共軛凸輪機構是一種利用凸輪同時與從動件保持兩個以上的接觸點，以達到從動件確動效果的機構類型。實際應用時，凸輪與從動件間可能存在著間隙。然而間隙將導致從動件撞擊凸輪表面，進而產生噪音與降低機構精度。為了避免共軛凸輪機構產生這種現象，本論文探討如何藉由調整凸輪與從搖擺式滾子動件間的中心距離來施加預壓，藉此消除凸輪與從動件間的間隙。
首先，利用速度瞬心的概念，計算調整軸心距離前後的凸輪輪廓。接著，以調整完軸心距離後的凸輪輪廓為基準，計算接觸點法線方向的輪廓變異量。最後，根據赫茲接觸應力的相關理論，計算調整軸心距前後接觸點的預壓力、接觸力與最大接觸應力。
本研究的結果指出，藉由調整軸心距產生的預壓力可有效消除凸輪與從動件間的間隙。假設僅凸輪與從動件滾子接觸點不為剛體的狀況下，當凸輪與滾子的材料皆為AISI 1045 鋼 冷拉且凸輪角速度為1200 rpm時，軸心距的調整量應落在-5 μm以內，以避免施加過大的預壓力導致材料的破壞。

Conjugate cam mechanisms are one of cam mechanisms, with two different cams contact with the follower in two or more than point simultaneously, keeping the follower positive. Generally, there might be the clearance between the cam and the follower. However, it can cause the follower to impact the cam, generate the noise and decrease the precision of the mechanism. In order to avoid this situation for the conjugate cam mechanisms, this work researches how to adjust the distance from cam center to the follower pivot to create preload and eliminate the clearance between the cam and roller follower.
First, based on the concepts of the velocity instant centers, calculating the cam profiles in different distances from the cam center to the follower pivot. Next, in the principle of taking the original cam profile as the standard profile, calculating the variation of the contact point between the cam and roller in the direction of the normal line of the contact point. Finally, from the concepts of the Hertz contact theory, calculating the force of the preload, the contact force and the maximum contact stress in different distances between the two rotation centers.
According to the researching result, the force of preload, created after adjusting the distance from the cam center to the follower pivot point, can eliminate the clearance between the cam and the roller effectively. In the assumption that only the contact point between the conjugate cam and roller follower is not rigid body, avoiding the material damage caused by the excessive force of preload, as the material of the cam and roller follower is AISI 1045 steel cold drawn and the angular velocity of the cam is 1200 rpm, the appropriate adjustment distance between two rotation centers should be less than .

[1] 顏鴻森、吳隆庸，2014，機構學，台灣東華書局股份有限公司，台北市，221-
303 頁。
[2] 林宏宇，1993，擺動式滾子從動件共軛板凸輪之最佳化設計，碩士論文，國
立清華大學動力機械工程學系，新竹市，30-36 頁、67-71 頁。
[3] Wu, L. I., 2003, “Calculating conjugate cam profile by vector equation,” Proceedings of the Institution of Mechanical Engineers Part C: Journal of Mechanical Engineering Science, Vol. 217, pp. 1117-1123.
[4] Wu, L. I., Wu, S. H., Yan, H. S., 1999, “Simplified graphical determination of diskcam curvature,” Mechanism and Machine Theory. Vol. 34, pp. 1023-1036.
[5] Rees-Jones, J., 1978, “Mechanisms, cam curvature and interference,” Engineering, May, pp. 460-463.
[6] Waldron, K. J., and Kinzel , G. L, 1999, Kinematics, Dynamics, And Design of Machinery, John Wiley & Sons, New York, pp. 349-360, pp. 365-366.
[7] Richard, S. H., Jacques Denavit, 1964, Kinematic synthesis of linkages, McGRAW-HILL, New York, pp. 59-63, pp. 140-144, pp. 295-308, pp. 315-320.
[8] 吳隆庸、張文桐，2004，“盤形凸輪輪廓及其加工刀具路徑之解析計算法，”
機械月刊，351 期，10 月號，72-87 頁。
[9] 張文桐，2007，平面凸輪機構之機械變異量分析及其應用，博士論文，國立
清華大學動力機械工程學系，新竹市，46-50 頁。
[10]王竹豪，2015 ，具三弧面中間桿的搖擺式從動件之盤形凸輪機構的設計，
碩士論文，國立清華大學動力機械工程學系，新竹市，159-164 頁。
[11]林煜晟，2016，偏心滾子用於平移式從動件之共軛平移凸輪機構的設計，碩
士論文，國立清華大學動力機械工程學系，新竹市，21-40 頁，51-54 頁，63-
81 頁。
[12]Norton, R. L., 1996, Machine Design : An Integrated Approach, Prentice-Hall, New Jersey, pp. 493-530.
[13]Martin, G. H., 1982, Kinematics and Dynamics of Machines, 2nd Ed., McGraw-Hill, New York, pp. 69-81.
[14]吳隆庸，洪嘉宏，張信良，2002，“盤型凸輪輪廓的向量式表示法，”技術學
刊，第十七卷，第一期，59-65 頁.
[15]Johnson, K. L., 1987, Contact Mechanics, Press Syndicate of the University of Cambridge, New York, pp.84-106.
[16]五楠圖書用品股份有限公司，2000，機械工程手冊，台中市，5－280-5－281
頁。
[17]Puttock, M. J., Thwaite, E. G., 1969, Elastic Compression of Spheres and Cylinders at Point and Line Contact, National Standards Laboratory Technical Paper, No. 25, Commonwealth Scientific and Industrial Research Organization, Australia Melbourne, pp.45-49.
[18]Roack, R. J., Young, Warren C., 1975, Formula of stress and strain, McGraw-Hill, New Jersey, pp.513-528.
[19]Stachowiak, G. W., Batchelor, A. W., 1993, Engineering tribology, Elsevier Science Publishers B.V., pp.351-353.
[20]Bhaeat Bhushan, 2002, Introduction to Tribology, John Wiley & Sons, N.Y.,pp.99-110.
[21]Menezes, P. L., Ingole, S. P., Michael Nosonovsky, Kailas, S. V., Lovell, M. R.,2013, Tribology for Scientists and Engineers : From Basics to Advanced Concepts, Springer, New York, pp.93-98.
[22]Nortan, R. L., 2009, Cam design and manufacturing handbook, Prentice-Hall, New Jersey, pp. 372-378.