SU579045A1 - Roll support assembly - Google Patents

Description

The invention relates to rolling piercing and relates to stand structures in which liquid-tray bearings are used. Known support unit proke roll, containing a pillow, mounted therein liquid friction bearing, sleeve insert in the inner bore of the pillow, composite, sleeve-pin in the form of a housing mounted on the conical surface of the neck of the roll, and split shank under radial-thrust bearing rolling (I. When such a support unit is in operation, the inner ring of the radially resistant bearing is rotated relative to the nut, which causes intense wear of the rubbing surfaces and leads to a gap in the cone This gap reduces the accuracy of rolling due to radial beats of the rolls and additional axial displacements of the roll that distort the shape of the gauge. In addition, the disappearance of the friction forces on the conical seat of the sleeve-axle causes that the periodically arising jamming moment in the radio-contact-thrust bearing is completely transmitted to the key connection of the bushing pin with the roller, causing contact of the bushing-bearing pin at the contact point . Such contact leads either to the rejection of the journal sleeve, or, if used further, to distortions on the roll, which cause deterioration of the working conditions of the bearing and the appearance of additional radial runout of the roll. To eliminate these drawbacks and increase the accuracy of the rolled profile by reducing the radial beats and reducing the axial shifts of the rolls associated with the conditions of the axle bushing, in the supposed support assembly the detachable shank is mounted on the conical surface of the neck of the roll and is equipped with an elastic element interacting with the end surface housing. The drawing shows the proposed reference node. The rolling mill support assembly contains a pillow 1 in which a liquid friction bearing is mounted, consisting of a support bush sleeve 2 assembly placed in the inner bore of the first pillow I, inside of which a trunnion sleeve is installed with a radial clearance and consisting of an interface with a conical surface neck roll body 3 and split shank 4. Detachable shank 4 is planted on the conical surface of the neck

roll and interacts with the housing 3 of the bushings and the sleeves through an elastic element 5 placed in an axial gap between their ends and compressed. At the same time, the ratio of the axial clearance between the ends of the casing 3 of the bush-axle of the agr-detachable shank 4 to the initial height yiT5 of the 5Toro element ranges from 0.6 to 0.85 and can be determined by the following relationship:

-{-WITH,

H

Where. S is the magnitude of the axial clearance between the ends of the sleeve sleeve case and the split shank;

Nd is the initial height of the elastic element; C is the relative deformation of the elastic element required to create the necessary force to press the body of the liner sleeve onto the tapered surface of the roll neck.

Placing in the axial gap between the ends of the body of the sleeve-axle and detachable shank of the elastic element maintains a constant force of pressing the body of the sleeve-axle onto the tapered surface of the roll shaft, the suit between the radial gaps causing the radial beats of the rolls.

The range of the S / H ratio is selected because of the occurrence of minimal residual deformations of the elastic element. The lower limit of the ratio can be adopted in the manufacture of the elastic element in the form of cup springs, and the upper - when using an elastomeric material. The necessary force of press-fit of the sleeve sleeve to the tapered surface of the roll neck is due to the provision of reliable connection of their surfaces and for wire and small-section mills can be taken as 3-5 tons.

The body 3 and the split shank 4 are fixed by rotation of the rotation shaft relative to the roll neck 6. The angular contact bearing 7 is mounted on the detachable shank 4 with tension and (ixirvan nut 8. When the angular contact bearing 7 fails, the split shank is assembled radially -persistent

bearing.

When the proposed reference node

the case 3 of the axle bushings perceives only n, 1 load due to the fact that it is .app (soian on the conical surface of the roll neck with a constant force. Since the split shank 4 of the axle bushings is conjugate to the tapered surface of the roll neck and fixed to it by a nut 8, the axial forces are perceived and transmitted to the angular contact bearing 7. The placement of the angular contact bearing 7 on a detachable shank for a tight fit prevents rotation of the inner ring of the angular contact bearing 7 relative to the secret 8, since The outer ring of the bearing is housed in a housing with a radial clearance.

The separation of the sleeve-pin on the body and the split shank, which are in contact with the tapered portion of the roll neck and separated by an axial gap, in which the elastic element is placed, provides:

.- the ability to continuously maintain the necessary force of pressing the sleeve sleeve body onto the conical surface of the shake roll;

- the perception of axial loads and periodically occurring jamming moment in the angular contact bearing with a detachable shank;

-the possibility of placing on the fit with the tension of a angular contact bearing on a detachable shank without dismantling an outdated angular contact bearing.

All this reduces the axial shifts of the rolls and reduces the thickness variation of the finished profile.

Claims (1)

1. Toder I. A. and others. Hydrodynamic support rolls. M., “Mechanical Engineering, 1968, €. 137-140. 8 7