RU1813941C - Cam clutch - Google Patents

Abstract

Usage: in the drives of technological machines, in particular forage harvesters for forced shutdown and shutdown of the working bodies. SUMMARY OF THE INVENTION: The drive 2 and driven 4 half-couplings are interconnected by end cams 5 and 6 with one-sided bevels. The coupling half 4 is spring-loaded relative to the cage 3 and is connected to its cams 8 by means of cams 7. The cams 7 and 8 are made with two-sided bevels. When transmitting torque to the clip 3, an axial force acts, perceived by the springs 16. The fixing means of the clip 3 in the circumferential direction is made in the form of a ratchet stopper. When the ratchet stop is engaged, the driven coupling 4 moves along the shaft 1, compressing the spring 13, and rotates until the cams 5 and 6 come out of engagement. There is a power circuit of the shaft 1 through the cams 7 and 8 with a clip 3 and its locking. 8 ill. R 8 J U / / .a 27 W C

Description

The invention relates to mechanical engineering and can be used in the drives of technological machines, in particular forage harvesters, for forced shutdown and shutdown of working bodies.

The purpose of the invention is to increase reliability and durability by reducing the level of dynamic loaded ™ coupling and working machine during shutdown.

In FIG. 1 shows a cam coupling, general view combined with a cut along the axis; figure 2 - section aa in fig. 1 (along the support ring); in Fig.Z - section BB in Fig.2 (diagram of functionally significant axial dimensions of the structural elements of the coupling); Fig. 4 shows the position of the parts in section B-B during transmission of the torque by the coupling in the direction of the working movement; in Fig. 5 - the position of the parts in the section BB at the initial instant of action of the brake pulse; in Fig. b - the position of the parts in the section BB at the time of the maximum value of the brake pulse; 7 is a graph of the power characteristics of the damping spring; on figs - section bb in fig. 1 (by stopping device after braking of the drive mechanism).

The cam coupling (Fig. 1) contains a driven shaft 1, a driven coupling half 2 mounted on it coaxially rotatably, a driven coupling half 4 located between them axially movable, spring-loaded to the driving coupling half 2 and provided with end cams 5 on both sides for interacting with similar mating cams b of the driving coupling half and additional cams 7 for interacting with the cams 8 of the cage, a cyclic locking device in the form of a support ring 9 located in the bore the leading coupling half 2 rotatably so that the ends of its protrusions 10 are in the same plane as the ends of the cams 6 of the driving coupling half. The support ring 9 interacts with its outer surface with the surface of the bore by friction forces. To interact with the end protrusions 10, a stop 11 is made on one of the cams 5 of the driven half coupling 11. The cams 5 and 6 are made with one-sided bevels, i.e. one side of the cam has an angle of elevation of the profile greater than the angle of friction, and the other side is less than the angle of friction. Cams 7 and 8 have two-sided bevels, i.e. both angles of raising the profile are greater than the angle of friction. On the cams 8, clips for interacting with the ends of the cams 7 are made

there are bearing pads 12, the distance his (Fig. H) from which to the hollows of the cams 8 of the cage, as well as the height he of the cam b of the driving coupling half, is not less than the difference in the axial dimension um of the driven coupling half 4 and the distance h d from the end face of the cams of the driving coupling halves 2 to thrust pads 12, wherein the height he cam 8 of the cage is not greater than the height h of the cams 7 of the driven coupling half and more than the height he cams 6 of the leading coupling half,

The cam coupling is provided with an adjustable return coil spring 13 of combined loading, secured by a hook 14 in the driven coupling half, and

a hook 15 in the cage, and additionally a package of Belleville springs 16, mounted on a movable 17 and a fixed 18 bushings,

# cages placed on the side of the outer end 19 between the stop 20 of the shaft 1 and the spring tension adjustment means, respectively. In this case, between the bushings 17 and 18 there is a gap greater than hs, but less than the smaller cam height hs or h.

The tension adjusting tool is advantageously made in the form of a nut 21 on the shaft with a lock washer 22, to prevent the cutting of the mustache of which a key 23 is installed between the shaft 1 and the fixed sleeve 18. The axial size of the set of half couplings 2, 4 and cage 3

® is limited by the stop of the sleeve 3 by the end 19 and into the end of the movable sleeve 17 and by the stop of the driving coupling half 2 with its outer end against the shoulder of the shaft 24 ..

A ratchet rim 25, which is an element of the stopping device, is filled on the outer surface of the yoke 5 yoke. The latter includes (FIG. 3) a housing 26 in which a drive through

pusher 28 electromagnet 29 dog

30, is pressed to the housing in the absence of a pull on the electromagnet with a return spring 31.

Drive of working machines and mechanisms

can be carried out not only from the shaft 1, 5, but also directly from the driven half-coupling 4, on the outer surface of which in this case there is an element for transmitting torque, for example

ring gear 32 (Fig. 1).

0 The coupling operates as follows.

When the working bodies rotate in the forward (working) direction, the torque of the leading coupling half 2 is transmitted to the driven coupling half 4 by the cam rows 5 and 6, the interacting sides with a lifting angle greater than the friction angle, as a result of which the torque effect causes axial in the cam gear. force acting on driven coupling half

4 and tending to move the latter along the shaft together with the cage, since the ends of the additional cams 7 of the coupling half 4 are supported on the supporting platforms 12 of the cage 3, as shown in Fig. 1 and Fig. 4. However, if the magnitude of the axial force applied to the cage and, consequently, the corresponding transmitted torque does not exceed the force of the disc spring package 16, the joint movement of the coupling half 4 and the cage is not possible.

When transmitting torque through the coupling, the protrusions 10 of the support ring 9 are within the volume that would be occupied by the parts of the cams 6 removed by the bore

: leading coupling half 2, and thus; : ye: interact with the cams 5 of the coupling half A. . ..,. / -. v..O .; :. :. ;; -: S-; .v When a signal is applied to the electromagnet 29, the latter moves the dog 30 through the pusher 28 until it contacts the teeth of the ratchet ring 25. The clip closes the housing 26. The additional cams 7 continue to rotate the driven coupling half 4 to come off reference areas 12 of the clip 3; the driven half-coupling under the action of axial force (torque) moves along the shaft 1, compressing and twisting (untwisting) the return spring 13, and at the same time

. rotates relative to the cams 6 of the driving coupling half 2 until the cams 5 and. 6 will not disengage, and the cams 7 extending into the hollows of the cams 8 will not begin to interact with the latter lateral sides, with an angle профил profile, as shown in FIG. When this occurs, the power circuit of the shaft 1 through the cams 7 and 8 and the stop device 25 with the housing

26. G -. -. :;,::, ::; - S:;, ::; -V., ...-: After the cams 5 and 6 disengage (in the initial period of relative rotation of the coupling halves 2 and 4 before the cams 7 and 8 come into contact with the sides), the stop 11 is engaged one of the protrusions 10, ogra. the movement of the support ring 9 is non-negligible. In this case, the ends of the protrusions 10 are mounted opposite the parts of the end surfaces of the cams 5 (at the same time), which geometrically impede the movement (inclusion) of the driven coupling half 4 under the action of the springs 16 or 13, as shown in Fig. 5.

In the case when, when braking the inertial masses of the working machine, the cams 7 of the driven coupling half and the cams 8 of the cage mesh, circumferential forces P exceeding the value determined by the relation:

P Pnp (h0) / tg (a-p). (1)

where Pnp (ho) is the force of the Belleville springs 16 previously deformed by the value h0, H;

a - the angle of the cams 7 and 8 (Fig.Z and 5) ;.

/ 3 - friction angle in cam engagement

7 and 8,. -,:, -,. . -. .-.-. .-: the clip begins to move along the shaft 1.

In this case, part of the kinetic energy of the rotating masses is transferred to the potential energy of the deforming packet of Belleville springs 16.; ; The maximum value of the absorbed energy of the maximal energy Pmax:

- yes:.,: l v ...,: /,:.; ::.;: -.:- .:;

,:,,:; y,;,;.; v: -, -. ;; .-... - -.,;..;:.... ,.; .., ,, ... . -. :.

JvnM "c /pnp(h)dh, J ,( Fig.7),(2)

, .-.; -, -; - ... . .

where the maximal deformation hi is determined by the amount of movement S ht-ho of the cage, up to the choice of the gap between the movable Γ It and the fixed 18 bushings, which should be less than the height of the cams 7 and 8, to avoid the latter coming out of engagement.

A selection of the above defined parameters Pnp (h), ho. hi, and in stand-by devices of shock type (for example,

ratchet) the value of the maximum braking force can be reduced to the calculated value of P, determined by the ratio

.o) - -.-.-.....: - /; -: - :, G: -:; ::: - ..; .- The nature of the dissipation of the energy potential of the PMAC springs will be determined the parameters of the stopping device, the drive system and the working machine. At the end of this process, the working machine stops completely, and the clutch occupies a stable position similar to that shown in Fig. 4. Further, after the clutch has been actuated, the rotation of the leading coupling half in the previous direction of the working movement until the drive is switched off relative to the support ring 9, which is blocked relative to the shaft 1 through the driven coupling half 4, accompanies the friction forces in the pair of the coupling coupling bore - the outer surface of the support ring. moment. friction forces on the support ring are balanced by the reaction force, which additionally presses the side surface of the protrusion 10 against the abutment 11, which increases the reliability of fixing the coupling halves in the off position.

The return of the coupling to its initial position should end with the fact that the ends of the cams 7 of the driven coupling half are mounted on the ends of the protrusions 12 of the cams

8 cages 3. For this coupling half 4, under the action of a untwisting (tightening) return spring, it must rotate relative to the casing 3 and move axially until the cams 5 are locked with the cams 6 of the driving coupling half 2,

However, in the case when after braking the working machine or mechanism from the side of the latter, the residual moment of the Bridge acts on the shaft 1, creating, due to the friction forces in contact of the tongue of the dog 30 with the ratchet tooth 25, the force Ftp, as shown in FIG. 8, the magnitude of which is substantially greater than the force of the dog return spring 31. Therefore, the known ratchet mechanism is jammed.

The cam clutch is returned to its original position by reversing the drive coupling half 2.

When the direction of rotation of the driving coupling half 2 changes, the friction force in the ring-bore pair changes direction, the stop 11 ceases to interact with the protrusions 10, the support ring 9 is carried away by the coupling half 2 in rotation relative to the driven coupling half 4 and comes off the ends of the cams 5, creating the possibility of axial movement of the latter under the action of the return spring 13 until the cams 5 and 6 interact with the non-slanted sides with an angle of elevation less than the friction angle. clutch 4 and associated working bodies. The coupling half 4 and the shaft 1 rotate relatively closed to the housing through a ratchet ring 25 of the cage 3 within the sector until the cams 7 and 8 interact

lateral sides with an angle / profile greater than the friction angle, since the additional cams 7 and cams 8 have a guaranteed overlap due to the choice of functionally significant geometric dimensions of the structural elements illustrated in FIG. Additional cams 7 are mounted on bearing pads 12; under the action of the circumferential force in the cam engagement, the cage 3 is reversed and the stopping device 25 is unlocked.

The clutch is returned to its initial state, as shown in Figs. 1 and 4, and can be turned on in the forward direction of rotation of the working bodies.

The operation of the device is similar in the case when the supporting pads 12 are made on the cams 7 of the driven coupling half.

Claims (1)

The claims A cam clutch containing coaxially mounted leading and driven half-couplings interacting via end cams with one-side bevels, a support ring placed in one of the half couplings with protrusions in contact with a stop fixed in the other half-clutch, a yoke, an unregulated spring installed between the yoke and driven half-coupling, adjustable spring pressing the clip to the driven half-coupling, stopping device placed with the possibility of interaction with the clip, while facing each other the ends of the cage and the driven coupling part formed with bevels additional cams, characterized in that, in order to reduce dynamic loads on other cams bevels formed bilateral. L Fig. I Ifr66l8l W: A FIG. 6 Fig.7 FIG. 8