管磨機(jī)的總體和結(jié)構(gòu)設(shè)計(jì) 張攀
管磨機(jī)的總體和結(jié)構(gòu)設(shè)計(jì) 張攀,管磨機(jī)的總體和結(jié)構(gòu)設(shè)計(jì),張攀,管磨機(jī),總體,整體,以及,結(jié)構(gòu)設(shè)計(jì)
畢業(yè)設(shè)計(jì)(論文)任務(wù)書
I、畢業(yè)設(shè)計(jì)(論文)題目:管磨機(jī)的總體和結(jié)構(gòu)設(shè)計(jì)
II、畢 業(yè)設(shè)計(jì)(論文)使用的原始資料(數(shù)據(jù))及設(shè)計(jì)技術(shù)要求:
1.原始資料:
①.管磨機(jī)的設(shè)計(jì)規(guī)格φ2.6×13m;
②.轉(zhuǎn)筒干燥機(jī)的其它主要技術(shù)參數(shù):入磨物料粒度:≤10mm; 填充率:30%;
磨機(jī)轉(zhuǎn)速:17.5r/min; 產(chǎn)量: 35t/h; 出料粒度:4900孔/平方厘米; 篩余量:≤12%
注:磨機(jī)的工作狀況:適用于大中型企業(yè)應(yīng)用,磨機(jī)的制造適用于中小型企業(yè)。
2.設(shè)計(jì)技術(shù)要求:
① 根據(jù)主要技術(shù)參數(shù)設(shè)計(jì)管磨機(jī)的結(jié)構(gòu)。
② 要求英文資料翻譯忠實(shí)原文。
③ 要求完成的設(shè)計(jì)能滿足實(shí)際要求,圖面及文字說明表達(dá)簡(jiǎn)潔、清晰、易讀懂,
圖紙?jiān)O(shè)計(jì)規(guī)范,符合制圖標(biāo)準(zhǔn)。能用于指導(dǎo)實(shí)際的生產(chǎn)、裝配。
④ 要求畢業(yè)論文敘述條理清楚,設(shè)計(jì)計(jì)算正確,論文格式規(guī)范。
III、畢 業(yè)設(shè)計(jì)(論文)工作內(nèi)容及完成時(shí)間:
1.收集有關(guān)資料,寫出開題報(bào)告; 第1周——第2周
2.外文翻譯(6000字符以上); 第3周—— 第4周
3.分析與研究:了解現(xiàn)有類似設(shè)備的工作原理,制訂設(shè)備工作原理圖。第5周——第7周
4.管磨機(jī)主要結(jié)構(gòu)設(shè)計(jì)及相關(guān)尺寸的計(jì)算。 第8周——第10周
5.管磨機(jī)各主要配件圖和總裝圖的繪制。 第11周——第14周
6.撰寫畢業(yè)論文一份 第15周——第16周
7.畢業(yè)設(shè)計(jì)審查、畢業(yè)答辯 第17周
Ⅳ 、主 要參考資料:
1 江旭昌.管磨機(jī).中國(guó)建材工業(yè)出版社,1992.12
2 金容容.水泥廠工藝設(shè)計(jì)概論.武漢工業(yè)大學(xué)出版社,1995.8
3 倪文龍.機(jī)械立窯.中國(guó)礦業(yè)大學(xué)出版社,1995.8
4 姜煜林.水泥熱工機(jī)械設(shè)備.武漢工業(yè)大學(xué)出版社,1996.12
5 許林發(fā).建筑材料機(jī)械設(shè)計(jì)(一).武漢工業(yè)大學(xué)出版 ,1990.8
6 朱敦群.新標(biāo)準(zhǔn)條件下水泥粉磨工藝的相應(yīng)措施《中國(guó)建材裝備》,2002.2
7 機(jī)械設(shè)計(jì)手冊(cè)(新版).第一卷、第二卷、第四卷、第五卷.北京:機(jī)械工業(yè)出版,2004.8
8 汪愷. 機(jī)械工業(yè)基礎(chǔ)標(biāo)準(zhǔn)應(yīng)用手冊(cè). 北京:機(jī)械工業(yè)出版社,2001.6。
9 金屬切削加工.P65.焊接、切割與膠接.P66.中國(guó)機(jī)械工程文摘.機(jī)械工業(yè)信息研究院.機(jī)械工業(yè)信息研究院出版社,2004.3
10 鄭萬才.機(jī)械設(shè)備裝備監(jiān)測(cè)及故障診斷綜述.P125.煤礦機(jī)械.煤礦機(jī)械出版社,2004.3
11 改進(jìn)球磨機(jī)齒輪潤(rùn)滑方式.P38.設(shè)備管理與維修.設(shè)備管理與維修雜志社,2004-NO.04
12 劉興才.磨機(jī)料漿緩沖槽的系統(tǒng)改造.P84-85.礦山機(jī)械.礦山機(jī)械雜志社,2004.3
13 吳宗澤.機(jī)械零件設(shè)計(jì)手冊(cè).北京:機(jī)械工業(yè)出版社, 2003.11。
14 王大康,盧頌峰.機(jī)械設(shè)計(jì)課程設(shè)計(jì). 北京:北京工業(yè)大學(xué)出版社,2002.2
15 時(shí)鈞.化學(xué)工程手冊(cè).北京:化學(xué)工業(yè)出版社,1996.1。
2 金容容.水泥廠工藝設(shè)計(jì)概論.武漢工業(yè)大學(xué)出版社,1995.8
3 倪文龍.機(jī)械立窯.中國(guó)礦業(yè)大學(xué)出版社,1995.8
4 姜煜林.水泥熱工機(jī)械設(shè)備.武漢工業(yè)大學(xué)出版社,1996.12
5 許林發(fā).建筑材料機(jī)械設(shè)計(jì)(一).武漢工業(yè)大學(xué)出版 ,1990.8
6 朱敦群.新標(biāo)準(zhǔn)條件下水泥粉磨工藝的相應(yīng)措施《中國(guó)建材裝備》,2002.2
7 機(jī)械設(shè)計(jì)手冊(cè)(新版).第一卷、第二卷、第四卷、第五卷.北京:機(jī)械工業(yè)出
出版,2004.8
8 汪愷. 機(jī)械工業(yè)基礎(chǔ)標(biāo)準(zhǔn)應(yīng)用手冊(cè). 北京:機(jī)械工業(yè)出版社,2001.6。
8
9 業(yè)信息研究院出版社,2004.3
9 金屬切削加工.P65.焊接、切割與膠接.P66.中國(guó)機(jī)械工程文摘.機(jī)械工業(yè)信息研究院.機(jī)械工業(yè)
信息研究院出版社,2004.3
10 萬才.機(jī)械設(shè)備裝備監(jiān)測(cè)及故障診斷綜述.P125.煤礦機(jī)械.煤礦機(jī)械出版社,2004.3
11 改進(jìn)球磨機(jī)齒輪潤(rùn)滑方式.P38.設(shè)備管理與維修.設(shè)備管理與維修雜志社,2004-NO.04
12 劉興才.磨機(jī)料漿緩沖槽的系統(tǒng)改造.P84-85.礦山機(jī)械.礦山機(jī)械雜志社,2004.3
13吳宗澤.機(jī)械零件設(shè)計(jì)手冊(cè).北京:機(jī)械工業(yè)出版社, 2003.11。
14 王大康,盧頌峰.機(jī)械設(shè)計(jì)課程設(shè)計(jì). 北京:北京工業(yè)大學(xué)出版社,2002.2
15 時(shí)鈞.化學(xué)工程手冊(cè).北京:化學(xué)工業(yè)出版社,1996.1。
航空工程 系 機(jī)械設(shè)計(jì)制造及其自動(dòng)化 專業(yè)類 0781053 班
學(xué)生(簽名): 張攀程
日期: 自 2011 年 3 月 1 日至 2011 年 6 月 1 日
指導(dǎo)教師(簽名):
助理指導(dǎo)教師(并指出所負(fù)責(zé)的部分):
航空工程 系(室)主任(簽名):
學(xué)士學(xué)位論文原創(chuàng)性聲明
本人聲明,所呈交的論文是本人在導(dǎo)師的指導(dǎo)下獨(dú)立完成的研究成果。除了文中特別加以標(biāo)注引用的內(nèi)容外,本論文不包含法律意義上已屬于他人的任何形式的研究成果,也不包含本人已用于其他學(xué)位申請(qǐng)的論文或成果。對(duì)本文的研究作出重要貢獻(xiàn)的個(gè)人和集體,均已在文中以明確方式表明。本人完全意識(shí)到本聲明的法律后果由本人承擔(dān)。
作者簽名: 日期:
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作者簽名: 日期:
導(dǎo)師簽名: 日期:
管磨機(jī)動(dòng)態(tài)特性及系統(tǒng)的測(cè)試分析
學(xué)生姓名:張攀程 班級(jí):0781053
指導(dǎo)老師:張曉榮
摘要:磨機(jī)是發(fā)電、選礦、化工和建材等重工業(yè)領(lǐng)域中最廣泛采用的粉磨機(jī)械,其主要機(jī)件有傳動(dòng)裝置、支承裝置、回轉(zhuǎn)筒體。 本文建立了邊緣傳動(dòng)式磨機(jī)系統(tǒng)的“小齒輪——傳動(dòng)軸——減速機(jī)大齒輪”橫向振動(dòng)的模型,分析計(jì)算了系統(tǒng)橫向振動(dòng)的動(dòng)態(tài)特性,對(duì)系統(tǒng)的載荷進(jìn)行了測(cè)試分析,同時(shí),還建立了磨機(jī)系統(tǒng)的扭轉(zhuǎn)振動(dòng)模型,利用遞推計(jì)算法對(duì)系統(tǒng)進(jìn)行了扭轉(zhuǎn)振動(dòng)動(dòng)態(tài)特性分析,驗(yàn)證了遞推計(jì)算法的通用性。最后,對(duì)Φ2.6×13m的磨機(jī)系統(tǒng)進(jìn)行了動(dòng)態(tài)特性的實(shí)例分析。 研究邊緣傳動(dòng)磨機(jī)系統(tǒng)的動(dòng)態(tài)特性,對(duì)避免由于激勵(lì)頻率接近或等于系統(tǒng)的固有頻率而導(dǎo)致共振及設(shè)備的失效,預(yù)測(cè)系統(tǒng)在可能激勵(lì)下的響應(yīng)特性,優(yōu)化系統(tǒng)結(jié)構(gòu)等等都具有很重要的意義。 用傳遞矩陣法及通用計(jì)算程序可以簡(jiǎn)便地分析邊緣傳動(dòng)磨機(jī)系統(tǒng)橫向振動(dòng)的固有特性,以及計(jì)算不同激勵(lì)情況下系統(tǒng)的響應(yīng),為研究邊緣傳動(dòng)磨機(jī)系統(tǒng)橫向振動(dòng)的動(dòng)態(tài)特性提供了一個(gè)方便有效的方法。 邊緣傳動(dòng)磨機(jī)系統(tǒng)是一個(gè)模態(tài)偶合較緊的系統(tǒng),因此,在磨機(jī)系統(tǒng)的設(shè)計(jì)、運(yùn)行中,應(yīng)注意使激勵(lì)頻率避開系統(tǒng)的固有頻率,以免發(fā)生設(shè)備的早期失效。 邊緣傳動(dòng)式磨機(jī)系統(tǒng)的傳動(dòng)軸的設(shè)計(jì)是合理的。 系統(tǒng)阻尼對(duì)系統(tǒng)的動(dòng)態(tài)特性影響很大,是系統(tǒng)的一個(gè)重要性能參數(shù)。 邊緣傳動(dòng)磨機(jī)系統(tǒng),可以通過實(shí)測(cè)低速軸的扭矩來確定系統(tǒng)中減速機(jī)的負(fù)載狀況。
關(guān)鍵詞:振動(dòng) 載荷 響應(yīng)特性 扭矩
指導(dǎo)老師簽名:
Tube Mill and testing of the system Dynamic Analysis
Student name:Zhang PanCheng Class:0781053
Supervisor:Zhang XiaoRong
Abstract:Tube Mill is important rules that Research for Dynamic characteristics of the mill system of single -pinion drives in operation to prevent damage from the resonance between fix frequency and bestir frequency In this paper , the pattern of Pinion---Drive shaft---Decelerator gear vertical vibration in the mill system of single -pinion drives is established . Dynamic characteristics of vertical vibration is analyzed and calculated ,and its excitation loads are tested Simultaneously , the model of torsion vibration in system is also established, its dynamic characteristics is analyzed by using recurrence calculus method , thus , this methods current is verified . Finally, the paper studied the dynamic characteristics of 2.6x13m mill system. Mill system of single - pinion drives is lighten, so the design and run of mill system, bestir frequency must avoid inhesion.The design of drive shaft is rational in mill system of single - pinion drives. It is very large that damp of system effect to dynamic characteristics, so the damp is a important parameter. Load of gear box can be decided by measuring of low speed shaft contort. In mill system of single - pinion drives.
Key words:vibration response characteristics load torque
Signature of Supervisor:
南昌航空大學(xué)科技學(xué)院2011屆學(xué)士學(xué)位論文
ALGORYTHMS FOR SPEED AND STRECH CONTROL
OF THE MAIN DRIVES OF AN STRECH-REDUCING
TUBE MILL
Dorian MACREA
SC IPROLAM SA, Negustori 23, Bucharest, Romania: dorian.macrea@iprolam.ro
Costin CEPISCA
Politehnica University, Spl.Indep.313, Bucharest, Romania
Abstract. This paper shows the drive solution, the speed references calculation and the automatic control of all speeds range for the assembly of the 24 stands belonging to a tretch-reducing mill for seamless pipes. The correlation between the speed control and the stretching control of the rolled pipe is also shown. The experimental results are real data associated to the most recent project that has been executed at a seamless pipe plant in China.
1 Introduction
The concept of common drives of the stands using distribution and differential gear-boxes represents a flexibility limitation of the performances of the mill but using it we can sensibly reduce the costs of the drives [1], [2]. Therefore, when we are designing rolling mills of this type, we have to study carefully the necessity and the utility of choosing individual drives for each stand or common drives [3].
If we are using a common reducer driven using main and overlapping drives the rotating speed ratios are changing simultaneously at all stands by control of the rotating speed at both (or one of the two) motors and maintaining the ratios for the rotating speeds of the rolling stands as been established by designing of the gears. Thus, in this drive system we can change only the speed average or the stretching average, but not the distribution of the deformation values in the individual sequence of the stands [4], [5].
If we may give up the advantages of the individual speed control on the pipe deformation and if we except a larger slipping between the rolls and the rolled material (a current status at easier rolling programs) we could accept a common drive with distribution and differential gears [6], [7].
2 Electromechanical drive solution
2.1. Speed control
The 4-motor drive consists of two drive groups which are mechanically separated from one another and, therefore, allow effective crop end control (CEC) even with close sequences of tubes. For this purpose, the entry mill stand group features exceptionally high gear ratios to obtain particularly large elongations (Figure 1). The roll speeds for stand position (i) are calculated as,
In the entry side drive group:
Figure 1: Schematic for SRM with Common Drive with Distribution and Differential Gears
With respect to the drive group on the run-out side:
The basis speed curve is characterized by high gear ratios in the entry drive group to enable positive differential gear action also in this area, i.e. identical direction of rotation of both basic and differential drives.
During the steady-state phase of the rolling process, the basic drives of this system run at identical speeds while the differential drive units operate at exactly synchronized speeds. The speeds are related by the following term:
whereby IKM and IKD are constants. The motors are synchronized automatically in the basic automation system.
2.2 Strech control
The motor speeds at changes in elongation are calculated with the rotational speed values resulting from the calculation of the changes in speed. This method ensures that the operator can effect a change in elongation by means of a change in speed, if necessary, if motor speed limits are reached with no change in speed. One input value is used for the change in elongation.
Input range: -100 ... +100%
Standard: 0 % (in rolling program)
Calculation: Conversion of the entered value P:
PS 1 P/100*P /100 (5)
with Pmax as internal limiting value, e.g. 20% in the actual project.
The following calculation results in a “pivoting” of the speed diagram with the pivot point IPSPP (Figure 2). One stand position is defined as the pivot point: IPSPP= IPSI.
This has the effect that the entry speed and thus the throughput of material remain more or ess constant.
Each gearbox is assigned to one motor. A characteristic value which is determined together with the rolling program, determines the gear stage (0 or 1). The corresponding gear ratios are indicated in the Table 1.
Further calculation of new motor speeds: IGRMD 1= 1 or gear ratio of the switching step chosen. The same is to be applied for IGRMD2, IGRDD1 and IGRDD2. For calculation reasons we define the variables X= IKM and Y = IKD.
Table 1
If only the stand group on the inlet side is occupied by roll stands and the drives on the run out side are not used to drive guide stands etc. the following applies:
Final calculation of new motor speed:
After every calculation of a motor speed, limit values are checked and corrected accordingly. The change in inlet and outlet speed can be calculated with the basic equation:
with:
IS - Inlet or outlet speed after change in elongation [m/s];
G - Gradient relationship of inlet or outlet speed [(m/s)/%] (in Rolling program);
AJ - Adjusted input value P [%];
IOS - Inlet or outlet speed at default settings of the motors [m/s].
If only the stand group on the inlet side is occupied by roll stands and the drives on the run-out side are not used to drive guide stands, the following applies: OSDD2 = 0, OSMD2 = 0.
Figure 3: Speed diagram ranges.
3 Experimental results
Table 2
Motor
speeds:
Figure 4: Experimental speed diagram
References
PROGRAM VARIABLES
IKM, IKD Rolling mill constants. The values are determined when drawing up the rolling program.
ISMD1 Speed of the basic motor of the inlet side drive group
ISDD1 Speed of the differential drive motor of the inlet side drive group
ISMD2 Speed of the basic motor of the outlet side drive group
ISDD2 Speed of the differential drive motor of the outlet side drive group
IPSPP Stand position number of the pivot point IPSI Stand position number of the initial pass stand IPSF Stand position number of the final stand
IGRSMD(i) Gear ratio at stand position “i” of the basic drive
IGRSDD(i) Gear ratio at stand position “i” of the differential drive ICF Correction factor with unequal speed ranges of the basic motors
IGRMD1 Gear ratio of basic motor 1
IGRMD2 Gear ratio of basic motor 2
IGRDD1 Gear ratio of differential drive motor 1
IGRDD2 Gear ratio of differential drive motor 2
OSMD1 Speed of the basic motor of the inlet side drive group
OSDD1 Speed of the differential drive motor of the inlet side drive group
OSMD2 Speed of the basic motor of the outlet side drive group
OSDD2 Speed of the differential drive motor of the outlet side drive group
ALGORYTHMS控制速度和斯特雷奇
作者:
多利安馬克雷亞
科斯廷切皮斯卡 Politehnica大學(xué)
出版日期:
2007年4月1日
出版信息:
Postprints,加州大學(xué)戴維斯分校
摘要:本文顯示驅(qū)動(dòng)解決方案,速度的計(jì)算和引用所有自動(dòng)速度控制范圍為24個(gè)裝配站屬于張力減為無縫鋼管廠。之間的速度控制和相關(guān)的拉伸,軋管控制也顯示。實(shí)驗(yàn)結(jié)果是真實(shí)的數(shù)據(jù)聯(lián)想到最近的項(xiàng)目已在執(zhí)行中國(guó)的無縫鋼管廠。
1簡(jiǎn)介
作者在展位分配和使用差動(dòng)齒輪箱的共同驅(qū)動(dòng)概念代表了該工廠的表現(xiàn)靈活性的限制,但我們可以合理地使用它減少驅(qū)動(dòng)器的成本[1],[2]。因此,當(dāng)我們正在設(shè)計(jì)的這種軋機(jī)型,我們要仔細(xì)研究的必要性和個(gè)人選擇的驅(qū)動(dòng)器實(shí)用每個(gè)站或共同驅(qū)動(dòng)器[3]。如果我們使用的是常見的減速驅(qū)動(dòng)使用的主要驅(qū)動(dòng)旋轉(zhuǎn)和重疊速度比率正在發(fā)生變化,同時(shí)在由旋轉(zhuǎn)速度控制所有攤位都(或一兩)馬達(dá)和維持的比例為代表,作為滾動(dòng)旋轉(zhuǎn)速度成立由齒輪設(shè)計(jì)。因此,在此驅(qū)動(dòng)器系統(tǒng),我們可以改變只速度平均或平均伸展,但不是在變形值的分布個(gè)人的立場(chǎng)[4] [5]序列。如果我們可以放棄對(duì)管道的變形和個(gè)人速度控制的優(yōu)點(diǎn)如果我們除了一大之間的軋輥和材料(1現(xiàn)狀在容易滑倒?jié)L動(dòng)計(jì)劃),我們可以接受一個(gè)共同的分布和差分驅(qū)動(dòng)齒輪[6] ,[7].
2機(jī)電驅(qū)動(dòng)解決方案
2.1。速度控制
4電機(jī)驅(qū)動(dòng)器由兩個(gè)驅(qū)動(dòng)集團(tuán)是由一個(gè)機(jī)械分離另外,因此,即使允許序列有效的作物接近年底控制(CEC)管。為此,該條目軋機(jī)機(jī)架齒輪組功能異常的比例高獲得特別大的伸長(zhǎng)率(圖1)。為立場(chǎng)位置(我的輥速度)的計(jì)算公式為,在進(jìn)入邊驅(qū)動(dòng)器組:
圖1:原理與普通車道與分布的固體火箭發(fā)動(dòng)機(jī)和齒輪差動(dòng)
關(guān)于對(duì)運(yùn)行在驅(qū)動(dòng)器出組方:
速度曲線的基礎(chǔ)的特點(diǎn)是在入門組高齒輪傳動(dòng)比,使差動(dòng)齒輪也積極在這一領(lǐng)域的行動(dòng),即對(duì)兩個(gè)基本相同的方向旋轉(zhuǎn)和差分驅(qū)動(dòng)器。
在軋制過程中的穩(wěn)態(tài)階段,在這個(gè)系統(tǒng)運(yùn)行的基本驅(qū)動(dòng)器而相同的速度差驅(qū)動(dòng)裝置操作完全同步的速度。該速度是有關(guān)下列條件:
據(jù)此IKM和IKD是常數(shù)。自動(dòng)同步電動(dòng)機(jī)的基本自動(dòng)化系統(tǒng)。
圖2:串聯(lián)驅(qū)動(dòng)器的速度差異圖
2.2斯特雷奇控制
在伸長(zhǎng)率變化的電機(jī)速度的計(jì)算值與轉(zhuǎn)速結(jié)果從計(jì)算速度的變化。這種方法可確保運(yùn)營(yíng)商可以用一個(gè)影響速度的變化意味著在伸長(zhǎng)率的變化,如果有必要,如果電機(jī)轉(zhuǎn)速在達(dá)到極限速度,沒有改變。一個(gè)輸入值用于改變伸長(zhǎng)率。
輸入范圍: -100 ... +100%
標(biāo)準(zhǔn): 0 %(在滾動(dòng)計(jì)劃)
計(jì)算方法:輸入的值P轉(zhuǎn)換:
與P波內(nèi)部限制值,例如20%的實(shí)際項(xiàng)目。
下面的計(jì)算結(jié)果在“旋轉(zhuǎn)式”的速度與支點(diǎn)圖IPSPP(圖2)。一個(gè)站的位置被定義為支點(diǎn):IPSPP =同側(cè)。
這樣做的效果是進(jìn)入速度,從而使更多的物質(zhì)吞吐量保持或頗為穩(wěn)定。
每個(gè)變速箱被分配到一個(gè)電機(jī)。這是一個(gè)特征值共同確定與滾動(dòng)計(jì)劃,確定了齒輪階段(0或1)。相應(yīng)的齒輪比率表1所示。
新發(fā)動(dòng)機(jī)的進(jìn)一步計(jì)算速度:IGRMD 1 = 1或齒輪的切換步驟比選擇。同樣是適用的IGRMD2,IGRDD1和IGRDD2。計(jì)算原因我們定義的變量X = IKM和..為Y = IKD
表1
如果只對(duì)進(jìn)口方的立場(chǎng)是占領(lǐng)輥組的立場(chǎng)和驅(qū)動(dòng)器上運(yùn)行一邊是不出來用于驅(qū)動(dòng)指導(dǎo)站等適用以下規(guī)則:
最后計(jì)算的新的發(fā)動(dòng)機(jī)轉(zhuǎn)速:
經(jīng)過每一個(gè)電機(jī)的速度計(jì)算,限值檢查和更正。在進(jìn)口和出口速度的變化可以計(jì)算的基本公式:
為了:
IS - 進(jìn)口或出口后伸長(zhǎng)[米/秒]變化的速度;
G- 入口或出口速度[(m / s的梯度關(guān)系)/%](在滾動(dòng)計(jì)劃);
AJ- 調(diào)整輸入值P [%];
IOS- 進(jìn)口或出口速度的馬達(dá)默認(rèn)設(shè)置[米/秒]。
如果只對(duì)進(jìn)口方的立場(chǎng)是占領(lǐng)輥組的立場(chǎng)和在跳動(dòng)的驅(qū)動(dòng)器一邊是不被用來驅(qū)動(dòng)指導(dǎo)站,以下適用于:OSDD2 = 0,OSMD2 = 0。
圖3:速度圖范圍
3.實(shí)驗(yàn)結(jié)果
表2
馬達(dá)
速度:
圖4:實(shí)驗(yàn)速度圖
程序變量
IKM, IKD軋機(jī)常數(shù)。值都在制定滾動(dòng)計(jì)劃。
ISMD1 速度在進(jìn)氣側(cè)驅(qū)動(dòng)電機(jī)組基本的變量
ISDD1 速度在進(jìn)氣側(cè)差動(dòng)驅(qū)動(dòng)器驅(qū)動(dòng)電機(jī)組的變量
ISMD2 速度對(duì)出口方的基本驅(qū)動(dòng)電機(jī)組的變量
ISDD2 速度的出口端驅(qū)動(dòng)器驅(qū)動(dòng)電機(jī)組差的變量
IPSPP 林分的支點(diǎn)位置號(hào)碼
IGRSMD 站在初始位置號(hào)碼傳遞的位置
IGRSDD 展臺(tái)的位置號(hào)碼的最后位置
IGRMD1 齒輪電機(jī)1的比例基本的變量
IGRMD2 齒輪電機(jī)2比基本的變量
IGRDD1 齒輪比率差動(dòng)驅(qū)動(dòng)電機(jī)1的變量
IGRDD2 齒輪比率差動(dòng)驅(qū)動(dòng)電機(jī)2的變量
OSMD1 速度在進(jìn)氣側(cè)驅(qū)動(dòng)電機(jī)組基本的變量
OSDD1 速度在進(jìn)氣側(cè)差動(dòng)驅(qū)動(dòng)器驅(qū)動(dòng)電機(jī)組的變量
OSMD2 速度對(duì)出口方的基本驅(qū)動(dòng)電機(jī)組的變量
OSDD2 速度的出口端驅(qū)動(dòng)器驅(qū)動(dòng)電機(jī)組差的變量
12
管磨機(jī)動(dòng)態(tài)特性及系統(tǒng)的測(cè)試分析
學(xué)生姓名:張攀程 班級(jí):0781053
指導(dǎo)老師:張曉榮
摘要:磨機(jī)是發(fā)電、選礦、化工和建材等重工業(yè)領(lǐng)域中最廣泛采用的粉磨機(jī)械,其主要機(jī)件有傳動(dòng)裝置、支承裝置、回轉(zhuǎn)筒體。 本文建立了邊緣傳動(dòng)式磨機(jī)系統(tǒng)的“小齒輪——傳動(dòng)軸——減速機(jī)大齒輪”橫向振動(dòng)的模型,分析計(jì)算了系統(tǒng)橫向振動(dòng)的動(dòng)態(tài)特性,對(duì)系統(tǒng)的載荷進(jìn)行了測(cè)試分析,同時(shí),還建立了磨機(jī)系統(tǒng)的扭轉(zhuǎn)振動(dòng)模型,利用遞推計(jì)算法對(duì)系統(tǒng)進(jìn)行了扭轉(zhuǎn)振動(dòng)動(dòng)態(tài)特性分析,驗(yàn)證了遞推計(jì)算法的通用性。最后,對(duì)Φ2.6×13m的磨機(jī)系統(tǒng)進(jìn)行了動(dòng)態(tài)特性的實(shí)例分析。 研究邊緣傳動(dòng)磨機(jī)系統(tǒng)的動(dòng)態(tài)特性,對(duì)避免由于激勵(lì)頻率接近或等于系統(tǒng)的固有頻率而導(dǎo)致共振及設(shè)備的失效,預(yù)測(cè)系統(tǒng)在可能激勵(lì)下的響應(yīng)特性,優(yōu)化系統(tǒng)結(jié)構(gòu)等等都具有很重要的意義。 用傳遞矩陣法及通用計(jì)算程序可以簡(jiǎn)便地分析邊緣傳動(dòng)磨機(jī)系統(tǒng)橫向振動(dòng)的固有特性,以及計(jì)算不同激勵(lì)情況下系統(tǒng)的響應(yīng),為研究邊緣傳動(dòng)磨機(jī)系統(tǒng)橫向振動(dòng)的動(dòng)態(tài)特性提供了一個(gè)方便有效的方法。 邊緣傳動(dòng)磨機(jī)系統(tǒng)是一個(gè)模態(tài)偶合較緊的系統(tǒng),因此,在磨機(jī)系統(tǒng)的設(shè)計(jì)、運(yùn)行中,應(yīng)注意使激勵(lì)頻率避開系統(tǒng)的固有頻率,以免發(fā)生設(shè)備的早期失效。 邊緣傳動(dòng)式磨機(jī)系統(tǒng)的傳動(dòng)軸的設(shè)計(jì)是合理的。 系統(tǒng)阻尼對(duì)系統(tǒng)的動(dòng)態(tài)特性影響很大,是系統(tǒng)的一個(gè)重要性能參數(shù)。 邊緣傳動(dòng)磨機(jī)系統(tǒng),可以通過實(shí)測(cè)低速軸的扭矩來確定系統(tǒng)中減速機(jī)的負(fù)載狀況。
關(guān)鍵詞:振動(dòng) 載荷 響應(yīng)特性 扭矩
指導(dǎo)老師簽名:
Tube Mill and testing of the system Dynamic Analysis
Student name:Zhang PanCheng Class:0781053
Supervisor:Zhang XiaoRong
Abstract:Tube Mill is important rules that Research for Dynamic characteristics of the mill system of single -pinion drives in operation to prevent damage from the resonance between fix frequency and bestir frequency In this paper , the pattern of Pinion---Drive shaft---Decelerator gear vertical vibration in the mill system of single -pinion drives is established . Dynamic characteristics of vertical vibration is analyzed and calculated ,and its excitation loads are tested Simultaneously , the model of torsion vibration in system is also established, its dynamic characteristics is analyzed by using recurrence calculus method , thus , this methods current is verified . Finally, the paper studied the dynamic characteristics of 2.6x13m mill system. Mill system of single - pinion drives is lighten, so the design and run of mill system, bestir frequency must avoid inhesion.The design of drive shaft is rational in mill system of single - pinion drives. It is very large that damp of system effect to dynamic characteristics, so the damp is a important parameter. Load of gear box can be decided by measuring of low speed shaft contort. In mill system of single - pinion drives.
Key words:vibration response characteristics load torque
Signature of Supervisor:
南昌航空大學(xué)科技學(xué)院2011屆學(xué)士學(xué)位論文
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