简易吊车设计【全套含CAD图纸、毕业论文】
毕业设计(论文)任务书I、毕业设计(论文)题目: 简易吊车设计II、 毕 业设计(论文)使用的原始资料(数据)及设计技术要求:设计一移动式简易吊车,要求提升的最大重量为 G=750 公斤,提升的线速度为 ,提升的最大高度为 适用于机械加工车间小范smv/46.0,5.2mH围内的起重和搬运。III、 毕 业设计(论文)工作内容及完成时间:1. 收集资料、外文资料翻译、开题报告 (2 周)2 月 23 日-3 月 8 日 2. 总体方案的确定 (1 周)3 月 9 日-3 月 15 日 3. 参数确定及设计计算 (3 周)3 月 16 日-4 月 5 日 4. 简易吊车装配图设计及零部件图设计 (7 周)4 月 6 日-5 月 24 日 5. 撰写毕业设计论文 (4 周)5 月 25 日-6 月 19 日 、 主 要参考资料:1 璞良贵,纪名刚主编.机械设计.第七版.北京:高等教育出版社,20012孙桓,陈作模主编.机械原理.第六版.北京:高等教育出版社,20023 成大先主编.机械设计手册.北京:化学工业出版社,20044 赵学田主编.机械设计自学入门.北京:冶金工业出版社,19825 Ye Zhonghe, Lan Zhaohui. Mechanisms and Machine Theory. Higher Education Press, 2001.7班学生: 日期: 自 日指导教师:助理指导教师(并指出所负责的部分):教研室主任: 附注:任务书应该附在已完成的毕业设计说明书首页。学士学位论文原创性声明本人声明,所呈交的论文是本人在导师的指导下独立完成的研究成果。除了文中特别加以标注引用的内容外,本论文不包含法律意义上已属于他人的任何形式的研究成果,也不包含本人已用于其他学位申请的论文或成果。对本文的研究作出重要贡献的个人和集体,均已在文中以明确方式表明。本人完全意识到本声明的法律后果由本人承担。作者签名: 日期:学位论文版权使用授权书本学位论文作者完全了解学校有关保留、使用学位论文的规定,同意学校保留并向国家有关部门或机构送交论文的复印件和电子版,允许论文被查阅和借阅。本人授权南昌航空工业学院可以将本论文的全部或部分内容编入有关数据库进行检索,可以采用影印、缩印或扫描等复制手段保存和汇编本学位论文。作者签名: 日期:导师签名: 日期: 毕业设计(论文)开题报告题目 简易吊车设计专 业 名 称 机械设计制造及其自动化班 级 学 号 学 生 姓 名 指 导 教 师 填 表 日 期 年 1 月 5 日1选题的依据及意义:1.选题的依据:该课题和本专业有关,符合本专业的培养目标及教学基本要求,能检验自己四年来的学习情况是否能够学以致用,同时也和本人未来的工作方向紧密相关。2.选题的意义:随着社会的发展,人类生活水平的提高。机械制造自动化技术也因与人类生活密切相关而成为机械制造中最活跃的一个研究领 。制造技术是以 制造技术与计 机技术 技术 自动 制技术 高 技术 合的 ,是一个 机械 与 技术 一 的 学 , 制造技术的技术和水平发生 的化。随着机械化的发展,中 机械设来currency1的用 “业。 人fifl有 以及人的 ,currency1人 成的时,”currency1的会用一 机 人,设而。吊车为设的一 , 有作简 易 动 用活方 ,简易吊车 动机 动和一开 动, 动和动 , 和 提 。2国内外研究概况及发展趋势(含文献综述):随着 技化 的 ,高 技的用来currency1, 设 高 高要求的机的 求 也 。以 的吊车也 工和社会的要求 ,为 ,吊车业的 和技术 。吊车 设计的 论 方与工是基 设计 论和方,用 学技术,以提高 用 意的价格和造 提高 的功能 缩短 开发周期为目的而 的相工作。吊车 论 方与技术研究的宗旨是从吊车作为特 设所要求的安全和可靠的工作目标发,特定技术 济约束条件下,造地成吊车的 设计, 其 用 货期和能要求的 提下到技术与 济最佳搭配。中的吊车设计的发展 历 一个曲折的 。以 currency1是以模仿原苏联的设计为主,凭借设计者的 验, 设计的 。从60年 ,开始 部件的开发设计与实验研究工作,从而 设计从仿制和 验设计渐走向实验研究和计 分析阶段。到 80年 ,随着宝 一些超 企业 外机的引 及与外 联合设计 制造 形 的采用,开始 引入 一些际 的先 技术与设计方。同时 计 机用技术引入设计领 , 吊车设计工作的发展 的动作用。 3研究内容及实验方案: 3.课题研究的主要 容:本课题主要是简 吊车的设计,也是简易吊车的 构设计方案分析及其设计计 ,以及 动装置的设计分析计 并确定。4.课题研究的实验方案:1) 简易吊车设计的初方案根据先选择的工作机构拟定“零部件,初计 确定工作机构的 号, 设计与计 动装置,确定 动方案,画 动示意图。最后依据所有的数据及图形,画制动 装置和 装置的 构图,然后拆画全部零件工作图, 稳定效核。2) 动装置设计的初方案根据 的功率和转速,选择 动机。确定 动方案,画 动示意图,并分配 动比。5目标、主要特色及工作进度主要目标:能学到currency1的知识,为今后工作打下良好的基础。主要特色:能较熟练用Matlab软件 Word软件及AUTOCAD2009软件来协助本次课设计。工作 :2月23日-3月8日fi 外文fi 开题报告。3月9日-3月15日方案的确定。3月16日-4月5日数确定及设计计 。4月6日-5月24日简易吊车装配图设计及零部件图设计。5月25日-6月19日毕业设计论文。 期目标:2008年6月20号 成毕业设计论文, 分 毕业 五、参考文献1 良 , 名 主 。机械设计。 。 :高 教 社,2001.2 , 作模主 。机械原 。 。 :高 教 社,2001.3 成先主 。机械设计 。 化工工业 社,2004.4 学 主 。机械设计自学入 。 : 工业 社,1982.5 ocurrency1a ao“.Mafi Torfl. r d“atorcurrency12001.简易吊车设计学生姓名:指导老师:摘要:本课题的目的就是设计一简易吊车来代替人力实现重物的搬运。该吊车的工作原理是:由电动机经带轮传动和一对开式齿轮传动,将运动和动力传给卷筒,再通过钢丝绳和滑轮组来提升重物。通过任务书中的条件参数,设计计算相关的数据,选择钢丝绳的种类和型号,进而计算出卷筒和滑轮的直径,确定一些其它的标准零部件。在此基础上进行传动装置的设计和计算,完成其进行结构设计,工作主要包括完成了轴的设计、确定了带轮的结构、齿轮的结构、卷筒的结构、滑轮的结构 、伸臂杆和支撑杆的结构,绘制了绘制了吊车的总装配图、制动轮装置和卷筒装置的结构图,完成部分零件工作图的设计。关键词:简易吊车 设计计算 结构设计 指导老师签名:Simple design of the cable carStudents name: Class: Supervisor: Abstract: The purpose of this project is to design a simple realization of the cable car to replace the human handling of heavy weights. The working principle of the cable car is: by the motor via a pulley drive and gear drive off, the movement and momentum to the drum, and then through the rope and pulleys to raise heavy objects group. Conditions through the parameters of the task book, design and calculation of relevant data, select the type and model of wire rope, and then calculated the diameter of the drum and pulley, to identify a number of other parts of the standards. Carried out on the basis of gear design and calculation, to complete its structural design, primarily include the completion of the design of the shaft to determine the structure of the pulley, the gear structure of the drum structure, block structure, under and the supporting bar of the structure, rendering a total mapping of the crane assembly, brake drum round of devices and device structure, the completion of the work of some parts of the design plans.Keyword: Simple cable car Calculation Structural DesignSignature of Supervisor: 一、设计参数1起吊重量1/t ,起吊速度0.5/(m/s),卷筒直径100/mm2工作年限为12年,两班制工作,小批量生产二、主要内容1总体方案分析、设计;2传动总体方案设计;3传动零件的设计、计算;4总体装配图和零件工作图绘制; 目 录1 绪论 (1)1.1 吊车的历史 (1)1.2 吊车国内外的研究现状 (1)1.3 吊车的发展趋势 (2)2 工作机构的设计(4)2.1 钢丝绳的选择 (4)2.1.1 钢丝绳的种类 (4)2.1.2 钢丝绳的型号(4)2.1.3 钢丝绳直径的选择(5)2.2 卷筒和滑轮直径的选择 (5)3 传动装置的设计和计算 (7)3.1 计算卷筒的功率 (7)3.2 计算卷筒的转速 (7)3.3 电动机的选择 (7)3.3.1 电动机类型的选择 (7)3.3.2 电动机转速的选择 (8)3.3.3 电动机功率的选择 (8)3.4 计算总传动比 (8)3.5 确定传动方案,画出传动示意图 (9)3.6 分配传动比 (9)3.7 计算效率。验算电动机的功率(10)3.8 计算各轴的转速、功率和转矩(10)3.9 制动器的选择(12)3.10 传动机构的设计和计算 (13)3.10.1 带传动 (13)3.10.2 齿轮传动 (15)3.11 画出总体结构方案图 (16)4 结构设计 (17)4.1 初算各轴的最小直径(17)4.2 带轮的结构(18)4.3 齿轮的结构(19)4.4 卷筒的结构(20)4.5 滑轮的结构(21)4.6 升臂杆和支撑杆的结构(21)4.6.1 升臂杆和支撑杆的尺寸(21)4.6.2 根据强度条件、决定升臂杆的材料和断面尺寸(22)4.6.3 根据强度条件,决定支撑杆的材料和断面尺寸(25)4.7 画制动轮装置和卷同装置的结构图 (26)4.8 绘制吊车的总装配图 (26)4.9 拆画重要零件图 (26)5 设计小结 (27)5.1 小结 (27)5.2 设计心得 (27)参考文献(29)致 谢(30)1M. Suk Effect of mechanical design of the suspension on dynamic loading processReceived: 2 July 2003 / Accepted: 24 February 2004 / Published online: 3 August 2005_ Springer-Verlag 2005Abstract: In designing a load/unload system utilized in hard disk drives, necessary care needs to be taken to ensure that the slider does not damage the disk surface during loading and unloading processes. However, a small deviation in the design point of the preload between the load-dome and flexure can lead to undesirableloading processes resulting in an adverse number of slider/disk contacts. In this study, we show that if the preload between the load-dome and flexure is too low, the slider can oscillate causing the corners of the slider to contact the disk multiple times even though the slider is a few microns away from the disk. In addition, the slider can be sucked down towards the disk resulting in a complete separation of the load-dome from the flexure assembly leading to uncontrolled loading conditions.This separation occurs while the suspension is still on the ramp, and thus no preload is exerted on the slider immediately following the separation. Consequently, the slider flies at a flying height higher than the design point until the gap between the load-dome and flexure closes. Hence, the suspension must be carefully designed to suppress slider oscillation and to ensure that the loaddome does not separate during the loading process.1 IntroductionOne of the requirements in designing a load/unload system utilized in hard disk drives is ensuring that the slider does not damage the disk surface during loading and unloading processes. Since it is difficult to avoid slider/disk contacts in entirety, however, the system is designed to minimize the number of slider/disk contact events and to lessen the consequences when contacts do occur. The likelihood of slider/disk contacts depends on the loading speed, disk speed, static attitude of the slider, air-bearing roughness, slider geometry, etc. For example, sliders with a large radius of curvature at its corners can eliminate disk damage by reducing the contact stress between the slider and disk surface (Suk and Gillis 1998). Many recent studies have considered the effect of suspension, limiter, and air-bearing designs on the robustness of the loading and unloading processes (Bogy and Zeng 2000; Hua et al. 2001; Liu and Zhu 2001; Zeng and Bogy 2000). Howeve2r, most of these studies have primarily focused on the unloading process since this part of the sequence usually reveals interesting dynamic processes due to the effects of negative pressure airbearing designs. The negative pressure region of the airbearing resists the unloading action resulting in storage of potential energy in the flexure and suspension assembly.When the slider is finally pulled away from the disk and the potential energy is released, the slider can oscillate violently (Fig.1). On the other hand, for areasonably well-designed system, the loading process does not exhibit such a behavior. Hence, most have primarily investigated the unloading process giving onl a cursory attention to the more critical loading process. Most designers of load/unload systems will find that the loading process can be more troublesome compared to the unloading process. Besides potentially causing damage to the disk, other problems can be encountered during the loading process. For example, in some instances, the slider may never load to the designed flying height, but rather, load at flying heights on the order of 1 lm (Suk et al. 2004). In this paper, we show how a small deviation in the mechanical design of the flexure/suspension assembly can increase the probability of slider/disk contacts that can lead to a significant number of disk contacts in one single load cycle. Specifically, we show that a suspension system with low preload between the flexure and loaddome can lead to loading of the slider at an uncontrolled static attitude and velocity. The problems associated with this particular aspect of design can be easily identified by measuring the full-body capacitance during the loading process.2 Description of experimentThe slider loading dynamics was investigated using a laser-Doppler vibrometer (LDV), 62 kHz frame rate high-speed camera, and full-body capacitance. The experimental setup consists of a standard load/unload tester. The capacitance meter measures the full-body capacitance between the slider and disk while the slider is loading onto the disk, similar to the one used in (Suk et al. 2004). The slider was loaded onto and unloaded from the disk using a moving ramp wh3ile keeping the slider/suspension assembly fixed over the OD region of the disk. The vertical motion of the trailing edge of the slider was measured using an LDV. All tests were carried out using an 84 mm glass disk and a negative pressure bobsled type slider with the disk rotating at 10 krpm. The pitch-static attitude (PSA) of the sliders used in the experiment was between 1 and 2_. To show the effect of lack of preload between the flexure and load-dome, we chose two suspension assemblies that are essentially identical with the exception of the preload. Since the difference in the magnitude of the preload is difficult to measure, only the existence of substantial difference is verified. To do this, we mount the head suspension assembly with normal preload (NPHSA) onto the ramp. A small weight, that is sufficient to cause load-dome separation from the flexure, is then attached to the flexure. The amount of separation is measured with a properly positioned CCD camera.Similar measurement is made for a head suspension assembly with low preload (LP-HSA). Figures 2 and 3 show optical images of the load-dome and flexure taken under the same conditions for both NP-HSA and LPHSA, respectively. A greater load-dome separation from the flexure is observed for LP-HSA than the NP-HSA, confirming that LP-HSA has lower preload than NPHSA. 3 Results and discussion negative pressure sliders The slide4r loads onto the disk and then follows the runout of the disk as expected. The bottom plot in Fig.3 is the corresponding full-body capacitance measurement, which shows a single jump in the capacitance at the moment the slider loads onto the disk. A similar measurement for LP-HSA is shown in Fig.5. In this case, the slider oscillates before loading onto the disk unlike the case with a higher preload between the load-dome and flexure. Furthermore, the sliders vertical loading velocity suddenly increases when the slider is about 50 lm away from the disk. Associated with this sudden increase in the velocity, the capacitance measurement reveals multiple sharp transitions. Following the transitions, the capacitance does not reach the maximum value for another 1 ms or so. These observations indicate a problem, but it is difficult to ascertain the precise dynamics due to the low measurement bandwidth. Higher resolution measurement reveals that the slider contacts the disk multiple times (Fig.6)note that this exact behavior does not occur for every suspension assembly, but varies from one suspension to another. Figure6 shows simultaneous measurement of full-body capacitance and LDV during loading for LP-HAS immediately before fully loading onto the disk surface. Capacitance measurement shows some oscillation about 2 ms before a step-like jump is observed. Note that the average height of the slider during these oscillations is on the order of a few microns. At this height, the suspension preload (not the preload between the flexure and load-dome) is still supported by the ramp. The LDV measurement shows that the slider actually contacts the disk and bounces on-and-off the disk oscillating at the same frequency as that of the measurement made with the capacitance meter. The slider then settles into what appears to be a loaded position, but the capacitance measurement shows that the slider has not fully reached the nominal flying height positionthe capacitance measurement is slightly lower in magnitude than the final value. It takes another 4 ms or so before the slider finally loads fully into the nominal flying height. Surprisingly, LDV is also able to measure this latter process as well. The corresponding arm mounted acoustic emission measurement shows slider/disk contact Fig. 4 Top LDV measurement of the loading motion of the trailing edge of the slider for a system with normal preload between the load-dome and flexure. Bottom Full-body capacitance measurement, which shows a single sharp transition as the slider loads onto the diskverifying the LDV and capacitance measurements of sliderdisk contact (Fig.7). The sligh5t delay in the AE signal is due to the fact the sensor is mounted at the suspension mount point, which is far removed from the location of the contact point. Another example of the loading process is shown in Fig.8 showing a similar behavior.The bounce followed by oscillations and slow settling into the nominal flying height has not been reported before. The reason for the observed deviation is due to the lack of preload between the slider and load-dome. During the loading process, the lack of preload results in oscillation of the slider as seen in Fig.5. This oscillation results in the slider corner contacting the disk multiple times when the slider comes close (on the order of a few microns) to the disk. Then, as the slider comes even closer to the disk, the negative suction force pulls the slider towards the disk separating the load-dome from the flexure. Under certain circumstances, the slider actually can also contact the disk during this phase of the process while the load/unload tab is still sliding on the ramp and the slider is a fraction of a micron away from the disk (Fig.9). This phenomenon is easy to see using a high-speed camera. A set of images captured with a high-speed camera for LP-HSA case is shown in Fig.10. It clearly shows load-dome separation from the flexure resulting in a partial loading on the disk while the load/unload tab is still on the ramp. In this particular case, we were unable to capture the slider/disk contacts using the high-speed camera. The initial phase of the measurements shown in Fig.5 is quite repeatable, i.e. the initial oscillation can be observed every time. However, the slider disk contact is not fully repeatable since this depends on many other parameters, such as, the vertical velocity of the disk at the time of loading and random excitation of the system due to airflow and mechanical vibrations. The suction force that causes the slider to jump towards 6the disk is due to a negative pressure force resulting from negative PSA of the slider relative to the disk surface. The relative PSA is usually negative while the suspension is on the ramp although the absolute PSA may be positive. As the suspension moves across the ramp, the relative PSA constantly changes ultimately reaching the absolute PSA value immediately before loading. During the time the relative PSA is negative, the negative pressure force will try to pull the slider towards the disk. If the sum of the flexure stiffness and the preload between the flexure and load-dome is less than this negative force exerted on the slider, the slider will move towards the disk at speeds higher than the desired speed separating the flexure from the load-dome. Furthermore, since the load-dome is separated from the flexure seen in Fig.10, there is no preload on the slider to push the slider towards the disk. As the gap between the load-dome and flexure closes and the preload of the suspension is transferred from the ramp to the slider, the slider is finally pushed into the nominal flying height as indicated by the final small increase in the capacitance and decrease in height as shown in the LDV measurements(Figs.4, 5, 7, 8). 4 Summary and conclusion Recent articles on load/unload have mainly dealt with the unloading process since the unload dynamics of negative pressure slider reveals an interesting behavior unlike the loading process. However, much more attention to detail is required for the loading process than the unloading process, since the affinity to cause disk damage is much greater during the former process than the latter. In this 7paper, we show that a small deviation in the design point of the preload between the load-dome and flexure can lead to adverse loadingprocesses resulting in an undesirable number of slider/ disk contacts.We show that if the preload between the load-dome and flexure is too low, the slider can oscillate and contact the disk multiple times even when the slider is a few microns away from the disk. Furthermore, we show that the slider can also be pulled down towards the disk completely separating the load-dome from the flexure assembly. This results in slider contacting the disk at an uncontrolled speed that can also lead to disk damage.The separation occurs while the suspension is still on the ramp, and thus there is no preload on the slider following the separation. This lack of preload allows the slider to fly at high flying heights until the gap between the flexure and load-dome closes. Hence, a prudent design of the suspension assembly is required to ensure that the combination of the flexure stiffness and the preload between the load-dome and suspension will be significant enough to defeat the negative pressure force keeping the load-dome attached to the suspension at all times and to suppress slider oscillations before loading.8ReferencesBogy DB, Zeng QH (2000) Design and operating conditions for reliable load/unload systems. Tribol Int 33(56):357366Hua W, Liu B, Sheng G, Li J (2001) Further studies of unload process with a 9D model. IEEE Trans Magn 37(4):18551858Liu B, Zhu LY (2001) Experimental study on head disk interaction in ramp loading process. IEEE Trans Magn 37(4):18091813Suk M, Gillis D (1998) Effect of slider burnish on disk damage during dynamic load/unload. ASME J Tribol 120(2):332338Suk M, Ruiz O, Gillis D (2004) Load/unload systems with multiple flying heights (presented at the 2002 ASME/STLE international tribology conference, Cancu n, Mexico). ASME J Tribol 126(2):367371Zeng QH, Bogy DB (2000) Effects of certain design parameters on load/unload performance. IEEE Trans Magn 36(1): 1401479M. Suk D. Gillis影响机械设计暂停动态加载过程收稿: 2003 年 7月 2 /接受: 2004 年 2月 24日/网上公布: 2005 年 8月 3 _斯普林格 2005年摘要:设计一个加载/卸载系统中使用的硬盘驱动器,必要时需要注意,确保在装货和卸货过程不会损害滑块碟片的表面。因为,在设计点的预负荷之间的穹顶和弯曲的一个小偏差可能会导致不良进程载入,造成一些滑块/磁盘不利的接触。在这项研究中,我们发现,如果预之间的负载圆顶和弯曲太低,滑块的摆动可能会造成角落的滑块接触磁盘过多,使滑杆远离磁盘几微米。此外,滑块可吸入下跌对磁盘造成了完全分离的负载圆顶,使柔性装配导致失控的负载条件。这种分离的情况仍然暂停在坡道,因此没有施加预压的滑块立即分离。因此,滑块苍蝇在飞行高度高于设计点,直到负载圆顶和弯曲之间的差距为零。因此,必须认真地暂停旨在制止滑块振荡,并确保不单独在负荷盘加载过程。1导言 其中一项要求设计 一个加载/卸载系统中使用的硬盘 驱动器是确保在装货和卸货过程滑 块不会损害碟片表面。因为这是难 以避免滑块/磁盘接触的全部内容, 因为,该系统是为了尽量多的减少 滑杆/磁盘接触事件和接触的后果 的发生。滑块/磁盘接触发生接触 的可能性取决于加载速度,硬盘速 度,静态的态度滑块,空气轴承粗 糙度,滑块几何等。例如滑块大曲率半径的弯道可以消除磁盘损害,降低接触应力之间的滑块和磁盘表面(Suk and Gillis 1998) 。许多最近的研究认为,影响暂停与限制器和空气轴承设计的鲁棒性和装卸过程有关(Bogy and Zeng 2000; Hua et al. 2001; Liu and Zhu 2001; Zeng and Bogy 2000) 。不过,这些研究主要集中在卸货的过程,因为这部分序列通常揭示有趣的动态过程的影响和负压空气轴设计。负压区域空气轴抗拒卸货行动导致的潜在能量储存在弯曲和悬挂装备中.当滑块终于脱离磁盘,势能释放,滑块振荡剧烈。另一方面,10为合理的设计系统,加载过程并没有表现出这样的行为。因此,大多数国家都已经在主要调查卸载进程给予粗略注意更重要的加载过程。大多设计师的加载/卸载系统会发现,加载过程可以比卸载过程更麻烦,。除了可能造成损害的磁盘,其他问题都可以遇到的加载过程。例如,在某些情况下,滑块可能永远无法达到负荷的设计飞行高度,而是在飞行高度负荷的命令 1流明(Suk et al. 2004) 。在本文中,我们显示一个小偏差的机械设计的弯曲/暂停大会可以增加概率滑块/磁盘接触,可能导致大量的磁盘接触单一负载周期。具体来说,我们表明,悬挂系统,低预弯曲之间和负荷盘可能导致装载的滑块不受控制静态的态度和速度。相关问题这方面的设计可以很容易地确定测量全身电容在加载过程。2描述的实验滑块载入中动态进行了研究用激光多普勒测振仪(激光多普勒) , 62千赫的帧速率的高速摄像头,全身电容。实验装置包括一个标准的加载/卸载测试。电容米措施全身电容之间的滑块和磁盘而滑块装上磁盘,一个类似于用在(Suk et al. 2004) 。滑块装上和卸下磁盘使用移动坡道,同时保持滑块/暂停固定的外径地区的磁盘。垂直运动的后缘的滑杆是用激光多普勒测量。所有的测试使用 84毫米玻璃磁盘和负压雪橇型滑块与磁11盘旋转 10 krpm进行。球场静态态度(简称 PSA )的滑块用于实验是介于 1和 2_ 。显示效果缺乏预弯曲之间和负载圆顶,我们选择两个暂停集会是基本相同,除预装。由于不同程度的预是难以衡量的,只有存在大量不同的是核实。要做到这一点,我们挂载头部悬挂大会正常预( NPHSA )进入坡道。一个小型的重量,这是足以造成负载穹顶脱离弯曲,然后附在弯曲。分离的数量来衡量一个适当的位置 CCD相机。类似的测量是用于头部暂停低大会预装(唱片白蛋白)。图2和图3显示的光学图像的负载圆顶和弯曲采取相同的条件下为 NP一人血清白蛋白和 LPHSA分别。更大的负载穹顶脱离弯曲是观察唱片白蛋白比 NP一人血清白蛋白,确认唱片白蛋白低预比 NPHSA 。 3结果与讨论负压滑块滑块负载到磁盘,然后按照跳动磁盘预期。底部的阴谋是在图 3的相应全身电容测量,这表明在一个单一的跳转电容此刻滑块负载到磁盘。类似的测量唱片- HSA的是显示在图 5 。在这种情况下,将滑块振荡在装货前到磁盘的情况不同,具有较高的预压荷载圆顶和弯曲。此外,滑盖的垂直加载速度突然增加时,滑块约为 50流明远离磁盘。与此相关的突然增加,速度,电容测量显示多个急剧转变。继过渡,电容不能达到的最高值为另一个 1毫秒左右。这些意见表明一个问题,但很难确定确切的动态,由于低测量带宽。更高分辨率的测量表明,滑块接触磁盘多次(图6 ) ,注意,这完全行为不会发生,每暂停大会,但不同暂停到另一个。图6显示同步测量全身电容和激光多普勒在装货唱片,已立即在完全加载到磁盘的表面。电容测量表明一些振荡约2毫秒之前的一个步骤样跳转得到遵守。请注意,平均身高滑块在这些振荡是对秩序的几个微米。在这一高度,暂停预(而不是预之间的柔性和负载圆顶)仍然是支持的坡道。在激光多普勒测量结果表明,滑块实际接触磁盘和弹跳上和12从磁盘振荡在相同的频率,在测量与电容米。滑块然后解决什么似乎是一个加载的位置,但电容测量表明,该滑块没有完全达到了标称飞行高度位置的电容测量略低规模比最后的值。另需4 毫秒或之前滑块最后负荷充分融入名义飞行高度。令人惊讶的是,激光多普勒也是能够衡量后者的进程。相应的胳膊安装声发射测量表明滑块/磁盘联络图。 4顶级激光多普勒测量负荷运动后缘的滑块的系统之间的正常预负荷圆顶和弯曲。底部全身电容测量,这显示出急剧转型滑块负载到磁盘核查激光多普勒和电容测量滑块磁盘接触(图7 ) 。稍有延误,声发射信号的原因是传感器安装在减震器点,这是远离的位置,联络点。另一个例子是在加载过程中显示图8显示了类似的行为。随后的反弹振荡和缓慢的名义解决飞行高度还没有报告过。的原因,观察偏差是由于缺乏预之间的滑块和负载圆顶。在装载过程中,缺乏预结果振荡滑块看到的图。这种振荡的结果滑块角落接触磁盘多次当滑块接近(在命令几微米)的磁盘。然后,将滑块来更接近盘,负吸力量拉动滑块对分离的磁盘负载圆顶从弯曲。在某些情况下,将滑块还可以联系实际的磁盘在此阶段的进程,而加载/卸载选项卡仍然是滑动的坡道和滑块的一小部分微米远离磁盘(图 9 ) 。这种现象很容易看到使用高速摄像头。一组拍摄 与一个高速摄像机唱片- HSA的案件中显示图。这清13楚地表明负载穹顶脱离弯曲造成了部分负荷,同时在磁盘上的加载/卸载选项卡仍然在坡道。在这种情况下,我们无法捕捉滑块/磁盘接触,利用高速摄像头。初期阶段的测量显示在图 5是相当重复的,即 初始振荡可以看到每一次。然而,滑块磁盘联系不完全重复的,因为这取决于许多其他参数,如垂直速度的磁盘在装载时和随机激励的制度,由于气流和机械振动。吸力的力量,使滑块跳转对磁盘是由于负面压力变压吸附造成负面的滑块相对于硬盘的表面。相对港务集团通常是消极的,而暂停的坡道上虽然绝对港务集团可能是积极的。作为全国暂停行动的坡道,相对港务集团不断变化最终达到绝对港务集团价值立即在装货前。在时间的相对港务集团是否定的,消极的压力将尝试拉滑块对磁盘。如果总和弯曲刚度和预紧力之间的柔性和负载圆顶不到这种消极力量施加的滑块,滑块将走向磁盘的速度高于预期的速度分离弯曲的负载圆顶。此外,由于负载圆顶是分开弯曲,图中可以看出,没有预装的滑杆推动滑块实现磁盘。随着之间的差距负载圆顶和弯曲关闭和预紧暂停从坡道滑块,滑块终于被推到名义飞行高度所示的最后略有增加电容和降低高度所显示的 LDV测量 (图.4 , 5 , 7 , 8 ) 。 4摘要和结论最近文章加载/卸载主要处理过程,因为卸载的卸载动态负压滑块揭示了一个有趣的行为不同,加载过程。然而,更多 注重细节是需要加载过程比卸货过程中,由于亲造成磁盘损害要大得多前进程在比后者。在本文中,我们表明,一个小偏差在设计点的预负荷之间的穹顶和弯曲可能会导致不良载入中 进程造成不良一些滑杆/磁盘接触。 我们发现,如果预之间的负载圆顶和弯曲太低,滑块可以摆动和接触磁盘多次即使滑杆是几微米远离磁盘。此外,我们表明,滑块也可以推倒对磁盘完全分开的负载圆顶从弯曲大会。这样的结果是滑块接触磁盘上失控速度也可能导致硬盘损坏。14分离时发生暂停仍然在坡道,因此没有预装以下的滑块分离。这种缺乏预使滑块飞行,飞行高度高,直到之间的差距弯曲和负载圆顶关闭。因此,谨慎的设计暂停大会必须确保该组合弯曲刚度和预紧力之间的负载圆顶和暂停将是很大的,足以承载负面压力保持负载圆顶重视暂停任何时候,以制止在装货前滑块振荡。15参考资料Bogy DB, Zeng QH (2000) Design and operating conditions for reliable load/unload systems. Tribol Int 33(56):357366Hua W, Liu B, Sheng G, Li J (2001) Further studies of unload process with a 9D model. IEEE Trans Magn 37(4):18551858Liu B, Zhu LY (2001) Experimental study on head disk interaction in ramp loading process. IEEE Trans Magn 37(4):18091813Suk M, Gillis D (1998) Effect of slider burnish on disk damage during dynamic load/unload. ASME J Tribol 120(2):332338Suk M, Ruiz O, Gillis D (2004) Load/unload systems with multiple flying heights (presented at the 2002 ASME/STLE international tribology conference, Cancu n, Mexico). ASME J Tribol 126(2):367371Zeng QH, Bogy DB (2000) Effects of certain design parameters on load/unload performance. IEEE Trans Magn 36(1): 140147
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