外文翻译-变频调速技术在风机、泵类中的应用分析

外文翻译-变频调速技术在风机、泵类中的应用分析
外文翻译-变频调速技术在风机、泵类中的应用分析

Frequency conversion transfer speed technology application of air

blower, pump type analyze

In industrial production and processing and manufacturing industry of the products, air blower, pump apparatus are in extensive application range; Its electric energy is consumed to account for with throttle loss and safeguarding, maintenance cost such as valve, relevant apparatus of guard 7%~25% of the production cost, it is a sum of big production expenses. With the deepening constantly of economic reform, the constant aggravation of the market competition; saving energy and reducing the cost has already become and reduced the production cost, raised one of the important means of product quality.

And the frequency conversion that developed at the beginning of the eighties adjusts speed technology, it is exactly the requirement for complying with development of industrial production automation, open a brand-new intellectual electrical machinery era. Change the outmoded mode that the ordinary motor can only be operated by way of making the speed, make motor and pull load can according to produce technological requirement adjust rotational speed export on condition that needn't have any change, thus reduce the consumption of the electrical machinery and achieve the goal that the system is operated high-efficiently.

At the end of the eighties, this technology was introduced to our country and popularized. Have already got practical application in the electrical machinery transmission apparatus in many kinds of trades such as the electricity, metallurgy, petroleum, chemical industry, papermaking, food, textile now. At present, frequency conversion adjusts a main developing direction that speed technology has already become modern electric transmission technology. Remarkable adjusting speed performance, prominent result of economizing on electricity, improve the operation operating mode of the existing equipment, improve systematic safe reliability and utilization rate of equipment and installations, lengthen advantages such as the service life of apparatus, etc. and get abundant embodiment with constant enlargement of the application.

Usually used mainly in the boiler and burn occasions such as system, drying system, cooling system, ventilating system, etc. in the industrial production, apoplexy machine apparatus of processing and manufacturing industry of products, control and regulate indexes such as pressure of burner hearth, wind speed, wind amount,

temperature, etc. so as to meeting the needs of craft and operation operating mode according to the need of producing. The most frequently used control means is to regulate the air door, size of making degree of guard to adjust the controlled target. In this way, no matter the demand size of production, the air blowers should all operate at full speed, but the change of the operation operating mode makes energy consume with the throttle losses of air door, guard. In process of production, not only control the precision and is limited but also cause a large amount of energy to waste losing with the apparatus. Thus lead to the fact the production cost increases, the service life of apparatus is shortened, the plant maintenance, maintenance cost can not be ranked.

The pump apparatus has broad application space on the production field too, propose water pump station, pond store pot give system of arranging, industry water circulatory system, hot exchange system use centrifugal pump, axial-flow pump, gear wheel pump, column fill in apparatus such as the pump Moreover adopt, adjust according to different production demand valve, reflux valve, stop valve, etc. reduce expenditure apparatus carry on flow, pressure, water level control of signal often. In this way, not merely cause a large number of energy to waste, the destruction of sealing properties such as the pipeline, valve, etc.; also accelerate wearing and tearing and vapors of the pump, body of valve and lose, damage the apparatus, influence production, jeopardize product quality when being serious.

Most of air blower, pump apparatus adopt the way in which the asynchronous motor drive directly and run, store in and start the electric current greatly, machinery is assaulted, protect the bad shortcoming of the characteristic electrically. Not only influence by apparatus service life, but also not at load can twinkling of an eye movement protect by apparatus, often present the pump and damage the phenomenon that the electrical machinery is burnt too at the same time.

In recent years, for the energy-conserving urgent need and requirement for improving constantly in product quality, in addition the adoption frequency conversion governor (abbreviated as the frequency converter) is easy to use, non-maintaining and controlling the precision high, and can realize the high functional characteristic; Therefore the scheme of adopting the frequency converter and driving begins to replace the control scheme of air door, guard, valve progressively.

The basic principle of adjusting speed technology of frequency conversion is to

import the relation that frequency is directly proportional to according to rotational speed and working power of electrical machinery: n =60f (1-s) / p, (n, f, s, p show the rotational speed, input frequency, electrical machinery and transfer to difference rate, electrical machinery magnetic pole logarithm respectively in type); Achieve the goal of changing the rotational speed of the electrical machinery through changing the motor working power frequency. The frequency converter is on the basis of principle described above adopts handing in - straight - hand in the power and vary technology, electric electron, microcomputer are controlled, etc. the comprehensive electric products that technology is all over.

Can know through the hydro mechanical philosophy: Air blower, pump apparatus belong to the torque load of square, its rotational speed n and flow Q, pressure H and power P of axle have the following relations: Q ∝ n, H∝ n2, P∝ n3;

I.e., the flow is proportional to rotational speed, the pressure is proportional to the square of rotational speed, the axle power is proportional to the cube of rotational speed.

Take a water pump as an example, its export presses the head for H0 (export presses the quiet pressure difference that the head i.e. entry to the pump and pipeline exports), the specified rotational speed is n0, it is r0 that the tube when the valve is made completely hinders the characteristic, under the specified operating mode and its corresponding pressure is H1, it is Q1 to export the flow.

In controlling at the scene, usually adopt the water pump to operate and export the valve to control the flow rapidly definitely. When the flow reduces 50% to Q2 from Q1, valve turn on degree reduce, make pipe network drag characteristic turn r0 into r1, systematic operating point order, move, order along direction me from original A to B; The pressure H1 of function reduced expenditure by it turns into H2. Water pump axle power actual value can by the formula: P =Q* H/ (η c* η b) *10-3 is obtained. Among them, P, Q, H, η c, η b express the power, flow, pressure, water pump efficiency, transmission device efficiency respectively, transmit as 1 directly. Suppose the total efficiency (η c* η b) 1, water pump order, move, order work, from A to B then, consumption that electrical machinery save for AQ1OH1 and area of BQ2OH2 bad. If adopt and adjust rotational speed n that the speed means changes the water pump, when the flow is reduced from Q1 by 50% to Q2, pipe network drag characteristic the same curve r0 then, systematic operating point order, move, order

along direction II from original A to C, the operation of the water pump is also more rational. All open in the valves, there are only pipe networks.

Under the situation of resistance, the system meets the flow requirement of the scene, energy consumption certainly will be reduced. At this moment, the consumption that the electrical machinery saves is bad for the area of AQ1OH1 and CQ2OH3. Degree is regulated and the rotational speed of water pump is controlled to relatively adopt the valve to be driven, obviously use the rotational speed of the water pump to control more valid and more reasonable, have prominent energy-conserving results.

In addition, valve make systematic pressure H rise regulate, this transform to pipeline and sealing property of valve into, threaten and destroy; And when the rotational speed is regulated, the systematic pressure H will be reduced with reducing of the rotational speed n of the pump, so will not exert a bad influence on the system.

It is easy to obtain from the comparison above: When demand for the flow of the water pump is dropped from 100% to 50% at the scene, adopt the rotational speed to regulate and regulate the power size corresponding to save BCH3H2 than the original valve, the energy-conserving rate is above 75%.

Similar to this, adopt frequency conversion transfer speed technology change pump type, air blower apparatus rotational speed come, control on-the-spot pressure, temperature, water level, etc. other course control the parameter, can control the characteristic and draw out the curve of relation and obtain the comparative result described above according to the system too. Namely adopt frequency conversion transfer speed technology change electrical machinery method of rotational speed, than adopt valve, guard regulate economic for energy-conservation, the apparatus operation operating mode will be obviously improved too.

变频调速技术在风机、泵类中的应用分析

在工业生产和产品加工制造业中,风机、泵类设备应用范围广泛;其电能消耗和诸如阀门、挡板相关设备的节流损失以及维护、维修费用占到生产成本的7%~25%,是一笔不小的生产费用开支。随着经济改革的不断深入,市场竞争的不断加剧;节能降耗业已成为降低生产成本、提高产品质量的重要手段之一。

而八十年代初发展起来的变频调速技术,正是顺应了工业生产自动化发展的要求,开创了一个全新的智能电机时代。一改普通电动机只能以定速方式运行的陈旧模式,使得电动机及其拖动负载在无须任何改动的情况下即可以按照生产工艺要求调整转速输出,从而降低电机功耗达到系统高效运行的目的。

八十年代末,该技术引入我国并得到推广。现已在电力、冶金、石油、化工、造纸、食品、纺织等多种行业的电机传动设备中得到实际应用。目前,变频调速技术已经成为现代电力传动技术的一个主要发展方向。卓越的调速性能、显著的节电效果,改善现有设备的运行工况,提高系统的安全可靠性和设备利用率,延长设备使用寿命等优点随着应用领域的不断扩大而得到充分的体现。

通常在工业生产、产品加工制造业中风机设备主要用于锅炉燃烧系统、烘干系统、冷却系统、通风系统等场合,根据生产需要对炉膛压力、风速、风量、温度等指标进行控制和调节以适应工艺要求和运行工况。而最常用的控制手段则是调节风门、挡板开度的大小来调整受控对象。这样,不论生产的需求大小,风机都要全速运转,而运行工况的变化则使得能量以风门、挡板的节流损失消耗掉了。在生产过程中,不仅控制精度受到限制,而且还造成大量的能源浪费和设备损耗。从而导致生产成本增加,设备使用寿命缩短,设备维护、维修费用高居不下。

泵类设备在生产领域同样有着广阔的应用空间,提水泵站、水池储罐给排系统、工业水(油)循环系统、热交换系统均使用离心泵、轴流泵、齿轮泵、柱塞泵等设备。而且,根据不同的生产需求往往采用调整阀、回流阀、截止阀等节流设备进行流量、压力、水位等信号的控制。这样,不仅造成大量的能源浪费,管路、阀门等密封性能的破坏;还加速了泵腔、阀体的磨损和汽蚀,严重时损坏设备、影响生产、危及产品质量。

风机、泵类设备多数采用异步电动机直接驱动的方式运行,存在启动电流大、机械冲击、电气保护特性差等缺点。不仅影响设备使用寿命,而且当负载出现机械故障时不能瞬间动作保护设备,时常出现泵损坏同时电机也被烧毁的现象。

近年来,出于节能的迫切需要和对产品质量不断提高的要求,加之采用变频调速器(简称变频器)易操作、免维护、控制精度高,并可以实现高功能化等特点;因而采用变频器驱动的方案开始逐步取代风门、挡板、阀门的控制方案。

PLC控制下的电梯系统外文文献翻译、中英文翻译、外文翻译

PLC控制下的电梯系统 由继电器组成的顺序控制系统是最早的一种实现电梯控制的方法。但是,进入九十年代,随着科学技术的发展和计算机技术的广泛应用,人们对电梯的安全性、可靠性的要求越来越高,继电器控制的弱点就越来越明显。 电梯继电器控制系统故障率高,大大降低了电梯的可靠性和安全性,经常造成停梯,给乘用人员带来不便和惊忧。且电梯一旦发生冲顶或蹲底,不但会造成电梯机械部件损坏,还可能出现人身事故。 可编程序控制器(PLC)最早是根据顺序逻辑控制的需要而发展起来的,是专门为工业环境应用而设计的数字运算操作的电子装置。鉴于其种种优点,目前,电梯的继电器控制方式己逐渐被PLC控制所代替。同时,由于电机交流变频调速技术的发展,电梯的拖动方式己由原来直流调速逐渐过渡到了交流变频调速。因此,PLC控制技术加变频调速技术己成为现代电梯行业的一个热点。 1. PLC控制电梯的优点 (1)在电梯控制中采用了PLC,用软件实现对电梯运行的自动控制,可靠性大大提高。 (2)去掉了选层器及大部分继电器,控制系统结构简单,外部线路简化。 (3)PLC可实现各种复杂的控制系统,方便地增加或改变控制功能。 (4) PLC可进行故障自动检测与报警显示,提高运行安全性,并便于检修。 (5)用于群控调配和管理,并提高电梯运行效率。 (6)更改控制方案时不需改动硬件接线。 2.电梯变频调速控制的特点 随着电力电子技术、微电子技术和计算机控制技术的飞速发展,交流变频调速技术的发展也十分迅速。电动机交流变频调速技术是当今节电、改善工艺流程以提高产品质量和改善环境、推动技术进步的一种主要手段。变频调速以其优异的调速性能和起制动平稳性能、高效率、高功率因数和节电效果,广泛的适用范围及其它许多优点而被国内外公认为最有发展前途的调速方式 交流变频调速电梯的特点 ⑴能源消耗低 ⑵电路负载低,所需紧急供电装置小 在加速阶段,所需起动电流小于2.5倍的额定电流。且起动电流峰值时间短。由于起动电流大幅度减小,故功耗和供电缆线直径可减小很多。所需的紧急供电

电子信息工程专业课程翻译中英文对照表

电子信息工程专业课程名称中英文翻译对照 (2009级培养计划)

实践环节翻译

高等数学Advanced Mathematics 大学物理College Physics 线性代数Linear Algebra 复变函数与积分变换Functions of Complex Variable and Integral Transforms 概率论与随机过程Probability and Random Process 物理实验Experiments of College Physics 数理方程Equations of Mathematical Physics 电子信息工程概论Introduction to Electronic and Information Engineering 计算机应用基础Fundamentals of Computer Application 电路原理Principles of Circuit 模拟电子技术基础Fundamentals of Analog Electronics 数字电子技术基础Fundamentals of Digital Electronics C语言程序设计The C Programming Language 信息论基础Fundamentals of Information Theory 信号与线性系统Signals and Linear Systems 微机原理与接口技术Microcomputer Principles and Interface Technology 马克思主义基本原理Fundamentals of Marxism 毛泽东思想、邓小平理论 和“三个代表”重要思想 概论 Thoughts of Mao and Deng 中国近现代史纲要Modern Chinese History 思想道德修养与法律基 础 Moral Education & Law Basis 形势与政策Situation and Policy 英语College English 体育Physical Education 当代世界经济与政治Modern Global Economy and Politics 卫生健康教育Health Education 心理健康知识讲座Psychological Health Knowledge Lecture 公共艺术课程Public Arts 文献检索Literature Retrieval 军事理论Military Theory 普通话语音常识及训练Mandarin Knowledge and Training 大学生职业生涯策划 (就业指导) Career Planning (Guidance of Employment ) 专题学术讲座Optional Course Lecture 科技文献写作Sci-tech Document Writing 高频电子线路High-Frequency Electronic Circuits 通信原理Communications Theory 数字信号处理Digital Signal Processing 计算机网络Computer Networks 电磁场与微波技术Electromagnetic Field and Microwave

ASP外文翻译原文

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毕业设计外文翻译原文.

Optimum blank design of an automobile sub-frame Jong-Yop Kim a ,Naksoo Kim a,*,Man-Sung Huh b a Department of Mechanical Engineering,Sogang University,Shinsu-dong 1,Mapo-ku,Seoul 121-742,South Korea b Hwa-shin Corporation,Young-chun,Kyung-buk,770-140,South Korea Received 17July 1998 Abstract A roll-back method is proposed to predict the optimum initial blank shape in the sheet metal forming process.The method takes the difference between the ?nal deformed shape and the target contour shape into account.Based on the method,a computer program composed of a blank design module,an FE-analysis program and a mesh generation module is developed.The roll-back method is applied to the drawing of a square cup with the ˉange of uniform size around its periphery,to con?rm its validity.Good agreement is recognized between the numerical results and the published results for initial blank shape and thickness strain distribution.The optimum blank shapes for two parts of an automobile sub-frame are designed.Both the thickness distribution and the level of punch load are improved with the designed blank.Also,the method is applied to design the weld line in a tailor-welded blank.It is concluded that the roll-back method is an effective and convenient method for an optimum blank shape design.#2000Elsevier Science S.A.All rights reserved. Keywords:Blank design;Sheet metal forming;Finite element method;Roll-back method

风机测试方案

通风机安全检测检验方案 山西公信安全技术有限公司 二〇一八年六月二十一日

通风机安全检测检验方案 为搞好通风管理、确保通风机装置安全、经济运行提供科学的依据,依据《煤矿在用主通风机系统安全检测检验规范》AQ1011-2005的规定要求,山西公信安全技术有限公司受炭窑坪煤业有限公司委托对该矿主通风机不同角度(+2.5,-2.5,0,+5,-5)进行安全检测检验。经现场查看和矿方对检测检验的要求,制订本方案。 一、确定通风网络的组成 本次通风机安全检测检验是在由防爆门、回风井、风硐、通风机、扩散器等部分组成可供调节的通风网络。 二、检测项目及测点布置 1.风压 利用风机现有静压测孔,接上矿井通风参数测定仪,直接测定各调节点的相对静压值。 位置:风机集流器处 形状:圆形 2.风量测定 在扩散器风流出口处安装智能测试风杯,测量风速。 3.电气参数 在主通风机电控柜的二次测线路中接入电动机经济运行测试仪,测取电动机的输入功率、电压、电流、功率因数等电气参数。 4.空气密度 用矿井通风参数仪测定风机房阴凉处的大气压力,用温湿度计在

风流出口处测取风流的温湿度,计算各调节工况点空气密度。 5.噪声 在距离通风机扩散器45°方向的3.4m处、离地高度1m处用声级计测取扩散器的A声级噪声。距通风机电机外壳1m外测量机壳辐射噪声。 6.转速 参照额定转速。 7.振动 用便携式测振仪在通风机直接与坚硬基础紧固连接处测量风机的振动。 8.轴承温度 利用矿方现有传感器直接读取数值。 9. 叶片径向间隙 用塞尺在主通风机叶片与机壳(或保护圈)的间隙处测量该间隙值。 三、测定条件 1.装置完好条件: ①测定前应检查通风机、电动机各零部件是否齐全,装配是否紧固,运行是否正常,备用风机确保在10分钟内启动,以保障在测定过程中通风机能安全运行。 ②通风机进风口或出风口至风量、风压测定断面之间应无明显漏风,以确保测定工作的准确性。

伺服电机外文文献翻译

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外文翻译原文

204/JOURNAL OF BRIDGE ENGINEERING/AUGUST1999

JOURNAL OF BRIDGE ENGINEERING /AUGUST 1999/205 ends.The stress state in each cylindrical strip was determined from the total potential energy of a nonlinear arch model using the Rayleigh-Ritz method. It was emphasized that the membrane stresses in the com-pression region of the curved models were less than those predicted by linear theory and that there was an accompanying increase in ?ange resultant force.The maximum web bending stress was shown to occur at 0.20h from the compression ?ange for the simple support stiffness condition and 0.24h for the ?xed condition,where h is the height of the analytical panel.It was noted that 0.20h would be the optimum position for longitudinal stiffeners in curved girders,which is the same as for straight girders based on stability requirements.From the ?xed condition cases it was determined that there was no signi?cant change in the membrane stresses (from free to ?xed)but that there was a signi?cant effect on the web bend-ing stresses.Numerical results were generated for the reduc-tion in effective moment required to produce initial yield in the ?anges based on curvature and web slenderness for a panel aspect ratio of 1.0and a web-to-?ange area ratio of 2.0.From the results,a maximum reduction of about 13%was noted for a /R =0.167and about 8%for a /R =0.10(h /t w =150),both of which would correspond to extreme curvature,where a is the length of the analytical panel (modeling the distance be-tween transverse stiffeners)and R is the radius of curvature.To apply the parametric results to developing design criteria for practical curved girders,the de?ections and web bending stresses that would occur for girders with a curvature corre-sponding to the initial imperfection out-of-?atness limit of D /120was used.It was noted that,for a panel with an aspect ratio of 1.0,this would correspond to a curvature of a /R =0.067.The values of moment reduction using this approach were compared with those presented by Basler (Basler and Thurlimann 1961;Vincent 1969).Numerical results based on this limit were generated,and the following web-slenderness requirement was derived: 2 D 36,500a a =1?8.6?34 (1) ? ??? t R R F w ?y where D =unsupported distance between ?anges;and F y =yield stress in psi. An extension of this work was published a year later,when Culver et al.(1973)checked the accuracy of the isolated elas-tically supported cylindrical strips by treating the panel as a unit two-way shell rather than as individual strips.The ?ange/web boundaries were modeled as ?xed,and the boundaries at the transverse stiffeners were modeled as ?xed and simple.Longitudinal stiffeners were modeled with moments of inertias as multiples of the AASHO (Standard 1969)values for straight https://www.360docs.net/doc/f611162958.html,ing analytical results obtained for the slenderness required to limit the plate bending stresses in the curved panel to those of a ?at panel with the maximum allowed out-of-?atness (a /R =0.067)and with D /t w =330,the following equa-tion was developed for curved plate girder web slenderness with one longitudinal stiffener: D 46,000a a =1?2.9 ?2.2 (2) ? ? ? t R f R w ?b where the calculated bending stress,f b ,is in psi.It was further concluded that if longitudinal stiffeners are located in both the tension and compression regions,the reduction in D /t w will not be required.For the case of two stiffeners,web bending in both regions is reduced and the web slenderness could be de-signed as a straight girder panel.Eq.(1)is currently used in the ‘‘Load Factor Design’’portion of the Guide Speci?cations ,and (2)is used in the ‘‘Allowable Stress Design’’portion for girders stiffened with one longitudinal stiffener.This work was continued by Mariani et al.(1973),where the optimum trans-verse stiffener rigidity was determined analytically. During almost the same time,Abdel-Sayed (1973)studied the prebuckling and elastic buckling behavior of curved web panels and proposed approximate conservative equations for estimating the critical load under pure normal loading (stress),pure shear,and combined normal and shear loading.The linear theory of shells was used.The panel was simply supported along all four edges with no torsional rigidity of the ?anges provided.The transverse stiffeners were therefore assumed to be rigid in their directions (no strains could be developed along the edges of the panels).The Galerkin method was used to solve the governing differential equations,and minimum eigenvalues of the critical load were calculated and presented for a wide range of loading conditions (bedding,shear,and combined),aspect ratios,and curvatures.For all cases,it was demonstrated that the critical load is higher for curved panels over the comparable ?at panel and increases with an increase in curvature. In 1980,Daniels et al.summarized the Lehigh University ?ve-year experimental research program on the fatigue behav-ior of horizontally curved bridges and concluded that the slen-derness limits suggested by Culver were too severe.Equations for ‘‘Load Factor Design’’and for ‘‘Allowable Stress Design’’were developed (respectively)as D 36,500a =1?4?192(3)? ?t R F w ?y D 23,000a =1?4 ?170 (4) ? ? t R f w ?b The latter equation is currently used in the ‘‘Allowable Stress Design’’portion of the Guide Speci?cations for girders not stiffened longitudinally. Numerous analytical and experimental works on the subject have also been published by Japanese researchers since the end of the CURT project.Mikami and colleagues presented work in Japanese journals (Mikami et al.1980;Mikami and Furunishi 1981)and later in the ASCE Journal of Engineering Mechanics (Mikami and Furunishi 1984)on the nonlinear be-havior of cylindrical web panels under bending and combined bending and shear.They analyzed the cylindrical panels based on Washizu’s (1975)nonlinear theory of shells.The governing nonlinear differential equations were solved numerically by the ?nite-difference method.Simple support boundary condi-tions were assumed along the curved boundaries (top and bot-tom at the ?ange locations)and both simple and ?xed support conditions were used at the straight (vertical)boundaries.The large displacement behavior was demonstrated by Mi-kami and Furunishi for a range of geometric properties.Nu-merical values of the load,de?ection,membrane stress,bend-ing stress,and torsional stress were obtained,but no equations for design use were presented.Signi?cant conclusions include that:(1)the compressive membrane stress in the circumfer-ential direction decreases with an increase in curvature;(2)the panel under combined bending and shear exhibits a lower level of the circumferential membrane stress as compared with the panel under pure bending,and as a result,the bending moment carried by the web panel is reduced;and (3)the plate bending stress under combined bending and shear is larger than that under pure bending.No formulations or recommendations for direct design use were made. Kuranishi and Hiwatashi (1981,1983)used the ?nite-ele-ment method to demonstrate the elastic ?nite displacement be-havior of curved I-girder webs under bending using models with and without ?ange rigidities.Rotation was not allowed (?xed condition)about the vertical axis at the ends of the panel (transverse stiffener locations).Again,the nonlinear distribu-

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