有关机械专业的英语自我介绍

第一篇：有关机械专业的英语自我介绍

Good afternoon!

It is really my honor to have this opportunity for an interview,I hope i can make a good performance today.I'm confident that I can succeed.Now i will introduce myself briefly

My name is XXX,I am 22 years old.I am from guangxi province.I will be graduated from Guangxi university of technology.My major is Mechanical Engineering and Automation.I think I'm a good team player and I'm a person of great honesty to others.Also I am able to work under great pressure.I have solid basic knowledge of machinery and skilled use of AtuoCAD, UG software, such as two-dimensional drawing and three-dimensional design.andI have passed CET4 and National computer rank examination certificate2 C.In June of last year, held in Nanning, I have won first prize in the National Mechanical Design and Innovation Competition ofGuangxi.I hope I can engage in the work of PCB, and I can work hard, thank you for giving me this opportunity to talk about these, and this is all I said.Thank you.下午好！

这真的是我的荣幸有这个机会进行面试，我希望我能有一个好的表现今天。我相信我能成功。

现在，我将简要地介绍一下自己

我的名字是XXX，今年22岁了，来从广西.我即将毕业于广西工学院。我的专业是机械工程及自动化。

我觉得我是一个有良好团队精神的人，对待别人我非常诚恳。同时，我也很能承受工作压力。

我有扎实的机械基础知识以及能熟练使用AtuoCAD，UG软件进行二维绘图和三维设计。我已经通过大学英语四级考试和全国计算机等级考试 C 二级。

去年六月，在南宁举行，我获得了全国机械创新设计大赛广西赛区一等奖。我希望我能从事PCB方面的工作，我会努力工作，谢谢你给我这个机会谈谈这些，我说完了，谢谢。

第二篇：机械专业英语

机械专业英语杨亚炬 20100334506

机电103班

考虑磨削力的磁悬浮磨床电主轴转子系统动态特性分析

摘要:以电磁轴承支承的磨床也主轴为研究对象，建立了转子的弹性支承模型，对其进行了模态分析，得出转子固有频率随支承刚度变化的规律;对施加磨削力时转子的稳态响应特性进行了分析，根据危险界面的节点位移，初步确定了主轴系统的稳定性。

关键词:电磁轴承支承系统;磨床电主轴;模态分析;稳态响应特性 引言

电磁轴承具有无摩擦、元磨损、高速度、高精度及可长期免维护等优点，因此被广泛应用于高速旋转类机械中。采用电磁轴承支承的磨床电主轴是典型的机电一体化系统，由于磨削过程的复杂性，其支承主轴系统的影响与其他轴承相比更为突出[1 刀。转子的动态特性是电磁轴承支承特性与转子结构动力学特性综合作用的结果。在对转子实施控制之前，研究转子本身的动力学行为对控制系统的设计是很重要的时。本文以某电磁轴承支承的磨床电主轴为研究对象，建立了转子的弹性支承模型，对其进行了模态分析和施加磨削力时的稳态响应特性分析。轴、砂轮连接杆、前后径向轴颈套、前后平衡环、止推盘和隔磁环等组成，其他部件与转轴之间采用过盈连接。

转子总重5.90kg，总长507mm，稳定悬浮时转子和径向轴承之间的间隙为0.2mm，轴向轴承

1.砂轮2 传感器3.前辅助轴承4.前径向轴承5.转轴6.轴向轴承7.冷却水套

8.电机部分9.后径向轴承10.后辅助轴承间隙为0.3mm。建立有限元模型

电磁轴承支承为典型的弹性支承，有限元分析模型采用16 个弹簧单元模拟径向电磁轴承的16 个磁极。止推盘两侧分别采用8 个弹簧转轴 根据转子的结构形式，用ANSYS 建立起转子的实体有限元分析模型，模态分析

支承刚度对转子固有频率的影晌根据转子的有限元分析模型，用ANSYS 对其进行模态分析[5J。忽略弹簧单元的阻尼，支承刚度在5X106~lXI09N/m 范围内变化阶模态，得到转子的正进动固有频率和负进动固有频率，进一步研究临界转速时，首先剔除负进动固有频率[6J。可以得到转轴前四阶固有频率随刚度变化曲线,转子的正进动固有频率随支承刚度的增大而增大，且转子的低阶固有频率随支承刚度增加的幅度较大。当支承刚度增大到1.6X10 8 N/m 时，转子的2~4 阶固有频率已无多

模态分析完毕后，将磨削激振力施加于砂轮 处进行谐响应分析，在砂轮外圆节点7746 处施加Y 方向力(实部为88.328N、虚部为1.9737N)和Z 方向力(实部为1.9737N、虚部为88.328N)，这样磨削力为一简谐力。COMBIN14 单元的刚度取2.0X10 7 N/m，为分析转子在高频段的响应，将激振力的频率范围扩大至0~1600Hz，分20 个载荷步进行谐响应分析。

当主轴工作在30000r/ min(对应额定工作频率500.0Hz)、48 OOOr/ min(对应最高工作频率800.OHz)，即转速处于一阶与二阶临界转速之间时，由转子的二阶振型(图5)可以看出，转子在砂轮、前保护轴承、前径向轴承和后径向轴承处的中心截面为危险截面。图7~ 图10 分别为砂轮、前保护轴承、前径向轴承和后

径向轴承处的振动幅值一频率响应后径向轴承处节点4484 振动幅值一频率响应曲线移增大幅值在一阶固有频率处最小，二阶固有频率处最大，三阶固有频率处次之。

磨床电主轴的结构参数如下:转子与前后保护轴承的间隙为O.lmm，与前后径向轴承的间隙为0.2mm。由表3 可知，当激振力频率达到转子一阶、三阶固有频率时，转子产生的共振位移在转曲线，在有限元模型上分别对应节点7746、7818、7559 和4484 的振动幅值频率响应。各危险截面的节点Y 方向位移如表3 所示。当激振力频率达到转子的固有频率时，转子的位移(振动幅值)会突然增大，通过前三阶的幅频响应曲线可以看出，转子位子间隙范围之内;但达到转子二阶固有频率时，转子产生的共振位移会超出间隙要求，使得转子与轴承碰撞，发生危险，因此应避免激振力频率达到转子的二阶固有频率。由转子的二阶振型可以看出，转子在后保护轴承处的径向位移小于后径向轴承处的径向位移，故可判定后保护轴承处在Y 方向的位移小于

2.0 X 10 一7 m。各危险截面的节点位移均在间隙范围内，因此可初步判定转子在额定转速和最高

转速下工作时，给其施加Fn = 88.328N、Ft =1.9737N 的磨削力，可稳定工作。结论

(1)完全弹性支承下，电主轴转子固有频率的总体变化趋势随支承刚度的增大而增大，并且在支承刚度较低时，固有频率随支承刚度的变化较大。当支承刚度到达一定值时，转子的前四阶固有频率趋于稳定，在设计控制系统时可控制轴承的刚度高于此值，以便转子具有稳定的临界转速。

(2)在施加了磨削激振力后，通过幅值频率响应分析确定了几个危险界面的节点位移，可初步判断主轴系统的稳定性。

Dynamic Analysis for Electric Spindle Rotor System of Magnetic Levitation Grinder

Considering Grinding Force

Abstract: This paper bui1t an elastic bearing model for the rotor of grinder electric spindlesupported by electromagnet bearing and analyzed the mode of the rotor , educed the laws about therotor inherent frequencies changing along with bearing stiffness.Then, it analyzed steady stateresponse characteristics of the rotor while applying grinding force.According to the nodedisplacements of danger interface ,stability of spindle system is ensured initially.Key words: supporting system of electromagnet bearing;grinder electric spindle;mode analysis;steady state response characteristics.Introduction

Electromagnetic bearings with no friction, wear yuan, high-speed, high precision and long-term maintenance-free, etc., it is widely used in high-speed rotating machinery.The electromagnetic bearing grinder electric spindle is a typical mechatronic systems, due to the complexity of the grinding process, the supporting spindle system compared with other bearing more prominent [1 knife.The dynamic characteristics of the rotor the electromagnetic bearing characteristics and rotor structure dynamics combined result.Before control of the rotor embodiment, the study rotor dynamic behavior of the control system design is very important.An electromagnetic bearing grinder electric spindle rotor elastic support model, its modal analysis and steady-state response characteristics in the grinding force is applied.Shaft, wheel connecting rod, front and rear radial journal cover, front and rear stabilizer ring, thrust plate, and every other magnetic interference connection between the other components and the shaft.The rotor total weight of 5.90kg, Total length 507mm, stable suspension of the rotor and the radial bearing gap of 0.2mm, and the axial bearingwheel sensor 3.Former auxiliary bearing front radial bearing 5.Shaft axial bearing cooling water jacket motor section 9 after radial bearing 10 after the auxiliary bearing clearance of 0.3 mm.Finite element model

The electromagnetic bearing the typical elastic support, finite element analysis model with 16 spring element to simulate the radial magnetic bearing 16 pole.On both sides of the thrust plate 8 spring pivot

Established with ANSYS based on the structure of the rotor, the rotor solid finite element analysis model, Modal Analysis Support stiffness IMPACT natural frequency

of the rotor based on the finite element analysis model of the rotor, modal analysis using ANSYS its [5J.The damping of the spring element is ignored, the the support stiffness 5X106 ~ lXI09N / m range order modal rotor is precession natural frequencies and negative precession natural frequency, further study of the critical speed, the first natural frequency [excluding the negative precession 6J.Can get the shaft first four natural frequency of the curve with the change in stiffness of the rotor is precession natural frequency with the support stiffness increases, and the rate of increase of the low-order natural frequency of the rotor with the bearing stiffness.The 2-4 order natural frequency of the rotor Found when the supporting stiffness increases to 1.6X10 8 N / m,Modal analysis after grinding exciting force is applied at the wheel at the harmonic response analysis, the Y direction of the force applied to the wheel outer node 7746(88 328N real part, imaginary part 1 9737N), and Z directions force(the real part of 9737N, the imaginary part of the 88 328N), so that the grinding force of a simple harmonic force.COMBIN14 element stiffness take 2.0x10 7 N / m for the analysis of the response of the rotor at high frequencies, the frequency range of the excitationforce is expanded to 0 to 1600Hz, 20 load step harmonic response analysis.Spindle 30000r / min(corresponding to the nominal operating frequency 500.0Hz), of 48 OOOr / min(corresponding to the maximum operating frequency of 800 OHZ)that speed in the first-order and second-order critical speed, the second rotor vibration type(Figure 5)can be seen, the rotor wheel, the front protective bearings, the radial bearing and the rear radial bearing at the center of a sectional view of the dangerous section.Figures 7 to 10 respectively for the wheel, the front protective bearings, the front radial bearing and a radial bearing at a frequency response of the vibration amplitude of the vibration amplitude of the radial bearing at the node 4484 frequency response curve shift increased amplitude in a The natural frequencies at the minimum, followed by the natural frequency of the second-order, third-order natural frequency.Of Grinder Spindle structure parameters are as follows: rotor protection before and after bearing clearance O.lmm the front and rear radial bearing clearance of 0.2 mm.Seen from Table 3, when the frequency of the excitation force to the rotor-order, third-order natural frequency, the resonance generated by the rotor displacement in the transfer curve in the finite element model, respectively corresponding to the nodes 7746, 7818, 7559 and 4484, the amplitude of vibration frequency response.The nodes in the Y direction of the dangerous section of the displacement shown in Table 3.When the frequency of the excitation force is reached when the natural frequency of the rotor, the rotor displacement(vibration amplitude)will suddenly increases, frequency response curve of the web through the first three can be seen, within the scope of the clearance of the rotor charts;but reached rotor Second Order natural frequency of the rotor of the resonance displacement will exceed the spacing requirements, so that the rotor and the bearing collision danger, the second natural frequency of the exciting force the frequency of the rotor should therefore be avoided.By the second-order vibration of the rotor can be seen, the radial displacement of the rotor after protection of the radial displacement of the bearing

is less than the radial bearing at the displacement of the bearings in the Y direction, it can be determined after protection Smaller

2.0 X 10 a m.Of the dangerous section of the nodal displacements gap preliminary determination rotor at rated speed and maximum

Speed work when applied to its Fn = 88.328N FT = 9737N grinding force can work stably.Conclusions

(1)fully resilient support, the overall trend of the natural frequency of the electro-spindle rotor with bearing stiffness increases, and the supporting rigidity is low, the larger the change of the natural frequency with the support stiffness.When the supporting rigidity reaches a certain value, the first four natural frequencies of the rotor is stabilized in the design of the control system can control the stiffness of the bearing is higher than this value, the stability of the critical speed for the rotor having.(2)In the grinding exciting force is applied by the amplitude frequency response analysis identified several risk interface nodal displacements can determine the initial stability of the spindle system.

第三篇：专业英语 自我介绍

英文自我介绍

Good afternoon everyone, It is really a great honor for me to

introduce myself.Firstly, My name is pengcheng.As you know, I am from Shandong province whose capital is jinan.Two years ago, in order to become a good doctor, I came to the Capital Medical UniverCity and recognized most of the people here.In the past two years, I had spent a great time in the campus and learned a lot of knowledge.Two years later, we meet again in the fuxing hospital and recognize some new students.I am enthusiastic and responsible in my Life, but sometimes I will be a little childish.My favorite game is F1.its speed makes my blood boil.My favorite star is Fernando Alonso who is an F1 driver

In the next two years, as your classmate, I hope to be able to get along well with everyone and keep in touch forever.As the student in charge of studies ,I hope that I can provide valuable information and help, I hope everyone can pass through the final exam.If this moment comes, I will say

第四篇：专业英语自我介绍

今天，我有幸得到这个机会站在这里，这是我自己一直以来的愿望，我希望到贵校继续深造，为我的梦想增加一个台阶，为我的成功迈进重要的一步。

各位教授，下午好：很高兴有机会能参加这次面试和各位教授交流。首先，我简洁地介绍一下自己，我叫宋孝方，今年25岁，来自河南商丘，2008年毕业于河南理工大学机械与动力工程学院，所学的专业是工业设计，其次，我想谈一下我四年的大学生活，让我学到了很多，很多的实践让我从从各个方面提高了自己，不但让我学会了如何思考，学习的方法，还让我看到了实践的重要性，作为一名学生，我深知学习机会的不易，我学习很努力，其中3年拿了学校的奖学金，我还积极地参加各种活动和设计大赛，曾在河南理工大学首届和第二届青少年科技文化节中分别荣获“摄影大赛优秀奖”和“节徽设计大赛二等奖”。在2007年中的“张江杯”设计大赛中工业设计类中设计的笔记本电脑荣获优秀奖。在大学中我也遇到了好的老

师和朋友，从他们身上我学到了很多东西，这对我能力的提高和成长起了很大的作用。最后，我想谈一下，我考研的原因和研究的方向，我喜欢做设计，当看着自己的创意和产品得到别人认可的时候是一件无比兴奋的事情；还有就是两年的工作经验让我认识到我专业知识的局限，感觉在设计方面还有很多东西要学，自己的知识和能力还远远不够，特别是在经济快速发展的今天，更需要通过系统的复习来提高自己的能力，来最大化地实现自我价值，想通过3年的学习来对工业设计有个更加深入的了解，我很喜欢学校的感觉和体现出来的学习氛围，到处充满着青春活力，有很多的机会让你去实践和尝试，让人可以深入思考和进行学术的研究。如果我有机会在这所学校学习，我计划把自己的研究方向定为工业设计，因为我发现设计在社会的发展中发挥了越来越重要的作用，特别在国家由制造业大国转变为创新型国家的时候更是如此，虽然现在中国整个社会对设计的认可还不是很高，特别是在一些中小型企业中，但是纵观一些发达国家的发展过程，不难发现，工业设计将会在社会发展起到不可替代的作用。

第五篇：机械专业英语自我介绍(最标准,屡试屡爽)

Good morning!

It is really my great honor to take this interview.Thank you very much for giving me the chance!

My name is xxx, I am 22 years old ,born in Shaaxi Province.I will graduate from Xi’an University of Technology in 2014 and I will get my bachelor degree after my graduation.My major is Mechanical engineering and Automation.During the past 3 years in the university, I spent most of my time on study, and I got two times the school scholarships, also I’ve passed CET-6 in 2011.I think I have built up a solid foundation for professional knowledge of my major, once I feel I fall behind others, I will find the reason as soon as possible and try my best to catch up with them.It is my long cherished dream to be an engineer and I will fully play my ability if I can work in Luxottica.In my spare time, I like to read books, watch movies and doing sports.Of all the sports , football is my favorite.It keeps me in good health and full of energy.Besides, I really enjoy watching English films.Because it can not only kill time, but also excise my listening skills.I know my English is not good enough, and I will continue to study and communicate with others as much as possible to practice my spoken English,In a nutshell, I love my major.And I am long for the work in this field.I’m really looking forward to get the chance to work in Luxottica.I am confident that I am qualified for the post , because I have such ability!And I will soon prove that your decision of choosing me is the wisest.That' all.Thank you for giving me the chance