt and pulley lagging and can also be dangerous. The proper method of stopping a belt like this is on the tail pulley or other pulley on the return belt after it leaves the take up. Another application where brakes are sometimes used is on belts running through a mobile stacker, to reduce the risk of the belt snagging; should the stacker be moved while the belt is stationary. Here again a brake would be fitted to the tail pulley and a holdback to the drive or head.。
