Cylindrical Gears. Calculation - Materials - Manufacturing by Linke, Herbert

By Linke, Herbert

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For the drive in Figure 1/17a, the mean gear ratio is given by |iM| = 1. 1) i = Ȧ1 Ȧ2 = − r2 r1 or ( i = − 2 ( a ′ / b ′ ) 1 + 1 - ( b ′ a′ ) 2 2 ) cos ij1 + 1 (1/20) In addition to the aforementioned classification of gears from kinematic perspectives (non-uniform and uniform transmission gears), other criteria are also used for the differentiation, such as • design (pedestal gears, planetary gears), • intended use (vehicle gears, turbo gears, crane gears), • possibilities of changing the gear ratio (switchable and non-switchable gears), • physical action mechanism (mechanical gears, hydraulic gears), • gear body form (cylindrical gears, bevel gears, worm gears).

The ST RGW 5744-86 also formed the basis of the new load-carrying capacity standard TGL 10545 (1989) of the former East Germany, also worked out by the TU Dresden. These values are somewhat lower than those laid down in DIN and ISO [1/20, 21] (by an order of 10%). There then ensued investigations into gears with internally toothed grinding steps [1/22, 1/23]. 2 Tooth Flank Stress – Pitting The derivation made by H. Hertz (1881) forms the basis for the calculation of the pitting resistance. A. Föppl recognised the significance of this theory, developed it further, presented it to designers and republished it in 1897.

1. 1. 3 Scuffing Load The increase in the power transmitted per spatial unit was also associated with a growth in the size of losses and the heating of the gears. The aviation industry, in particular, has provided new requirements and cases of damage. As scuffing has now been identified more frequently, efforts were undertaken to take into account this phenomenon in the calculation. H. Hofer (ZF Friedrichshafen) places the band resulting from (d·b) in relation to the power transmitted or lost. This was considered as a heat accumulation value (or as a variable for scuffing safety) (1926): Sa = z1 m b 20 N (1/13) z1 number of teeth (pinion) m module in mm b face width in mm N power in hp This did not yet provide the link to the work to determine wear that had been carried out considerably earlier, including by Poncelet (1826), Weißbach (1852), Bach (1881), Stribeck (1894) and Schiebel (1911).

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