围板包装箱自动化铆接装置的设计【含CAD图纸】
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无锡太湖学院毕业设计（论文）开题报告题目： 围板包装箱自动化生产线铆接装置的设计 信机 系 机械工程及自动化专业 学 号： 0923108 学生姓名： 张亚卫 指导教师： 何雪明（职称：副教授 ） 2012年5月12日课题来源 ：工厂科学依据：1.课题的科学意义 围板箱作为产品外包的物流设施，具有可重复使用，能回收、降低成本、环保等优点。且越来越受客户的欢迎，使用量巨大。2. 研究现状及发展前景研究内容： 围板包装箱作为产品的外包物流设备具能够重复使用，可回收、降低运输成本、环保等优点。在运输产品方面受到广泛的运用，需求日益增加。现有的围板箱生产方式落后，并且在生产中人为因素较大，这使得围板箱的生产上存在着生产效率低，质量不稳定等缺陷，严重影响着围板箱的应用。 通过对现有围板箱生产工艺的分析研究，并结合围板箱生产上的要求，提出了生产工艺改进方案。依据凸轮技术为基础，完成围板包装箱自动化铆接装置的设计，通过对自动化铆接装置的分析，描绘出机床的工作循环图，装配图及电气控制图等，利用UG软件对钻铆系统进行三维建模。拟采取的研究方法、技术路线、实验方案及可行性分析，熟悉围板加工流程，对工作过程进行具体分析研究，了解围板目前生产工艺，分析改进。拟采取的研究方法、技术路线、实验方案及可行性分析：方案：放第一块围板定位夹紧钻四个孔移位对围板另一端进行钻孔移位定位夹紧上铰链插8个铆钉铆接8个铆钉移位可行性分析：实现围板的钻孔后对两块围板的一次定位夹紧，上铰链铆钉，钻铆移位。对钻孔后围板的一次定位夹紧加工，避免了围板在上铰链铆钉的的过程中因为移位而导致铆钉无法装配到位的问题。很大程度上缩短了的生产时间提高了围板的生产效率。研究计划及预期成果：2012年11月12日-2009年12月25日：按照任务书要求查阅论文相关参考资料，填写毕业设计开题报告书。2013年1月11日-2013年3月5日：填写毕业实习报告。2013年3月8日-2013年3月14日：按照要求修改毕业设计开题报告。2013年3月15日-2013年3月21日：学习并翻译一篇与毕业设计相关的英文材料。2013年3月22日-2013年4月11日：UG三维建模。2013年4月12日-2013年4月25日：围板包装箱自动化铆接装置模型的设计2013年4月26日-203年5月20日：毕业论文撰写和修改工作。特色或创新之处： 通过对现有生产工艺的分析，提出对钻孔后围板的一次定位夹紧对一个铰链的铆接思想，用UG绘图软件进行三维建模，模拟仿真，较直观的检验方案的可行性。已具备的条件和尚需解决的问题 用UG软件对所设计的围板包装箱自动化生产线进行三维实体仿真，针对现有围板生产工艺的分析，结合实际生产过程中存在的各种问题，对围板包装箱生产线做合理的改进。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 中文译文4.3 在喷油螺杆压缩机的流量 4.3.1 网格生成的油润滑压缩机 阳极和阴极的转子有40个数值细胞沿各叶片间的圆周方向，6细胞在径向和轴向方向上的112。这些形式为转子和壳体444830细胞总数。为了避免需要增加网格点的数量，如果一个更精确的计算是必需的，一个适应的方法已应用于边界的定义。 时间变化的数量为25，在这种情况下，一个内部循环。的对阳极的转子转一圈所需的时间步骤的总数是那么125。在转子中的细胞数为每个时间步长保持相同。以实现这一目标，一个特殊的网格移动程序开发中的时间通过压缩机转速的确定步骤，正如4章解释。对于初始时间步长的数值网格图4-15提出。 图4数值网格喷油螺杆压缩机444830细胞4.3.2数学模型的油润滑压缩机 数学模型的动量，能量，质量和空间方程问题，如第2.2节所描述的，但一个额外的方程的标量属性油的浓度的增加使石油对整个压缩机性能的影响进行计算。本构关系是一样的前面的例子。石油是一种被动的物种在模型处理，这不混合液体-空气的背景。对空气的影响占通过物质和能量的来源是加上或减去的主要流模型相应的方程。在这种情况下，动量方程通过拖曳力的影响如前所述。 建立工作条件和从吸气开始全方位1巴压力获得6，7压力的增加，8和9条近450000细胞放电，数值网格对于每一种情况下只有25时间步骤来获得所需的工作条件，其次是进一步的25的时间的步骤来完成一个完整的压缩机循环。每个时间步所需的约30分钟的运行时间在一个800 MHz的AMD 速龙处理器计算机内存需要约450 MB。4.3.3对油的数值模拟和实验结果的比较淹没式压缩机 在压缩机中的腔室，在压缩机内的循环的实验得到的压力历史和测得的空气流量和压缩机功率的情况下，测量的速度场担任了宝贵的基础，以验证CFD计算的结果。要获得这些值， 5/6喷油压缩机中，已经描述的，测试安装在压缩机实验室在城市大学伦敦，如图4-16上的钻机。4-16喷油螺杆空气压缩机5 / 6-128mm（= 90mm）在测试床4.3流的喷油螺杆压缩机 该试验台满足螺杆压缩机的接受所有pneurop /程序的要求试验。压缩机是根据ISO 1706和交付流程测试测定了BS 5600。高质量的压力传感器测量的压力，与在入口带到压缩机的读数，从压缩机排出和在分离器。温度是通过热电偶测量FeCo入口和放电从压缩机、油分离器后。测量透射电子显微镜温度也被两个，油和冷却水的入口端油冷却器。从冷却器和压缩机的油流量的计算能量和质量平衡。通过实验室型转矩仪传感器测量扭矩的IML色氨酸500连接发动机和压缩机驱动轴之间。压缩机是由一个100千瓦的柴油发动机的最大输出驱动，这可能在可变速度操作。测得的是压缩机的转速频率计、信号转换为电流后，转移到一个数据记录器。图4-17电脑屏幕上的压气机试验台的测量程序 压缩机流量测量到BS 5600与所述的孔板通过压力换能器的PDCR 120/35WL超过压差测量经营范围为0200千帕所有相关的脉动量的测量值被用于获得的热力学循环的细节。 这些，在截留容积的压力应用是最重要的，因为它需要绘制机器的PV图。因此，从开发建设的整个光伏图仅需4离散点在机器外壳的压力变化的记录。ENDEVCO压阻式传感器， E8180B被用于测量瞬时同时压缩机中的绝对压力值。每个传感器重新有线的压力在一个叶片空间。从开始的吸入端， 4反式生产者被定位在所述压缩机壳体的变化记录在每个连续叶片空间。当绘制顺序，他们给了压力 - 时间整个压缩机工作循环的图。在两个压缩机的横截面图4-18速度矢量图4 18速度矢量在两个压缩机横截面前截面由不得通过吸入口,底部截面B-B 所有测量值被自动记录和转移到个人电脑通过一个高速InstruNet数据记录器。 数据采集系统启用高速测量的频率以超过2千赫。 收购和测量程序的电脑是写给这在Visual Basic,允许在线测量和计算,压缩机工作参数。 一个电脑屏幕上记录的测量程序给出了图4 17。在图4-18中，在两个横截面的速度矢量。其中一个这些是通过进气口和油喷射管，另一个是靠近排出。图4-19示出了在通过压缩机的垂直截面中的速度。高的速度值的差距，两者之间的转子和他们的住房和两个转子之间，所产生的尖锐的压力梯度通过的间隙。这些有清楚区别的速度在叶片间区域其中的流体流动相对缓慢。引起的流体流有仅由运动的数值网格，这是产生的方式，以跟随的运动在时间上的转子。最上方的图显示了通过的吸入口和油喷射开口的横截面。再循环吸入口是巨大的，因为油的位置，似乎是高喷射孔。如果油注入已进一步向下游的位置，再循环已经减少。底部的图，它示出了横靠近排放口部分，表明更多的再循环环存在于叶片与较低压力下，如在该图的顶部可见。在高压区域进行平滑处理的速度相对较低的值，类似的壁的速度在一定程度上。在轴向截面C-C速度场，它穿过转子沿转子内尖，在图4-19所示图4-19速度矢量在压缩机轴向截面CC 平滑的速度是在高压力区域中可见的右端的图像。在压缩机的上部，其中，低压力和低气压梯度时，流态多弯曲，从而表明流漩涡。也有在吸入口的远端再循环的同时，在同时，流经端口的轴向的一部分是更密集 在截面A-A的油分布和压力场被显示在顶部和底部图分别如图4-20所示。如前所述，一些流体再循环从工作腔的吸入口通过压缩机间隙。图4-20表示，与空气一起，油从逸出加压工作腔室的吸入口，通过转子到转子漏路径。在吸入口的油的存在下也肉眼观察期间这种压缩机的测试。然而，没有测量，用其制成的。图4-20截面通过入口和喷油口A-A油顶质量浓度，底压力分布 一些有限的结果，在油分布的实验研究兴等人（2001 ）公布的螺杆式压缩机。在这种情况下，油流观察到通过使由透明材料制成的压缩机壳体。虽然作者没有完整地记录了他们的结果，它似乎从什么他们出版的3-D计算所得到的油流模式在他们的实验中获得的那些类似。在吸入口的热油的存在下，虽然有益的转子的润滑，增加了气体的工作腔室的温度，然后再关闭。这减少了被困的质量因此压缩机的容量，是另一个的影响不由螺杆压缩机的过程的一维模型，建模。图4-21显示了在压缩机内的压力分布与阳极转子转速为5000rpm 。这个数字表示内的压力的每个工作腔几乎是均匀的，并且其可以被视为例如几乎所有的计算和比较。由于这个原因，所得到的结果的3-D计算可以与从测量得到的那些相比。图4-21两个转子之间的轴向部分 - 压力分布 在工作腔的内压力的变化，如图4-22所示，作为一个阳转子轴角度的功能。这里的压力轴角图与从压缩机测试结果相比。结果显示放电的压力是 6，7， 8和9巴绝对压力在轴速度为5000rpm 。在所有情况下，进气压力为1巴。预测和之间的协议测量值是合理的，尤其是在压缩过程中。一些差异被记录在吸入和排出区。那些在抽吸区域是可能的后果，在图中可见的流量波动4-19 ，这表明，在抽吸过程中的流动和在最开始的压缩还没有这样衰减。另一方面，压阻式传感器用于测量压力进行在较低的压力更高的错误确保接近零在这些领域的差异，这是。记录的差异在高压端，在放电过程中，可能产生的被导致的无法捕捉真正geometryaccurately的。计算出的放电端口简化了从真实的。它也映射到具有相对低的细胞数。的计算精度上的网目尺寸的影响是分析在第4.3.5节中更详细地说明。英文原文The male and female rotors have 40 numerical cells along each interlobe in the circumferential direction, 6 cells in the radial direction and 112 in the axial direction. These form a total number of 444,830 cells for both rotors and the housing.To avoid the need to increase the number of grid points, if a more precise calculation is required, an adaptation method has been applied to the boundary definition.The number of time changes was 25 for one interlobe cycle in this case. The total number of time steps needed for one full rotation of the male rotor is then 125. The number of cells in the rotors was kept the same for each time step. To achieve this, a special grid moving procedure was developed in which the time step was determined by the compressor speed, as explained in Chapter 4. The numerical grid for the initial time step is presented in Figure 4-15.Figure 4-15 Numerical grid for oil injected screw compressor with 444,830 cells4.3.2 Mathematical Model for an Oil-Flooded Compressor The mathematical model consists of the momentum, energy, mass and space equations, described in section 2.2, but an additional equation for the scalar property of oil concentration was added to enable the influence of oil on the entire com-pressor performance to be calculated.The constitutive relations are the same as in the previous example. The oil is treated in the model as a passiveapryspecies, which does not mix with the background fluid - air. Its influence on the air is accounted arefor through the energy and mass sources which are added to or subtracted from the appropriate equation of the main flow model. In this case, the momentum equation is affected by drag forces as described earlier. To establish the full range of working conditions and starting from a suction pressure of 1 bar to obtain an increase in pressure of 6, 7, 8 and 9 bars at dis-charge, a numerical mesh of nearly d450,000 cells was used. For each case only 25 time steps were required to obtain the required working conditions, followed by a further 25 time steps to complete a full compressor cycle. Each time step needed about 30 minutes running time on an 800 MHz AMD Athlon processor. The computer memory required was about 450 MB.4.3.3 Comparison of the Numerical and Experimental results for an Oil-Flooded CompressoIn the absence of velocity field measurements in the compressor chamber, an experimentally obtained pressure history within the compressor cycle and the measured air flow and compressor power served as a valuable basis to validate the results of the CFD calculation. To obtain these values, the 5/6 oil flooded compressor, already described, was tested on a rig installed in the compressor labo-ratory at City University London, Figure 4-16.Figure 4-16 Oil-Injected air screw compressor 5/6-128mm (a=90mm) in the test bedThe test rig meets all Pneurop/Cagi requirements for screw compressor acceptance tests. The compressor was tested according to ISO 1706 and its delivery flow wasmeasured following BS 5600. The pressures were measured with high quality pressure transducers, with readings taken at the inlet to the compressor, discharge from the compressor andin the separator. The temperatures were measured by FeCo thermocouples at the inlet to and discharge from the compressor and after the oil separator. Measurements of temperature were also taken of both, the oil and the cooling water at the inlet end of the oil cooler. The oil flow rate was calculated from the cooler and compressor energy and mass balances.Torque was measured by a laboratory type torque meter transducer IML TRP500 connected between the engine and the compressor driving shaft. The compressor was driven by a diesel engine prime mover of 100 kW maximum output,which could operate at variable speed. The compressor speed was measured by a frequency meter and the signal was transferred to a data logger after converting to current.Figure 4-17 Computer screen of compressor test rig measuring programThe compressor flow was measured by an orifice plate according to BS 5600 with the differential pressure measured by a pressure transducer PDCR 120/35WL over an operating range of 0-200 kPa.The measured values of all relevant pulsating quantities were used to obtain details of the thermodynamic cycle. Of these, the pressure in the trapped volume was the most significant since it was required to plot the machine p-V diagram. Accordingly, a method was developed to construct an entire p-V diagram from the recording of pressure changes at only 4 discrete points in the machine casing.Endevco piezoresistive transducers E8180B were used to measure the instan-taneous values of the absolute pressure in the compressor. Each transducer re-corded the pressure in one interlobe space. Starting from the suction end, 4 transducers were positioned in the compressor casing to record the changes in each consecutive interlobe space. When plotted in sequence they gave a pressure-time diagram for the whole compressor working cycle.Figure 4-18 Velocity vectors in the two compressor cross sectionsTop cross section A-A through the suction port, Bottom cross section B-B All measured values were automatically logged and transferred to a PC through a high-speed InstruNet data logger. The data acquisition system enabled high speed measurements to be made at frequencies of more then 2 kHz. An acquisition and measuring program for the PC was written for this in Visual Basic that permitted online measurement and calculation of the compressor working parameters. A computer screen record of this measuring program is given in Figure 4-17. In Figure 4-18 the velocity vectors in two cross sections are presented. One of these is through the inlet port and oil injection pipe and the other is close to dis-charge. Figure 4-19 shows the both locities in the vertical section through the com-pressor. High velocity values in the gaps, both between the rotors and their hous-ing and between the two rotors, are generated by the sharp pressure gradients through the clearances. These are clearly distinguished from the velocities in the interlobe regions where the fluid flows relatively slowly. The fluid flow is caused there only by movement of the numerical mesh, which is generated in a manner to follow the movement of the rotors in time. The top diagram shows the cross section through both the suction port and oil injection openings. Recirculation in the suction port is substantial and seems to be high because of the position of the oil injection hole. If the oil injection had been positioned further downstream, the recirculation would have been reduced. The bottom diagram, which shows a cross section close to the discharge port, indicates that more recirculation is present in the lobes with lower pressures, as is visible in the top of the diagram. The velocities in the high pressure regions are smoothed to relatively low values, to some ex-tent similar to the wall velocities. The velocity field in the axial section C-C, which crosses both rotors along therotor bore cusp, is shown in Figure 4-19.Figure 4-19 Velocity vectors in the compressor axial section C-CSmoothing of the velocities is visible in the high pressure regions at the right end of the figure. In the upper portions of the compressor, where both, low pressures and low pressure gradients occur, flow patterns are more curved, thus indicating flow swirls. There is also recirculation in the far end of the suction port while, at the same time, the flow through the axial part of the port is more intensive.The oil distribution and pressure field in the cross section A-A are shown on the top and bottom diagrams of Figure 4-20 respectively. As noted earlier, some fluid recirculates from the working chamber to the suction port through the compressor clearances. Figure 4-20 indicates that together with air, the oil escapes from the pressurised working chamber to the suction port through the rotor-to-rotor leakage paths. The presence of oil in the suction port was also observed visually during tests on this compressor. However, no measurements were made of it.Figure 4-20 Cross section through the inlet port and oil injection port A-ATop mass concentration of oil, Bottom - Pressure distributionSome limited results of an experimental investigation on oil distribution within a screw compressor are published by Xing et al (2001). In that case, the oil flow was observed by making the compressor casing from a transparent material. Although the authors do not have a complete record of their results, it appears from what they published that the oil flow patterns obtained from the 3-D calculations are similar to those obtained in their experiments. The presence of hot oil in the suction port, although beneficial for the lubrication of the rotors, increases the gas temperature before the working chamber is closed. This reduces the trapped mass and hence the compressor capacity and is another of the effects which are not modelled by one-dimensional models of screw compressor processes. Figure 4-21 shows the pressure distribution within the compressor with a male rotor speed of 5000 rpm. This figure indicates that the pressure within the each working chamber is almost uniform and that it can be regarded as such for almost all calculations and comparisons.
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