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十吨位桥式起重机大车运行机构设计【10张CAD图纸和说明书】

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关键词：: 10 吨位桥式起重机大车运行机构设计 cad 图纸以及说明书仿单

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摘要

桥式起重机是一种工作性能比较稳定，工作效率比较高的起重机。随着我国制造业的发展，桥式起重机越来越多的应用到工业生产当中。在工厂中搬运重物，机床上下件，装运工作吊装零部件，流水在线的定点工作等都要用到起重机。在查阅相关文献的基础上，综述了桥式起重机的开发和研究成果,重点对桥式起重机大车运行机构、端梁、主梁、焊缝及连接进行设计并进行强度核算,主要是进行端梁的抗震性设计及强度计算和支承处的接触应力分析计计算过程。设计包括电动机,减速器,联轴器,轴承的选择和校核。设计中参考了许多相关数据, 运用多种途径, 利用现有的条件来完成设计。本次设计通过反复考虑多种设计方案, 认真思考, 反复核算, 力求设计合理;通过采取计算机辅助设计方法以及参考他人的经验, 力求有所创新;通过计算机辅助设计方法, 绘图和设计计算都充分发挥计算机的强大辅助功能, 力求设计高效。

关键词：桥式起重机,大车运行机构,主梁，端梁，焊缝

Abstract

Bridge crane is a kind of performance is stability, the working efficiency is relatively high crane. Along with the development of China's manufacturing industry,bridge crane is applied to industrial production more and more . Carrying heavy loads in factories , machine tool fluctuation pieces, shipping work on the assembly line for hoisting parts, the designated work with a crane.On the basis of literature review, summarized the bridge crane development and research results, focusing on bridge crane during operation organization, main beam,end beam weld and connection for design and the strength calculation; Mainly for the girders extent design and strength calculation and the support of contact stress analysis program in calculation. Design including motor, reducer, coupling, bearing choosing and checking.

The design refer to many related information, reference to apply a variety of ways, make the existing conditions to complete design. By considering various design scheme repeatedly, thinking deeply,strive to design reasonable; By taking computer aided design method and reference the experience of others,strive to make innovation; Through computer aided design method, graphics and design calculations give fullplay to the powerful auxiliary function, computer to design efficient.

Key words: bridge crane; during operation organization; main beam; end beam;weld

摘要 IV

Abstract V

目录 VI

1 绪论 1

1.1 起重机背景及其理论 1

1.2 实际意义 1

1.3 研究现状及存在问题 1

1.4 起重机国内与国外发展动向 2

1.4.1 国内桥式起重机发展动向 2

1.4.2 国外起重机的发展动向 2

1.5 桥式起重机设计的主要内容 3

2 大车运行机构的设计 5

2.1 设计的基本原则和要求 5

2.1.1 机构传动方案 5

2.1.2 大车运行机构具体布置的主要问题： 5

2.2 大车运行机构的计算 6

2.2.1 确定机构的传动方案 6

2.2.2 选择车轮与轨道，并验算其强度 6

2.2.3 运行阻力计算 8

2.2.4 选择电动机 9

2.2.5 验算电动机的发热功率条件 9

2.2.6 减速器的选择 10

2.2.7 验算运行速度和实际所需功率 10

2.2.8 验算起动时间 10

2.2.9 起动工况下校核减速器功率 11

2.2.10 验算启动不打滑条件 11

2.2.11 选择制动器 13

2.2.12 选择联轴器 14

2.2.13 浮动轴的验算 14

2.2.14 缓冲器的选择 15

3 端梁的设计 17

3.1 端梁的尺寸的确定 17

3.1.1端梁的截面尺寸 17

3.1.2 端梁总体的尺寸 17

3.2 端梁的计算 17

3.3 主要焊缝的计算 20

3.3.1 端梁端部上翼缘焊缝 20

3.3.2 下盖板翼缘焊缝的剪应力验算 21

4 端梁接头的设计 22

4.1 腹板和下盖板螺栓受力计算 22

4.2 计算螺栓和焊缝的强度 24

4.2.1 螺栓的强度校核 24

4.2.2 焊缝的强度校核 24

5 焊接工艺设计 26

6 结论与展望 30

致谢 31

参考文献 32

1 绪论

1.1 起重机背景及其理论

桥式起重机是架设在高架轨道上运行的一种桥架型起重机，又称为天车。桥式起重机的桥架沿着铺设在两侧的高架轨道纵向运行，起重小车沿着铺设在桥架上的轨道横向运行，构成覆盖一定面积的工作区域，这样可以充分利用桥架下面的空间吊运、装卸货物，不受地面设施、货物的阻碍。桥式起重机广泛地应用在室内外仓库、厂房、机场、港口和露天货物场所等处。二十世纪以来，随着钢铁、机械制造业和铁路、港口、航空运输及交通业的的发展，大大的促进了起重运输机械行业的发展。对起重运输机械的性能也提出了更高的要求。现代起重运输机械担当着繁重的货物搬运任务，是工厂、港口、货运铁路等工作部门实现货物搬运、装卸现代化、机械化的关键。因而起重机的金属结构都用质量可靠的钢材制造，并用焊接代替铆接，不但简化机构，缩短了制造时间，而且大大地减轻了自身的重量，焊接结构是现代金属结构的特征。我国是应用起重机械最早的国家之一，我们的祖先采用杠杆搬运石料建造城墙，就是利用起重设备节省人力、装卸货物的例子。几千年的封建统治和近代革命战争的影响，我国工业基础薄弱，自行设计制造的起重机械很少，绝大多数起重运输机械需要依靠进口。新中国成立以来，随着冶金、钢铁工业的发展，起重运输机械也获得了很好的发展，全国刚解放就建立了全国最大的大连起重机械厂，1949 年10月，在该厂试制成功我国第一台起重量为50 吨，跨度为22.5m 的桥式起重机。为培养起重运输机械专业的人才，多所高等工业学校，创办了起重运输机械专业。到目前为止，我国通用门式起重机和工程起重机已摆脱了仿制进口，完全有能力设计制造各种大型先进的起重设备。无论从结构形式，还是性能指针都达到世界领先水平。

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内容简介：: 编号毕业设计（论文）相关资料题目：十吨位桥式起重机大车运行机构设计系专业学号：学生姓名：指导教师：（职称：）（职称：）目录一、毕业设计（论文）开题报告二、毕业设计（论文）外文资料翻译及原文三、学生“毕业论文（论文）计划、进度、检查及落实表”四、实习鉴定表毕业设计（论文）开题报告题目：十吨位桥式起重机大车运行机构设计系专业学号：学生姓名：指导教师：（职称：）（职称：）课题来源生产实践需求科学依据（包括课题的科学意义；国内外研究概况、水平和发展趋势；应用前景等）1 课题的科学意义桥式起重机广泛地应用在室内外仓库、厂房、码头和露天贮料场等处。二十世纪以来，由于钢铁、机械制造业和铁路、港口及交通运输业的的发展，促进了起重运输机械的发展。对起重运输机械的性能也提出了更高的要求。现代起重运输机械担当着繁重的物料搬运任务，是工厂、铁路、港口及其他部门实现物料搬运机械化的关键。2 国内外研究概况、水平和发展趋势起重机作为一种古老的机械，时至今日，在其承载结构、驱动机构、取物装置、控制系统及安全装置等各方面都有了很大的发展，其设计理论、制造工艺、检测手段等都逐渐趋于完善和规范化，并已经成为一种较完善的机械。但由于生产发展提出新的使用要求，起重机的种类、形式也需要相应地发展和创新，性能也需要不断变化与究善。由于现代化设计方法的建立和计算机辅助设计等现代设计手段的应用，使起重机设计思维观念和方法有了进一步的更新，其它技术领域和相邻工业部门不断取得的新科技成果在起重机上的渗透、推广应用等，更使起重机的各方面不断地丰富更新。因此，起重机面向现代化、智慧化、更安全可靠方便的方向发展。3 应用现状及其前景加入世贸组织后，虽然国内市场(特别是配套件)将受到较大冲击，但同时也给我们带来新技术的应用，使国内主机和配套件企业更清晰认识到差距，更多地了解国产产品存在的致命问题，必将引导主机和配套件企业的技术创新和技术进步。随着工程机械产品近十年来随着技术的引进、消化、吸收，有了长足的进步，产品性能、可靠性、外观都有较大幅度的提高，但同国外工程机械比较来看，还存在较大差距，就工程起重机而言，今后的发展主要表现在如下几个方面：（1）整机性能，由于先进技术和新材料的应用,同种型号的产品，整机重量要轻20%左右。随着结构分析应用和先进设备的使用,结构形式更加合理（2）高性能、高可靠性的配套件,选择余地大、适应性好,性能得到充分发挥（3）电液比例控制系统和智能控制显示系统的推广应用（4）操作更方便、舒适、安全、保护装置更加完善（5）向吊重量大、起升高度、幅度更大的大吨位方向发展。研究内容十吨位桥式起重机大车运行机构设计确定机构传动方案选择电动机，并验算电动机的发热功率条件选择减速器，制动器，联轴器端梁的设计运用 CAD 绘制装配图零件图撰写毕业设计论文拟采取的研究方法、技术路线、实验方案及可行性分析去实习工厂实地研究学习，查阅桥式起重机的相关资料，分析总结。按照机械设计的相关要求按步骤进行设计和验算。明确设计要求，调查研究，收集设计资料，绘出零件图，装配图。按照步骤，实验方案可行。研究计划及预期成果研究计划：2012 年 11 月 12 日-2012 年 12 月 2 日：教师下达毕业设计任务，学生初步阅读资料，完成毕业设计开题报告。2013 年 1 月 21 日-2013 年 3 月 1 日：指导毕业实习。2013 年 3 月 4 日-2013 年 3 月 15 日：确定总设计方案。2013 年 3 月 18 日-2013 年 3 月 22 日：总体设计（包括参数计算及结构分析计算）。2013 年 3 月 25 日-2013 年 4 月 5 日：总体设计（完成参数计算及结构分析计算后绘制草图；装配图）。2013 年 4 月 8 日-2013 年 4 月 26 日：零件设计。2013 年 4 月 29 日-2013 年 5 月 25 日：毕业论文说明书撰写和修改工作。预期成果：认识了解桥式起重机的相关知识了解和工作方式。设计出 10 吨位桥式起重机的大车部分。完成毕业设计论文和 CAD 制图。特色或创新之处对桥式起重机进行全面的了解，分析设计桥式起重机的大车机构已具备的条件和尚需解决的问题我已学习机械数控专业三年之久，掌握了一些这专业的部分知识，老师也给了一些参照资料，可以进行这方面的研究。尚需解决的问题：（1）车轮的计算及车轮的设计对各部件之间连接方法和传动方式的选择。（2）进给部件的强度刚度校核需要对进给部件的强度和刚度有保证，满足工作时的受力要求，需要进行校核计算。指导教师意见指导教师签名：年月日教研室（学科组、研究所）意见教研室主任签名：年月日系意见主管领导签名：年月日外文资料翻译及原文英文原文：Fatigue life prediction of the metalwork of a travelling gantrycraneAbstractIntrinsic fatigue curves are applied to a fatigue life prediction problem of the metalwork of a traveling gantry crane. A crane, used in the forest industry, was studied in working conditions at a log yard, an strain measurements were made. For the calculations of the number of loading cycles, the rain flow cycle counting technique is used. The operations of a sample of such cranes were observed for a year for the average number of operation cycles to be obtained. The fatigue failure analysis has shown that failures some elements are systematic in nature and cannot be explained by random causes.卯 1999 Elsevier Science Ltd. All rights reserved.Key words: Cranes; Fatigue assessment; Strain gauging1. IntroductionFatigue failures of elements of the metalwork of traveling gantry cranes LT62B are observed frequently in operation. Failures as fatigue cracks initiate and propagate in welded joints of the crane bridge and supports in three-four years. Such cranes are used in the forest industry at log yards for transferring full-length and sawn logs to road trains, having a load-fitting capacity of 32 tons. More than 1000 cranes of this type work at the enterprises of the Russian forest industry. The problem was stated to find the weakest elements limiting the cranes fives, predict their fatigue behavior, and give recommendations to the manufacturers for enhancing the fives of the cranes.2. Analysis of the crane operationFor the analysis, a traveling gantry crane LT62B installed at log yard in the Yekaterinburg region was chosen. The crane serves two saw mills, creates a log store, and transfers logs to or out of road trains. A road passes along the log store. The saw mills are installed so that the reception sites are under the crane span. A schematic view of the crane is shown in Fig. 1.1350-6307/99/$一 see front matter 1999 Elsevier Science Ltd. All rights reserved.PII: S 1 3 5 0 一 6307(98) 00041 一 7A series of assumptions may be made after examining the work of cranes:if the monthly removal of logs from the forest exceeds the processing rate, i.e. there is a creation of a log store, the crane expects work, being above the centre of a formed pile with the grab lowered on the pile stack;when processing exceeds the log removal from the forest, the crane expects work above an operational pile close to the saw mill with the grab lowered on the pile;the store of logs varies; the height of the piles is considered to be a maximum;the store variation takes place from the side opposite to the saw mill;the total volume of a processed load is on the average k=1.4 times more than the total volume of removal because of additional transfers.2.1. Removal intensityIt is known that the removal intensity for one year is irregular and cannot be considered as a stationary process. The study of the character of non-stationary flow of road trains at 23 enterprises Sverdlesprom for five years has shown that the monthly removal intensity even for one enterprise essentially varies from year to year. This is explained by the complex of various systematic and random effects which exert an influence on removal: weather conditions, conditions of roads and lorry fleet, etc. All wood brought to the log store should, however, be processed within one year.Therefore, the less possibility of removing wood in the season between spring and autumn, the more intensively the wood removal should be performed in winter. While in winter the removal intensity exceeds the processing considerably, in summer, in most cases, the more full-length logs are processed than are taken out.From the analysis of 118 realizations of removal values observed for one year, it is possible to evaluate the relative removal intensity g(t) as percentages of the annual load turnover. The removal data fisted in Table 1 is considered as expected values for any crane, which can be applied to the estimation of fatigue life, and, particularly, for an inspected crane with which strain measurement was carried out (see later). It would be possible for each crane to take advantage of its load turnover per one month, but to establish these data without special statistical investigation is difficult. Besides, to solve the problem of life prediction a knowledge of future loads is required, which we take as expected values on cranes with similar operation conditions.The distribution of removal value Q(t) per month performed by the relative intensity q(t) is written aswhere Q is the annual load turnover of a log store, A is the maximal designed store of logs in percent of Q. Substituting the value Q, which for the inspected crane equals 400,000 m3 per year, and A=10%, the volumes of loads transferred by the crane are obtained, which are listed in Table 2, with the total volume being 560,000 m3 for one year using K,.2.2. Number of loading blocksThe set of operations such as clamping, hoisting, transferring, lowering, and getting rid of a load can be considered as one operation cycle (loading block) of the crane. As a result to investigations, the operation time of a cycle can be modeled by the normal variable with mean equal to 11.5 min and standard deviation to 1.5 min. unfortunately, this characteristic cannot be simply used for the definition of the number of operation cycles for any work period as the local processing is extremely irregular. Using a total operation time of the crane and evaluations of cycle durations, it is easy to make large errors and increase the number of cycles compared with the real one. Therefore, it is preferred to act as follows.The volume of a unit load can be modeled by a random variable with a distribution function(t) having mean22 m3 and standard deviation 6;一 3 m3, with the nominal volume of one pack being 25 m3. Then, knowing the total volume of a processed load for a month or year, it is possible to determine distribution parameters of the number of operation cycles for these periods to take advantage of the methods of renewal theory 1.According to these methods, a random renewal process as shown in Fig. 2 is considered, where the random volume of loads forms a flow of renewals: In renewal theory, realizations of random:，，，having a distribution function F-(t), are understoodas moments of recovery of failed units or request receipts. The value of a processed load:，，afterth operation is adopted here as the renewal moment.Let F(t)=P t . The function F-(t) is defined recurrently,nLet v(t) be the number of operation cycles for a transferred volume t. In practice, the total volume of a transferred load t is essentially greater than a unit load, and it is useful therefore totake advantage of asymptotic properties of the renewal process. As follows from an appropriatelimit renewal theorem, the random number of cycles v required to transfer the large volume t hasthe normal distribution asymptotically with mean and variance.without dependence on the form of the distribution function 月 t) of a unit load (the restriction isimposed only on nonlattice of the distribution).Equation (4) using Table 2 for each averaged operation month,function of number of load cycles with parameters m,. and 6,., which normal distribution in Table 3. Figure 3 shows the average numbers of cycles with 95 % confidence intervals. The values of these parametersfor a year are accordingly 12,719 and 420 cycles.3. Strain measurementsIn order to reveal the most loaded elements of the metalwork and to determine a range of stresses, static strain measurements were carried out beforehand. Vertical loading was applied by hoisting measured loads, and skew loading was formed with a tractor winch equipped with a dynamometer. The allocation schemes of the bonded strain gauges are shown in Figs 4 and 5. As was expected, the largest tension stresses in the bridge take place in the bottom chord of the truss (gauge 11-45 MPa). The top chord of the truss is subjected to the largest compression stresses.The local bending stresses caused by the pressure of wheels of the crane trolleys are added to the stresses of the bridge and the load weights. These stresses result in the bottom chord of the I 一 beambeing less compressed than the top one (gauge 17-75 and 10-20 MPa). The other elements of the bridge are less loaded with stresses not exceeding the absolute value 45 MPa. The elements connecting the support with the bridge of the crane are loaded also irregularly. The largest compression stresses take place in the carrying angles of the interior panel; the maximum stresses reach h0 MPa (gauges 8 and 9). The largest tension stresses in the diaphragms and angles of the exterior panel reach 45 MPa (causes 1 and hl.The elements of the crane bridge are subjected, in genera maximum stresses and respond weakly to skew loads. The suhand, are subjected mainly to skew loads.1, to vertical loads pports of the crane gmmg rise to on the otherThe loading of the metalwork of such a crane, transferring full-length logs, differs from that ofa crane used for general purposes. At first, it involves the load compliance of log packs because ofprogressive detachment from the base. Therefore, the loading increases rather slowly and smoothly.The second characteristic property is the low probability of hoisting with picking up. This is conditioned by the presence of the grab, which means that the fall of the rope from the spreader block is not permitted; the load should always be balanced. The possibility of slack being sufficient to accelerate an electric drive to nominal revolutions is therefore minimal. Thus, the forest traveling gantry cranes are subjected to smaller dynamic stresses than in analogous cranes for general purposes with the same hoisting speed. Usually, when acceleration is smooth, the detachment of a load from the base occurs in 3.5-4.5 s after switching on an electric drive. Significant oscillations of the metalwork are not observed in this case, and stresses smoothly reach maximum values.When a high acceleration with the greatest possible clearance in the joint between spreader andgrab takes place, the tension of the ropes happens 1 s after switching the electric drive on, theclearance in the joint taking up. The revolutions of the electric motors reach the nominal value inO.r0.7 s. The detachment of a load from the base, from the moment of switching electric motorson to the moment of full pull in the ropes takes 3-3.5 s, the tensions in ropes increasing smoothlyto maximum. The stresses in the metalwork of the bridge and supports grow up to maximumvalues in 1-2 s and oscillate about an average within 3.5%.When a rigid load is lifted, the accelerated velocity of loading in the rope hanger and metalworkis practically the same as in case of fast hoisting of a log pack. The metalwork oscillations are characterized by two harmonic processes with periods 0.6 and 2 s, which have been obtained from spectral analysis. The worst case of loading ensues from summation of loading amplitudes so that the maximum excess of dynamic loading above static can be 13-14%.Braking a load, when it is lowered, induces significant oscillation of stress in the metalwork, which can be r7% of static loading. Moving over rail joints of 3 mm height misalignment induces only insignificant stresses. In operation, there are possible cases when loads originating from various types of loading combine. The greatest load is the case when the maximum loads from braking of a load when lowering coincide with braking of the trolley with poorly adjusted brakes.4. Fatigue loading analysisStrain measurement at test points, disposed as shown in Figs 4 and 5, was carried out during the work of the crane and a representative number of stress oscillograms was obtained. Since a common operation cycle duration of the crane has a sufficient scatter with average value 11.5min, to reduce these oscillograms uniformly a filtration was implemented to these signals, and all repeated values, i.e. while the construction was not subjected to dynamic loading and only static loading occurred, were rejected. Three characteristic stress oscillograms (gauge 11) are shown inFig. 6 where the interior sequence of loading for an operation cycle is visible. At first, stressesincrease to maximum values when a load is hoisted. After that a load is transferred to the necessary location and stresses oscillate due to the irregular crane movement on rails and over rail joints resulting mostly in skew loads. The lowering of the load causes the decrease of loading and forms half of a basic loading cycle.4.1. Analysis of loading process amplitudesTwo terms now should be separated: loading cycle and loading block. The first denotes one distinct oscillation of stresses (closed loop), and the second is for the set of loading cycles during an operation cycle. The rain flow cycle counting method given in Ref. 2 was taken advantage of to carry out the fatigue hysteretic loop analysis for the three weakest elements: (1) angle of the bottom chord(gauge 11), (2) I-beam of the top chord (gauge 17), (3) angle of the support (gauge 8). Statistical evaluation of sample cycle amplitudes by means of the Waybill distribution for these elements has given estimated parameters fisted in Table 4. It should be noted that the histograms of cycle amplitude with nonzero averages were reduced afterwards to equivalent histograms with zero averages.4.2. Numbers of loading cyclesDuring the rain flow cycle counting procedure, the calculation of number of loading cycles for the loading block was also carried out. While processing the oscillograms of one type, a sample number of loading cycles for one block is obtained consisting of integers with minimum and maximum observed values: 24 and 46. The random number of loading cycles vibe can be describedby the Poisson distribution with parameter =34.Average numbers of loading blocks via months were obtained earlier, so it is possible to find the appropriate characteristics not only for loading blocks per month, but also for the total number of loading cycles per month or year if the central limit theorem is taken advantage of. Firstly, it is known from probability theory that the addition of k independent Poisson variables gives also a random variable with the Poisson distribution with parameter k,. On the other hand, the Poisson distribution can be well approximated by the normal distribution with average, and variation ,. Secondly, the central limit theorem, roughly speaking, states that the distribution of a large number of terms, independent of the initial distribution asymptotically tends to normal. If the initial distribution of each independent term has a normal distribution, then the average and standard deviation of the total number of loading cycles for one year are equal to 423,096 and 650 accordingly. The values of k are taken as constant averages from Table 3.5. Stress concentration factors and element enduranceThe elements of the crane are jointed by semi-automatic gas welding without preliminary edge preparation and consequent machining. For the inspected elements 1 and 3 having circumferential and edge welds of angles with gusset plates, the effective stress concentration factor for fatigue is given by calculation methods 3, kf=2.r2.9, coinciding with estimates given in the current Russian norm for fatigue of welded elements 4, kf=2.9.The elements of the crane metalwork are made of alloyed steel 09G2S having an endurance limit of 120 MPa and a yield strength of 350 MPa. Then the average values of the endurance limits of the inspected elements 1 and 3 are ES 一 l=41 MPa. The variation coefficient is taken as 0.1, and the corresponding standard deviation is 6S-、一 4.1 MPa.The inspected element 2 is an I-beam pierced by holes for attaching rails to the top flange. The rather lar

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