![]() ![]() Table 4.3 presents the calculations where the profile shift coefficient has been set at x 1 and x 2 at the beginning. In the meshing of profile shifted gears, it is the operating pitch circle that is in contact and roll on each other thatportrays gear action. These values are obtainable from themodified center distance and the following formulas : ![]() The key items in profile shifted gears are the operating(working) pitch diameters (d w) and the working (operating) pressure angle (α w). In this case,it will be necessary to resort to profile shifting or to employ helical gears to obtain as near a transmission ratioas possible.įigure 4.2 shows the meshing of a pair of profile shifted gears. Note, that the number of teeth will probably not be integer values when using the formulas in Table 4.2. of Teeth z 1 + z 2 2a / m 36 5 Number of Teeth z z 1 + z 2 / i + 1 i (z 1 + z 2) / i + 1 16 20 Item Symbol Formula Example Pinion (1) Gear (2) 1 Module m Set Value 3 2 Center Distance a 54.000 3 Speed Ratio i 1.25 4 Sum of No. The calculation formulas are in Table 4.1.įig. The meshing of standard spur gears means the reference circlesof two gears contact and roll with each other. The standard spur gear is a non-profile-shifted spur gear.įigure 4.1 shows the meshing of standard spur gears. ![]() This section introduces calculation methods of standard spur gears, profileshifted spur gears, and linear racks. The calculations for spur gears are also simple and they are used as the basisfor the calculations for other types of gears. Spur Gears are the simplest type of gear. Tooth dimensionssuch as root diameter or tooth depth are considered when gear cutting. Tip diameter) are necessary for processing the gear blanks. This section introduces the dimension calculations for spur gears, helical gears, gear rack, bevel gears, screw gears, and worm gear pairs. J Sci Technol Technical Universities 61:73–77Ĭhat T, Van Uyen L (2007) Design and calculus of mechanical transmissions systems (in Vietnamese), vol 1.Gear dimensions are determined in accordance with their specifications, such as Module (m), Number of teeth (z), Pressureangle (α), and Profile shift coefficient (x). Pi VN, Dac VQ (2007) Optimal calculation of partial transmission ratios of worm-helical gear reducers for minimal gearbox length. J Sci Technol-Thai Nguyen University, 1(4):36 Pi VN, Dac VQ (2005) Optimal calculation of total transmission ratio of worm-helical gear reducers. In: Proceedings of the national conference on engineering mechanics, vol. J Sci Technol Thai Nguyen University 1(41):65–69Ĭhat T (1993) Some problems of kinematics calculation of transmission mechanics system (in Vietnamese). Pi Vu Ngoc, Dac Vu Quy (2007) Calculation of total transmission ratio of two step worm reducers for the best reasonable gearbox housing structure (in Vietnamese). Miloiu G, Dobre G, Visa F, Vintila H (1996) Optimal design of two step gear units, regarding the main paramaters. Mashinostroenie Publishing, Moskova (in Russian) Trernapski CA, Trekharev GA (1984) Design of mechanical transmission system. Hiep Nguyen Trong, Van Lam Nguyen (1979) Design of machine elements (in Vietnamese). ![]()
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