SU1421930A1 - Planetary precessional gear - Google Patents

Abstract

The invention relates to gears with varying speeds and can be used in drives with variable; speed. The circuit of the invention is an extension of the range of adjustment of the transmission ratio for. by making the inner cavity of the satellite hub 5 eccentric with oblique teeth 7 and placed in the latter, intermediate elements 9 and 10 with balls 12, spherical hub 13 and the rotation mechanism. The change in the transfer pitch is achieved by the fact that when the tilt angle of the groove 14 of the spherical sleeve 13 is zero, the rotation of the drive shaft 16 does not cause the rotation of the satellite 5. When the slope angle of the groove 14 changes, the satellite gains rotation increasing with an increase in the slope angle of the groove 14. 1 h. P. f-dy, 4 ill. .

Description

cl

N9

with so

. | l

Figure 1 GC

The invention relates to gears with varying speeds and can be used in various fields of engineering, in particular in the reduction of engineering, automotive, in various mechanisms with frequent switching on and off of rotation of actuators with a continuously running engine.

The aim of the invention is to expand the range of adjustment of the gear ratio by placing in the satellite hub a ball transmission

FIG. 1 shows a transmission precession with rate control -ti; in fig. 2 is a section A-A in FIG. 1 in FIG. 3 is a view of an annular protrusion formed on the surface of a spherical sleeve; Fig, 4 - the performance of the cage teeth.

Precessional gear with speed control contains body 1, central wheel located in it

2c teeth in the form of a tapered roller

3 rigidly connected with the driven shaft

4, a satellite 5 with teeth 6 of a rectilinear profile .. The inner surface of the hub of the satellite 5 is eccentric relative to the axis of the

 Cottages with oblique teeth 7 circular profile, on its inner surface and is a clip 8. In. the latter includes intermediate elements 9 and 10, having grooves 11 on the exposed surface, in which balls 12 are placed, and rigidly connected to housing 1,,

The spherical sleeve 13, on the outer surface of which the groove 14 is closed, is mounted on a crank sleeve 15 placed on the drive shaft 16 and has a turning mechanism. The latter consists of curved Spitz 17, made on the outer surface of the sleeve 15 and on the inner surface of the sleeve 18 connected through the bearing 19 to the fork 2D, and to the drive shaft 16 by means of splines 21;

Intermediate elements 9 and 10 are installed at an angle to the tooth of 7 m, which provides the same size and direction of rotation of the satellite 5..

The eccentricity of the holder 8 should provide input and output of the teeth 6 to the satellite. 5 of the clutches with rollers

3 central wheel 2. At the same time

d

five . 0

five

P

five

the precession angle is determined by the odds. Q

mule f arctg -, where a is distance - SL

from the intersection of the forming teeth 6 and the rollers 3 (precession center) to the median plane of the grooves 14.

The eccentricity of the spherical sleeve 13 should ensure the removal of the balls 12 from engagement with the non-working portion of the groove 14.

On the spherical surface of the sleeve 13 instead of the groove 14, you can perform an annular protrusion 22, the radius of curvature of the sides of which is equal to the radius of the balls 12 (Fig, 3).

The transmission works as follows.

The rotation of the drive shaft 16 through the sleeve 15 is transmitted to the spherical sleeve 13. When the sleeve 13 rotates due to its eccentric installation, the groove 14 alternately interacts with the balls 12 of the intermediate elements 9 and 10. By tilting the groove 14, the balls 12 move along the grooves 11, which leads to interaction with teeth 7, forcing satellite 5 to rotate around its axis, and also to make a precessional movement around the center of precession 23. When performing a precessional movement around the center of precession 23, the satellite 5 enters and outputs tooth 6 of meshing with the rollers 3 of the central wheel 2, Due to the teeth difference 6 and the rollers 3, the central wheel 2 rotates with reduction

five

0

g

B 6

where Zа and Z are the number of rollers and teeth of the central and satellite wheels, respectively. . . .

In this case, the 1st shaft 4 rotates with an angular velocity

and VC

-.-.- I-M7i

where Sl ach - angular: speed leading

shaft)

i - gear ratio ball transmission.

The sign of L depends on the ratio of the number of teeth 6 and rollers 3. With Z - Z 4 + b il Zj, and npn Z j Z j - 1, ia - Zv

Changing the gear ratio is achieved as follows when the angle of inclination of the groove 14 is zero, the rotation of the drive shaft 16, and with it the bushings 13 do not cause movement of the balls 12 (the amplitude of the groove 14 is zero), and therefore, the satellite 5 remains stationary. At a certain angle of inclination of the groove 14, the holder 8, and with it the satellite 5, receives a certain rotation, increasing with increasing angle of inclination of the groove 14

Thus, the transmission allows the speed of the output shaft 4 to vary in a wide range up to a full stop when the drive shaft 17 is continuously rotated.

Claims (2)

1. Planetary precession gear with speed control, co0 five 0 holding the body, located in it the driven and driving shafts, the central wheel and the satellite, characterized in that, in order to expand the range of gear ratio control, the inner cavity of the satellite hub is made eccentric with oblique teeth of a circular profile on its inner surface, and the transmission is equipped placed in the cavity of the latter at least two intermediate elements connected with the housing, a spherical sleeve with a closed groove and a mechanism for changing the angle of the latter, 2. Transfer under item 1, -o tl and h and - y and a. the fact that - on the outer surface of the spherical sleeve is annular protrusion, the radius of curvature of the sides of which is equal to the radius of the balls of the intermediate element i (Rig. G