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湘玉竹切片机的设计[含CAD图纸和文档全套资料打包]

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湘玉竹切片机的设计[含CAD图纸和文档全套资料打包].zip

湘玉竹切片机的设计

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关键词：: 含CAD图纸和文档全套资料打包湘玉竹切片机的设计含全套cad图纸 CAD图纸全套 CAD图纸和切片机的设计

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内容提要

　　　本设计用于湘玉竹的切片，其主要特点为旋切式切片，通过计算平带的长度和刀具的宽度,设计在平带上装了八把刀片，每次切得1mm,使得其效率比同类产品要高，从而提高生产效益。基本的工作原理:机构由电动机传递动力给V带,通过V带的减速,再由V带将动力传递给平带轮从而带动刀片完成切片。在切片的同时通过变频电动机与齿轮齿条的配合，使得压紧机构对物料进行压紧，然后进行切片。这里设计的旋切式湘玉竹切片机，虽然是针对湘玉竹而进行的设计，但也可以用到其它的相关领域，其主要特点是效率较高。

Summary

　　　The design is used to slice polygonatum. It’s main characteristic is spin slice. By calculating the length of flat belt and the width of cutting tool and designing to install 8 blades on flat belt, it can make every cut 1mm, which makes it’s efficiency higher than other kindred products’. Therefore, the production efficiency is improved. Basic working theory: through electromotor, machine transfers power to V belt; through speed-down of V belt and to transfer the power to flat belt wheel by V belt, it makes the blades to slice. When slicing, the match between frequency conversion electromotor and gear and rack makes press institute to press the material to slice. Although the spin slice polygonatum slice machine is designed for polygonatum, it can also be used in other relational field. It ‘s main characteristic is high efficiency.

1 前言

　　　玉竹又名尾参，玉参、萎蕤、铃铛菜,为百合科玉竹,以根状茎入药。根茎味甘、微苦，具有养阴润燥、生津止渴的功效，适用于肺胃阴伤、燥热咳嗽、咽干口渴、内热消渴等病的治疗，并可作高级滋补食品、佳肴和饮料。

　　　另栽培玉竹经济效益十分可观，是农民生产致富的一条好门路。玉竹产量很高，2年生玉竹一公顷最高可产75000千克，一般可产45000千克；3年生玉竹一公顷最高可产12000千克，一般可产75000千克。切片加工要求尾参已经成为半干品，并已拔须。由于它的内部结构，决定它只允许竖着切片，而不能在其他任何方向切。同时，切片厚度要比较小和均匀。

　　　目前，尾参的加工，主要停留在落后的手工加工阶段，无以应对大规模生产和大批量的加工需求，特别是用手按着药物，刀片在底下切割的形式，限制了人的自由和提高了劳动强度，降低了工作效率,所创造的效益也极其的少，难以达到现在市场的需求，目前国内也有一些切片机，但它们的效率也不是很高，如由邵阳神风动力制造有限责任公司研究的一种玉竹切片机每小时可加工玉竹片２０－３０公斤，玉竹片最长可达２０－３０ｃｍ长。

　　　因此本人对以前的切片机进行参考，进行改进，将其刀片改为旋切式的，提高机构的切片效率设计出此作品。

2 设计思路及整体方案

2.1 整体设计思路

　　　本人设计的旋切式湘玉竹切片机，主要是由电动机经V带降速并传递给平带动力，从而使平带进行旋转运动，使刀片对湘玉竹进行旋切。由齿条和弹簧的的配合使得刀片在切完一箱湘玉竹后，立即更换物料箱，并且压紧物料进行切割。见图1。

2.2设计方案

　　　通过平带的传动与切割，完成切片过程；同时使用齿条和弹簧使得压紧元件能够很好的压紧，在即将切完时迅速的退出并且更换物料箱；至于刀片，将其用铆钉钉入平带中，物料箱固定在机架上的导轨上，随着平带的旋转运动，刀片也跟着运动，同时，在平带上安装了8把刀片，使得其效率非常的高。

2.3 机构示意图

　　　小平带轮1——通过它的轴与V带轴连接，为主动轮；机架2——通过它支撑与连接机架平台，起到固定的作用；机架平台3——用来支撑物料箱上的导轨；平带4——在上面安装刀片，切片的同时也支撑物料；定位元件5——用电机控制它的运动情况，在切片的时候固定物料箱；压紧轮6——用来压紧平带，保证平带的强度；刀片7——用铆钉铆在平带上，切片的元件；压紧机构8——它与电机配合，用来压紧物料；物料箱9——用来盛放物料的装置；导轨10——设计在物料箱的两侧，正好架在机架平台上；支撑板11——支撑平带；大带轮12——机构的从动部件。

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刀片部件.png

夹紧装置.png

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内容简介：: On the profile design of transmission splines and keysDaniel Z.Li Abstract: Splines and keys are machinery components placed at the interface between shafts and hubs of power-transmitting elements. A spline (or key) is usually machined (or attached) onto the shaft of a power-transmitting pair, and the corresponding groove is cut into the hub. The influence of spline profiles on the performance of power transmission is investigated in this paper. The optimal design of spline profiles for three different design criteria is presented. The method of calculus of variation is used to determine profile functions for maximum value. Analytical results are successfully obtained. They show that the splines with involute profiles lead to uniform deformation on the hub, in addition they can carry the maximum transmission load capacity. On the other hand, radial straight profiles result in optimum transmission efficiency. We think that these findings are worthy reporting and also believe that this approach could be used for the spline design with other performance criteria imposed.1 IntroductionA key is a machinery component placed at the interface between a shaft and the hub of a power-transmitting element such as gear and sprocket . A spline performs the same function as a key in transmitting torque from the shaft to the mating element . The main difference between splines and keys is that splines are integral with the shaft but keys are inserted between shaft and hub. As compared with one or two keys used for load transmission, there are usually four or more splines on a shaft. Therefore, the transmission torque is more uniform and the loading for each spline is lower. Splines play an important role in transmitting torque and their profiles do have the influence on the performance of power transmission. Unlike the conjugate profiles, the shaft with splines and hub have the same rotation axis and they are in surface contact without relative motion, they are connected together and have the same angular velocity. Therefore, it seems that any profiles except the shaft surface can be used for the design of splines. However, the load between the spline and hub is not evenly distributed over the entire contact surface in practice. The load may always concentrate on a small portion of contact surface and deformthe hub surface. This results in undesired clearance between the shaft and hub and will lead to serious damage of hub surface as the working cycles increase. To solve these problems, how the profiles of splines affect the torque transmission needs to be further investigated to find out the suitable design of spline profiles.Currently there are two main types of splines used, namely, straight-sided and involute splines. The involute splines provide the mating element with self-centering and can be machined with standard hob cutter used to cut gear teeth. To date, the related research work focuses on conjugate profiles and gear design as well as the design of profile curvatures for reducing the wear of contact surfaces. However, none of them can be applied to the profiles of splines directly due to different working conditions. Also, there is no research work on how to design spline profiles under given requirements. In this paper, the basic equations for spline profiles are established and used to synthesize desired profiles for different design objectives. Three design objectives, uniform deformation, maximum torque transmission, and optimum efficiency, are used to determine spline profiles. Analytical solutions are successfully obtained.2 Problem description and basic assumptionsAs shown in fig .1, The hub is driven by the shaft and the spline is fixed on the shaft. The radius of the shaft, the height of the spline, and the number of spline teeth are determined by the design requirements and cannot be altered. Only the spline profile can be modified to improve the performance of transmission. To simplify the design problem for analysis, the following assumptions were made:(1) The spline is a rigid body.Compared with the hub, the spline is made of hard material and assumed no deformation after applying the load.(2) The hub is under elastic deformationThe surface deformation of the hub is within the range of elasticity and the surface stress is proportional to the normal deformation.(3) There is no beam deformation on the spline.For spline keys, usually the height of tooth shape is small relative to its width. Therefore, we assume there is no accumulated deformation at the free end. The only deformation is the normal deformation on the hub surface.(4) There is no clearance between the spline and hub when they are in contact. (Surface contact)The profile of the spline is exactly the same as that of the hub without considering manufacturing errors. They are in surface contact without clearance.3 Spline profile for uniform hub deformationThe first design objective is to have the uniform deformation on the surface of the hub, which also implies the uniform stress on the hub. This design can ensure the surface stress is evenly distributed and avoid the failure of material at some weak points. Referring to fig.2, Let denote the radius of shaft and denote a small rotation angle of spline. Since we assume that the spline is a rigid body, the change between two spline positions will be the deformation of the hub. 4 Its simply to confirmed the dangerous sections Prerequisite that traditional design method considered whether pair influence part design variable of working state, for instance stress , intensity , safety coefficient , load , environmental factor , material performance , part size and structural factor ,etc., deal with the single value variable confirmed. Describe part mathematical model of state , i.e. variable and relation of variable , to go on single value vary and win the dangerous section through deterministic function.There are several methods that usually the dangerous sections are determined: 4.1 Minimum diameter of the spline Spline dangerous sectional reliability very getting high, this to confirm according to traditional design experience because of diameter of spline. If require appropriate reliability value, then the diameter of the axle can select smaller value for use .4.2 Safety coefficient law of dependability While adopting the safety coefficient law design of dependability , must know the distribution types of stress and intensity and be distributed estimated value of the parameter . And the accumulation of dependability data is a long-term job, therefore we must utilize the existing data materials , it is (such as the terminal theorem in the centre and 3 rules to use relevant theorems and rule ), to confirm the distribution types of a lot of random variables involved of design process and is distributed the parameter. In the safety coefficient of dependability is calculated , deal with all design parameters involved a random variable, link the concept of safety coefficient to concept of dependability , thus set up corresponding probability model. Because of considering the uncertainty (randomness ) of the phenomenon taking place in project reality and sign parameter, therefore can announce the original appearances of the things even more. Theory analysis and practice indicate , the dependability design is designed more than traditional machinery , can punish some problem of the design , raise product quality , reduce part size effective, thus save the raw materials , lower costs .5 Concluding remarksThe mechanical reliability design is one kind of modern design theory and the method which in the recent several dozens years develop, it take improves the product quality as the core, take the theory of probability, the mathematical statistic as the foundation, synthesizes using the engineering mechanics, the system engineering, the operations research and so on the multi-disciplinary knowledge studies the mechanical engineering most superior design question. At present, the reliability design theory tended to the consummation, but uses in the machine parts design project actual very being actually few truly. When uses the reliable security method of correlates design, must know the stress and the intensity distributed type and the distributed parameter estimated value. But the reliable data accumulation also is a long-term work, thus we must use the existing data material, the utilization related theorem and the principle, determined in the design process involves many random variable distributed types and distributed parameter. In this paper the optimal design of spline (or key) profiles for three different design criteria is presented. The method of calculus of variation is used to determine profile functions for maximum value. Analytical results are successfully obtained. It shows that the splines with involute profiles lead to uniform deformation on the hub, in addition they can carry the maximum transmission load capacity. On the other hand radial straight profiles result in optimum transmission efficiency. We believe similar approach could be used to determine other spline profiles when new performance criteria are imposed.References1 Robert L. Mott, Machine Elements in Mechanical Design, third ed., Prentice-Hall Inc., 1999.2 M.F. Spotts, Design of Machine Elements, third ed., Prentice-Hall Inc., 1961.3 Joseph E. Shigley, Larry D. Mitchell, Mechanical Engineering Design, fourth ed., McGraw-Hill Inc., 1983.4 D.C.H. Yang, S.H. Tong, J. Lin, Deviation-function based pitch curve modification for conjugate pair design, Transaction of ASME Journal of Mechanical Design 121 (4) (1999) 579586.5 S.H. Tong, New conjugate pair designtheory and application, PhD Dissertation, Mechanical and Aerospace Engineering Department, UCLA, 1998.6 F.L. Litvin, Gear Geometry and Applied Theory, Prentice-Hall Inc., 1994.7 D.B. Dooner, A.A. Seireg, The Kinematic Geometry of Gearing, John Wiley & Sons Inc., 1995, pp. 5663.8 Y. Ariga

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