SU1550248A1 - Safety jaw clutch - Google Patents

Abstract

The invention relates to mechanical engineering, in particular, to devices for the transmission of a moment of limited magnitude. The purpose of the invention is to increase the durability of the coupling. Half coupling (П) 3 is mounted on the shaft 1 motionless in the axial direction, П 4 - freely. The coupling halves are in contact with each other by means of profile cams. The p 4 is in contact with the aid of additional profile cams also with the bushing 2 connected to the shaft 1 by means of a splined connection. The angle profile of the main cams exceeds the angle profile of the additional cams. P3 and 4 are clamped to each other by a compression spring 6. When transmitting torque, axial forces arise on the cams of both groups, the difference between them is balanced by the force of compression of the spring 6. When overloaded, P 4 moves to the right and the left group of cams disengages from each other . Due to the small force of the spring 6, the level of dynamic loads that occur when triggered, is very small, which increases the durability of the coupling. 2 Il.

Description

3155

The invention relates to mechanical engineering, in particular, to devices for torque transmission and rotation — a limiting quantity.

The purpose of the invention is to increase durability by reducing the level of dynamic loads in the clutch operation mode.

FIG. 1 schematically shows a cam clutch, longitudinal section; in fig. 2 is a view A of FIG. one.

The safety cam clutch contains a hollow shaft 1, on which sleeve 2 is installed with the help of splines. The half couplings 3 and 4 are mounted rotatably relative to the shaft 1, and the half coupling 3 also has the possibility of axial displacement. The coupling halves 3 and C are in contact with each other by means of profile cams (Fig. 2). The sleeve 2 and the coupling half k are also in contact with each other with the help of additional pro-; fel cams. In the extreme left position of the coupling half 4 (Fig. 1), the cams of the sleeve 2 and the coupling half k are installed with a clearance along the entire perimeter of the profiles of the cams (Fig. 2). The profile angle (i.e., the angle of inclination of the side surface of the cam to the axial plane of the coupling) of the cams of the coupling half 3 and the contacting cams of the coupling half 4 exceeds the same angle of the cams of the sleeve 2 and the cams of the coupling half in contact with them (Fig. 2). The material of the cams of parts 2-k is chosen in such a way that the coefficients of friction are the same in both cam interfaces, which ensures the same character of change in the value of the coefficients of friction depending on external conditions. The axial fixation on the right of sleeve 2 is carried out with nuts 5 screwed on the threaded end of shaft 1. Pressing coupling halves 3 and 4 against each other statically provides compression force of the spring 6, which is adjusted by a nut 7 screwed on the threaded section of sleeve 2. Gaps between the cams of the sleeve 2 and the half-coupling 4 are chosen so large that the cams of the sleeve 2 do not prevent the half-coupling 4 from moving to the right when triggered to a distance that would ensure disengagement from one another

and carry them

0

cams coupling half 3 and k telny rotation.

The clutch works as follows.

The torque from the driving shaft 1 is transmitted by means of a spline connection to the sleeve 2. Due to the fact that the coupling half 3 is influenced by a moment of resistance from the driven drive side parts, the coupling half connected to it remains stationary. until the gaps between the side planes of the cams and the bushings 2 and the coupling half k are selected. After that, both coupling halves are rotated and axial forces are generated on the cams (primary and secondary).

The condition of the axial equilibrium of the coupling half k is

F, F, + F

etc

OR

F,

gde fi

ETC

axial force on the cams of the left group (Fig. 2); axial force on the cams of the right group; initial compression force of the spring 6.

five

0

five

0

five

As the torque increases, the forces F increase and F2, the force Ff increases by a larger amount than the force Ft and when the maximum torque is reached, the left group of cams disengages, and then, after turning a certain angle of the coupling half 4, engages under the force of the spring 6. Due to the fact that the spring force can be quite small (this is achieved by selecting the values of the angles "i and p), the process of re-coupling of the cams of the coupling half 3 and k is accompanied by dynamic loads, a small ranks that skazyvaets positively on increasing dolgopechnosti cams. Thus, the right group of cams creates axial force during torque transmission, which, besides. with the force of the spring 6, provides the power closure of the left group of cams and thereby helps to reduce the spring force. The adjustment of the limiting torque transmitted by the clutch is carried out by changing the compressive force of the spring 6 with a nut 7 Using the invention improves the durability of the clutch and improves the dynamics of the actuation process.

i

Claims (1)

Invention Formula Cam clutch, containing coaxially mounted and connected by means of profile cams half coupling, one of which is movable in the axial direction and is spring-loaded adjustable spring, characterized in that, in order to increase durability for by reducing the level of dynamic loads in the operation mode of the clutch, it is equipped with a fixed sleeve with profile cams, and additional profile cams are made on the moving coupling half, with additional cams of the moving coupling half and cams of the fixed sleeve installed with a gap around the perimeter of the cam profiles with the option. interaction, and the angle of the profile of the main cams of the half-coupling is greater than the angle of the profile of the additional cams of the lower half-coupling and the cams of the fixed sleeve. IDL FIG. 2