SU1647173A1 - Flexible expanding clutch - Google Patents

Description

one

(21) 4688461/27 (22) 05.05.89 (46) 07.05.91. Bul №17

(71) Vilnius Institute of Civil Engineering

(72) B.P. Spruogis, L.A. Zubavicius, V.L.Turla, A.Yu.Shatas, A.P.Shlap Lis, Yu.I. Yurevich, E.P. Yurkonis and A.R. Yakshtas (53) 621.825.7 (088.8)

(56) USSR Copyright Certificate g. 712560, cl. F 16 D 43/14, 1978.

(54) ELECTRON-CURRENT COUPLING

(57) The invention relates to mechanical engineering and instrument making, in particular to elastic-dynamic couplings, and can be used to connect shafts and transmit torque in machines and mechanisms of reversible drives, as well as with significant radial and angular displacements of the connected shafts. The purpose of the invention is to increase the carrying capacity, reliability and enhanced operational capabilities. The elastic spring ring 8 connecting the shafts of the drive and driven coupling half is made of a composite, consisting of a series of spring concentrically arranged rings with different thicknesses. In order to increase the damping properties, the elastic ring 8 can be made of alternating rings, one part of which is made of a metallic material, and the other part of a synthetic material. When transmitting torque under the influence of centrifugal forces, ring 8 tries to take the form of an ideal circle. In this case, the driving half coupling tends to occupy the initial position, i.e. load position. In the case of angular misalignments of the connected shafts, the ring 8 is rotated on the rollers 6 and 10 of the coupling halves having a curvilinear surface and relieves contact stresses. 5 hp f-ly, 9 ill.

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The invention relates to the field of engineering and instrument-making, in particular to elastic-dynamic couplings, and can be used to connect shafts and transmit torque in reversible drive machines, as well as with significant radial and angular shifts of connected shafts, mainly in drives of equipment operating under severe conditions (with pulsating loads, transients, with all types of misalignment of the connected shafts and in frequently reversible drives).

The purpose of the invention is to increase the carrying capacity, reliability and enhanced operational capabilities.

Figure 1 shows a centrifugal clutch, a general view; figure 2 is a section a - a in figure 1; Fig. 3 shows a connecting element consisting of a series of concentric spring rings of metal and, accordingly, alternating metallic and synthetic materials: in Fig. 5 and b, sections B - B in Fig. 3; 7 and 8 - supporting elements in the form of rollers under the convex and concave composite connecting elements; figure 9 - elastic coupling clutch, general view, option.

The centrifugal clutch consists of a lead 1 and a driven 2 half couplings. The hub 1 of the drive half coupling through shanks 3 and 4, using fingers 5 is connected to the support rollers 6. The hub of the driven coupling half 2 goes into the drum 7, covering the driving coupling half 1, and the freely installed elastic ring 8. The supporting elements of the driven coupling half are rollers 9 , hinged with fingers 10 in the end walls of the drum (figures 1 and 2).

The elastic spring ring 8 is made of a composite, consisting of a series of spring concentrically arranged rings, 1 closely fitting their surfaces to each other, the thicknesses of which increase from the center to the periphery according to the ratio R2 / h3 const, where R is the average diameter of the elastic ring; h is the thickness of the ring (fig.Z). The damping properties are enhanced when the elastic ring 8 is made of a composite of alternating rings, one part of which is made of a metallic material, and the other part of the spring rings is made of a synthetic material (for example, a composite material, etc.).

A spring-loaded elastic ring B, the average diameter of which is equal to the diameter of the centers of the axes of the support rollers 6 of the driving and 10 driven half couplings, is slightly stretched by the supporting elements 6 of the driving half coupling and is covered by the supporting elements 10 of the driven half coupling. After assembly in a static position, the elastic ring 8 covers the support rollers 6

the leading coupling half and is covered by the support rollers 10 of the driven coupling half (Fig. 1), the angle between the common axes of the rollers 6 and the rollers 10 is 90 °. Elastic ring 8 represents an ellipse shape. The rim 11 of the driven coupling half and the sides of the forks of shanks 3 and 4 of the driving coupling half protect the rim 11 from falling out.

The profile of the elastic ring 8 depends on the shape of the support rollers. With the aim of

5, the best compensation of all types of misalignment of the connected shafts is advisable to use concave rollers (Fig.7) or convex rollers (Fig.8). The concavity of the roller of radius RI (Fig.7) corresponds to the cross section of the composite

0 elastic ring 8, in which the radius of curvature of the outer and inner rings correspond to the radius of the bulge Rt (figure 5). The convexities of the roller with radius Ra (Fig. 8) respectively correspond to the radius of the concave 5 of the elastic ring 8 R2 (Fig. B).

The compensating capacity of the coupling is increased by making the surface of the holes in the rollers under the fingers 5 barrel-shaped, if the fingers 5 are made

0 cylindrical, or in reverse order. The rim 11 in the driven half coupling can be made resilient to prevent breakage during overloads.

Elastic centrifugal coupling works

5 as follows.

Under the influence of torque, the driving half-coupling rotates relative to the driven in the direction of rotation, and the nature of the initial deformation of the coupling element 8 changes. In the case of a limiting Deformation, the rollers 6 of the drive shaft and the rollers 10 of the driven half coupling approach each other by contacting through the elastic ring 8.

As the revolutions increase under the influence of centrifugal forces, ring 8 tries to take the form of an ideal circle (as well as under the influence of restoring potential forces). The leading coupling half 1 in this case tends to assume the position it had in the absence of a load.

At certain loads and the magnitude of the angular frequency of rotation, the corresponding dynamic equilibrium of the clutch is defined, characterized by the angle between the axes of the drive rollers 6 and the rollers 10 of the driven coupling half.

In the case of angular misalignments of the connected shafts, the ring 8 rotates on rollers with a curved surface on

a certain angle, thereby removing the contact voltage.

For small and medium torques, with high requirements for compensation of misalignments of the connected shafts, ring 8 in the static state can be extended so that the large axis of the ellipse n (Fig.9) is so much larger than the small axis of the ellipse t, that The deformations of the coupling covered by the ring 8 and the supporting rollers covering the ring 8 do not come together and are in the spring-loaded state.

In the case of small torsional vibrations of the driving or driven half coupling at the points of contact of the connecting elastic element with the bearing surfaces, slip does not occur, and only small bending vibrations are observed.

Claims (6)

1. An elasto-centrifugal coupling containing a leading coupling half and a driven bowl half-coupling leading, supporting elements mounted on the coupling half and in contact with the latter a multi-layered elastic spring ring with tightly adjacent to each other layers, so that capacity, reliability and expansion of operational capabilities, the elastic spring ring is made composite in the form of concentrically arranged rings with different thickness, placed with an increase in their thickness lenii from the center to the periphery facing the ring Aa The surfaces of the supporting elements of both coupling halves and adjacent surfaces of the outer and inner rings of the composite elastic ring are curved in axial section with the same radius of curvature, while the ratio of the radius of each ring in the second degree to its thickness in the third degree is constant. 2. The coupling according to claim 1, characterized in that, in order to increase the damping properties of the coupling, one part of the spring concentric rings is made of metal, the other part is made of synthetic material and the rings are arranged in alternate order. 3. Coupling according to claims 1 and 2, characterized in that, in order to increase the compensating abilities, the bearing support elements are made in the form of fingers fixed on the coupling half with rollers mounted on them with a barrel-shaped outer surface. 4. Coupling according to claims 1 - 3, characterized in that the surfaces of the holes in the rollers for the fingers are barrel-shaped and the surfaces of the fingers are cylindrical. 5. The coupling according to claims 1 - 3, which is different in that the surfaces of the fingers are barrel-shaped and the surfaces of the holes in the rollers for the fingers are cylindrical. 6. Coupling pop. 1-5, characterized in that the rim of the driven coupling half is made elastic. ten 2 about I N Qo SP  SP ABOUT hpi Fig 9