SU1323796A1 - Toothed gearing - Google Patents

Abstract

The invention relates to mechanical engineering and can be used in power and kinematic drives. The aim of the invention is to eliminate the uneven wear of the teeth under the conditions of dry and boundary friction by leveling the amount of wear on the active profile of the teeth of the wheels. In gearing with external cycloid gearing, which contains wheels 1 and 2, the profiles of their teeth are formed by a circular auxiliary centroid 3, whose center is located on the line of the center distance between the transmission pole and the center of the larger wheel, the radius r of the auxiliary centroid is equal to one fourth of the radii of the initial cylinders wheels 3 il. - (L with soo CD O

Description

From the condition of running in circles (centroid) with radii Ra-i and g follows

R 2r-sin R, | -sin (C (i) -c) c R, i / 2r;

X, -R ,, | sin f, + R ,,, i2.) cos ((c + l) xf1;

Y, R, -cos9, H- R. ,, ((c + 1) -f1)

Similarly, for the second wheel in the coordinate system X9Y2 with the beginning at point 02 true

15

Hg - R „2sinf2. + RK -1) -f2);

sin (c f |;

Cos

The invention relates to mechanical engineering and can be used in power and kinematic drives.

The purpose of the invention is to eliminate uneven wear of teeth in dry and boundary friction conditions by leveling the amount of wear on the active tooth profile of the wheels.

FIG. 1 shows the transfer, offensive appearance; in fig. 2 — plotting to derive an equation for cycloidal profiles; 10 FIG. 3 is a plan of the speeds of sliding and rolling of a cycloidal transmission.

A cog gear consists of two wheels I and 2 with centers of rotation at points O | and O2, for which, 2, Rai, 2, R /, 2 are the radii of the initial circles, the circles of the peaks and the cavities of the teeth, respectively, the point O is the center of the auxiliary centroid 3, g is the radius of the auxiliary centroid. The profile 4 of the teeth of the first wheel is outlined by an epicycloid, the profile 5 of the teeth 20 of the second wheel is outlined by a hypocycloid. Both of these curves were obtained using a single auxiliary centroid of radius g. The center of this centroid lies on the OiO2 line of the inter-axial distance-Velocity V and cycloidal cycloidal between the VV pole of the transmission and the centro 25, j profiles (see Fig. 3); from the wheels and removed from point W to the distance

g 0.25 (R, 2-R.i).

The calculation of the thickness of the worn layer of teeth of the wheels can be carried out according to the formula

hl, 2 C0nst- li, 2-n |, 2,

where 1, 2 is the specific slip of the teeth; P, P2 - the number of revolutions of the wheels.

((С ,, 2Y, R, 2 со5ф2 ч- R.

-1) f2).

sin (with f |) C

in ((sp2-

sin

4k Ri coi cosvi; R2C02 COZY2,

where 0) 1 and U2 are the angular rotational speeds of the wheels;

RI D x1 + / ;; R2 X2 + 35Cosv, -% | -Ri There are recommendations to ensure uniform wear of the teeth of the wheels in a gear, in which to ensure hi h2 you must perform

A, 2 A, - 2.

where ii2 is the gear ratio of the wheels. Equations of cycloidal profiles of the first wheel (see Fig. 1 and 2)

iRi R ,, | + TR,

In the coordinate system XiYi with the beginning at the point Oi right

Xi -R.i sin f | + R-cos (oC + f |);

Y R, i cos F1 4-R sin (DC- | -f1), where R: c. | - the radius of the initial circumference of the wheel;

F1 is the running angle of the centroids (initial circumference) of the wheel;

 gearing angle in gear; RI is the radius vector of the cycloidal profile drawn from the center Oi of the point K of the contact of the teeth;

R is the radius vector drawn from the transmission pole W to the point K of the contact of the teeth of the wheels;

R / r /.

From the condition of running in circles (centroid) with radii Ra-i and g follows

R 2r-sin R, | -sin (C (i) -c) c R, i / 2r;

X, -R ,, | sin f, + R ,,, i2.) cos ((c + l) xf1;

Y, R, -cos9, H- R. ,, ((c + 1) -f1).

Similarly, for the second wheel in the coordinate system X9Y2 with the beginning at point 02 true

Speed V and rolling cycloidal

Hg - R „2sinf2. + RK -1) -f2);

sin (c f |;

Cos

Speed V and rolling cycloidal ((C ,, 2Speed V and rolling cycloidal

Y, R, 2 со5ф2 ч- R.

-1) f2).

sin (with f |) C

in ((sp2-

sin

j profiles (see fig. 3)

4k Ri coi cosvi; R2C02 COZY2,

where 0) 1 and U2 are the angular rotational speeds of the wheels;

RI D x1 + / ;; R2 X2 + 35Cosv, -% | -Ri- - Rt.

The specific slip profiles are defined by the dependencies

V,

,

C ii2-G

From the condition of uniform cycloidal profiles 2

50 on the other hand

(2

2.g

from where

, 25 (ii2-1) -R.i 0.25 (R.2 R; ;-). 55 Transmission works as follows. When the wheel 1 rotates in the direction Ш1, its tooth with its profile 4 acts on the profile 5 of the tooth of the second wheel, causing it to rotate in the direction of sod. Profiles 4 and 5 in relative motion touch each other at point K, which moves along an arc of an auxiliary centroid of radius r.

Claims (1)

Invention Formula A gear transmission with external cycloid gearing, containing gear wheels, the tooth profiles of which are formed by a circular auxiliary centroid, whose center is located on the line of the axial distance between the transmission pole and the center of the larger wheel, so as to eliminate uneven tooth wear. under the conditions of dry and boundary friction, the radius of the auxiliary centroid is equal to one fourth of the radii of the initial cylinders of the wheels. fig.z Editor N. Kishtulinets Order 2950/41 VNIIPI USSR State Committee for Inventions and Discoveries 1 13035, Moscow, Zh-35, Raushsk nab. 4/5 Production and printing company, Uzhgorod, ul. Project, 4 Compiled by M. Levinsky Tehred I. Veres Circulation 811 Proofreader N. King Subscription