INGENIOUS MECHANISMS. FOR DESIGNERS AND INVENTORS. VOLUME I. Mechanisms 'and Mechanical Movements Selected from Automatic Machines. INGENIOUS MECHANISMS. FOR DESIGNERS AND INVENTORS. VOLUME II. Mechanisms and Mechanical Movements Selected from Automatic Machines. IN this third,volume of INGENIOUS MECHANISMS. FOR DESIGNERS AND INVENTORS a large number of mechanisms and mechanical movements not.
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presented in Volumes I, II and III 'of "Ingenious Mechanisms for Designers and Inventors." Intermittent Worm-Gear Train. The worm-gear drive shown in Fig. Ingenious Mechanisms For Designers And Inventors Volume 2 1st Edition (FREE ) Ingenious. Mechanisms Vol.1 - pdf - My CMS - Tue, 02 Apr. Ingenious Mechanisms: (Four Volume Set) (Ingenious Mechanisms for Designers & Inventors) [Franklin D. Jones] on saicumspecsacont.tk *FREE* shipping on.
When roller C reaches position Y, rotation of the cam ceases, and it remains at rest during the continued movement of the roller to the extreme left position X. On the return movement, no rotation of cam B is produced until roller C again contacts the angular groove at position Z. Since the vertex of the angular groove surfaces are not aligned with the centers of the axial grooves, the roller cannot return to the groove previously traversed, but must enter the next one.
Continued movement of roller C causes cam B and shaft A to rotate to the next station, and the cycle is repeated.
Cylindrical Cam Positions Figures 5 and 6 show two views of a mechanism designed to guide a strand of wire through an irregular path in a ma- chine which produces a woven wire product. The purpose of' this mechanism is to create a continuously varying pattern in the weave. Position of the wire strand W in the weave pattern must bear a given relationship to other parts of the weave over a required length of the fabric, and then repeat.
Figure 5 is a plain view of the mechanism, and Fig. The driving shaft A carries the worm B, which meshes with the worm-gear C on shaft D. Shaft D carries the cylindrical cam E, which imparts a transverse guiding movement to wire W.
The two rounded grooves in cam E are identical, although the axes of the grooves are offset from the shaft axis and are degrees apart. Shaft G receives motion from worm B through worm-gear F and carries the disc H, which is connected to block J by the man I.
Block J is attached to the dovetailed slide K, which is PIa? Sixty turns of shaft A are required to completely cycle follower M through a single out-and-back traverse of rotating cam E. Slide K carries the dovetailed slide L, which in turn mounts the roller follower M.
The follower roll is held in contact with cam E by the spring N attached to a pin in slide L and a pin in bracket o attached to slide K. In operation, the rotation of worm B transmits rotary motion to cam E through worm-gear C and shaft D,. As slide K moves, roller M traverses axially along cam E, following the grooves which are constantly varying in width and depth as a result of the rotation of cam E.
The position of slide L in slide K is continually changing except when roller M is in contact with the cylindrical periphery of cam E. As the strand of wire W feeds through a hole in the leg of slide L, its position is guided by the movement of slide L.
In the diagrams, which show the position of the mechanism at the beginning of the cycle, wire W is guided in a straight path until roller M begins to follow the right-hand groove in cam E. Thus the wire is moved from start position. It returns to its start- ing position when roller M returns to the periphery of cam E.
After a short period of rest, slide L again moves as roller M enters the second groove. This is followed by a period of rest as roller M again reaches the periphery of camE. Worm-gears C and F are of different pitch diametei-s.
G has thirty teeth and F has twenty teeth. Therefore, the rotation of cam E and the movement of slide K are not synchronized.
Thus the path followed by roller M varies as the varying contours of the cam are presented to it. This, action results in varying rest periods at the ends of the movement of slide K, as well as a varying timing pattern and positioning of slide L at different points of the cycle, setting up an intricate pattern in the positioning of wire W. As stated, worm-gears C and F have thirty and twenty teeth, respectively, having a ratio of 3 to 2.
Therefore, for a complete cycle, gear F must complete three revolutions, and gear C must complete two revolutions. To develop a computational model for synthesis, a formal foundation for mechanisms design must be laid by rationalizing the process of mechanical synthesis.
Rationalization in synthesis implies that complex mechanical motions can be described in terms of primitives or building blocks. In this paper, we present a matrix methodology that forms the basis for a computable approach to design synthesis. In this methodology, the continuous design space of a mechanisms domain is discretized into functional subspaces, and each subspace is represented uniquely by a conceptual building block.
The matrix scheme serves as a formal means to a represent and reason with the building blocks at different levels of abstraction, b generate alternate conceptual design configurations, and c facilitate rapid simulation of design concepts by connecting a series of building blocks.
This process is experimental and the keywords may be updated as the learning algorithm improves. This is a preview of subscription content, log in to check access. Preview Unable to display preview. Download preview PDF.
References Artobolevski, I. Brown, D. Chase, M. Chironis, N. Datseris, P. Denavit, J. Dixon, J. Erdman, A. Faltings, B.