关 键 词：

JS1127 半自动 平压模切机 设计

资源描述：

以上为资料预览概图，下载文件后为完整一套设计。【清晰，无水印，可编辑】dwg后缀为cad图，doc后缀为word格式，png和jpg，gif后缀为资料预览图片。有疑问可以咨询QQ：529358737

内容简介：

目 录第一章 概述31.1选题依据31.2课题的意义4第二章 半自动平压模切机的方案选型52.1送料模切机构52.2机械运动方案的选择102.3运动循环图的拟定15第三章 半自动平压模切机的传动设计163.1电动机的选择163.2传动比的分配193.3计算传动装置的运动参数和动力参数193.4 V带传动设计203.5减速器的齿轮设计223.6轴的设计263.7轴承的选择和校核31第四章 半自动平压模切机的模切机构设计334.1平面六杆滑块机构设计334.2链条及链轮的设计344.3凸轮机构的设计35总结37致谢38参考文献39英文文献及翻译.40 摘要机械设计是工科高等学校机械类，机电类等专业必修的一门技术基础课，我们在学习基础知识的同时，也应更加注重对知识的整体运用和实践。半自动平压模切机是印刷包装行业压制纸盒、纸箱等纸制品的专用设备,应用非常广泛。本文从拟定运动循环图出发，通过查找机械设计手册，比较不同方案，选择了最合适的传动系统和执行机构，并且对其工作原理，结构设计和几何参数进行了深刻的分析和计算。设计完成后，用Auto CAD画出半自动模切机的装配图以及相关的零件图。该模切机具有结构简单，紧凑，效率高，易操作等特点。关键词：机械设计 半自动平压模切机 Auto cad AbstractMechanical design is engineering colleges machinery, mechanical and electrical and other technical professionals a compulsory basic course, we have to learn the basics, but also should pay more attention to the overall use of knowledge and practice. Semi automatic platen die-cutting machine is the printing and packaging industry to suppress cartons, cardboard boxes and other paper products, special equipment, is widely used. This departure from the intended motion cycle chart, Mechanical Design Handbook by looking to compare different options and choose the most suitable transmission and executive bodies, and its working principle, structure design and geometric parameters of the in-depth analysis and calculations. Design is complete, use Auto CAD draw semi-automatic cutting machine assembly drawings and associated parts diagram. The cutting machine has a simple and compact structure, high efficiency, easy operation and so on.Key words: Mechanical Design Semi automatic die-cutting machine AutoCAD 第一章 概述1.1 选题依据： 本课题其研究的目标为设计可实现对各种规格的白纸板，厚度在4mm以下的瓦楞纸板，以及各种高级精细的印刷品进行压痕、切线、压凹凸。本课题主要研究模切机总体方案设计，模切机传动系统的设计，主执行机构设计（机构选型）及其结构设计，对主要零部件进行强度和力的计算，产要求绘制所设计方案的机构运动简图，绘制模切机的装配和重要零件的零件图。1.2 课题的意义： 平压平模切机是目前应用最广泛的最普遍的类型，也是国内外生产厂家最多的机型。平压平模切机可以用于各种类型的模切，既能模切瓦楞纸板、卡纸、不干胶，又能模切橡胶、海绵、金属板材等，既能人工续纸半自动模切，也能全自动高速联动模切。半自动平压模切机的精准度比比一般的模切机要高。他的工作原理最具有代表性的，所以研究它也及其重要。平压平模切机分为立式、卧式两种。立式模切机俗称“老虎嘴”机，其特点是精准度比圆压圆模切机好，售价便宜，突出的缺点是安全系数低，多年来始终没有彻底解决杜绝伤残事故问题，工伤事故时有发生，在当今国家重点保证人身安全并已立法的大环境下，如果还是解决不了安全问题，必然要退出市场。卧式模切机分为半自动模切机、全自动模切机以及带清废和不带清废四种。它们的共同特点是精准度比较准确，效率比“老虎嘴”机高，比圆压圆低，处于中位。近二十年来，平压模切机是使用最广泛且技术发展最快的机型。作为一个刚刚毕业的大学生，要想以后在实际的工作当中有自己的技术进步与技术创新，就必须先搞懂基本设备的基本原理以及各个部分的工作原理。为以后实现模切机的数字化和智能化做好充分准备。当前，国外先进自动平压平模切机的工作速度普遍在75009000张小时左右。瑞士BOBST公司生产的SPRINT?EPA106-PER?自动模切压痕机(带全清废单元)达到了12000张小时的单机模切压痕速度。与此相比较，我国生产的自动平压平模切机工作速度较低，一般在55007500张小时左右。从模切精度上讲，国外先进自动平压模切机的模切精度通常可以控制在01mm左右，而国产自动平压模切机的模切精度绝大多数在015ham02mm范围内，只有少量机型能够达到01mm的模切精度。另外，国产自动平压平模切机在高速工作时，模切精度大幅度下降，并伴有大量噪声，机器磨损非常严重，影响了国产自动平压平模切机在国内和国际市场的竞争力。如何解决以上问题，使产品向高速、高精度、高稳定性的方向 NOVEL METHOD OF REALIZING THE OPTIMAL TRANSMISSION OF THE CRANK-AND-ROCKER MECHANISM DESIGN Abstract: A novel method of realizing the optimal transmission of the crank-and-rocker mechanism is presented. The optimal combination design is made by finding the related optimal transmission parameters. The diagram of the optimal transmission is drawn. In the diagram, the relation among minimum transmission angle, the coefficient of travel speed variation, the oscillating angle of the rocker and the length of the bars is shown, concisely, conveniently and directly. The method possesses the main characteristic. That it is to achieve the optimal transmission parameters under the transmission angle by directly choosing in the diagram, according to the given requirements. The characteristics of the mechanical transmission can be improved to gain the optimal transmission effect by the method. Especially, the method is simple and convenient in practical use. Keywords：Crank-and-rocker mechanism, Optimal transmission angle, Coefficient of travel speed variation INTRODUCTION By conventional method of the crank-and-rocker design, it is very difficult to realize the optimal combination between the various parameters for optimal transmission. The figure-table design method introduced in this paper can help achieve this goal. With given conditions, we can, by only consulting the designing figures and tables, get the relations between every parameter and another of the designed crank-and-rocker mechanism. Thus the optimal transmission can be realized. The concerned designing theory and method, as well as the real cases of its application will be introduced later respectively. 1. ESTABLISHMENT OF DIAGRAM FOR OPTIMAL TRANSMISSION DESIGN It is always one of the most important indexes that designers pursue to improve the efficiency and property of the transmission. The crank-and-rocker mechanism is widely used in the mechanical transmission. How to improve work ability and reduce unnecessary power losses is directly related to the coefficient of travel speed variation, the oscillating angle of the rocker and the ratio of the crank and rocker. The reasonable combination of these parameters takes an important effect on the efficiency and property of the mechanism, which mainly indicates in the evaluation of the minimum transmission angle. The aim realizing the optimal transmission of the mechanism is how to find the maximum of the minimum transmission angle. The design parameters are reasonably combined by the method of lessening constraints gradually and optimizing separately. Consequently, the complete constraint field realizing the optimal transmission is established. The following steps are taken in the usual design method. Firstly, the initial values of the length of rocker 3l and the oscillating angle of rocker are given. Then the value of the coefficient of travel speed variation K is chosen in the permitted range. Meanwhile, the coordinate of the fixed hinge of crank Apossibly realized is calculated corresponding to value K. 1.1 Length of bars of crank and rocker mechanism As shown in Fig.1, left arc GC2 is the permitted field of point A. The coordinates of point A are chosen by small step from point 2C to point G. The coordinates of point A are 02hyycA (1) 22AAyRx (2) where 0h, the step, is increased by small increment within range(0,H). If the smaller the chosen step is, the higher the computational precision will be. R is the radius of the design circle. d is the distance from 2C to G. 2c o s)2c o s (22c o s33lRld (3) Calculating the length of arc 1AC and 2AC, the length of the bars of the mechanism corresponding to point A is obtained1,2. 1.2 Minimum transmission angle min Minimum transmission angle min(see Fig.2) is determined by the equations3 322142322m i n2)(c o sllllll (4) 322142322m a x2)(c o sllllll (5) m a xm i n180 (6) where 1lLength of crank(mm) 2lLength of connecting bar(mm) 3lLength of rocker(mm) 4lLength of machine frame(mm) Firstly, we choose minimum comparing min with min. And then we record all values of min greater than or equal to 40 and choose the maximum of them. Secondly, we find the maximum of min corresponding to any oscillating angle which is chosen by small step in the permitted range (maximum of min is different oscillating angle and the coefficient of travel speed variation K). Finally, we change the length of rocker 3l by small step similarly. Thus we may obtain the maximum of min corresponding to the different length of bars, different oscillating angle and the coefficient of travel speed variation K. Fig.3 is accomplished from Table for the purpose of diagram design. It is worth pointing out that whatever the length of rocker 3l is evaluated, the location that the maximum of min arises is only related to the ratio of the length of rocker and the length of machine frame 3l/4l, while independent of 3l. 2. DESIGN METHOD 2.1 Realizing the optimal transmission design given the coefficient of travel speed variation and the maximum oscillating angle of the rocker The design procedure is as follows. (1) According to given K and , taken account to the formula the extreme included angle is found. The corresponding ratio of the length of bars 3l/4l is obtained consulting Fig.3. 18011KK (7) (2) Choose the length of rocker 3l according to the work requirement, the length of the machine frame is obtained from the ratio 3l/4l. (3) Choose the centre of fixed hinge D as the vertex arbitrarily, and plot an isosceles triangle, the side of which is equal to the length of rocker 3l(see Fig.4), and 21DCC. Then plot 212CCMC, draw NC1, and make angle 9012NCC. Thus the point of intersection of MC2 and NC1 is gained. Finally, draw the circumcircle of triangle 21CPC. (4) Plot an arc with point D as the centre of the circle, 4l as the radius. The arc intersections arc GC2 at point A. Point A is just the centre of the fixed hinge of the crank. Therefore, from the length of the crank 2/ )(211ACACl (8) and the length of the connecting bar 112lACl (9) we will obtain the crank and rocker mechanism consisted of 1l, 2l, 3l, and 4l.Thus the optimal transmission property is realized under given conditions. 2.2 Realizing the optimal transmission design given the length of the rocker (or the length of the machine frame) and the coefficient of travel speed variation We take the following steps. (1) The appropriate ratio of the bars 3l/4l can be chosen according to given K. Furthermore, we find the length of machine frame 4l(the length of rocker 3l). (2) The corresponding oscillating angle of the rocker can be obtained consulting Fig.3. And we calculate the extreme included angle . Then repeat (3) and (4) in section 2.1 3. DESIGN EXAMPLE The known conditions are that the coefficient of travel speed variation 1818. 1K and maximum oscillating angle 40. The crankandrocker mechanism realizing the optimal transmission is designed by the diagram solution method presented above. First, with Eq.(7), we can calculate the extreme included angle 15. Then, we find 93. 0/43ll consulting Fig.3 according to the values of and . If evaluate 503l mm, then we will obtain 76.5393. 0/504l mm. Next, draw sketch(omitted). As result, the length of bars is 161l mm,462l mm,503l mm,76.534l mm. The minimum transmission angle is 3698.462)(arccos322142322minllllll The results obtained by computer are 2227.161l mm, 5093.442l mm, 0000.503l mm, 8986.534l mm. Provided that the figure design is carried under the condition of the Auto CAD circumstances, very precise design results can be achieved. 4. CONCLUSIONS A novel approach of diagram solution can realize the optimal transmission of the crank-and-rocker mechanism. The method is simple and convenient in the practical use. In conventional design of mechanism, taking 0.1 mm as the value of effective the precision of the component sizes will be enough. NOVEL METHOD OF REALIZING THE OPTIMAL TRANSMISSION OF THE CRANK-AND-ROCKER MECHANISM DESIGN Abstract: A novel method of realizing the optimal transmission of the crank-and-rocker mechanism is presented. The optimal combination design is made by finding the related optimal transmission parameters. The diagram of the optimal transmission is drawn. In the diagram, the relation among minimum transmission angle, the coefficient of travel speed variation, the oscillating angle of the rocker and the length of the bars is shown, concisely, conveniently and directly. The method possesses the main characteristic. That it is to achieve the optimal transmission parameters under the transmission angle by directly choosing in the diagram, according to the given requirements. The characteristics of the mechanical transmission can be improved to gain the optimal transmission effect by the method. Especially, the method is simple and convenient in practical use. Keywords ：Crank-and-rocker mechanism, Optimal transmission angle, Coefficient of travel speed variation INTRODUCTION By conventional method of the crank-and-rocker design, it is very difficult to realize the optimal combination between the various parameters for optimal transmission. The figure-table design method introduced in this paper can help achieve this goal. With given conditions, we can, by only consulting the designing figures and tables, get the relations between every parameter and another of the designed crank-and-rocker mechanism. Thus the optimal transmission can be realized. The concerned designing theory and method, as well as the real cases of its application will be introduced later respectively. 1. ESTABLISHMENT OF DIAGRAM FOR OPTIMAL TRANSMISSION DESIGN It is always one of the most important indexes that designers pursue to improve the efficiency and property of the transmission. The crank-and-rocker mechanism is widely used in the mechanical transmission. How to improve work ability and reduce unnecessary power losses is directly related to the coefficient of travel speed variation, the oscillating angle of the rocker and the ratio of the crank and rocker. The reasonable combination of these parameters takes an important effect on the efficiency and property of the mechanism, which mainly indicates in the evaluation of the minimum transmission angle. The aim realizing the optimal transmission of the mechanism is how to find the maximum of the minimum transmission angle. The design parameters are reasonably combined by the method of lessening constraints gradually and optimizing separately. Consequently, the complete constraint field realizing the optimal transmission is established. The following steps are taken in the usual design method. Firstly, the initial values of the length of rocker l3 and the oscillating angle of rocker are given. Then the value of the coefficient of travel speed variation K is chosen in the permitted range. Meanwhile, the coordinate of the fixed hinge of crank A possibly realized is calculated corresponding to value K . 1.1 Length of bars of crank and rocker mechanism As shown in Fig.1, left arc C2G is the permitted field of point A . The coordinates of point A are chosen by small step from point C2 to point G . The coordinates of point A are yA yc2 h0 (1) xA R2 y 2 (2) A where h0 , the step, is increased by small increment within range(0, H ). If the smaller the chosen step is, the higher the computational precision will be. R is the radius of the design circle. d is the distance from C2 to G . d l3 c o s 2R c o s ( ) l3 c o s (3) 2 2 2 Calculating the length of arc AC 1 and AC 2 , the length of the bars of the mechanism corresponding to point A is obtained1,2. 1.2 Minimum transmission angle min Minimum transmission angle min (see Fig.2) is determined by the equations3 l 2 l 2 (l l )2 c o s m i n 2 3 4 1 (4) 2l l 2 3 l 2 l 2 (l l )2 c o s m a x 2 3 4 1 (5) 2l l 2 3 180 (6) m i n m a x where l1 Length of crank(mm) l2 Length of connecting bar(mm) l3 Length of rocker(mm) l4 Length of machine frame(mm) Firstly, we choose minimum comparing with . And then we record min min all values of min greater than or equal to 40 and choose the maximum of them. Secondly, we find the maximum of min corresponding to any oscillating angle which is chosen by small step in the permitted range (maximum of min is different oscillating angle and the coefficient of travel speed variation K ). Finally, we change the length of rocker l3 by small step similarly. Thus we may obtain the maximum of min corresponding to the different length of bars, different oscillating angle and the coefficient of travel speed variation K . Fig.3 is accomplished from Table for the purpose of diagram design. It is worth pointing out that whatever the length of rocker l3 is evaluated, the location that the maximum of min arises is only related to the ratio of the length of rocker and the length of machine frame l3 / l4 , while independent of l3 . 2. DESIGN METHOD 2.1 Realizing the optimal transmission design given the coefficient of travel speed variation and the maximum oscillating angle of the rocker The design procedure is as follows. (1) According to given K and , taken account to the formula the extreme included angle is found. The corresponding ratio of the length of bars l3 / l4 is obtained consulting Fig.3. K 1 180 (7) K 1 (2) Choose the length of rocker l3 according to the work requirement, the length of the machine frame is obtained from the ratio l / l . 3 4 (3) Choose the centre of fixed hinge D as the vertex arbitrarily, and plot an isosceles triangle, the side of which is equal to the length of rocker l3 (see Fig.4), and C DC . Then plot C M C C , draw C N , and make angle 1 2 2 1 2 1 C C N 90 . Thus the point of intersection of C M and C N is gained. 2 1 2 1 Finally, draw the circumcircle of triangle PC C . 1 2 (4) Plot an arc with point D as the centre of the circle, l4 as the radius. The arc intersections arc C G at point A . Point A is just the centre of the fixed hinge of 2 the crank. Therefore, from the length of the crank l1 (AC AC ) / 2 (8) 1 2 and the length of the connecting bar l2 AC1 l1 (9) we will obtain the crank and rocker