SU670757A1 - Toothed gearing with intersecting gear axes - Google Patents

Description

washes wheels; in fig. 2 - intersecting axles of the wheels, the axis of their helical relative motion and the direct line of gearing transmission, with the plane of the drawing parallel to the last two straight lines; in fig. 3 is a view along arrow A in FIG. 1, the plane of the drawing of which is perpendicular to the pinion axis (the face involute gear profile is shown, the projection of its longitudinal line and the projection of the engagement line, with the twin wheel conventionally not shown); in fig. 4 is a view along arrow B in FIG. 1, the plane of the drawing is perpendicular to the wheel axis (the transverse involute tooth profile of the wheel is shown together with its main circumference, the projection of the longitudinal line of the tooth and the line of engagement, with the gear not shown conventionally).

The transmission contains engaging gear 1 and wheel 2, the axles 3 and 4 of which intersect at an angle S and are separated from each other by the shortest distance uw. The axial perpendicular p 5 is shown in FIG. 2, 3, and 4. The axis 6 of the screw relative motion (see Figs. 1-3) is with the axles 3 and 4 of the wheels of the corners EI and Er and is removed from them by the shortest distance GI and Ya (see Fig. 2 and 3). Here, the equalities 2i + 22 2 and ai-f are fulfilled.

The transverse tooth profiles in cross section of the Ti-TI and TZ-Tr planes perpendicular to the axes 3 and 4 of the wheels 1 and 2 are outlined by the involutes 7 and 8 of the main circles of radii hf, and Hb ,, which vary according to a linear law Gf . ZjtgEi.

At the point of tangency. To the surfaces of the teeth, there is a general normal to the surfaces of the teeth at this point parallel to the inter-axial perpendicular 5. The common normal intersects the axis 6 of the screw relative motion at a right angle, for example, at the point / C.

Thus, such a set of contact normals, such as normals 9, 10 and I (see Fig. 1 and 2), satisfying the condition that there are no axial component forces in the gear pair, forms the Q plane (see Fig. 1 and 2), passing through the axial perpendicular p 5 and the axis of the screw relative movement of the wheels.

To form a transmission with a zero component force, a line of engagement 12 can be taken in the Q plane, intersecting the axis 6 of the screw relative motion at an angle b and the axial perpendicular 5 at the point O. The distance from point O to axis 3 in FIG. 2 is indicated by ayu, and up to axis 4 - by ozo.

The current radius Ri and the polar angle φ, the longitudinal lines 13 and 14 of the interacting teeth are chosen depending on

K, y (a,. ± Z, J + Zf -L ,:

Zi

sin 2 /

cos 2 / cos S

The longitudinal lines 13 and 14 of the teeth lie on the hyperboloids of rotation 15 and 16 (see Fig. 1).

These dependencies are calculated

Kb,, Л,, (see Fig. 3, 4), as well as the angles F1 and FZ for the current points of the longitudinal lines of the teeth 13 and 14 of the gear 1 and the wheel 2. As an example in FIG. 1-4, a gear is taken with the following meshing characteristics: 2 axes crossing angle 90 °, shortest center distance ach, 50 mm, gear ratio n-2. As can be seen from the constructions, the right pn is a common normal to the transverse involute profile of m 7 and 8 (see Fig. 3 and 4) and to the longitudinal lines of the teeth 13 and 14 (see Fig. 2, 3, 4 ). Consequently, nn is a common surface normal.

the teeth at the point of contact / (, and since it is parallel to the inter-axial perpendicular 5, the axial component of the force at this point K is zero. Similar reasoning is valid for any points on the engagement line 12.

The invention makes it possible to eliminate axial forces in the gear pair, eliminate the need to install thrust bearings, and thereby increase the efficiency of the gear train with the intersection axles of the wheels.

Claims (1)

Invention Formula The gears with the intersecting axles of the wheels and the point contact of the interacting teeth, whose working surfaces in the sections perpendicular to the axles of the wheels, are made in the form of involutes circumference, and the engagement line of the interacting teeth is a straight angle constituting with the axis of the helical relative motion of the wheels, characterized in that, in order to eliminate axial forces in the transmission and increase efficiency, the radii rf. main circles of transverse involute tooth profiles are variable and linearly variable g. ,, and the current radius r and the polar angle jc of the longitudinal lines of the interacting teeth are selected according to dependences CSS tgo + 2ftg% I. ± Zi COS Zi In sini; Cos; cos 5 , 2 - gear and wheel index; Zi is the distance from the end plane, in which the current point of the tooth line lies, to the axial perpendicular; the angle between the axis of the gear or wheel and the axis of the screw relative movement; the intersection angle of the engagement line with the axis of the screw relative motion of the transmission; the distance between the point of intersection of the engagement line and the axial perpendicular to the axis of the corresponding wheel, with the plus sign for the gear and the minus sign for the wheel in the formula for Ri. Sources of information taken into account in the examination 1. Litvin F. L. Theory of gearing. M., “Science, 1968, p. 374. W E