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弧面凸轮数控转台的设计-机械部分【2张CAD图纸+毕业论文】【答辩优秀】

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目      录

摘    要………………………………………………………………………1

Abstract…………………………………………………………………………1

第1章 绪论2

1.1引言2

1.2弧面分度凸轮的概述2

1.3国内外发展状况概述2

1.4弧面凸轮及弧面凸轮机构的研究展望3

第2章 总体方案设计5

2.1弧面凸轮分度机构的基本结构和工作原理5

2.2主要运动参数6

2.3凸轮运动规律7

2.4弧面凸轮廓面设计10

2.5计算14

第3章 蜗轮蜗杆传动的设计17

3.1蜗杆传动的简介17

3.2普通圆柱蜗杆传动的基本参数及其选择17

3.3普通圆柱蜗杆传动的几何尺寸计算19

3.4蜗杆传动的失效形式、计算准则及常用材料20

3.5蜗杆传动的载荷和应力分析21

3.6蜗杆传动的强度计算23

3.7蜗杆传动的效率23

第4章轴的设计25

4.1Ⅲ轴的设计计算25

4.2Ⅱ轴的设计计算25

4.3轴的设计计算25

结论27

参考文献28

附录：英文翻译29

第1章 绪论2

1.1引言2

1.2弧面分度凸轮的概述2

1.3国内外发展状况概述2

1.4弧面凸轮及弧面凸轮机构的研究展望3

第2章 总体方案设计5

2.1弧面凸轮分度机构的基本结构和工作原理5

2.2主要运动参数6

2.3凸轮运动规律7

2.4弧面凸轮廓面设计10

2.5计算14

第3章 蜗轮蜗杆传动的设计17

3.1蜗杆传动的简介17

3.2普通圆柱蜗杆传动的基本参数及其选择17

3.3普通圆柱蜗杆传动的几何尺寸计算19

3.4蜗杆传动的失效形式、计算准则及常用材料20

3.5蜗杆传动的载荷和应力分析21

3.6蜗杆传动的强度计算23

3.7蜗杆传动的效率23

第4章轴的设计25

4.1Ⅲ轴的设计计算25

4.2Ⅱ轴的设计计算25

4.3轴的设计计算25

结论27

参考文献28

附录：英文翻译29



弧面凸轮数控转台的设计

摘  要：弧面分度凸轮机构是由美国人C.N.Neklutin于20世纪20年代发明的，并由其所创建的Ferguson公司首先进行了系列化、标准化生产。该机构是用于两垂直交错轴间的间歇分度步进传动。由弧面分度凸轮、从动转盘以及在从动转盘径向均布的滚子组成。由于弧面分度机构具有传动速度高、分度精度和动力学性能好、承载能力大、可靠性好等优点，所以广泛应用于各种自动机械，如烟草机械、包装机械、加工中心换刀机械手等。

分度凸轮机构具有结构简单，能自动定位以及动静比可任意选择的特点，与棘轮机构、槽轮机构、针轮机构等几种传统的间歇运动机构相比，更适合于要求高速、高分度精度的场合，因而广泛应用于各种多工位自动机械、直线步进机械中。随着自动机械向高速化、精密化、轻量化的方向发展，现有分度凸轮机构已难满足更高要求的需要。

关键词：弧面分度凸轮，参数分析，运动仿真



The globoidal indexing cam rotary table

Abstract:The globoidal indexing cam mechanism,which consists of a driving globoidal indexing cam and driven turret with four or six cylindrical rollers was firstly designed by an American,C.N.Neklutin,in 1920s and was manufactured by his own company in series and standard.The globoidal indexing cam mechanism has been using in many kinds of automatic machinery.It has great advantage over other indexing mechanisms,such as high speed、precise index and excellent kinetics.

The indexing cam mechanisms are more suitable to the work conditions where high speed and accurate output precision are needed,and have been widely used in all kinds of multi-steps machines,linear intermittent machines due to their advantages of simple structure,automatic positioning compared with other intermittent mechanisms. However,existing indexing cam mechanisms can’t meet the requirements of the fast development of automatic machines.

Key words：globoidal indexing cam,Parameter analysis,Motion simulation.


第一章 绪论

1.1引言

在当代机械制造业飞速发展过程中，现代机床制造业正在向“高速、精密、复合、智能和环保”的方向前进，而高速、高效加工在其中扮演着重要角色。在发达国家，围绕高速、高效的新型的机构，不仅在技术开发方面投入了大量精力，而且在应用推广方面取得了前所未有的进展。弧面凸轮分度机构是由输入轴上的弧面凸轮与输出轴分度轮上的滚动轴承无间隙垂直啮合，从而实现间歇输出的新型传动机构。采用弧面凸轮分度机构的弧面凸轮分度箱，它已成为当今世界上精密驱动的主流装置。它具有高速性能好，运转平稳，传递扭矩大，定位时自锁，结构紧凑、体积小，噪音低、寿命长等显著优点，是代替槽轮机构、棘轮机构、不完全齿轮机构等传统间歇机构的理想产品，产品广泛应用配套于各种组合机械、机床加工中心、烟草机械、化工灌装机械，印刷机械、电器制造装配自动生产线等需把连续运转转化为步进动作的各种自动化机械上的必备的理想功能部件。


内容简介：
MATHEMATICAL COMPUTER PERGAMON Mathematical and Computer Modelling 29 (1999) 69-87 MODELLING Curvature Analysis of Roller-Follower Cam Mechanisms HONG-SEN YAN Department of Mechanical Engineering, National Cheng Kung University Tainan 70101, Taiwan, R.O.C. WEN-TENG CHENG Department of Mechanical Engineering, I-Shou University Ta-Shu, Kaohsiung Hsien 840, Taiwan, R.O.C. (Received January 1996; accepted January 1998) Abstract-The equations related to the curvature analysis of the roller-follower cam mechanisms are presented for roller surfaces being revolution surface, hyperboloidal surface, and globoidal surface. These equations give the expressions of the meshing function, the limit function of the first kind, and the limit function of the second kind. Once these functions are known, the principal curvatures of the cam surface, the relative normal curvatures of contacting surfaces, and the condition of undercutting can be derived. Three particular cam mechanisms with hyperboloidal roller are illustrated and the numerical comparison between 2-D and 3-D cam is given. 1999 Elsevier Science Ltd. All rights reserved. Keywords-&m mechanism, Roller-follower, Principal curvature, Undercutting, Limit function. NOMENCLATURE a A,B,C &,&act b c, d I-h1 E h-II, linl *(3) shortest distance between axes zi and z, coefficients of equation of meshing derivatives of the coefficients A, B, C with respect to time shortest distance between axes zs and z3 offset coordinates of center of base circle for roller surface 3 x 1 translational displacement of the roller relative to the cam at the origin one of fundamental magnitudes of the first order for roller surface principal directions of C3 roller surface in coordinate system Ss unit normal of roller surface C3 N(3) b$)l T TV) t R P131 $1 92 t Tijl surface normal of the roller unit normal of roller surface C3 in coordinate system 53 radius of generating circular arc of globoidal roller position of points on roller sur- face Ci in coordinate system Si distance from points on roller surface to z-axis rotation matrix from coordinate systems S3 to Sr linear displacement of the cam along axis .Zi linear displacement of the follower along axis to time transformation matrix from coordinate systems Sj to Si 0895-7177/99/$ - see front matter 1999 Elsevier Science Ltd. All rights reserved PII: SO895-7177(98)00179-4 Typeset by &G-TkX ntsH.-S. YAN AND W.-T. CHENG relative sliding velocity at contact point between the roller and the cam relative sliding velocity between the roller and the cam in coordinate system S3 components of relative sliding velocity uf31) in coordinate system S3 *t $), ,w 2 e,u components of relative sliding velocity uf31) in coordinate system Sn (T 4 x 4 relative velocity matrix of the roller with respect to the cam 7131 3 x 4 relative velocity matrix of the roller with respect to the cam Wl coordinates of points on roller surface C3 in coordinate sys- tem S3 “ coordinates of points on roller surface C3 in coordinate sys- wz,wy,wz tem S3 twisted angle from axis zi to axis zo about axis xi wnz I 4ly twisted angle from axis z2 to axis z3 about axis 12 twisted angle of generating line hyperboloidal surface Pl31 angular displacement of the cam E?C rotating about axis .zi 9 angular displacement of the follower rotating about axis ze meshing function limit function of the second kind principal normal curvatures of roller surface Ci curvilinear coordinates of roller surfaces angle between principal direc- tions of mutually contacting surfaces Cl and C3 relative velocity between the roller and the cam at the origin in coordinate system S3 components of relative velocity t7131 angular velocity of the cam relative angular velocity between the roller and the cam in coordinate system S3 components of relative angular velocity w() in coordinate system S3 components of relative angular velocity w() in coordinate system Sn 3 x 3 relative angular velocity matrix of the roller with respect to the cam coefficients limit function of the first kind INTRODUCTION For designing of a transmission mechanism imparted by a higher pair, the relative location be- tween the input axis and the output axis, and the input-output relation are generally specified. Based on conjugate surfaces, the input link and the output link contact with each other. After the selection of a generating surface being one of mutually contacting surfaces, the generated surface, i.e., the other contact surface, is determined. The generated surface is solved by the equation of meshing at the point of contact. Furthermore, the curvatures of contact surfaces should be analyzed. On one hand, the dimensions of these contacting surfaces are limited in order to avoid surface interference and inappropriate tool cutting. On the other hand, the relative curvature between contacting surfaces influences on the stresses and deformations of the contacting bodies at the point of contact. The curvature properties of cam profiles and pitch curves were derived by graphical methods or analytical geometry l-4. These equations derived for the curvatures of cam profile are restricted to various particular types of cam mechanisms. For specified generating surfaces, the curvatures of generated surfaces can be derived from differential geometry and kinematic relations between mutually contacting surfaces. Litvin 5-71 presented a method to determine the principal curvatures and the principal directions of the generated surfaces, and the relative normal curvatures of mating surfaces in terms of those of generated surfaces for gear mechanisms. Dhande and Chakraborty &lo used the same concept to derive the curvature relations of various planar and spatial cam mechanisms. Chen ll used the geometric and kinematic concepts to obtain the formula of reduced curvature of two conjugate surfaces with conjugate motions of ntsCurvature Analysis 71 two degrees of freedom. Wu and Luo 12 used the concept of differential geometry of surfaces to develop a systemic theory of conjugate surfaces. The limit functions of the first kind and the second kind are defined to analyze the curvature relations and the limit points of conjugate surfaces. This paper intends to analyze the curvature properties of the roller-follower cam mechanisms. We investigate the following three types of rollers: revolution surface, hyperboloidal surface, and globoidal surface. The first type is the general one of the roller surface, and the surfaces of the latter two types are generated by a straight line and a circular arc individually. The general coordinate systems of the roller-follower cam mechanisms are given. Additionally, the surface geometry of the rollers are educed. In general, the curvatures of the cam surface, the relative curvatures of the contacting surfaces, and the condition of undercutting depends on the meshing function and the limits functions 12. Here, we only evaluate these functions that are determined by the geometry of the roller surface, the relative location of the screw axes, and the relative motion between the cam and the follower. Finally, three particular cam mechanisms with hyperboloidal roller are illustrated. Figure 1. Coordinate systems. TRANSFORMATION MATRICES AND LIMIT FUNCTIONS For the roller-follower mechanism shown in Figure 1, the roller surface Cs contacts to the cam surface Ci. The settings of the coordinate systems for four-link cam mechanisms are identical. The coordinate systems Si(q, yi, pi) and Sc(zc, yc,zc) are fixed to the frame while the moving coordinate systems Si(zi, yi, .q), &(Q, ys, 4, and Ss(zs,ys, es) are fixed to the cam, the fol- lower, and the roller, respectively. All z-axes are directed along the rotation axis or the screw axis of the moving bodies. Axes xi and xc lie along the common perpendicular between axes zi and to, and axes 22 and x3 lie along the common perpendicular between axes z2 and 3. The distance between axes zi and axis 0 is a, and the twisted angle that screws axis zi into axis zo along axis zi is cr. Similarly, the distance and the twisted angle between axes 2 and 3 are b and p, respectively. The cam screws around the input axis zi with angular displacement 41 and translational displacement 1, whereas the coordinate system Si coincides with coordinate sys- tem Si in the initial position. Likewise, to the motion of the cam, the follower screws around the nts72 H.-S. YAN AND W.-T. CHENG output axis zs with angular displacement q5s and translational displacement ss for the coordinate system Ss being transformed to SO. Point M on Cs expressed in coordinate system Ss is rc3) and the corresponding coordinates in coordinate system Sr is r cl). The rotation of the roller has no influence to the input-output relation since the roller has a surface of revolution about its rotation axis. Therefore, the roller is assumed to be fixed rigidly to the follower. By employing 4 x 4 transformation matrix, the transformations between these coordinates systems are represented by 0 a Tiol = 0 Ca -6% 0 1 0 Sa CCY 0 0) 00 0 1 Tll=L O C41 -S& 0 0 Wl Wl 0 0 0 0 ls1 (2) 0 0 01 cdJ2 -w2 0 0 To21 = ;” F ; 8”, , I 1 (3) 0 0 01 T23 = 0 cp -sp 0 (4 where we designate sine and cosine of the corresponding angle as symbols C and S, and the subscript ij in the designation Tij is the transformation matrix from coordinate systems Sj to s+ Transformation matrix Trs can be obtained by the successive matrix multiplication P13l = Pii GoI To21 P231. (5) Transformation matrix Trs is expressed in partition matrix as follows: P131 P13l fT131 = O 1 l where Rrs is a rotation matrix and drs is a translation column vector. Taking the derivatives of transformation matrix Tls, relative velocity matrix Wrs, and rela- tive angular velocity matrix firs are given by w131 = T131T i;3 = ;l3 $1 , (7) p131 = R131T &3l, (8) where qs is a translational velocity column vector and TK is the derivative of Tls with respect to time. The components of matrices Tls, Wrs, and l&13 are given in the Appendix. These compo- nents are applied to the kinematics of the roller-follower cam mechanisms. Let the homogeneous coordinates of the point on the roller surface in coordinate system Ss be 4% u, = zp(e,u) yf(e,u) zf(e,u) llT, 6-J) where f3 and u are the curvilinear coordinates of the roller surface. ntsCurvature Analysis 73 Using transformation matrix Trs, the corresponding position vector rp) for the cam surface in coordinate system Sr is given by #) = T13 #I . The relative velocity between the roller and the cam is given by 1 v3 t31) = W;, $1 , 1 (11) where wT31 = 1 Pl31 71311. (12) Expanding equation (1 l), we have where w, wy, and w, are the components of the relative angular velocity between the roller and the cam, and TV, rr, and rz are the components of the relative translational velocity between the roller and the cam at the origin of coordinate system S3. All the components of the relative velocities are expressed in coordinate system S3. For the roller-follower cam mechanism, the meshing function Cp is defined as qe,u,q E n(3) .vl) = nf W, q . (14) For the cam surface being conjugate to the roller surface at the point of contact, the equation of meshing is given by (e, 21, t = 0. (15) Simultaneous solution of equations (9) and (15) determines the contact line on the roller sur- face for any given time t, and simultaneous solution of equations (10) and (15) determines the corresponding contact line on the roller surface in the meantime. The limit function of the second kind at for mutually contacting surfaces Cr and C3 is expressed as (a,(e,u,t) = np T w; ?-a) * (16) Let KY and $) be the principal curvatures of the roller surface C3, and in and bn be the corresponding principal directions in coordinate system S3. Then, the limit function of the first kind E is defined as 7,12 Q=Jvnz+Iry+, E = K$nz + wn Y, (17) C=$)VnY-IIZ, where wnz, WQ, ynxr and vnV are the components of the relative angular and sliding velocities in the tangent plane of mutually contact surfaces C3 and Cr as follows: wnIs = wp T in 1 9 my = w3 1 (31) T bn, (18) v& = p T in, 1 Iv = $1) 1 T lid 09) where We” is a 3 x 1 column matrix corresponding to matrix (Qr3. nts74 H.-S. YAN AND W.-T. CHENG Again, the principal curvatures of the cam surface Ci and surface as follows 7: the principal directions on this tan(2a) = 25c ( $1 - $1 E + (62 - S2) “y) - $) = ( .f) + I$) )*+(c2-t2) W(2U) . CAM MECHANISMS FOR ROLLERS WITH REVOLUTION SURFACES (20) (21) (22) The general type of the roller surface is a surface generated by rotating a planar curve about its rotation axis. The coordinates of a surface of revolution (Figure 2) and the surface normal are expressed in coordinate system Ss as follows: )(8,“) = R(U)cY R(U)9 21 llT ) (23) (e, IL) = llN(3)ll-1 ce se -R+) IT , where N(3) = (1 + R2)/2 and R(U) is the radius from the point on the surface to the axis 23. Its derivative is exnressed as Figure 2. Surface of revolution. The principal curvatures of the roller surface are c3) = -R-r $3) -I 61 II II , fir = R” llNt3) ll-3 . (25) The corresponding principal directions are given by inI =-se ce 01 T, bn = llN(3)ll-1 R%f3 RS0 llT. (26) Substituting equations (13) (23) and (24) into equation (14), the meshing function is given by = NC31 -l(AsinB+BcosB+C), II II where A = rv - (u + RR)wz, B = rl: + (u + RR)wy, and C = -Rr,. (27) ntsCurvature Analysis 75 The equation of meshing is given by cp = 0 or U&B + v,SB - u,R = 0. (28) Moreover, the limit function of the second hind is given by Qt = II II Nc3) - (At sin 0 + Bt cos 0 + Ct), (2% where At = iy -(u+RR)&, Bt = iz +(u+RR)&, and Ct = -Ri,. Now, we express the relative sliding velocity and the relative angular velocity in coordinate system Sn. Substituting equation (26) into equation (18), we have wrrz = -sew, + cew, , (30) wny = II II Nt3) -l (R (cew, + sew,) + w,) . (31) Combining equations (13) (19), and (23), and using equation (28) we have ez = -seu, + ceu, (32) u&l = II II Nt3) v,. (33) Substituting equations (25) and (30) to (33) into equation (17), we have c = R-l llN(3)i1-1( seu, - ceu, + RR (cewz + sew,) + RU,) , (34) C = R llN(3)11-2 U, + sew, - cew, (35) 9 = R- l/N(3)11-1( -Bu, -Au, - TU, + (l+ Rt2 + RR)u,2) +$. (36) CAM MECHANISMS FOR ROLLERS WITH HYPERBOLOIDAL SURFACES The hyperboloidal surface is generated by a certain motion of a straight line revolved about its rotation axis. The coordinates of a hyperboloidal surface (Figure 3) and the surface normal are expressed in coordinate system Ss as follows: (37) (38) where llN(3)11 = (c2 + (zctanysecy)2)1/2. c Y 0 z XP 2 Figure 3. Hyperboloidal surface. nts76 H.-S. YAN AND W.-T. CHENG The principal curvatures of the roller surface are (3) _ 61 - II II N(3) - , I$ = (ctan+y)2 llN(3)1/-3. (3% The corresponding principal directions are given by in = E-12 -y3 x3 olT bn = NC31 II II - Ee1j2 xsutan2 y ysutan2 y EIT , (40) where E = c2 + (utany)2. Substituting equations (13), (37), and (38) into equation (14), the meshing function is given by Cp = Nc3) -l(AsinB+BcosB+C), I/ /I (41) where A = C(T -CL,) + u (tanr(, + a!,) - csec2yw,) + u2 tanysec2yw, B=c(7,+dWy)-U(tanY(7y-_dWI)-csec2YWy)+U2tanysec2yw, C = -u tan2 77,. The equation of meshing is given by Q = 0 or x3uz + y3uzI - u tan2 yv, = 0. (42) From equation (41), the equation of meshing is a quadratic equation when the curvilinear coordinate u is considered as an unknown parameter. If the curvilinear coordinate u appears in the equation of meshing, u can be solved to be function of t and 0 for the contact line. Furthermore, the limit function of the second kind is given by Qt = NC31 - (AtsinB+BtcosO+Ct), II II (43) where At = c(iy - e!&) + u (tan r(iz + ckj,) - c set” y&) + u2 tan y sec2 ytiy , Bt = c(iz + dcj,) - u (tan$ iY - ti,) - csec2 yLjy) + u2 tan y sec2 y3, C, = -u tan2 riz. Substituting equation (40) into equation (18), the relative angular velocity in coordinate sys- tem Sn are given by wnz = E-li2( -y3wz + x3wy), (44) Wry = II II N(3) - E-“2 (u tan2 y (xgwz + yswy) + Ew,) . (45) Combining equations (13), (19), and (37), and using equation (42), we have vns = E-12(-y3, + x3vy), (46) Q-la, = II II N(3) ,9-/2vz. (47) Substituting equation (39) and equations (44) to (47) into equation (17), we have - sucew, - susew, + CWZ, C = -r-l secuu, + Sf3w, - CBw, k= r(c +lrCu) -TCu(&rz + vyrr/ + &rz) +r(cSu - dC2L)(v,wy - vYwz) - csec2 UV + &. (62) (63) (64) ROLLERS OF AXIS-SYMMETRIC QUADRIC SURFACES The roller surface may be generated by a planar quadratic curve revolved about its rotation axis. The implicit form of the axis-symmetric quadratic equation in R and z is represented by aR2+bRz+ccz2+dR+ez+f =O, (65) where R2 = x2 + y2. Equation (65) can be expressed in explicit form as follows: R(z) = alz + a2 f (a3z2 + adz + ab)12, (66) where al = -b/(2a), a2 = -d/(2a), aa = (b2 - 4ac)/(2a)2, a4 = (2bd - 4ae)/(2a)2, and as = (d2 - 4af)/(2a)2. Taking the first derivative of equation (66), we have R = al f 2a3.z + a4 2da3,z2 + a42 + a5 * Taking the second derivative of equation (66), we have R” = f -(2a32 + a4)2 a3 4(asz2 + a42 + as)3/2 +( asz2 + a4.z + as)12 (67) Substituting equations (66) to (68) into the equations related to the cam mechanism with roller of revolution surface, the cam profile and curvature analysis for generating surface being axis- symmetric quadric surface can be derived. In what follows, we shall transform the parametric forms of the hyperboloidal surface and the globoidal surface into axis-symmetric quadric surfaces. Considering equation (37) for the hyperboloidal surface, the distance from the point on the surface to z-axis is R(u) = (c” + u2 tan2 7) 12. (6% Besides, let the curvilinear coordinate u be u=z-d. Substituting
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