第一篇：有關機械專業的英語自我介紹

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！

這真的是我的榮幸有這個機會進行面試，我希望我能有一個好的表現今天。我相信我能成功。

現在，我將簡要地介紹一下自己

我的名字是XXX，今年22歲了，來從廣西.我即將畢業于廣西工學院。我的專業是機械工程及自動化。

我覺得我是一個有良好團隊精神的人，對待別人我非常誠懇。同時，我也很能承受工作壓力。

我有扎實的機械基礎知識以及能熟練使用AtuoCAD，UG軟件進行二維繪圖和三維設計。我已經通過大學英語四級考試和全國計算機等級考試 C 二級。

去年六月，在南寧舉行，我獲得了全國機械創新設計大賽廣西賽區一等獎。我希望我能從事PCB方面的工作，我會努力工作，謝謝你給我這個機會談談這些，我說完了，謝謝。

第二篇：機械專業英語

機械專業英語楊亞炬 20100334506

機電103班

考慮磨削力的磁懸浮磨床電主軸轉子系統動態特性分析

摘要:以電磁軸承支承的磨床也主軸為研究對象，建立了轉子的彈性支承模型，對其進行了模態分析，得出轉子固有頻率隨支承剛度變化的規律;對施加磨削力時轉子的穩態響應特性進行了分析，根據危險界面的節點位移，初步確定了主軸系統的穩定性。

關鍵詞:電磁軸承支承系統;磨床電主軸;模態分析;穩態響應特性 引言

電磁軸承具有無摩擦、元磨損、高速度、高精度及可長期免維護等優點，因此被廣泛應用于高速旋轉類機械中。采用電磁軸承支承的磨床電主軸是典型的機電一體化系統，由于磨削過程的復雜性，其支承主軸系統的影響與其他軸承相比更為突出[1 刀。轉子的動態特性是電磁軸承支承特性與轉子結構動力學特性綜合作用的結果。在對轉子實施控制之前，研究轉子本身的動力學行為對控制系統的設計是很重要的時。本文以某電磁軸承支承的磨床電主軸為研究對象，建立了轉子的彈性支承模型，對其進行了模態分析和施加磨削力時的穩態響應特性分析。軸、砂輪連接桿、前后徑向軸頸套、前后平衡環、止推盤和隔磁環等組成，其他部件與轉軸之間采用過盈連接。

轉子總重5.90kg，總長507mm，穩定懸浮時轉子和徑向軸承之間的間隙為0.2mm，軸向軸承

1.砂輪2 傳感器3.前輔助軸承4.前徑向軸承5.轉軸6.軸向軸承7.冷卻水套

8.電機部分9.后徑向軸承10.后輔助軸承間隙為0.3mm。建立有限元模型

電磁軸承支承為典型的彈性支承，有限元分析模型采用16 個彈簧單元模擬徑向電磁軸承的16 個磁極。止推盤兩側分別采用8 個彈簧轉軸 根據轉子的結構形式，用ANSYS 建立起轉子的實體有限元分析模型，模態分析

支承剛度對轉子固有頻率的影晌根據轉子的有限元分析模型，用ANSYS 對其進行模態分析[5J。忽略彈簧單元的阻尼，支承剛度在5X106~lXI09N/m 范圍內變化階模態，得到轉子的正進動固有頻率和負進動固有頻率，進一步研究臨界轉速時，首先剔除負進動固有頻率[6J?？梢缘玫睫D軸前四階固有頻率隨剛度變化曲線,轉子的正進動固有頻率隨支承剛度的增大而增大，且轉子的低階固有頻率隨支承剛度增加的幅度較大。當支承剛度增大到1.6X10 8 N/m 時，轉子的2~4 階固有頻率已無多

模態分析完畢后，將磨削激振力施加于砂輪 處進行諧響應分析，在砂輪外圓節點7746 處施加Y 方向力(實部為88.328N、虛部為1.9737N)和Z 方向力(實部為1.9737N、虛部為88.328N)，這樣磨削力為一簡諧力。COMBIN14 單元的剛度取2.0X10 7 N/m，為分析轉子在高頻段的響應，將激振力的頻率范圍擴大至0~1600Hz，分20 個載荷步進行諧響應分析。

當主軸工作在30000r/ min(對應額定工作頻率500.0Hz)、48 OOOr/ min(對應最高工作頻率800.OHz)，即轉速處于一階與二階臨界轉速之間時，由轉子的二階振型(圖5)可以看出，轉子在砂輪、前保護軸承、前徑向軸承和后徑向軸承處的中心截面為危險截面。圖7~ 圖10 分別為砂輪、前保護軸承、前徑向軸承和后

徑向軸承處的振動幅值一頻率響應后徑向軸承處節點4484 振動幅值一頻率響應曲線移增大幅值在一階固有頻率處最小，二階固有頻率處最大，三階固有頻率處次之。

磨床電主軸的結構參數如下:轉子與前后保護軸承的間隙為O.lmm，與前后徑向軸承的間隙為0.2mm。由表3 可知，當激振力頻率達到轉子一階、三階固有頻率時，轉子產生的共振位移在轉曲線，在有限元模型上分別對應節點7746、7818、7559 和4484 的振動幅值頻率響應。各危險截面的節點Y 方向位移如表3 所示。當激振力頻率達到轉子的固有頻率時，轉子的位移(振動幅值)會突然增大，通過前三階的幅頻響應曲線可以看出，轉子位子間隙范圍之內;但達到轉子二階固有頻率時，轉子產生的共振位移會超出間隙要求，使得轉子與軸承碰撞，發生危險，因此應避免激振力頻率達到轉子的二階固有頻率。由轉子的二階振型可以看出，轉子在后保護軸承處的徑向位移小于后徑向軸承處的徑向位移，故可判定后保護軸承處在Y 方向的位移小于

2.0 X 10 一7 m。各危險截面的節點位移均在間隙范圍內，因此可初步判定轉子在額定轉速和最高

轉速下工作時，給其施加Fn = 88.328N、Ft =1.9737N 的磨削力，可穩定工作。結論

(1)完全彈性支承下，電主軸轉子固有頻率的總體變化趨勢隨支承剛度的增大而增大，并且在支承剛度較低時，固有頻率隨支承剛度的變化較大。當支承剛度到達一定值時，轉子的前四階固有頻率趨于穩定，在設計控制系統時可控制軸承的剛度高于此值，以便轉子具有穩定的臨界轉速。

(2)在施加了磨削激振力后，通過幅值頻率響應分析確定了幾個危險界面的節點位移，可初步判斷主軸系統的穩定性。

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：專業英語 自我介紹

英文自我介紹

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：專業英語自我介紹

今天，我有幸得到這個機會站在這里，這是我自己一直以來的愿望，我希望到貴校繼續深造，為我的夢想增加一個臺階，為我的成功邁進重要的一步。

各位教授，下午好：很高興有機會能參加這次面試和各位教授交流。首先，我簡潔地介紹一下自己，我叫宋孝方，今年25歲，來自河南商丘，2008年畢業于河南理工大學機械與動力工程學院，所學的專業是工業設計，其次，我想談一下我四年的大學生活，讓我學到了很多，很多的實踐讓我從從各個方面提高了自己，不但讓我學會了如何思考，學習的方法，還讓我看到了實踐的重要性，作為一名學生，我深知學習機會的不易，我學習很努力，其中3年拿了學校的獎學金，我還積極地參加各種活動和設計大賽，曾在河南理工大學首屆和第二屆青少年科技文化節中分別榮獲“攝影大賽優秀獎”和“節徽設計大賽二等獎”。在2007年中的“張江杯”設計大賽中工業設計類中設計的筆記本電腦榮獲優秀獎。在大學中我也遇到了好的老

師和朋友，從他們身上我學到了很多東西，這對我能力的提高和成長起了很大的作用。最后，我想談一下，我考研的原因和研究的方向，我喜歡做設計，當看著自己的創意和產品得到別人認可的時候是一件無比興奮的事情；還有就是兩年的工作經驗讓我認識到我專業知識的局限，感覺在設計方面還有很多東西要學，自己的知識和能力還遠遠不夠，特別是在經濟快速發展的今天，更需要通過系統的復習來提高自己的能力，來最大化地實現自我價值，想通過3年的學習來對工業設計有個更加深入的了解，我很喜歡學校的感覺和體現出來的學習氛圍，到處充滿著青春活力，有很多的機會讓你去實踐和嘗試，讓人可以深入思考和進行學術的研究。如果我有機會在這所學校學習，我計劃把自己的研究方向定為工業設計，因為我發現設計在社會的發展中發揮了越來越重要的作用，特別在國家由制造業大國轉變為創新型國家的時候更是如此，雖然現在中國整個社會對設計的認可還不是很高，特別是在一些中小型企業中，但是縱觀一些發達國家的發展過程，不難發現，工業設計將會在社會發展起到不可替代的作用。

第五篇：機械專業英語自我介紹(最標準,屢試屢爽)

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