SU1638394A1 - Clutch - Google Patents

Abstract

The invention relates to mechanical engineering and is intended for the transmission of torque, preferably in nutrunners with high torque. The purpose of the invention is to enhance the functionality by providing rotation of the driven shaft at different speeds and transmitting different moments. The clutch consists of a drive shaft 1 and a follower shaft 18 connected by means of a planetary mechanism, the carrier of which is connected to the driven shaft. In the cavity of the drive shaft there is an intermediate element in the form of a tapered disk 15, pressed by the spring 16. In the initial position, the tapered disk pushes the balls, which, being in the grooves of the shaft 1 and the bushes 7, connect them. The moment is transmitted from the drive shaft through the carrier to the driven shaft. If the moment on the shaft 18 exceeds the calculated one, the balls move to the center of the coupling, connecting the grooves 2 of the drive shaft with the grooves 10 of the shank of the sun wheel. The rotation will then be transmitted from shaft 1 to shaft 18 through a planetary mechanism with a decrease in rotation frequency and an increase in torque. The use of the coupling in the wrenches will increase productivity and reduce size and energy consumption. 9 il.

Description

P

Jl.

14

I

R

w

18

75

ABOUT

oh

00

with y

15

FIG. one

The invention relates to mechanical engineering and is intended to transmit a rotation, preferably in high torque torque wrenches.

The aim of the invention is to enhance the functionality by providing rotation of the driven shaft at different speeds and torques depending on the moment of resistance on the driven shaft.

FIG. 1 schematically shows the proposed coupling in the initial position, a variant with a planetary gearbox; in fig. 2 is a section A-A in FIG. one; in fig. 3 - the same, in the mode of increased torque; in fig. 4 — node I in FIG. 2; in fig. 5 — node II in FIG. one; in fig. 6 — node I in FIG. 2 in an intermediate position; in fig. 7 - node II in FIG. 1 in an intermediate position; in fig. 8 - node I in the mode of increased torque; in fig. 9 - node II in the mode of increased torque.

The clutch contains a drive shaft 1 with a cavity made therein with through slots 2 in its walls in which balls 3 are placed. One of the walls of the grooves is made with a straight section and a bevel 4 that forms an angle y with a radius. The straight section is in conjunction with the outer surface of the shaft and the bevel along lines 5 and 6. The outer surface of the shaft 1 covers the inner surface of the sleeve 7 connected to the planet carrier. In the walls of the sleeve 7 are grooves 8, one of the walls of which is located at an angle a to the radius. The slopes of the slots 2 and 8 are directed in opposite directions.

With the inner surface of the cavity in ala 1, the shank 9 of the sun wheel of the planetary mechanism is matched, on the end surface of which there are equal spaced slots 10, with protrusions 11, the tops of which are made with a chamfer 12, (Fig. 5). The number of grooves 10 is equal to the number of grooves 2 and 8. In the axial direction, the mutual position of the parts 1.7 and 9 is fixed by a spring ring 13 and shoulder 14. With the balls 3 there is a conical surface of the disk 15 located inside the shaft 1 and pressed against the balls by the spring 16.

The depth of the grooves 10, the outer diameter of the sleeve 7 and the diameter of the balls are chosen in such a way that, being in extreme positions - extended towards the periphery or recessed, the balls can connect the drive shaft 1 only with either the sleeve 7 or the shank 9.

FIG. 1, the clutch is depicted in combination with a planetary mechanism consisting of satellites 17 of the carrier 18, rigidly coupled to the output shaft (spindle) of the sun wheel 19 and the fixed epicyclic wheel 20.

The clutch works as follows.

In the initial position, the cone disk 15 by means of the spring 16 pushes the balls to the periphery until they stop into the bevels of the slots 9 of the sleeve 7, connecting the drive shaft 1 and the driven shaft 18. When transmitting the rotating moment, the force Pi, angled (Fig. 4), from line 6 through the ball 3 is transmitted to the bevel of the groove 8. The reaction from the bevel P2 is laid out on the horizontal and vertical Rvert. components. By selecting the force of the spring 16, the angle a and the angle e (Fig. 5), the position is reached when the vertical force Rc of the disk is greater than Pvert., When a certain moment is transmitted.

If this moment is exceeded, the force Rvert will increase on the shaft 18, it will exceed the value of the force Rconus (Fig. 5), as a result of which the ball 3 will move to the coupling axis and will take the position shown in Fig. 5. 6

In this position, the ball 3 disengages from the shaft 1 the sleeve 7 and engages the shank 9 with it.

The angle between forces 2 and PI fi (Fig. 5) will cause the ball to jam at

the upper position, at angle dc, the ball is jammed with a tapered disc 15. Therefore, when choosing the angles of the bevels and the disc cone, it is necessary to observe the ratios a - p, d fi, where r is the angle of deceleration. The force PA from the rib 5 acts on the ball at an angle of 0 (Fig. 6), and the force PS from the protrusion 11 acts at an angle. The addition of the vertical component forces P4 and PS creates a force Rwert, which exceeds the magnitude of Rhonus, which leads to continued movement of the ball down to the axis of the coupling until it stops at the bottom of the groove 10 (Fig. 8).

In this position the value is Rvert. is determined by the angle of the bevel 4 and the angle Ј and must exceed the cone (Fig. 9). Thus, the shaft 1 is engaged with the sun wheel 19 and the rotation is transmitted through the planetary mechanism to the shaft 18 with a decrease in the rotation frequency and an increase in the moment.

If the lowering of the ball 3 from the initial one (Fig. 4) to an intermediate position (Fig. 6) occurs at the moment when the protrusion 11 is under it, then the last, thanks to the chamfer 12, will shift, compressing the spring 16 along slots 2 and 8 and thus bypass the protrusion 11. When reducing the resistance moment on the shaft 18, the reverse is reduced. and

The ball 3 is pushed by the force P of the disk cone 15 to its initial position.

Claims (1)

Thus, the proposed clutch allows the rotational speed to be automatically changed depending on the moment of resistance on the driven shaft. The clutch can be used in conjunction with a planetary or other gearbox. The use of a coupling in nutrunners will allow the nut to be made with a high rotational speed and tightening with a large moment, which will lead to an increase in labor productivity, a reduction in the size of the nutrunner and a decrease in energy consumption. Claims of the clutch, containing the drive and driven shafts, connected by means of a planetary mechanism, the carrier of which is connected to the driven shaft, an intermediate element mounted in a cavity made at the end of the drive shaft, and a sleeve springed relative to the bottom of the cavity, with grooves A-A Direction of rotation Fm.1 Schi covering the drive shaft and connect; with the carrier, the clutch elements in the form of balls, grooves are made on the drive shaft and the sun wheel, the balls are installed in the grooves of the drive shaft with the possibility of interaction with the grooves of the sun wheel and bushings and are in contact with an intermediate element, characterized in that, in order to expand the functional capabilities by providing rotation of the driven shaft at different speeds, the intermediate element is designed as a conical disk, the grooves in the driven shaft and carrier hub are made with oppositely directed bevels, while the angles of the cone of the disk and bevel are related by the relations / g and d / g, where I is the angle of self-braking: D is the angle between the tangent and the line, connecting edge of the groove of the drive shaft with the center of the ball. 0t / 9.3 iH  / 7. V / r FIG. 6 f 7 bonus S. 15 7