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轴承 检测 装置 外观设计

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轴承检测装置的外观设计,轴承,检测,装置,外观设计

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AAA-ABBB-B 100170701.79907145 HT2006302071GB/T 276-199451zcjczz-0541 HT200zcjczz-043 1HT200zcjczz-032145 HT200zcjczz-021145 HT200zcjczz-01JB/ZQ4450-1986761094318.952610152551:7101zcjczz-00 1.2.,3.,4.,5. 1 2 34 5 6 737050268.1281.5274388.8704007920365.1265370512143444137.6563235302459020119180175381.4373112601851.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.80.872.5352512304511647273.9281.453.23.26.46.4 2302071HT200GB/T 276-1994132zcjczz-00-04-016.4 1 21:3105zcjczz-00-05AAA-A4010+0.05-0.0151202028354025+0.03-0.011001254545171750110704026 1.220250HBS;2.R1.5;3.1.5x45.4.GBT 1824-m.305050AB1.61.61.61.63.22840GB6170-861M10x120840GB5782-8610+0.05-0.0125+0.03-0.011850.04A0.04A0.030.031:11072zcjczz-00-02-01 1 2BBB-B204092020405078045.15+0.1-0.05100.053435843923531535 A152M4440GB9287-861M4x35440GB5782-86H7/r8101515200.03A0.043.21.61.63.23.21.170210HBS;2.R3;3.1.5x454.1:1BB10103zcjczz-00-04-01 1 2B-BCCC-C1001141209418419076.44x10300.05374050500.052530383860512+0.04-0.0313150.01H7h73061.31.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.990.0533 74.90.030.03101001530AB0.03B11201034342M12440GB9787-861M 12 x172440GB5782-860.04B201.61.61.63.23.23.2 1 21zcjczz-00-03-011:2109CBBBBB-B3302404501009202152535301102045353046957550259151002512017014221.1470198.5285.814.5160351.51554412840203051554073.93420147.120.3359.7344.64263061.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.23.9207.13.23.22302074GB/T 276-19941 21zcjczz-00-03-011031:3zcjczz-00-03 1 2BBB-BCCC-C127152506.5502051025024988013071.8355.5170301.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.4750402501002231.116.51014010.7402725.223.9244.9zcjczz-00-033.23.20.55.91:3104 1 22302071GB/T 276-199411145 HT200zcjczz-00-03-01BB2598047050412308.1330120575525290240330450880H7h84035100359.720 30 54034260240251803050290754160160512011416211.698.720.330637.1504050151.667.1250353025421021541.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.211HT200zcjczz-00-01-011302071HT200GB/T 276-19945347.9 zcjczz-00-011:3102 1 23.23.26.4BB-B14419098.82830.61308.287.4920B50H7/h7103015.468.312004.560059.617.6121.9203338151.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m. V221.5R1.5R64.5201.61.615951.690.71:2109zcjczz-00-03-01AAA-ABBB-B1130202697.6550528.311008010030317.6109109702903506909001700440359395.11200636.7620104023029050638.8535.210R20R310145.110R20R110784.1451.34.1428.71205010201101202x60506x5028026015R5R504050128.7424.1154.4573.4689.11.,;2.GB/T 1804-m.3.R3-R5. 37033510R20R70815.184.945R5090R858.11237.5943260600550540105011003010606010907085129.7149.3109.12015106040100115.120 1590502091.4115.1324.9100189.8304.14080205R153032.95020152R18.2A1020308.71028.21035403010405140310430A0.05A1.6zcjczz-00-051061:7AAA-ABBB-B 100170701.79907145 HT2006302071GB/T 276-199451zcjczz-0541 HT200zcjczz-043 1HT200zcjczz-032145 HT200zcjczz-021145 HT200zcjczz-01JB/ZQ4450-1986761094318.952610152551:7101zcjczz-00 1.2.,3.,4.,5. 1 2 34 5 6 737050268.1281.5274388.8704007920365.1265370512143444137.6563235302459020119180175381.4373112601851.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.80.872.5352512304511647273.9281.453.23.26.46.4 2302071HT200GB/T 276-1994132zcjczz-00-04-016.4 1 21:3105zcjczz-00-05AAA-A4010+0.05-0.0151202028354025+0.03-0.011001254545171750110704026 1.220250HBS;2.R1.5;3.1.5x45.4.GBT 1824-m.305050AB1.61.61.61.63.22840GB6170-861M10x120840GB5782-8610+0.05-0.0125+0.03-0.011850.04A0.04A0.030.031:11072zcjczz-00-02-01 1 2BBB-B204092020405078045.15+0.1-0.05100.053435843923531535 A152M4440GB9287-861M4x35440GB5782-86H7/r8101515200.03A0.043.21.61.63.23.21.170210HBS;2.R3;3.1.5x454.1:1BB10103zcjczz-00-04-01 1 2B-BCCC-C1001141209418419076.44x10300.05374050500.052530383860512+0.04-0.0313150.01H7h73061.31.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.990.0533 74.90.030.03101001530AB0.03B11201034342M12440GB9787-861M 12 x172440GB5782-860.04B201.61.61.63.23.23.2 1 21zcjczz-00-03-011:2109CBBBBB-B3302404501009202152535301102045353046957550259151002512017014221.1470198.5285.814.5160351.51554412840203051554073.93420147.120.3359.7344.64263061.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.23.9207.13.23.22302074GB/T 276-19941 21zcjczz-00-03-011031:3zcjczz-00-03 1 2BBB-BCCC-C127152506.5502051025024988013071.8355.5170301.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.4750402501002231.116.51014010.7402725.223.9244.9zcjczz-00-033.23.20.55.91:3104 1 22302071GB/T 276-199411145 HT200zcjczz-00-03-01BB2598047050412308.1330120575525290240330450880H7h84035100359.720 30 54034260240251803050290754160160512011416211.698.720.330637.1504050151.667.1250353025421021541.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m.211HT200zcjczz-00-01-011302071HT200GB/T 276-19945347.9 zcjczz-00-011:3102 1 23.23.26.4BB-B14419098.82830.61308.287.4920B50H7/h7103015.468.312004.560059.617.6121.9203338151.220250HBS;2.R1.5;3.1.5x45.4.GB/T 18204-m. V221.5R1.5R64.5201.61.615951.690.71:2109zcjczz-00-03-01AAA-ABBB-B1130202697.6550528.311008010030317.6109109702903506909001700440359395.11200636.7620104023029050638.8535.210R20R310145.110R20R110784.1451.34.1428.71205010201101202x60506x5028026015R5R504050128.7424.1154.4573.4689.11.,;2.GB/T 1804-m.3.R3-R5. 37033510R20R70815.184.945R5090R858.11237.5943260600550540105011003010606010907085129.7149.3109.12015106040100115.120 1590502091.4115.1324.9100189.8304.14080205R153032.95020152R18.2A1020308.71028.21035403010405140310430A0.05A1.6zcjczz-00-051061:7 存档编码：无无锡锡太太湖湖学学院院 0909 届届毕毕业业作作业业周周次次进进度度计计划划、检检查查落落实实表表系别：信机系班级：机械97 学生姓名：鲁浩课题（设计）名称：轴承检测装置的外观设计 开始日期:周次起止日期工作计划、进度 每周主要完成内容存在问题、改进方法指导教师意见并签字备 注12013.3.4下达毕业设计任务实习实训，参与工作存在问题：对于实际操作不是很了解。改进方法：参与工作，逐渐了解，参与其中。22013.3.8填写毕业设计开题报告填写毕业设计开题报告存在问题：对课题难易程度理解不够，难点分析不足，分析能力欠缺，许多问题不是很明白。改进方法：在指导老师的帮助下，进一步消化本课题。32013.3.11检查毕业设计准备情况修改完善毕业设计开题报告存在问题：对课题难点分析不足，分析能力欠缺，对课题理解不深，头脑里没设计的东西的概念改进方法：在指导老师的帮助下，整改开题报告。42013.3.16查阅参考资料查阅与设计有关的参考资料不少于10本，其中外文不少于2本存在问题：由于工作原因，空闲时间很少，查阅资料太少。改进方法：利用一切时间，去图书馆和网上查找相关资料52013.3.23轴承检测装置的外观的设计方案分析任务书、查找资料，分析系统设计步骤，确定方案存在问题：缺乏设计经验，设计方案不合理。改进方法：多去咨询导师了解检测装置的外观设计，重新确立完善设计方案。62013.4.1轴承检测装置的外观设计结构分析与计算确定系统结构，计算得出结构的尺寸存在问题：装置结构设计不合理，尺寸计算有误差公式运用错误，对机构的连接不正确。改进方法：查阅多种参考资料，改进装置的结构，提高计算正确率。系别：信机系班级：机械97 学生姓名：鲁浩课题（设计）名称：轴承检测装置的外观设计 开始日期:72013.4.15轴承检测装置外观设计各机构确定根据轴承检测装置的原理图，分析工作状况存在问题：缺乏专业知识，对各种自动机械不了解，工作情况不够清楚改进方法：多了解实际生产过程和查找资料，重新确定各种自动机械设计各部分。82013.4.20装配图绘制检测装置外观设计各机构装配图存在问题：对UG运用不熟悉，画图速度较慢改进方法：重新确定合理的表达视图，多加运用绘图软件，提高画图速度92013.4.25装配图绘制外观造型设计和检测机构装配图存在问题：装配图中部分连接地方不正确，配合标注不准确。改进方法：按自动机械设计完善连接方式，根据互换性确定配合。102013.4.28气缸图绘制气缸图存在问题：气缸图中技术要求填写不合理，明细栏填写不正确。改进方法：按机械制图要求改正不当之处。112013.5.5说明书、摘要、小结初步构思说明书和摘要，对格式进行修改存在问题：系统设计不够具体，思路不够清晰。改进方法：根据导师的要求进行修改，完善说明书和摘要。122013.5.13检查、指导设计说明书、摘要和小结编写完成设计说明书、摘要和小结存在问题：说明书的格式不规范，摘要不合理，关键词不恰当。改进方法：根据说明书规范要求更改，重新按要求编写摘要。132013.5.15上交资料、答辩整理所有资料上交指导教师，答辩资料整理欠合理，按学院要求整理并装订，进行答辩 说明： 1、“工作计划、进度”、“指导教师意见并签字”由指导教师填写，“每周主要完成内容”，“存在问题、改进方法”由学生填写。 2、本表由各系妥善归档，保存备查。Screw Compressors Mathematical 2.4 Review of Most Popular Rotor Profiles 37Fig. 2.21. “N” Rotors in 5-6 configurationFig. 2.22. “N” Rotors in 5-7 configuration38 2 Screw Compressor GeometryFig. 2.23. “N” rotors in 6/7 configurationsealing lines, small confined volumes, involute rotor contact and proper gate rotor torque distribution together with high rotor mechanical rigidity.The number of lobes required varies according to the designated compressor duty. The 3/5 arrangement is most suited for dry air compression, the4/5 and 5/6 for oil flooded compressors with a moderate pressure difference and the 6/7 for high pressure and large built-in volume ratio refrigeration applications.Although the full evaluation of a rotor profile requires more than just a geometric assessment, some of the key features of the “N” profile may be readily appreciated by comparing it with three of the most popular screw rotor profiles already described here, (a) The “Sigma” profile by Hammertoe,1979, (b) the SRM “D” profile by Absterge 1982, and (c) the “Cyclin” profile by Hough and Morris, 1984. All these rotors are shown in Fig. 2.20 where it can be seen that the “N” profiles have a greater throughput and a stiffer gate rotor for all cases when other characteristics such as the blow-hole area,confined volume and high pressure sealing line lengths are identical.Also, the low pressure sealing lines are shorter, but this is less important because the corresponding clearance can be kept small.The blow-hole area may be controlled by adjustment of the tip radii on both the main and gate rotors and also by making the gate outer diameter equal to or less than the pitch diameter. Also the sealing lines can be kept very short by constructing most of the rotor profile from circles whose cen tres are close to the pitch circle. But, any decrease in the blow-hole area will increasethe length of the sealing line on the flat rotor side. A compromise between these trends is therefore required to obtain the best result.2.4 Review of Most Popular Rotor Profiles 39Rotor instability is often caused by the torque distribution in the gate rotor changing direction during a complete cycle. The profile generation procedure described in this paper makes it possible to control the torque on the gate rotor and thus avoid such effects. Furthermore, full involute contact between the “N” rotors enables any additional contact load to be absorbed more easily than with any other type of rotor. Two rotor pairs are shown in Fig. 2.24 the first exhibits what is described as “negative” gate rotor torque while the second shows the more usual “positive” torque.Fig. 2.24. “N” with negative torque, left and positive torque, right2.4.13 Blower Rotor ProfileThe blower profile, shown in Fig. 2.25 is symmetrical. Therefore only one quarter of it needs to be specified in order to define the whole rotor. It consists of two segments, a very small circle on the rotor lobe tip and a straight line. The circle slides and generates cycloids, while the straight line generates involutes.40 2 Screw Compressor GeometryFig. 2.25. Blower profile2.5 Identification of Rotor Position in Compressor BearingsThe rotor axial and radial forces are transferred to the housing by the bearings. Rolling element bearings are normally chosen for small and medium screw compressors and these must be carefully selected to obtain a satisfactory design. Usually, two bearings are employed on the discharge end of each of the rotor shafts in order to absorb the radial and axial loads separately.Also, the distance between the rotor center lines is in part determined by the bearing size and internal clearance. Any manufacturing imperfection in the bearing housing, like displacement or eccentricity, will change the rotor position and thereby influence the compressor behaviour. The system of rotors in screw compressor bearings is presented in Fig. 2.26.The rotor shafts are parallel and their positions are defined by axes and . The bearings are labeled 1 to 4, and their clearances, as well as the manufacturing tolerances of the bearing bores, and in the x and y directions respectively, are presented in the same figure. The rotor center distance is and the axial span between the bearings is a.All imperfections in the manufacture of screw compressor rotors should fall within and be accounted for by production tolerances. These are the wrong position of the bearing bores, eccentricity of the rotor shafts, bearing clearances and imperfections and rotor misalignment. Together, they account for the rotor shafts not being parallel. Let rotor movement in the y direction contain all displacements, which are presented in Fig. 2.27, and cause virtual rotation of the rotors around the , and axes, as shown in Fig. 2.27. Let2.5 Identification of Rotor Position in Compressor Bearings 41Fig. 2.26. Rotor shafts in the compressor housing and displacement in bearingsFig. 2.27. Rotors with intersecting shafts and their coordinate systemsrotor movement in the x direction cause rotation around the , and axes, as shown in Fig. 2.28. The movement can cause the rotor shafts to intersect. However, the movement causes the shafts to become non-parallel and non-intersecting. These both change the nature of the rotor position so that the shafts can no longer be regarded as parallel. The following analytic-alapproach enables the rotor movement to be calculated and accounts for these changes.Vectors and ,now represent the helicoid surfaces of the main and gate rotors on intersecting shafts. The shaft angle is the rotation about.42 2 Screw Compressor GeometryFig. 2.28. Rotors with non-parallel and non-intersecting shafts and their coordinate systems (2.15) (2.16)Since this rotation angle is usually very small, the relationship (2.16) can be assumed. Equation (2.15) can then be simplified for further analysis.The rotationwill result in a displacement in the x direction and a displacement in the z direction, while there is no displacement in the y direction. The displacement vector becomes:In the majority of practical cases, is small compared with and only displacement in the x direction need be considered. This means that rotation around the Y axis will, effectively, only change the rotor center distance. Displacement in the z direction may be significant for the dynamic behaviour of the rotors. Displacement in the z direction will be adjusted by the rotor relative rotation around the Z axis, which can be accompanied by significant angular acceleration. This may cause the rotors to lose contact at certain stages of the compressor cycle and thus create rattling, which may increase the compressor noise. Since the rotation angle , caused by displacement within the tolerance limits, is very small, a two-dimensional analysis in the rotor end plane can be applied, as is done in the next section.2.5 Identification of Rotor Position in Compressor Bearings 43As shown in Fig. 2.28, where the rotors on the nonparallel and nonintersecting axes are presented, vectors r1= x1,y1,z1 and r2, given by (2.10) now represent the helicoid surfaces of the main and gate rotors on the intersecting shafts. is the rotation angle around the X axes given by (2.11). (2.17) (2.18)Since angle is very small, it can be expressed in simplified form as in (2.18).Further analysis is then facilitated by writing (2.17) as: The rotation will result in displacement in the y direction and dis-placement in the z direction, while there is no displacement in the x direction. The displacement vector can be written as:Although, in the majority of practical cases, displacement in the z direction is very small and therefore unimportant for consideration of rotor interference,it may play a role in the dynamic behaviour of the rotors. The displacement in the z direction will be fully compensated by regular rotation of the rotors around the Z axis. However, the angular acceleration involved in this processmay cause the rotors to lose contact at some stages of the compressor cycle. Rotation about the X axis is effectively the same as if the main or gate rotor rotated relatively through angles or respectively and the rotor backlash will be reduced by . Such an approach substantially simplifies the analysis and allows the problem to be presented in two dimensions in the rotor end plane. Although the rotor movements, described here are entirely three-dimension-al, their two-dimensional presentation in the rotor end plane section can be used for analysis. Equation (2.2) serves to calculate both the coordinates of the rotor meshing points ,on the rotor helicoids and ,in the end plane from the given rotor coordinates points and . It may also be used to determine the contact line coordinates and paths of contact between the rotors. The sealing line of screw compressor rotors is somewhat similar to the rotor contact line. Since there is a clearance gap between rotors, sealing is effected at the points of the most proximate rotor position. A convenient practice to obtain the clearance gap between the rotors is to consider the gap as the shortest distance between the rotors in a section normal to the rotor helicoids. The end plane clearance gap can then be obtained from the normal clearance by appropriate transformation.If is the normal clearance between the rotor helicoid surfaces, the cross product of the r derivatives, given in the left hand side of (2.5), which defines.螺杆压缩机2.4审查最流行的转子型线 37图.2.21.“N”转子在5-6配置图.2.22. “N”转子在5-7配置38 2螺杆式压缩机几何图.2.23. “N”转子6/7的配置密封线，小局限于卷，渐开线转子的接触和正确的门转子与转子的机械刚性高扭矩分配。所需的波瓣的数目，根据指定的压缩机的工作而变化。3/5的安排是最适合于干燥的空气压缩，4/5和5/6的石油淹没具有适度的压力差的压缩机6/ 7内置的体积比制冷的高压和大应用程序。虽然全面评估的转子型线，需要的不仅仅是一个几何评估，一些关键功能的“ N”配置文件可能它有三个最流行的螺丝比较容易理解在这里已经描述了转子型线， （一） “西格玛”配置文件 Bammert1979年， （二）， （三） SRM“ D” Astberg1982年的档案，并在“ CYCLON ”个人资料霍夫和莫里斯，1984年。所有这些转子的示于图中. 2.20地方可以看出，在“N”公司有一个更大的吞吐量和一个更硬的闸转子可用于所有情况下，当其他特性，如吹孔区域，密闭体积和高压力的密封线的长度是相同的。此外，在低压力密封线短，但，这是不太重要的因为相应的间隙可以保持很小。可以控制的吹塑孔区域的尖端半径调整的两个主转子和闸转子，并通过使栅极的外径等于或小于的节圆直径。此外，密封线可以保持非常短的转子型线，圈，其中心是通过构建距离的节圆。但是，吹孔区域的任何减少会增加转子侧上的平坦的密封线的长度。之间的折衷因此，这些趋势要求，以获得最佳的结果。2.4 审查最流行的转子型线 39在闸转子的扭矩分配通常是由转子失稳一个完整的周期过程中改变方向。该配置文件的生成过程本文中描述的，使得它能够控制栅极上的扭矩转子，从而避免这种影响。此外，完整的渐开线之间的联系的“N”的转子允许任何额外的触点负载更容易被人体吸收比与任何其他类型的转子。两个转子对示于图.2.24什么被描