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136 Ion Bostan et al creation and management of parametrical models of the mechanical assemblies on the basis of CAD-CAE. 2. General Information The ever-growing requirements, especially, concerning the bearing capacity, the kinematical accuracy and the kinematical possibilities, impose the necessity to develop a new type of planetary gearing with distinct performances. The gearing improving is one solution of the problem. Novicov - Wildhaber, Symarc and other gearings have increased considerably the bearing capacity of gear. Another direction of developing gears is the design of new types of mechanical gears. The creative search of designers has crowned with the elaboration of a new type of gearing – harmonic gear. W. Musser, an American engineer, patented the action principle of the harmonic gear in 1959. Starting that year W. Musser patented a big number of diverse constructive diagrams for harmonic gears (teeth, friction and tapped gears) and couplings, and demonstrated the possibilities of the new construction principle of mechanical gears. Thus, in 1961, the harmonic drive was produced at one of the American companies, for the first time at industrial scale. Harmonic drive are compact and possess increased bearing capacity; they provide high kinematical accuracy and possibility to transmit motion in sealed mediums, which is one of the basic advantages of harmonic drive. As their disadvantages we can mention reduced reliability of the flexible element (and, thus, of the gear, on the whole), reduced working order at high speeds, and also some technological difficulties. By the end of the 70s Prof. Ion Bostan designed a new type of gears, new in principle, - processional planetary gears with multiple gearing (B o s t a n, 1991). Over 20 years, research was carried out comprising the total range of problems from the idea to the implementation: fundamental theory of the precessional gearengineering calculation procedures-Know-How manufacturing technologiesapplications. The research results have been published in over 450 scientific papers, in about 150 patents, in 3 monographs and in one design guidebook. The absolute multiplicity of the processional gear (up to 100% of teeth pairs, geared simultaneously, compared to 5-7% in classical gears) provides increased bearing capacity and kinematical accuracy, small dimensions and mass. In addition to the above said, extended kinematical possibilities (±8÷3600 compared to 79÷300 in sinusoidal gears), reduced acoustic emission and solution of all technological problems, as advantages, open new perspectives for precessional planetary gears utilisation in various fields of mechanical engineering (B o s t a n, 1991). On the whole, processional planetary gears can be divided in two basic groups: - power processional planetary gears; - kinematical processional planetary gears.
As the planetary processional transmission is the new transmission, in the beginning of effectuation the simulation and calculation with programs CAE it is necessary to calculate theoretically base parameters. On fig. 1 is shown kinematical scheme of planetary processional transmission, but on fig. 2 is shown the design of planetary processional transmission. The main elements of transmission make: crankshaft 1, block satellite 2, fixed wheel gear 3 and mobile wheel gear 4. The important point this that, having such design (single-stage) is possible to receive transfer rate up to 3600, using Bul. Inst. Polit. Iaşi, t. LVI (LX), f. 2, 2010 137 designs of double-stage it is possible to receive transfer rate up to 14 million. Obviously that, having such big transfer rate, there are big loadings on a tooth. This problem is solved by that, all teeth it is participate in the gearing, and loading is transferred by half from them. Meaning that, all teeth are in gearing at the big loadings, the kinematic error is small. Fig. 1 – Kinematical scheme of planetary processional transmission. Principle of functioning of the planetary processional transmission the following: crankshaft 1 with inclined section to specify a block satellite 2 spatially spherical movement, block satellite by means of roller crown interaction with fixed wheel gear 3 and mobile wheel gear 4 (having a special structure generated by means of the equations), in turn a mobile wheel gear 4 it is rigidly connected with output shaft of a reducer, transfers the moment and speed of rotation. The direction of rotation of an input shaft and output shaft can be in one or in different directions. It is visible and in calculation of transfer rate if it has positive number we have an identical rotation. The transfer rate of a planetary processional transmission is defined by the relation (1). 1 3 6 2 7 4 5 Fig. 2 – Design of planetary processional transmission. (1) Zg Z 1 a i =− , ZbZg − Zg Za 2 1 where: 1 , 2 are Z g Z g number of a roller the crown satellite g1 and g2 ; Z a and Zb is represented number of a teethes the cog-wheels a and b .
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BULETINUL INSTITUTULUI POLITEHNIC D
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