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重慶科技學院 畢業(yè)設計（論文） 題 目 φ20-φ90高精度棒材矯直機設計 姓 名__劉 川 __ 學 號_2004440118 院（系）機械工程學院 專業(yè)班級 機械設計制造及其自動化本科2004級 指導教師_ 職 稱_高級工程師 評 閱 人___ _ 職 稱___ 2008年6月10日 注 意 事 項 1. 設計（論文）的內(nèi)容包括： 1) 封面（按教務處制定的標準封面格式制作） 2) 題名頁 3) 中文摘要（300字左右）、關鍵詞 4) 外文摘要、關鍵詞 5) 目次頁（附件不統(tǒng)一編入） 6) 論文主體部分：引言（或緒論）、正文、結(jié)論、參考文獻 7) 附錄（對論文支持必要時） 2. 論文字數(shù)要求：設計（論文）字數(shù)理工類不少于1.5萬字，文科類不少于1.2萬字。 3. 附件包括：任務書、文獻綜述、開題報告、外文譯文、譯文原文（復印件）。 4. 文字、圖表要求： 1) 文字通順，語言流暢，書寫字跡工整，打印字體及大小符合要求，無錯別字，不準請他人代寫。 2) 工程設計類題目的圖紙，要求部分用尺規(guī)繪制，部分用計算機繪制，所有圖紙應符合國家技術標準規(guī)范。圖表整潔，布局合理，文字注釋必須使用工程字書寫，不準用徒手畫。 3) 畢業(yè)論文須用A4單面打印，論文50頁以上的雙面打印。 4) 圖表應繪制于無格子的頁面上。 5) 軟件工程類課題應有程序清單，并提供電子文檔。 5. 裝訂順序 1) 設計（論文） 2) 附件 按照任務書、文獻綜述、開題報告、外文譯文、譯文原文（復印件）次序裝訂 3) 教師指導畢業(yè)設計（論文）情況記錄表 4) 其它 學生畢業(yè)設計（論文）原創(chuàng)性聲明 本人以信譽聲明：所呈交的畢業(yè)設計（論文）是在導師的指導下進行的設計（研究）工作及取得的成果，設計（論文）中引用他（她）人的文獻、數(shù)據(jù)、圖件、資料均已明確標注出，論文中的結(jié)論和結(jié)果為本人獨立完成，不包含他人成果及為獲得重慶科技學院或其它教育機構(gòu)的學位或證書而使用其材料。與我一同工作的同志對本設計（研究）所做的任何貢獻均已在論文中作了明確的說明并表示了謝意。 畢業(yè)設計（論文）作者（簽字）： 簽字日期 年 月 日 重慶科技學院本科生畢業(yè)設計 目錄 目 錄 中文摘要 I 英文摘要 II 1 緒 論 1 1.1設計課題背景 1 1.2設計依據(jù) 1 1.3矯直設備的發(fā)展概況 1 1.4分類及工作原理 3 1.4.1 壓力矯直機 3 1.4.2輥式矯直機 3 1.4.3 斜輥式矯直機 3 1.4.4拉伸矯直機 3 1.4.5拉伸彎曲矯直機 4 2 鋼材矯直理論 1 2.1“ 矯直”的定義 1 2.2反彎矯直的基本原理 1 3二輥滾光矯直機的工作原理 4 3.1二輥滾光矯直機的簡介 4 3.2二輥滾光矯直機的工作原理 4 3.3設計二輥滾光矯直機所涉及到的主要參數(shù) 10 3.4國內(nèi)外現(xiàn)在生產(chǎn)這種矯直機的廠家 11 4二輥滾光矯直機力能參數(shù)計算 12 4.1矯直力的計算 12 4.1.1求導程t 12 4.1.2求彈性極限彎矩Mmax 13 4.1.3求傾角： 13 4.1.4軸承承受力的總和 14 4.2 二輥滾光矯直機功率計算 14 4.2.1軸承的消耗功率 14 4.2.2滑動摩擦的消耗功率 14 4.2.3滾動摩擦的消耗功率 14 4.2.4塑性彎曲變形的消耗功率 15 4.2.5消耗總功率 15 4.3電機驅(qū)動功率 12 4.4關于機架、機座及軸承蓋的設計 15 5二輥滾光矯直機輥系設計 18 5.1矯直輥的組成 18 5.2.矯直輥材料 18 5.3矯直輥尺寸計算 19 5.4矯直速度計算 20 5.5矯直輥強度計算 21 5.6軸承的壽命校核 23 6二輥滾光矯直機傳動裝置的選擇及液壓過載保護 25 6.1二輥滾光矯直機傳動裝置的選擇 25 6.1.1矯直機主傳動裝置的組成 25 6.1.2矯直機主傳動裝置類型 25 6.1.3萬向連接軸 25 6.1.4聯(lián)接軸的總體的配置及其平衡裝置 26 6.1.5主減速機 27 6.2二輥滾光矯直機的液壓過載保護裝置 28 7二輥滾光矯直機的安裝與維護 30 7.1二輥滾光矯直機的安裝 30 7.1.1基礎 30 7.1.2設置安裝基準 30 7.1.3設置墊板 30 7.1.4矯直機的吊裝、找正、找平、找標高 31 7.1.5二次灌漿 31 7.1.6試運轉(zhuǎn) 31 7.2二輥滾光矯直機的維護 31 7.2.1二輥滾光矯直機的維護和修理制度 31 7.2.2二輥滾光矯直機的潤滑 32 8總結(jié) 34 9致謝 35 10參考文獻 36 重慶科技學院本科生畢業(yè)設計 中文摘要 摘 要 隨著科技的進步，人們對棒材的需求量越來越大、對其精度要求也越來越高，以前人們采用平行輥矯直機矯直管、棒等圓形斷面條材，圓材在矯直過程中容易產(chǎn)生自轉(zhuǎn)現(xiàn)象，并且只能矯直圓材垂直于輥軸的縱向剖面上的彎曲。在這種情況下斜二輥矯直機的問世解決了以前平行輥矯直機所解決不了的棒材、管材的矯直問題，在這種情況下，我們對二輥滾光矯直機進行設計。 本文重點對鋼材矯直工藝及工作原理，斜輥矯直機的工作原理、特點、結(jié)構(gòu)等進行了介紹，同時對二輥棒材矯直機力能參數(shù)的計算進行了分析，提出了本次設計二輥棒材矯直機的基本思路。矯直機的機架、機座、傳動等部分設計不屬于本次設計的重點，所以在這里只是作了簡單的介紹，但是由于時間比較倉促，本文對矯直機的液壓壓下裝置、矯直機的安裝與維護沒有做出詳盡的介紹，限于本人的水平，文中有誤漏之出，還請批評指正。 關鍵詞：棒材 矯直工藝 二輥棒材矯直機 矯直力能參數(shù) 1 重慶科技學院本科生畢業(yè)設計 Abstract ABSTRACT With the advancement of technology, people's growing demand for the bar, its accuracy is also getting higher and higher, before people parallel roller leveler straightening tubes, rods and other circular cross-section of the build, round-wood in hand Direct the process of rotation is easy to produce, and only straightening roundwood roll axis perpendicular to the longitudinal section on the bend. In this case the ramp roll straightening machine resolved before the advent of parallel roll straightening machine can not be resolved by the bar, pipe straightening of the problem, in this case, we design roll on the roller-straightening machine. The steel straightening process and working principle, ramps roll straightening machine works, characteristics, such as the structure was introduced, while two of the roll bar straightening machine can be calculated parameters of an analysis of the proposed The design of the roll bar leveler of the basic ideas. Straightening machine rack, engine, transmission and other parts of the design are not the focus of this design, so here is a brief introduction, but because of the time hasty comparison, the paper leveler of the hydraulic pressure devices, Straightening machine installation and maintenance have not made detailed introduction, I am limited to the level of error in the text of a leak, also invited criticism correction. Key words: bars；Straightening process；the two roll bar straightening machine；straightening of the power parameters 1 緒 論 1.1設計課題背景 長期以來，矯直機因彎曲由人工檢測，壓彎量人為設定不夠準確，全過程都靠手工操作，效率低，矯直精度全憑操作者經(jīng)驗來決定等缺點，一直作為一種補充矯直設備來使用。所以矯直必須檢測工件的原始彎曲，測量彎曲量、確定最佳矯直點、設定壓彎量。由于缺少可靠的檢測手段和認識上的一些人為因素，以前這些工作只能靠人工來完成。因此以前的矯直機有以下缺點：彎曲人工檢測、壓彎量人工設定不夠準確，效率低，矯直精度全憑操作者經(jīng)驗來決定，降低了生產(chǎn)效率。而且現(xiàn)在人們對棒材的需求量越來越大、對其精度要求也越來越高，在情況下斜二輥矯直機的問世解決了以前平行輥矯直機所解決不了的棒材、管材的矯直精度問題，在這種情況下，我們對二輥滾光矯直機進行設計。 The company Severstal completed the successful introduction of new in-line plate-straightening machines (PSMs) on its 2800 and 5000 mills in August 2003 1, 2, 3. The main design features of the machines are as follows: each machine is equipped with hydraulic hold-down mechanisms (to improve the dynamics and accuracy of the machine adjustments and more reliably maintain a constant gap); the machines have mechanisms to individually adjust each work roller with the aid of hydraulic cylinders (this broadens the range of straightening regimes that can be realized by providing a measure of control over the change in the curvature of the plate); each work roller is provided with its own adjustable drive (to eliminate rigid kinematic constraints between the spindles); the system of rollers of the PSM is enclosed in cassettes (to facilitate repairs and reduce roller replacement costs); the PSM has a system that can be used to adjust the machine from a nine-roller straightening scheme to a five- roller scheme in which the distance between the rollers is doubled (this is done to widen the range of plate thick- nesses that the machine can accomodate). Thus, the new straightening machine is a sophisticated multi-function system of mechanisms that includes a wide range of hydraulically and electrically driven components controlled by digital and analog signals. The entire complex of PSM mechanisms can be divided into two functional groups: the main group, which includes the mechanisms that partici- pate directly in the straightening operation (the hold-down mechanisms, the mechanisms that individually adjust the rollers, the mechanisms that adjust the components for different straightening regimes, the mechanism that moves the top roller of the feeder, and the main drive); the auxiliary group (which includes the cassette replacement mechanism, the spindle-lock- ing mechanism, and the equipment that cools the system of rollers). Although the PSM has a large number of mechanisms, the use of modern hydraulic and electric drives has made it possible to almost completely automate the main and auxiliary operations performed on the PSM and the units that operate with it. Described below are the features and the automatic control systems for the most important mechanisms of the plate- straightening machine. The operating regimes of those mechanisms are also discussed. The hydraulic hold-down mechanisms (HHMs) of the sheet-straightening machine function in two main regimes: the adjustment regime; the regime in which the specified positions are maintained. There are certain requirements for the control system and certain efficiency criteria for each regime. In the adjustment regime, the control system for the hydraulic hold-down mechanisms must do the following: synchronize the movements of the hydraulic cylinders and keep the angular deeflection within prescribed limits; maximize speed in adjusting the machine for a new plate size; maintain a high degree of accuracy in positioning the mechanisms; Metallurgist, Vol. 48, Nos. 78, 2004 AUTOMATING THE CONTROL OF MODERN EQUIPMENT FOR STRAIGHTENING FLAT-ROLLED PRODUCTS Yu. N. Belobrov, V. G. Smirnov, A. I. Titarenko, V. A. Perekhodchenko, and I. L. Sinelnikov UDC 621.982 Novokramatorsk Machine Plant AO. Translated from Metallurg, No. 8, pp. 5156, August, 2004. 406 The control system has the following requirements when operating in the maintenance regime: stabilize the coordinates of the top cassette and the top roller of the feeder with a high degree of accuracy; minimize the time needed to return the equipment to the prescribed coordinates when deviations occur (such as due to the force exerted by a plate being straightened). Need for synchronization. Experience in operating the plate-straightening machine in plate shop No. 3 at Severstal has shown that the most problematic factor in adjusting the machine is the nonuniformity of the forces applied to the hydraulic cylinders. This nonuniformity is due to the asymmetric distribution of the masses of the moving parts of the PSM (in par- ticular, the effect of the weight of the spindle assembly). Displacement of the “hydraulic zero point” relative to the “electri- cal zero point” in the servo valves is also a contributing factor. * The latter reason is more significant, the smaller the volume of the hydraulic cylinder. Thus, the HHM of the top roller of the feeder is the most sensitive to drift of the zero point. There are also other factors that affect the dynamism, simultaneousness, and synchronism of the operation of the hold-down mechanisms: differentiation of the frictional forces on parts of the hydraulic cylinders due to different combinations of devia- tions in the dimensions of the mated parts, despite the narrow tolerances; differences in the “springing” characteristics and the indices characterizing the inertia of the hydraulic supply chan- nels (due to differences in the lengths of the pipes leading from the servo valves to the hydraulic cylinders). Thus, since the PSM is not equipped with devices to mechanically synchronize the operation of the cylinders, the transmission of signals of the same amplitude to the inputs of the servo valves inevitably results in a speed difference that can seriously damage the mechanisms. To minimize and eliminate the effects of the above-mentioned factors, we developed an algorithm for electrical syn- chronization of the hold-down mechanisms. The HHM of the top cassette, composed of four hold-down cylinders and four balancing cylinders, is designed to ensure mobile adjustment of the machine to set the required size of straightening gap (in accordance with the thickness of the plate) and maintain that gap with a specified accuracy in the presence and absence of a load on the housings from the straightening force. The hydraulic system of the hold-down mechanism is designed in such a way that only one chamber of the hydraulic cylinders is used as the working chamber. The second chamber is always connected to the discharge channel. The top cassette is lowered when the balancing forces are overcome by the hold-down cylinders. The cassette is raised only by the action of the balancing cylinders. This arrangement has made it possible to eliminate gaps in the positioning of the equipment. 407 Fig. 1. Block diagram of the control system of the hydraulic cylinder. * The hydraulic zero point is the position that the slide valve occupies when it covers the delivery and discharge mains. The electrical zero point is the control signal that should move the valve to the hydraulic zero point. These points should ide- ally coincide, but in actual servo valves with zero overlap there is always a certain amount of displacement that results in leakage of the hydraulic fluid. The HHM of the top roller of the feeder consists of two hydraulic cylinders. Hydraulic fluid is fed into the plunger chamber when the roller is to be lowered and is fed into the rod chamber when it is to be raised. Control Principles. Individual circuits have been provided (Fig. 1) to control the hydraulic cylinders of the hold- down mechanisms. The control signal (X ctl ) sent to the input of the servo valve is formed by a proportional-integral (PI) con- troller (to improve the sensitivity of the system, we chose to use valves with “zero” overlap). The signal sent to the input of the controller (the error signal X err ) is formed as the difference between the control-point signal for position (X cpt ) and the feedback signal (X f.b ). The latter signal is received from the linear displacement gage (G) of the given hydraulic cylinder. The gages of the HHM for the top cassette are built into the balancing hydraulic cylinders (HCs). The cylinders are installed in such a way that their movements can be considered to be equal to the displacements of the corresponding cylin- der rods, with allowance for certain coefficients. The gages in the HHM for the top roller of the feeder are incorporated directly into the hold-down cylinders. The integral part of the controller is activated only during the final adjustment stage and during stabilization of the prescribed coordinate. When the displacements exceed a certain threshold value, the functions of the PI controller are taken over by a proportional (P) controller with the transfer function W(s) = k. Thus, X ctl (t) = kX err (t). When there are significant differences between the displacements of the working rollers, the difference (error) between the control point and the feedback signal from the linear displacement gage reaches values great enough so that the output signal which controls the operation of the servo valve reaches the saturation zone. In this case, further regu- lation of the displacement rate and, thus synchronization of the movements of the cylinders becomes impossible as long as the error exceeds the value at which X ctl is greater than the boundary value for the saturation zone (X sat ). The limit- ing error the largest error for which X ctl does not reach saturation is inversely proportional to the gain of the con- troller k: X err X sat /k. Solving the given problem by decreasing k leads to a loss of speed in the adjustment of the PSM and a decrease in control accuracy during the straightening operation. Thus, to keep the control signal from reaching the saturation zone when there are substantial displacements, the system was designed so that the input of the controller is fed not the actual required value (X rq ) but an increment (D X) of a magnitude such that the condition kD X X sat is satisfied. The control point is increased by the amount D X after the position of the cylinder has been changed by the amount corresponding to the incre- ment having the largest lag relative to the cylinders direction of motion. The adjustment of the control point is continued until the difference between the required value and the actual position of the mechanism becomes less than the increment: X rq X f.b D X. Then the input of the controller is fed the value X cpt , which is equal to the required adjustment: X cpt = X rq . The adjustment is thus completed. Use of the principle of a stepped increase in the control point makes it possible synchronize the movements of the cylinders and set the control point with a high degree of accuracy for almost any ideal repetition factor. Mechanisms for Individual Adjustment of the Working Rollers. The plate-straightening machine is designed so that each working roller can be moved vertically, which is done by means of a hydraulic cylinder acting in concert with a V-belt drive. The cylinders are supplied with power from servo valves operated with proportional control. A linear displacement gage is built into each cylinder to obtain a feedback signal on the position of the roller. Since these gages are actually transmiting information on the position of the cylinder rods rather than the working rollers themselves, the following conversion is performed to obtain the rollers coordinates: X rol = k red X f.b , where k red is the gear ratio of the drive; X f.b is the position of the cylinder rod measured by the linear displacement trans- ducers. Thus, a position feedback circuit is provided to control the position of each working roller. Figure 1 presents a dia- gram of one of the circuits. The control signals are generated by means of the PI controllere, which has made it possible to achieve a high degree of accuracy in adjusting the system without sacrificing speed. 408 The individual drive of the rollers. The above-described design is based on the use of individual ac drives with motors of different powers fed from frequency converters. Each individual drive offers the following advantages over a group drive: greater reliability thanks to the absence of additional loads on the components of the mechanisms due to differ- ences between the linear velocities of the working rollers and the speed of the plate; the possibility that the machine could continue to operate if one or even several drives malfunction; in this case, the corresponding rollers would be removed from the straightening zone; the possibility that the linear velocities of the rollers could be individually corrected in accordance with the actual speed of the plate; such a correction could be made either as a preliminary measure (on the basis of measured and calculated values) or during the straightening operation (on the basis of the data obtained from the frequency con- verters, which employ artificial intelligence). The main drive of the straightening machine rotates nine straightening rollers and two housing rollers. This drive must be highly reliable in operation, since the fact that the PSM is installed in the mill line means that sizable production losses can be incurred if the drive fails to work properly even for a short period of time. The requirements that must be satisfied by the drive are determined by the operational and design features of the machine as a whole: the plate being straightened must create a rigid kinematic coupling between the straightening rollers, the rollers of the housing, and the adjacent sections of the roller conveyors; the plate should undergo elongation during the straightening operation as a result of plastic deformation, with the increments in length being different on each working roller due to the differentiation of the bending radii; this sit- uation leads to a nonuniform increase in the speed of the plate as it moves toward the end of the PSM; it must be possible to use working rollers of different diameters (this being done, for example, due to nonuniform wear or regrinding); the loads on the rollers should be differentiated in accordance with the chosen straightening regime; reverse straightening should be possible. In light of the above factors and the actual operating regimes of the plate-straightening machine being discussed here, the following requirements can be established for the electric drive: regulation of speed within broad limits, including startup of the motors under load; operation in the reverse regime; a rigid characteristic w = (M); high degree of accuracy in maintaining the prescribed speed; fully synchronous operation. The element base. The drive of the rollers was built with the use of asynchronous three-phase motors having a short- circuit rotor. The motors were designed by the German company VEM. They can continue to function under severe over- loads and are reliable in operation. The motors are controlled by SIMOVERT frequency converters made by the German firm Siemens. Their modular design facilitates maintenance and repair, and the presence of a built-in microprocessor block makes it possible to execute most of the functions involved in controlling the operation of the drive (maintain the prescribed speed with a high degree of stability, recalculate the frequency of rotation in accordance with the actual diameters of the rollers, diagnose the condition of the drive, control the drives operation, and exchange information on the PROFIBUS network). Motors of different powers are used in the system because of the differentiated distribution of the moments between the working rollers. Using different motors has made it possible to significantly reduce the cost of the electrical equipment and improve the performance characteristics of the machine as a whole. The machine has three main operating regimes: the working regime (semi-automatic and automatic), the transport regime, and the cassette replacement regime. Figure 2 shows a block diagram of the operations connected with realization of the working regime. In the semi- automatic variant of this regime, the operator controls the PSM from a control panel. In this case, the operator can do the following: choose the straightening regime from a database; correct the chosen regime; adjust the regime manually, which 409 requires that the operator indicate the desired position of the bottom cassette (for five- or nine-roll straightening); adjust the gap between the top and bottom cassettes; set the coordinates for individual adjustment of the working rollers; choose the straightening speed and direction; generate a command to begin adjusting the machine to the specified regime. The machine is adjusted to the chosen regime automatically. After the adjustment is completed, a signal is sent to the control panel indicating that the coordinates of the mechanisms have been changed and that the rollers have reached their prescribed working speeds. In the automatic variant of the working regime, the plate-straigthening machine is adjusted on the basis of data sent through a data network from a higher-level system. These data include the following information: the thickness of the plate being straightened; the group of steels (information on the properties of the material); the temperature of the plate at the inlet to the PSM. The PSM is adjusted in several stages: preliminary adjustment based on the plate thickness and steel group, for cold-rolled plates (t = 20C); further adjustment on the basis of data obtained from a pyrometer installed roughly 50 m from the PSM; final adjustment on the basis of data obtained from a pyrometer installed at the entrance to the machine. In the automatic variant, control over the roller conveyors adjacent to the machine is switched over to the control system of the PSM as the next plate approaches the machine. In this case, the plate cannot enter the working zone of the machine until the adjustment is completed. If it is necessary to pass a plate through the machine without straightening it, the machine is changed over to the transport regime. In this case, the top crossarm and the cassette are elevated a prescribed amount and the speed of the rollers is changed so that it is equal to the speed of the adjacent roller conveyors. The cassette replacement regime is used in the event of breakage of a roller or when it is necessary to regrind the working and backup rollers. In this case, the operator can control the operation of the auxiliary mechanisms: the spindle- locking mechanism, the roll-out cart, the mechanism that locks the bottom cassette and the cart in position, and the hydraulic cylinder that moves the cart. The mechanisms are fixed in position by means of noncontact transducers. PSM Control System. Control of the plate-straightening machine required the development of a powerful, high- capacity system that could provide the desired control accuracy in combination with rapid operation. 410 Working regime Semi-automatic Automatic Straightening regime Adjustment regime Straightening regime Adjustment regime Non-reversing straightening Reversing straightening Five-roll regime Nine-roll regime Five-roll regime Nine-roll regime Five-roll regime Nine-roll regime Fig. 2. Block diagram of the working regime of the PSM. The control system that was created is divided into two levels: the base level, and an upper level. The diagnostic system was created as a separate system. A second controller was also provided, to control the pump station of the PSM. The base level of the control system employs a SIMATIC S7 industrial programmable controller, while the upper level and the diagnostic system were built on the basis of standard computers. The computer used for the upper-level system also serves as the control panel for the PSM. The different elements of the control system are linked by two loops of a PROFIBUS network (Fig. 3). The first loop functions as the communications link between the controller, the upper-level computer, the diagnostics station, and the pump-station controller. The second loop links the PSM controller with the functional elements of the system (the frequen- cy converters, linear displacement gages, and remote input/output module). The functions of the control system were divided between the base level and the upper level on the basis of the fol- lowing pr