RU2057261C1 - Compensation clutch - Google Patents

Abstract

FIELD: mechanical engineering. SUBSTANCE: clutch has two clutch parts made up as concentrically arranged sleeves. The sleeves are provided with openings which are uniformly arranged and coincident with ports 3 and 8 in side surfaces over periphery. Each port 8 of the outer clutch are provided with two fixed axles 9 shifted in the periphery direction. The axles have one guide rollers. The distance between the axles is greater than the diameter of the roller. Port 3 of the inner clutch part is provided with fixed axles 4 having two guide rollers 5. The rollers of the clutch parts are interconnected through flexible link 11 of closed loop. The rollers of each port of the outer clutch part are enclosed by the flexible link to define a loop. The loop is then goes into the figure eight and lies on the rollers of the inner clutch part and further rounds the adjacent rollers of the inner clutch part from the side of the clutch center. EFFECT: enhanced reliability. 2 cl, 3 dwg

Description

 The invention relates to mechanical engineering and can be used to connect the shafts of machines and mechanisms that transmit torque under conditions of distortions and displacements of the axes of the connected shafts.

Known elastic coupling containing two flange coupling halves with cantilevered fingers located at their ends, which sequentially bend around a tape endless flexible link [1]
The disadvantage of this coupling is its limited service life due to the destruction of the flexible link in places of friction against the fingers and significant overloads arising in the flexible link during the transmission of circumferential forces.

A compensation coupling is also known, comprising two coupling halves connected by means of a flexible link, the middle part of which is located in the holes made on one of the coupling halves, and the ends are fixed on the other coupling half, as well as a means of tensioning the flexible link, made in the form of a compression spring, the flexible link being made in the form of separate segments, the ends of which are fixed on splined bushings located on a splined shaft belonging to one of the coupling halves [2]
The disadvantage of this coupling is its limited working life due to the uneven distribution of the load between the individual segments of the flexible link, caused by the impossibility of obtaining the same lengths and the difficulty of terminating the ends, as well as significant vibrations caused by the imbalance of the coupling due to the presence of movable mates between the splined shaft and flange bushings.

Closest to the proposed one is an elastic expansion coupling, containing the driving and driven coupling halves with end protrusions arranged uniformly around the circumference, interconnected by means of elastic rings enveloping the protrusions from mutually opposite sides, the protrusions of the coupling halves being placed at the same distance from the coupling axis, the number of protrusions per each coupling half is at least three, each protrusion is in contact with all rings, the number of rings is even, and rollers are mounted on each protrusion with the possibility of rotation on mortars in their points of contact with rings [3]
The disadvantage of this clutch is the limited compensating ability for misalignment and misalignment of the axes of the connected shafts under conditions of contacting the protrusions of the coupling halves caused by significant torque, which leads to an increase in the load on the bearing assemblies of the connected machines and mechanisms and, as a consequence, to their premature failures.

 The objective of the invention is the increase in the compensating ability of the coupling when transmitting significant torques.

 To solve this problem, in a compensation coupling containing two half-couplings with protrusions evenly spaced on a circle at mutually facing ends in the form of axes with guide rollers interconnected by a flexible closed loop link, the half-couplings are made in the form of cups concentrically placed in one another with evenly spaced circles and circumferentially aligned windows on the lateral surfaces, axes are fixed in the half-coupling windows, and in each window of the outer half-coupling with offset in the circumferential direction two axes are fixed with one guide roller on each of them with a distance between the axles greater than the diameter of the roller, and in the windows of the inner half coupling, one axis is fixed with two guide rollers, the guide rollers of each window of the outer half coupling are covered by a flexible loop-like link with a transition in the form of a figure eight onto the roller of the inner coupling half and with further bending of adjacent rollers of the inner coupling half from the center of the coupling.

 In FIG. 1 shows a compensation sleeve, section; in FIG. 2, section AA in FIG. 1; in FIG. 3 diagram explaining the operation of the coupling.

 The expansion coupling consists of two coupling halves: the drive includes a hub 1, to which a shell 2 is attached, forming an inner cup with it, on its side surfaces there are through windows 3 in which axles 4 are fixed with two guide rollers 5 each.

 The driven half-coupling also consists of a hub 6 and a shell 7, forming a larger diameter cup concentrically covering the driving coupling. On the side surface of the glass of the driven coupling half, opposite the windows of the driving coupling half, there are through windows 8 in which in the circumferential direction at a distance greater than the diameter of the guide roller, there are two axles 9 having one guide roller 10.

 The coupling halves are interconnected by a flexible link 11 of the closed loop, which sequentially loops around the rollers 10 with the transition in the form of an "eight" on the roller 5 of the drive coupling half, with further bending of adjacent rollers of the drive coupling half from the center of the coupling.

 The coupling operates as follows (Fig. 3).

создает силу натяжения

в гибком звене 11, которое вследствие упругой деформации позволяет повернуться ведущей полумуфте относительно ведомой вокруг продольной оси на угол γ При этом нарушается равенство углов α₁ и α₂ образованных ветвями гибкого звена и касательными окружностями ведомой полумуфты, проведенными к точкам осей с направляющими роликами. Причем угол α₁ имеет тенденцию к уменьшению, а угол α₂ к увеличению, принимая значение α $\genfrac{}{}{0ex}{}{\text{I}}{\text{1}}$ и α $\genfrac{}{}{0ex}{}{\text{I}}{\text{2}}$ Поэтому проекция силы

силы натяжения гибкого звена

на касательную со стороны угла возрастает, а подобная проекция

силы натяжения гибкого звена

со стороны угла α₂ уменьшается. Поэтому крутящий момент со стороны окружной силы

больше, чем со стороны силы

. Разность этих крутящих моментов, умножаемая на число таких звеньев, и составит величину крутящего момента на ведомой полумуфте, которая определяется моментом сопротивления со стороны ведомой полумуфты. При увеличении передаваемого крутящего момента возрастает значение угла α₂ уменьшая проекцию

силы натяжения

, увеличивая общий крутящий момент.When torque M _cr is applied in the leading coupling half, the circumferential force arising from this

creates tension

in the flexible link 11, which, due to elastic deformation, allows the leading coupling half to rotate relative to the driven around the longitudinal axis by an angle γ. This violates the equality of the angles α ₁ and α ₂ formed by the branches of the flexible link and the tangent circles of the driven coupling half drawn to the points of the axes with guide rollers. Moreover, the angle α ₁ tends to decrease, and the angle α ₂ to increase, taking the value α $\genfrac{}{}{0ex}{}{\text{I}}{}$$\genfrac{}{}{0ex}{}{}{\text{1}}$ and α $\genfrac{}{}{0ex}{}{\text{I}}{}$$\genfrac{}{}{0ex}{}{}{\text{2}}$ Therefore the projection of force

flexible link tension

on the tangent from the angle increases, and a similar projection

flexible link tension

from the angle α ₂ decreases. Therefore, the torque from the side of the circumferential force

more than from the side of power

. The difference of these torques, multiplied by the number of such links, will be the amount of torque on the driven coupling half, which is determined by the moment of resistance from the driven coupling half. When the transmitted torque increases, the value of the angle α ₂ decreases, reducing the projection

tension forces

increasing total torque.

 The proposed coupling has a high compensating ability at all stages of operation due to the elastic deformation of the flexible link and due to the possibility of its partial movement along the guide rollers. The maximum transmitted torque depends on the strength of the flexible link and the number of half-coupling windows, which determines the number of working links, which should be at least two. The coupling allows you to transmit torque in both directions of rotation, regardless of which half coupling will be the leading one.

Claims (2)

 1. COMPENSATION COUPLING, containing the leading and driven half-couplings with protrusions evenly spaced on a circle at the mutually facing ends in the form of axes with guide rollers interconnected by a flexible closed-loop link, characterized in that the half-couplings are made in the form of cups concentrically placed in one another evenly spaced around the circumference and circumferentially aligned windows on the lateral surfaces, the axes are fixed in the windows of the coupling halves, with each window of the outer coupling half with displacement in the circumference In this direction, two axes are fixed with one guide roller on each of them with a distance between the axles greater than the diameter of the roller, and in the windows of the inner coupling half, one axis is fixed with two guide rollers.  2. The clutch according to claim 1, characterized in that the guide rollers of each window of the outer half coupling are looped with a flexible link with a transition in the form of a figure eight on the roller of the inner half coupling and with further bending of adjacent rollers of the inner half coupling from the center of the coupling.

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