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

By Linke, Herbert

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Sample text

It then assumes the position B1; B1 is the point sought (the point associated with A1) of the counter-profile (B) for the drawn position of the profile A. Figure 1/24 Constructing a point on the counter-profile The individual rotations are made clear in Figure 1/24 by means of hatched triangles. ). The length of these sections is to be chosen so that the arc and chord lengths do not considerably differ from each other. , the determining tool. For this purpose, it is expedient to make use of the previously mentioned division of the pitch circles into equal arc segments.

As in this case the transmission in fact takes place in an interlocking manner (by the teeth meshing), the circumferential speed is the same at the point of contact of the rolling gear bodies (rolling cylinders); refer to Figure 1/33. 3 as negative quantities, Equation (1/34) also applies to internal gears. The gear ratio i of a gear pairing is equal to the negative relationship of the (pitch circle) diameter of the output gear to that of the input gear. Often, only the magnitude of the gear ratio is determined, and the negative sign in Equations (1/33) and (1/34), expressing the reversal of rotation, is omitted.

They are described in detail in Section 2. The tooth profile of cycloid gears is formed by hypocycloids and epicycloids [2], [5], [14]. Their advantages include the high degree of load-carrying capacity (pitting) and the fact that smaller numbers of teeth are more readily realisable than in involute straight gears. Against this, however, are the significant disadvantages that tools with cycloid gears are not straight-flanked – which makes them expensive – and cycloid gears are extremely sensitive to centre distance deviations.

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