Roller-Cam Systems Design: Development of a Profile Analysis Software. O.E. Simolowo, M.Phil.* and O.A. Bamiro, Ph.D. Department of Mechanical Engineering, University of Ibadan, Ibadan, Nigeria. *E-mail: oe.simolowo@mail.ui.edu.ng ABSTRACT give the most optimal performance. This is because of the tedious analysis and synthesis The different options involved in cam systems coupled with the lengthy repetitive and multi- design such as types of cams and followers, stage numerical procedure involved in the design. number of applicable standard cam functions, In addition, cams have been found over the divisions of follower motion-segments, and years, to be hard to make compared with their possible combinations of follower displacement design (Chen, F. 1997). Several tests have to be profiles, among others, were critically studied to carried out on the cam system prior to the determine the structure and capabilities of a manufacturing stage before their final production software package suited for extensive design (Owadasa, 2004). One of such tests is the profile analyses. The software was applied in the design test for discontinuity of follower motion profiles. of cam profiles with selected follower and cam This test involves the generation of several functions and the results obtained were found profiles of a particular cam (using various input comparable with those obtained from numerical design criteria) so as to see if there are methods and existing software packages. discontinuities in these profiles. Synthesized cam systems with discontinuities in the profiles of (Keywords: cams, design, software, analyses) higher derivatives of motion such as acceleration and jerk will result in high vibrations when used in high speed cams. Thus, the process of designing, INTRODUCTION prototyping and manufacturing a cam will naturally take a very long time if the profiles have The relevance and role of cams in modern to be generated manually during the process of machine systems has made their continuous profile test for discontinuity. Consequently, study necessary and inevitable. Literature software packages are being developed for the searches have shown that there is a trend in the design of different cam systems. structure, usage, and design of cam systems towards better and more accurate output. The software developed for the design of cam in Research has been carried out on almost all this research work, like others is capable of aspects relating to cam systems since their handling various cam profiles can now be invention and introduction into the engineering syntheses and testing within seconds during the world in the last century. design and manufacturing. The developed software has extended the capability of the Cam systems are equivalent to four-bar existing packages and computer algorithms for mechanisms and are usually of one-degree the design analyses of different cam systems. freedom (Shigley and Uicker, 1980). They play (Yoshio T. and Sabry A. 1983; Olaniyi,1997; very important roles in modern machinery and are Udoh, 2001; Akinwole, 2004; Simolowo, 2004). extensively used in internal combustion engines, The present software algorithm calculates the machine tools, printing press, packaging values of the follower displacement and its machines and many other applications (Norton, derivatives and further generates their profiles R. 1998; Oyawale, 2001). They provide the against corresponding cam angles. It also obtains simplest means of achieving any desired follower critical design output parameters of roller cams. In motion such as found in complicated automatic this interactive package the user has options to operations. select (i) follower motions, (ii) cam functions, (iii) motion segments, and (iv) cam angle increments The design of cam-follower systems is a process among other parameters. Some of the unique that requires highly computerized procedures to features of the software that aids better design The Pacific Journal of Science and Technology –20– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY analysis include: (i) Increased choice of input derived from the convolution theorem for Fourier parameters for cam design and (ii) Application of transforms was used to systematically modify different input parameters to different cam cam-type profiles which accomplished the dual segments in a single design among other task of smoothing starts and stops, as well as features. improving its residual vibration characteristics (Gupta and Wiederrich, 1986). Also, the Regular- Falsi and Newton-Raphson of iterative numerical Trends in Cam Design solution of nonlinear equations are among the mathematical methods that have been used in the Cam-type motions are increasingly being used in optimum design of plate cam size avoiding many dynamic systems to move loads with undercutting (Yoshio and Sabry, 1983). smooth starts and stops (Gupta and Wiederrich, 1986). They make the attainment of almost any In recent times the trend in cam design is towards desired follower motion possible (Oyawale, 2001). producing better motion requirements for high- From the standpoint of engineering application speed applications. To this end, equations for a cams have the following advantages over number of standard types of displacement curves fundamental kinematics four-bar linkages that are that can be used to address most high-speed used for similar purposes. cam motion requirements have been considered. These equations include those for trigonometric (1) Their designs are better understood, and and polynomial functions among others. The with the application of recent CAD common approach in this method of design is to procedures, are made easier and faster. synthesize appropriate motion curves with these (2) The actions they produce are most standard equations. accurate to forecast. (3) They produce desired complicated motions that are difficult for linkages, PRESENTATION OF DESIGN PARAMETERS such as causing the follower system to FOR ROLLER CAMS remain stationary during a portion of a cycle. In this section the design input (required) and (4) They occupy less space when compared output (calculated) parameters and their with linkage systems equations are presented as shown in Figure 1. The input parameters are: Changes have taken place generally in all aspects of cam systems since their application in 1. Cam/follower pressure angle (φ) various areas of machinery design. However, the 2. The roller radius Rr. most prominent and relevant to this research 3. The prime circle radius (Ro) work are those trends in the area of their design. 4. The eccentricity (Є) Various methods have been applied over the years in the design of cam systems so as to give the best design in terms of calculating critical The output parameters include: output parameters and generation of cam and motion profiles. One of the earliest methods used 1. The roller cam coordinates (u, v). in the generation of cam profiles was the use of 2. The radius of curvature of cam profile (ρ) graphical layout method (Jensen, 1968; Shigley 3. The radius of curvature of pitch circle (ρpitch) and Uicker, 1980). This method entailed the 4. The follower displacement and derivatives (y, transfer of distances from the displacement y' and y") diagram of the follower onto the cam drawing so as to generate the cam profile. The method Cam/Follower Pressure Angle however, had the problem of undercutting (inability to produce a complete cam profile An expression for pressure angle is given in without sharp edges). Equation (1) (Shigley, 1980): Various mathematical methods have also been φ = tan-1((y’ – є)/ ((R 2 – є2)1/2o + y)) (1) applied to cam systems in an attempt to find the best way of designing the components. On the From (1) it can be seen that once the modification of cam-type profiles, a procedure displacement equations y are known Ro and ε can The Pacific Journal of Science and Technology –21– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY be adjusted to get an appropriate pressure angle and analysis of all follower and cam φ. Pressure angle φ is continuously changing with profiles generated as compared with a the rotation of the cam and therefore we require maximum of few possible increments in the extreme values of φ. existing packages. 2. Application of different angular increment Minimum Radius Of Curvature and Cam to different cam segment in a single Coordinates simulation for every profile generated. Examples of this feature are shown in To calculate the radius of curvature of the cam screenshots 2, 3 and 4 below. Existing profile (ρ), the radius of curvature of the pitch packages apply only same angular curve (ρpitch) equation is given by: increment to all the motion segments in a single cam design. 3 / 2 ⎡ ⎤ 3. Application of different roller radii in (R + y)2⎢ o +( y ') 2 ⎥ segment-by-segment simulation of cam ρpitch = ρ + R = ⎣ ⎦ (2) r 2 2 profile as shown in screen shot 5. In (Ro + y) + 2( y ' ) − (Ro + y) y ' ' existing packages, only a specified roller radius is used for all the motion segments is used. The rectangular coordinates (u, v) of the in a particular simulation. cam profile of plate cam with a reciprocating roller follower are given by: 4. Presentation of motion derivatives results in both linear and radial dimensions. u = ( R −ε 2 + y )sinθ + ε cos+ R sin(φ −θ ) (3a) Other packages consider either linear or o r radial dimensions in their result output. ( 5. Distinct graphics demarcation of different v = Ro −ε 2 + y )sinθ −ε cos− Rr sin(φ −θ ) (3b) motion segments on every cam profile generated as shown in screen shots 2, 3, 4, and 5. This makes for easy correction Cam Functions and Follower Motions and re-design of the affected segments that can be easily identified. Where φ is the pressure angle given by Equation (1) (Shiegley, 1980). The cam functions are 6. Simplified and less cumbersome designs expressed in terms of the follower displacements on increased interfaces. and their derivatives. The cycloid and modified harmonic are presented later in Equations (5a) – These features among others make the (6f). developed software more extensive in design analyses, synthesis and simulation based on the following reasons. SOFTWARE ARCHITECTURE 1. More cam profiles can be generated by The software structure and features enhancing the software because of the increased comprehensive and extensive cam design choice of cam angle increments. analyses for plate cams with roller followers carried out in this work are here by presented in 2. Different design analyses are possible for this section. various segments of a cam profile within a single simulation based on its ability to apply different increments and roller radii Features of Developed Software in these segments. The peculiar features of the developed software compared with features of widely used software 3. Ability to give precise segment of design include the following: defects such as cursps and carry out faster and more accurate re-design 1. Possibility of using a wider range of procedures based on graphics (color) angular increments in design simulation distinction for each segments. The Pacific Journal of Science and Technology –22– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY 4. Its universality in design simulation (iii) Radius of curvature of cam profile ρ using applications due to its ability to handle equation (2) and the minimum value ρmin both linear and radial displacement for that segment derivatives. (iv) The values of cam coordinates u and v using equations (3a and 3b) respectively. Software Structure and Interface 3. The overall φmax, φmin and ρmin from all the φmax, Software for design analyses of roller cam φmin and ρmin of the different segments systems has been designed in this work. This considered in the design are calculated. developed software is suitable for extensive cams design analyses. The developed algorithm using 4. The ρpitch using overall ρmin and equation (2) is an object-oriented high level language (Byron S, also computed. 2004; Evangelos, P, 2002) was based on numerical procedures obtained from the literature. Software Procedure for Determining R with The software structure consists of five different oφ > 35o program modules. They are: Max In the design of plate cams using roller follower, (1) Declaration of program statements and variables the values of φmax must be checked so as not to o (2) Selection of design options exceed 30 to 35 in each of the follower motion (3) Generation of follower motion values, design segments. For cases with φmax exceeding these output parameters and cam coordinates. values in one or more of the segments, the (4) Generations of Cam and follower profile sequence of operation of the algorithm is (5) Description of subprogram and public described below. functions called in modules 2 - 4 above. 1. The values of maximum pressure angle Φ (30-o The software interface development for the 35 ) for each of the motion segments are read as overall software is based on the overall cam input values. design option chart of the developed software shown in Figure 2. The figure is a representative 2. In each of the follower motion segments, with diagram of the designed active screens common the given Lift L, Cam angular difference β, initial to the roller follower options for the software. The and final angles of cam rotation, the algorithm screens are in three parts. (i) Input screens (1-4); calculates the following; (ii) Tutor screens (5-7); (iii) Result output screens (8-15). (i) y’ and y” for each increment in cam angle using the equations of the required cam Sequence of Algorithm Operations functions. (ii) Ro : making Ro the subject of the formula The sequence of operations of the developed given in equation (1) to arrive at: algorithm is presented below. 2⎛ ⎞ 1. The following input parameters are read into ⎛ y'−ε ⎞Ro= ⎜⎜ ⎟ − y⎟ + ε (4) the computer; prime circle radius Ro, roller radius ⎜⎜ tanφ ⎟ ⎟⎝⎝ ⎠ ⎠ Rr and eccentricity ε based on the design criteria 3. The overall maximum values of the prime circle 2. For specified cam angle intervals within each radius Ro from all the calculated values in the motion segment; the algorithm calculates the different follower motion segments are following: determined. (i) The follower displacement and Once the new value of prime circle radius Ro is derivatives y’ and y” using the equations determined following the steps described above, of the required cam function. a complete re-design is carried out for the motion (ii) The pressure angle φ using equation (1). segments using the newly calculated prime circle The φmax and φmin for each segment. φmax radius Ro. must not exceed 30 to 35o. The Pacific Journal of Science and Technology –23– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY Vfollower= VP24 Pressure angle φ Follower Common normal (Axis of transmission) 4 Common tangent (Axis of slip) A R r y φ Prime D VP24 circle R a O 2 O C 2 P24 Pitch curve Cam profile Base circle e x RP24 Figure 1: Plate Cam in Contact with Reciprocating Roller Follower The Pacific Journal of Science and Technology –24– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY Figure 3: Representation of Display Screens for the Developed Software. The Pacific Journal of Science and Technology –25– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY SOFTWARE RESULTS VALIDATION AND 5b) and (6a – 6f), respectively. Four different APPLICATION design case studies were used in the validation. The first case study involved the computation of Validation Methodology the prime circle radius Ro for a cycloid rise motion while the second and third design cases In the validation of the software using numerical considered the calculation of maximum pressure results, the procedures presented earlier for the angles φmax for modified harmonic and cycloid numerical and software design of roller cam motion respectively. The minimum radius of systems were adhered to. Three critical design curvature was determined using the numerical parameters as presented by Shigley and Uicker, and software procedures for a cycloid-rise (1980) were used in the results validation Viz. motion in the fourth case. Shown in Table 1 are determination of (i) minimum prime circle radius the input parameters for the design cases Ro (ii) maximum pressure angle φmax (iii) considered in the software validation. θ1 and θ2 minimum radius of cam curvature ρmin. The are the angles specifying the range of the values of y, y', y" of the cycloid and Modified motion segment being considered. harmonic motions employed in the result validation were obtained from Equations (5a & Cycloid – Rise Motion ⎛ θ 1 2πθ ⎞ Modified Harmonic Rise-Motion: y = L⎜⎜ − sin ⎟⎟ ⎝ β 2π β ⎠ 1For 0 ≤θ ≤ β y′ L ⎛ ⎜ 1 cos 2πθ ⎞ 8 = ⎜ − ⎟⎟ (5a) β ⎝ β ⎠ y L⎡= ⎢0.43990085 θ − Z1⎤⎥ y′′ 2πL sin 2πθ= ⎣ β ⎦ β 2 β Where ⎡ ⎤Z1 ⎛= ⎢0.0350062sin⎜⎜4π θ ⎞ β ⎟ ⎟⎥ 2 L ⎛ θ ⎞ ⎣ ⎝ ⎠⎦y′′′ = 4π 3 cosβ ⎜ ⎜2π ⎟⎟ ⎝ β ⎠ y' L ⎡ ⎤ = 0.43990085 ⎢1− cos ⎛ ⎜⎜4π θ ⎞ ⎟ β β ⎟⎥ ⎣ ⎝ ⎠⎦ Cycloid – Return Motion y"= 5.5279571 L sin⎛4π θ ⎞⎜ ⎟ (6a) β 2 ⎜ ⎟⎝ β ⎠ ⎛ y L⎜1 θ 1 sin 2πθ ⎞ = ⎜ − + ⎟⎟ y′′′β 2π β = 69.4663577 L cos⎛⎜4π θ ⎞⎟ ⎝ ⎠ β 3 ⎜⎝ β ⎟⎠ ⎛ ⎞ y′ L= − ⎜⎜ 1− cos 2πθ ⎟⎟ (5b) 1 7 β β For β ≤ θ ≤ β , ⎝ ⎠ 8 8 ⎡ y L 0.28004957 0.43990085 θ ⎤2πL 2πθ = ⎢ + − Z2⎥ y′′ = − 2 sin ⎣ β ⎦β β Where ⎡ ⎤ L ⎛ θ ⎞ Z 2 = ⎢0.31505577cos ⎛ 4π θ π ⎞ ⎜⎜ − ⎟⎟⎥ y′′′ = −4π 2 cos⎜2π ⎟ ⎣ ⎝ 3 β 6 ⎠⎦ β 3 ⎜ ⎟⎝ β ⎠ ⎡ ⎤ y'= 0.43990085 L ⎢1+ 3sin ⎛ 4π θ π ⎞ ⎜⎜ − ⎟⎟⎥ (6b) β ⎣ ⎝ 3 β 6 ⎠⎦ The Pacific Journal of Science and Technology –26– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY L ⎛ 4π θ π ⎞ Where ⎡Z5 0.31505577cos⎛ 4π θ π ⎞⎤ y"= 5.5279571 2 cos⎜⎜ − ⎟⎟ = ⎢ ⎜⎜ − ⎟⎟⎥ β ⎝ 3 β 6 ⎠ ⎣ ⎝ 3 β 6 ⎠⎦ L ⎡ ⎛ 4π θ π ⎞⎤ y′′′ L= −23.1553 3 sin ⎛ 4π θ π ⎞ ⎜ − ⎟ y'= −0.43990085 ⎢1+ 3sin⎜⎜ ⎟ β ⎜ − ⎟⎟⎥ β ⎝ 3 β 6 ⎠ ⎣ ⎝ 3 β 6 ⎠⎦ 7 For β ≤θ ≤ β , y"= −5.5279571 L cos⎛ 4π θ π ⎞⎜⎜ − ⎟⎟ (6e) 8 β 2 ⎝ 3 β 6 ⎠ L ⎧ y′′′ = 23.1553 3 sin ⎛ 4π θ π ⎞ ⎜⎜ − ⎟⎟ y = L⎨0.56009915+ 0.43990085 θ ⎫ − Z3⎬ β ⎝ 3 β 6 ⎠ ⎩ β ⎭ 7 ⎪⎧ ⎡ ⎤⎫ For β ≤θ ≤ β , Z3 = ⎨0.0350062sin 2π ⎛2 θ 1⎞⎢ ⎜⎜ − ⎟⎟ ⎪ 8 ⎩⎪ ⎣ ⎝ β ⎥⎬ ⎠⎦⎪⎭ y ⎧= L⎨1- 0.56009915+ 0.43990085 θ ⎫ − Z6⎬ ⎧ ⎡ ⎤⎫ ⎩ β ⎭ y'= 0.43990085 L ⎪1 cos 2π⎛2 θ− ⎜ −1⎞⎟ ⎪⎨ ⎢ ⎜ ⎟⎥⎬ ⎧⎪ ⎡ ⎛ θ ⎞⎤⎫β ⎪⎩⎪ ⎣ ⎝ β ⎠⎦⎭⎪ Where Z6 = ⎨0.0350062sin⎢2π⎜⎜2 −1⎟β ⎟⎥⎬ ⎩⎪ ⎣ ⎝ ⎠⎦⎪⎭ ⎡ ⎤ y"= 5.5279571 L2 sin⎢2π ⎛2 θ ⎞⎜⎜ −1⎟⎟⎥ (6c) ⎧ ⎡ ⎤⎫β ⎣ ⎝ β ⎠⎦ y'= −0.43990085 L ⎪ ⎨1− cos⎢2π ⎛ θ ⎞ ⎜2 −1⎟ ⎪ β ⎪ ⎜ β ⎟⎥ ⎬ ⎩ ⎣ ⎝ ⎠⎦⎪⎭ ⎡ ⎤ y′′′ = 69.4663577 L ⎛ θ ⎞3 cos⎢2π⎜⎜2 −1⎟⎟⎥ L ⎡ ⎤β ⎣ ⎝ β ⎠⎦ y"= −5.5279571 2 sin⎢2π ⎛ θ ⎞ ⎜⎜2 −1⎟⎟⎥ β ⎣ ⎝ β ⎠ ⎦ (6f) ⎡ ⎤ Modified Harmonic Return-Motion: y′′′ = −69.4663577 L 3 cos 2π ⎛ θ ⎞ ⎜ β ⎢ ⎜ 2 −1⎟ β ⎟⎥ ⎣ ⎝ ⎠⎦ 1 For 0 ≤θ ≤ β , 8 Software Application y ⎡ θ ⎤= L⎢1- 0.43990085 − Z 4⎥ The developed software was used to carry out ⎣ β ⎦ sample simulation of 2, 3, 4, 6, and 7 motion ⎡ ⎛ θ ⎞⎤ segments for the roller follower design option. Where Z4 = ⎢0.0350062sin⎜⎜4π ⎟⎟⎥ The final motion and cam profiles are presented ⎣ ⎝ β ⎠⎦ in screenshots 1, 2, 3, 4, and 5, respectively. The ⎡ y' 0.43990085 L 1 cos⎛ θ ⎞ ⎤ simulations also show some of the improved = − ⎢ − ⎜⎜4π ⎟⎟⎥ (6d) features of the software as discussed earlier β ⎣ ⎝ β ⎠⎦ Simulation Results y′′′ = −69.4663577 L cos⎛⎜⎜4π θ ⎞ ⎟⎟ Figures 2, 3, 4, and 5 show that all the results β 3 ⎝ β ⎠ obtained from the two methods (software and L ⎛ θ ⎞ numerical) are within the same ranges. The y"= −5.5279571 sin⎜4π ⎟ choice of cam motions for the case study designs β 2 ⎜⎝ β ⎟⎠ considered in the validation of research results 1 7 have been limited to existing data in literatures. For β ≤ θ ≤ β , They are the Cycloid (half and full) and the 8 8 Modified Harmonic motions. The Full cycloid and ⎡ θ ⎤ M. Harmonic have been taken into consideration y = L⎢1- 0.28004957+ 0.43990085 − Z5⎥ since the software can handle these design ⎣ β ⎦ options. The Pacific Journal of Science and Technology –27– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY Table 1: Input Parameters for Software Validation Case Studies. DESIGN CASES (1) (2) (3) (4) (5) θ1 (DEG) 0 163.5 0 163.5 163.5 θ2 (DEG) 182 300 182 300 300 β (DEG) 182 136.5 182 136.5 136.5 L (MM) 64.26 76.20 64.26 76.20 76.20 φ (DEG) 30 30 + + + RO (MM) + + 82.5 82.5 82.5 RR (MM) + + + + 12.7 CAM MOTION CYCLOID M. HARMONIC CYCLOID M. HARMONIC CYCLOID FOLL. MOTION RISE RETURN RISE RETURN RISE +THESE VALUES ARE NOT NEEDED AS INPUT FOR INDICATED DESIGN CASE STUDY case1 Ro min Shigley Ro min Software 0 10 20 30 40 50 (mm) Figure 2: Numerical Results (Shigley and Uicker) vs. Software Results for Design Case 1. The Pacific Journal of Science and Technology –28– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY case2 case3 0 10 20 30 40 (Degrees) Figure 3: Numerical Results (Shigley and Uicker) vs. Software Results for Design Cases 2 and 3. case 4 Rho min Shigley Rho Min. Software 0 20 40 60 80 (mm) Figure 4: Numerical Results (Shigley and Uicker) vs. Software Results for Design Case 4. The Pacific Journal of Science and Technology –29– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVE Max.P.Angle Max.P.AngleR Software ShigleySITY OF IBADAN LIBRARY Software Shigley 70 60 50 40 30 20 10 0 case1(Ro) case2 (P.A) case3 (P.A) case4 (Rho) Figure 5: Combined Numerical Results (Shigley and Uicker) vs. Software Results for All Cases. Screenshot 1: Display of Y, Y’, Y” and cam Profile for 2-segmented Motion (Roller follower) on a Single Interface. The Pacific Journal of Science and Technology –30– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY Shown in screen shot 1 is the combination of the involved in cam systems design has justified the displacement profile and its derivatives for a 2- need for the continuous development of various motion segment (Rise- Return) simulation carried software in this area. The software design out by the software. Screen shot 2 shows a roller algorithm entailed the use of standard cam profile for 3-motion displacement profile. It trigonometric and polynomial cam functions in also shows the application of two different angular simulating the follower motion derivatives; increments in the generation of the cam profile. In determining the follower and cam design screen shot 3, simulation is carried out for a 4- parameters; generating the cam coordinates; and motion displacement. Also, different degree finally drawing the follower motions and cam increments have been applied to the four different profiles. segments. In screen shot 4, the segment-by- segment application of the increased cam angle increment in the generation of a 6-motion Among some of the features of the developed segment cam profile is shown. Screen shot 5 is a software, there are some unique ones. They design output showing a 7-motion segment cam include; increased angular increment in profile with different roller radii simulated over the generating all the cam and follower profiles and in different motion segments. calculating all design parameters; segment by segment application of the increased angular increment in generating cam and follower profiles CONCLUSION and determination of other values; presentation of design results to include the rotational and linear Software algorithms that can be used for more dimensions for all follower motions and its comprehensive deign analysis of plate cam derivatives. Using it to simulate cam systems with systems with reciprocating roller follower has various follower motion requirements validated been developed. The many design combinations, the software. The results obtained conformed to repetition of calculations coupled with plotting of those of other related works for the same set of hundreds of cam and follower profile points follower motion requirements. Screenshot 2: Cam Profile Simulation using Different Degree Increments and Same Roller Radius for Three Motion Segments. The Pacific Journal of Science and Technology –31– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY Screenshot 3: Cam Profile Simulation using Different Degree Increments and Same Roller Radius for Four Motion Segments. Screenshot 4: Cam Profile Simulation using Different Degree Increments and Same Roller Radius for Six Motion Segments. The Pacific Journal of Science and Technology –32– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY Screenshot 5: Cam Profile Simulation using Different Roller Radius for Seven Motion Segments. REFERENCES 8. Norton, R.L. 1998. Design of Machinery. McGraw 1. Akinwole, O.A. 2004. “Computer Aided Design of Hill Book Company: New York, NY. High Speed Cams: Software Development and Design Analysis Of Polynomial Functions”. Project 9. Olaniyi, M.O. 1997. “Cam Design: Computer Submission: Department of Mechanical Approach”. Project Submission. Department of Engineering, University of Ibadan, Nigeria. Mechanical Engineering, University of Ibadan, Nigeria. 2. Byron S. G. 2004. Schaum’s Outlines Visual BASIC. Tata McGraw-Hill Publishing Company: 10. Owadasa . 2004. “Computer Aided Design of High New Delhi, India. Speed Cams: Software Development and Design Analysis of Polynomial Functions”. Project. 3. Chen, F.Y. 1997. “A Survey of the State-of-the-Art Department of Mechanical Engineering, University of Cam System Dynamics”. Mechanism Machine of Ibadan, Nigeria. Theory. 12: 201-204 11. Oyawale. F.A. 2001, Engineering Drawing. 4. Evangelos, P. 2002. Mastering Visual Basic 6. Lensprint & Company: Lagos, Nigeria. BPB Publications: New Delhi, India. 12. Shigley. J.E. and Uicker J.J. 1980. Theory of 5. Gupta K.C. and Wiederrich, J.L. 1986. “On the Machines and Mechanisms. McGraw-Hill Book Modification of Cam-Type Profiles”. Journal of Company: Auckland, NZ. Mechanism of Machine Theory. 21(5):439-440. 13. Simolowo, O. E. 2004. “Computer Aided Design of 6. Jensen C.H. 1968. Engineering Drawing and Cam Profiles”. Master of Philosophy Dissertation. Design. McGraw-Hill Company Limited: Toronto, Department of Mechanical Engineering, University Canada. of Ibadan, Nigeria 7. Norton, R.L. 2000. “DYNACAM for Windows”. 14. Simolowo O.E. and Olaniyi, M. 2004, “Design and http//www.designofmachinery.com/cam Simulation Algorithm For Cam System Analysis”. The Pacific Journal of Science and Technology –33– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY Nigerian Society of Engineers Technical SUGGESTED CITATION Transactions Journal. 39 (4): 70-82 Simolowo, O.E. and O.A. Bamiro. 2009. “Roller- 15. Udoh ,E.M. 2001. “Computer Aided Design of Cams”. Bachelor of Science Project. Department of Cam Systems Design: Development of a Profile Mechanical Engineering, University of Ibadan, Analysis Software”. Pacific Journal of Science Nigeria and Technology. 10(1):20-34. 16. Yoshio, T. and Sabry, A.E. 1983. “A “Computer- Pacific Journal of Science and Technology Aided Method for Optimum Design of Plate Cam Size Avoiding Undercutting and Separation Phenomena–1”. Mechanism and Machine Theory. 18 (2): 157-163. ABOUT THE AUTHORS O. E. Simolowo lectures at the Department of Mechanical Engineering, University of Ibadan in Nigeria. He holds a Masters of Philosophy degree in Mechanical Engineering from the same institution. He is a corporate member of the Nigerian Society of Engineers and a Registered Engineer of the Council for the Regulation of Engineering in Nigeria. His areas of research and specialization are Machine Design, Engineering Software Development, and Solid Mechanics of which he has publications in learned journals. O. A. Bamiro is a professor of Solid Mechanics at the Department of Mechanical Engineering University Of Ibadan, Nigeria. He obtained his B.Sc. degree in Mechanical Engineering from Nottingham University, England and Doctor of Philosophy degree at the McGill University, Montreal, Canada. He is a fellow of the Nigerian Society of Engineers and also Fellow of the Academy of Science in Nigeria. He has published widely in his research areas which include Systems Dynamics, Engineering and Strategic Planning Software Development in the area of management decision making. He is currently the Vice-Chancellor of the University of Ibadan. Nigeria. The Pacific Journal of Science and Technology –34– http://www.akamaiuniversity.us/PJST.htm Volume 10. Number 1. May 2009 (Spring) UNIVERSITY OF IBADAN LIBRARY