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HD600多向混合机的设计【8张CAD图纸和说明书】

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hd600 多向 混合 设计 cad 图纸 以及 说明书 仿单
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目   录

第一章  概述 1

第二章  传动系统的设计 6

2.1传动方案的设计 6

2.2带轮传动的设计 8

2.3第一级齿轮传动的设计 10

2.4第二级齿轮传动的设计 15

2.5链轮传动的设计 18

第三章  部分轴的设计 21

3.1轴Ⅱ的设计 21

3.2轴Ⅲ的设计 24

3.3轴Ⅳ的设计 27

第四章  其他零件的设计 28

设计心得 30

参考文献 31

附录Ⅰ 31

HD600多向运动混合机的设计

摘要：HD600多向运动混合机广泛应用于医药、食品、轻工业等行业，能在三维空间实现回转、平移、翻转等复杂运动，是一种高效的混合设备。在该设计任务书中，我综合分析了该混合机的空间运动结构，并对该混合机传动系统进行了详细的说明计算，同时对空间6杆机构进行运动分析，最后绘制出该混合机的装配图和各主要零件的零件图。

该机的混合筒多方向运动，物料无离心力作用，无比重偏析及分层、积聚现象，各组分可有悬殊的重量比，混合率达99.9％以上，是目前各种混合机中的一种较理想产品。 筒体装料率大，最高可达90％（普通混合机仅为40％），效率高，混合时间短。筒体各处为圆弧过渡，经过精密抛光处理。多向运动混合机的优势在于其特殊的工作原理，以及桶体结构的设计无死角，不污染物料，出料方便，清洗容易，操作简单等优点。

多向运动混合机的混料桶具有X、Y、Z方向的三维运动，多方向运动的功能，物料在容器内作旋转、翻转、湍动和剪切作用，使物料在混合时不产生积聚现象，对不同比重，不同密度和状态的物料混合不产生离心力的影响和偏折；混合时间短，某些物料5-8分钟即可混合均匀。既提高了工作效率，又达到了极高的均匀度，混合均匀性达到99.9%以上。因其最大装载系数可达0.9(普通混合机为0.4～0.6)这一特点，大大缩短了混合物料的时间，提高了混合物料效率。


关键词：混合机  传动系统    空间6杆机构  



HD600 multi-sport mixer to the design 

Abstract: HD 600multi-sport mixer widely used in medicine ,food and light industries, can realize rotary, translation, roller and some other complex sports in the three-dimensional. It’s a highly efficient hybrid device. In this design of the assignment, I have analyzed the HD400 mixer of more space to the sports movement mixer structure comprehensively, and the mixer containing a detailed description of transmission, while using the 6R outfit of mixer. At last, I drew a assembly map and all the major parts maps of this mixer.

Hybrid multi-barrel machine direction, material is not centrifugal force, no specific gravity segregation and stratification, accumulation of the phenomenon, each component may have poor weight ratio, mixing rate of 99.9%, and is one of a variety of mixer kinds of better products. Cylinder loading rate is high, up to 90% (ordinary mixer only 40%), high efficiency, short mixing time. Throughout the transition for the arc tube, after the polishing treatment. Multi-directional movement mixer has the advantage of special works, as well as the design of barrel structure no dead, no contaminated material, the material convenient, easy to clean, and easy operation. 

Multi-directional movement mixer mixing bucket with X, Y, Z direction of the three-dimensional motion, multi-direction function, the material in the container for rotating, flipping, turbulence and shear, so that does not produce the material in the mixed accumulation phenomenon, different specific gravity, density, and status of different materials mixed centrifugal force does not produce the impact and deflection; mixing time is short, some of the material can be mixed for 5-8 minutes. Not only improves the work efficiency, but also to achieve a high uniformity, mixing uniformity of 99.9% or more. Its maximum load factor of up to 0.9 (normal mixer 0.4 ~ 0.6) this feature, greatly reducing the time the mixed materials to improve the efficiency of the hybrid materials.

Key words: mixer   transmission system     6R outfit  


第一章  概述

多向混合机广泛应用于化工、医药、食品、粉末冶金、涂料、电子、军工、材料等粉体混合领域。粉体混合的质量有时在生产过程中起着关键的作用,例如在化工生产中，均匀的粉体混合为反应创造良好条件；在医药固体制剂的生产中,极微量的药效成分与大量增量剂混合的均匀水平直接影响着药的质量；在粉末冶金中各种不同成分的混合均匀水平影响着材料的强度。混合设备的发展直接影响着粉体混合单元操作的效果。随着纳米技术的发展,粉体混合更显示出它的重要性。

1.1混合机的概念

混合机是利用机械力和重力等，将两种或两种以上物料均匀混合起来的机械。混合机械广泛用于各类工业和日常生活中。混合机可以将多种物料配合成均匀的混合物，如将水泥、砂、碎石和水混合成混凝土湿料等；还可以增加物料接触表面积，以促进化学反应；还能够加速物理变化，例如粒状溶质加入溶剂，通过混合机械的作用可加速溶解混匀。

常用的混合机分为气体和低粘度液体混合器、中高粘度液体和膏状物混合机械、热塑性物料混合机、粉状与粒状固体物料混合机械四大类。


内容简介：
附件 2：外文原文 ABSTRACT Conical involute gears (beveloids) are used in transmissions with intersecting or skew axes and for backlash-free transmissions with parallel axes. Conical gears are spur or helical gears with variable addendum modification (tooth thickness) across the face width. The geometry of such gears is generally known, but applications in power transmissions are more or less exceptional. ZF has implemented beveloid gear sets in various applications: 4WD gear units for passenger cars, marine transmissions (mostly used in yachts), gear boxes for robotics, and industrial drives. The module of these beveloids varies between 0.7 mm and 8 mm in size, and the crossed axes angle varies between 0and 25. These boundary conditions require a deep understanding of the design, manufacturing, and quality assurance of beveloid gears. Flank modifications, which are necessary for achieving a high load capacity and a low noise emission in the conical gears, can be produced with the continuous generation grinding process. In order to reduce the manufacturing costs, the machine settings as well as the flank deviations caused by the grinding process can be calculated in the design phase using a manufacturing simulation. This presentation gives an overview of the development of conical gears for power transmissions: Basic geometry, design of macro and micro geometry, simulation, manufacturing, gear measurement, and testing.1 IntroductionIn transmissions with shafts that are not arranged parallel to the axis, torque transmission ispossible by means of various designs such as bevel or crown gears , universal shafts , or conical involute gears (beveloids). The use of conical involute gears is particularly ideal for small shaft angles (less than 15), as they offer benefits with regard to ease of production, design features, and overall input. Conical involute gears can be used in transmissions with intersecting or skew axes or in transmissions with parallel axes for backlash-free operation. Due to the fact that selection of the cone angle does not depend on the crossed axes angle, pairing is also possible with cylindrical gears. As beveloids can be produced as external and internal gears, a whole matrix of pairing options results and the designer is provided with a high degree of flexibility;Table 1.Conical gears are spur or helical gears with variable addendum correction (tooth thickness)across the face width. They can mesh with all gears made with a tool with the same basic rack. The geometry of beveloids is generally known, but they have so far rarely been used in power transmissions. Neither the load capacity nor the noise behavior of beveloids has been examined to any great extent in the past. Standards (such as ISO 6336 for cylindrical gears ), calculation methods, and strength values are not available. Therefore, it was necessary to develop the calculation method, obtain the load capacity values, and calculate specifications for production and quality assurance. In the last 15 years, ZF has developed various applications with conical gears: Marine transmissions with down-angle output shafts /1, 3/, Fig. 1 Steering transmissions /1/ Low-backlash planetary gears (crossed axes angle 13) for robots /2/ Transfer gears for commercial vehicles (dumper) Automatic car transmissions for AWD /4/, Fig. 22 GEAR GEOMETRY2.1 MACRO GEOMETRYTo put it simply, a beveloid is a spur gear with continuously changing addendum modification across the face width, as shown in Fig. 3. To accomplish this, the tool is tilted towards the gear axis by the root cone angle ? /1/. This results in the basic gear dimensions:Helix angle, right/lefttan =tancosLR, cosinta(1)Transverse pressure angle right/lefttancostant,LtR(2)Base circle diameter right/left(3)LRtnLdRZim,cosThe differing base circles for the left and right flanks lead to asymmetrical tooth profiles at helical gears, Fig. 3. Manufacturing with a rack-type cutter results in a tooth root cone with root cone angle . The addendum angle is designed so that tip edge interferences with the mating gear are avoided and a maximally large contact ratio is obtained. Thus, a differing tooth height results across the face width.Due to the geometric design limits for undercut andtip formation, the possible face width decreases as the cone angle increases. Sufficiently well-proportioned gearing is possible up to a cone angle of approx. 15.2.2 MICRO GEOMETRYThe pairing of two conical gears generally leads to a point-shaped tooth contact. Out-side this contact, there is gaping between the tooth flanks , Fig. 7. The goal of the gearing correction design is to reduce this gaping in order to create a flat and uniform contact. An exact calculation of the tooth flank is possible with the step-by-step application of the gearing law /5/, Fig. 4. To that end , a point (P ) with the radiusrP1and normal vectorn1is generated on the 1original flank. This generates the speed vector V with1P(4)0cosin11PPrvFor the point created on the mating flank, the radial vector rp :2(5)12PPraand the speed vector apply2PV(6)0cosin212PPrVThe angular velocities are generated from the gear ratio:(7)12zThe angle is iterated until the gearing law in the form(8)0121Pvnis fulfilled. The meshing point Pa found is then rotated through the angle 2(9)21zaround the gear axis, and this results in the conjugate flank point P .23 GEARING DESIGN3.1 UNDERCUT AND TIP FORMATIONThe usable face width on the beveloid gearing is limited by tip formation on the heel and undercut on the toe as shown in Fig. 3. The greater the selected tooth height (in order to obtain a larger addendum modification), the smaller the theoretically useable face width is. Undercut on the toe and tip formation on the heel result from changing the addendum modification along the face width. The maximum usable face width is achieved when the cone angle on both gears of the pairing is selected to be approximately the same size. With pairs having a significantly smaller pinion, a smaller cone angle must be used on this pinion. Tip formation on the heel is less critical if the tip cone angle is smaller than the root cone angle, which often provides good use of the available involute on the toe and for sufficient tip clearance in the heel.3.2 FIELD OF ACTION AND SLIDING VELOCITYThe field of action for the beveloid gearing is distorted by the radial conicity with a tendency towards the shape of a parallelogram. In addition, the field of action is twisted due to the working pressure angle change across the face width. Fig. 5 shows an example of this. There is a roll axis on the beveloid gearing with crossed axes; there is no sliding on this axis as there is on the roll point of cylindrical gear pairs. With a skewed axis arrangement, there is always yet another axial slide in the tooth engagement. Due to the working pressure angle that changes across the face width, there is varying distribution of the contact path to the tip and root contact. Thus, significantly differing sliding velocities can result on the tooth tip and the tooth root along the face width. In the center section, the selection of the addendum modification should be based on the specifications for the cylindrical gear pairs; the root contact path at the driver should be smaller than the tip contact path. Fig. 6 shows the distribution of the sliding velocity on the driver of a beveloid gear pair.4 CONTACT ANALYSIS AND MODIFYCATIONS4.1 POINT CONTACT AND EASE-OFFAt the uncorrected gearing, there is only one point in contact due to the tilting of the axes. The gaping that results along the potential contact line can be approximately described by helix crowning and flank line angle deviation. Crossed axes result in no difference between the gaps on the left and right flanks on spur gears. With helical gearing, the resulting gaping is almost equivalent when both beveloid gears show approximately the same cone angle. The difference between the gap values on the left and right flanks increases as the difference between the cone angles increases and as the helix angle increases. This process results in larger gap values on the flank with the smaller working pressure angle. Fig.7 shows the resulting gaping (ease-off) for a beveloid gear pair with crossed axes and beveloid gears with an identical cone angle. Fig.8 shows the differences in the gaping that results for the left and right flanks for the same crossed axes angle of 10 and a helical angle of approx. 30. The mean gaping obtained from both flanks is, to a large extent, independent of the helix angle and the distribution of the cone angle to both gears.The selection of the helical and cone angles only determines the distribution of the mean gaping to the left and right flanks. A skewed axis arrangement results in additional influence on the contact gaping. There is a significant reduction in the effective helix crowning on one flank. If the axis perpendicular is identical to the total of the base radii and the difference in the base helix angle is equivalent to the (projected) crossed axes angle, then the gaping decreases to zero and line contact appears. However, significant gaping remains on the opposite flank. If the axis perpendicular is further enlarged up to the point at which a cylindrical crossed helical gear pair is obtained, this results in equivalent minor helix crowning in the ease-off on both flanks. In addition to helix crowning, a notable profile twist (see Fig. 8) is also characteristic of the ease-off of helical beveloids. This profile twist grows significantly as the helix angle increases. Fig.9 shows how the profile twist on the example gear set from Fig.7 is changed depending on the helix angle. In order to compensate for the existing gaping in the tooth engagement, topological flank corrections are necessary; these corrections greatly compensate for the effective helix crowning as well as the profile twist. Without the compensation of the profile twist, only a diagonally patterned contact strip is obtained in the field of action, as shown in Fig. 10.4.2 FLANK MODIFICATIONSFor a given degree of compensation, the necessary topography can be determined from the existing ease-off. Fig. 11 shows these types of typographies, which were produced on prototypes. The contact ratios have improved greatly with these corrections as can be seen in Fig.12. For use in series production, the target is always to manufacture such topographies on commonly used grinding machines. The options for this are described in Section 6. In addition to the gaping compensation, tip relief is also beneficial. This relief reduces the load at the start and at the end of meshing and can also provide lower noise excitation. However, tip relief manufactured at beveloid gears is not constant in amount and length across the face width. The problem primarily occurs on gearing with a large root cone angle and a tip cone angle deviating from this angle. The tip relief at the toe is significantly larger than that at the heel. This uneven tip relief must be accepted if relief of the start and end of meshing is required. The production of tip relief using another cone angle as the root cone angle is possible; however, this requires an additional grinding step only for the tip relief. Independently of the generating grinding process, targeted flank topography can be manufactured by coroning or honing; the application of this method on beveloids, however, is still in the early stages of development.5 LOAD CAPACITY AND NOISE EXCITATION5. 1 APPLICATION OF THE CALCULATION STANDARDSThe flank and root load capacity of beveloid gearing can only approximately be deter-mined using the calculation standards (ISO6336, DIN3990,AGMA C95) for cylindrical gearing. A substitute cylindrical gear pair has to be used, which is defined by the gear parameters at the center of the face width. The profile of the beveloid tooth is asymmetrical; that can, however, be ignored on the substitute gears. The substitute center distance is obtained by adding up the operating pitch radii at the center of the face width.When viewed across the face width, individual parameters will change, which significantly influence the load capacity. Table 2 shows the main influences on the root and flank load capacities. The larger notch effect due to the decrease in the tooth root fillet radius towards the heel is in opposition to the increase in the root thickness. In addition, there is a smaller tangential force on the larger operating pitch circle at the heel; at the same time, however, the addendum modification on the heel is smaller. The primary influences are nearly well-balanced so that the load capacity can be calculated sufficiently approximate with the substitute gear pair. The load distribution across the face width can be considered with the width factors (e. g. K and K in DIN/ISO) and should be determined from HFadditional load pattern analyses.5.2 USE OF THE TOOTH CONTACT ANALYSISA more precise calculation of the load capacity is possible with a three-dimensional tooth contact analysis, as used at cylindrical gear pairs. The substitute cylindrical gear pair can be used in this analysis and the contact conditions are considered very well with flank topography. This topography is obtained from the superimposition of the load-free contact ease-off with the flank corrections used on the gear. In this process, the contact lines are determined on the substitute cylindrical gear and they differ slightly from the contact at the beveloid gear. Fig. 13 shows the load distributions calculated in this manner as compared to the load patterns recorded, and a very goodcorrelation can be seen.This tooth contact analysis also generates the transmission error resulting from the tooth mesh as vibrational excitation. It can, however, only be used as a rough guide. The impreciseness in the contact behavior calculated has a stronger effect on the transmission error than it does on the load distribution.5.3 EXACT MODELING USING THE FINITE-ELEMENT METHODThe stress at the beveloid gears can also be calculated using the finite-element method. Fig. 14 shows examples of the modeling of the transverse section on the gears. Fig. 15 shows the computer-generated model in the tooth mesh section and the stress distribution calculated with PERMAS /7/ on the driven gear in a mesh position. The calculation was carried out for multiple mesh positions and the transmission error can be determined from the rotation of the gears.5.4 TESTS REGARDING LOAD CAPACITY AND NOISEA back-to-back test bench with crossed axes, upon which gear pairs from AWD transmissions were tested, was used to determine the load capacity, Fig.16. Different corrections were produced on the test gears in order to ascertain their influence on the load capacity. There was good correlation between the load capacity in the test and the FE (finite element) results. Particularly noteworthy is an additional shift of the load pattern towards the heel due to the increased stiffness in this area. This shift is not discernable in the calculation with the substitute cylindrical gear pair. Simultaneous to the load capacity tests, measurements of the transmission error and rotational acceleration were conducted in a universal noise test box, Fig. 17. In addition to the load influence, the influence of additional axis tilt on the noise excitation was also examined in these tests. With regard to this axis tilt, no large amount of sensitivity in the tested gear sets was found.6 MANUFACTURING SIMULATIONWith the assistance of the manufacturing simulation, machine settings and movements with continuous generation grinding as well as the produced profile twist can be obtained. Production-constrained profile twist can be considered as early as the design phase of a transmission and can be incorporated into the load capacity and noise analyses. Simulation software for the manufacturing of beveloids was specially developed at ZF, which is comparable to /9/.6.1 PRODUCTION METHODS THAT CAN BE USED FOR BEVELOIDSOnly generating methods can be used to produce the beveloid gearing, because the shape of the tooth profile changes significantly along the face width. Only very slightly conical beveloids can be manufactured with the acknowledgment that there is profile angle deviation even with the shaping process. Hobs are the easiest to use for pre-cutting. Gear planning would theoretically be useable as well; however, the kinematics required makes this not really feasible on existing machines. Internal conical gears can then only be precisely manufactured with pinion-type cutters if the cutter axis is parallel to the tool axis and the cone is created by changing the center distance. If the internal gear is manufactured with a tilted pinion cutter axis such as used for crown gears, this results in a hollow crowning and a profile twist without corrective movements. These deviations are small enough to be ignored for minor cone angles. For final processing, continuous generation grinding with a grinding worm appears to be the best option. If the workpiece or tool fixture can be additionally tilted， then partial generation methods are also applicable. Processing in a topological grinding process is also possible (e.g. 5-axis machines), but with great effort, when the cone angle of the gearing can be considered in the machine control. In principle, honing and coroning can also be used for the processing; however, the application of these methods in beveloids still needs extensive development. The targeted hollow crowning can be created in the generation grinding process in the dual-flank grinding process via a bowshaped reduction in the center distance. This method results in a profile twist, that is the reverse of the profile twist from the contact gaping. Thus, this method provides extensive compensation fo
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