SU1251986A1 - Working stand for rolling sectional shape - Google Patents

Description

to rolling 1m stanl for

) pf reiin; It is about 11 pp. (.) I1H1, that is, to the npoKaiKM of small-sized pinstripe and rod.

The purpose of the invention is to reduce the cage haberite and its metal intensity.

FIG. 1 ripej CTanjiOHa cage, cross section; in fig. 2 shows section A-A in FIG. 1 (in the pitch of the thinner rolls in Fig. 3 - section B-B in Fig. 1 (in the area of distribution rings).

The cage consists of lead 1 and one 2 nd wheel), rolls, hydraulic cylinders 3 with plungers, roll bars 4 and 5, distribution rings 6 and 7, bearings 8, housing 9. Gear rolls 1 and 2 are P gear between by myself. The driven gear roller 2 has a cantilever neck, and the driving gear roller 1 has a cantilever neck and a shank connected through a reducer and a coupling with an electric motor, a reducer (mu () and engine not shown). Guy; 1 cylinders 3 are located along the radii of the cantilever necks of the gear rolls 1 and 2 from the non-driven side of the stand. The hydraulic cylinders 3 are connected to the surfaces of the drive side actuator side drive gears 1 and 2 channels, the outlets of the KoTop iix are also arranged radially. Rollers 4 and 5 are rolled out in the form of meals, loosely mounted; en P) 1x on the gears of the rolls I and 2) of the drive side of the stand. On cantilever gear necks, H) 1X rolls 1 and 2, on the drive side of the stand, distribution rings, 6 and 7, are provided with grooves located along the circumference ia of their inner surface, one of which (1 porn) is connected to iacocoM, and the other (drain ) with a drain line. Distribute rings 6 and 7 Connection 1Ы with electric motor, for example, through the clutch and worm gears (electric motors, clutch and worm gears are not shown).

Prokatnye 4 and 5 are combined with hydraulic cylinders 3 in such a way that the planes in which hydraulic cylinders 3 are located coincide with the longitudinal symmetry planes of 4 and 5. Distribution rings 6 and 7 of the diameter 1s on the necks of gear wadcs 1 and 2 are thus that the distribution grooves of the X rings are aligned with the output of Canada.

To work works in the following way.

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Lead mecTeiie ying va.chock 1 when rotating from the engine. Drift 1 is the tail 1 roll 2 driven; 1 roll with roll 1 in a rotation in the opposite direction. Distribution 6 and 7, whose position is fixed {relative to the frame of the child by the screw mechanisms, remain stationary. Hydraulic cylinders 3, connected kana; ai with head 1 grooves distribution; and the codecs 6 and 7, are under pressure, and the pressure in the hydraulic cylinders 3 connected to the drain grooves is zero. During the rotation of the gear wheel, as a result of its rotation from the distribution ring, the first (against the direction of rotation of the gear wheel) of the hydraulic cylinders connected to the pressure groove is connected to the drain groove and at the same time the first of the hydraulic cylinders connected to the drain groove is connected with pressure channel. After rotation of the gear wheel to the position, equal to the angular pitch of the hydraulic cylinders 3, the process of switching the hydraulic cylinders is repeated. As a result, in the process of rotation of the gear insert, the resultant of the cactus developed by its hydraulic cylinders retains approximately the same direction. At the same time, it is located in the plane of the axes of the hydraulic cylinders and, in its middle position, is directed from the middle of the projection onto this plane of the drain groove of the distribution ring, sitting on the gear roll, to the middle of the projection of its pressure groove. The resultant force developed by the hydraulic cylinders 3 presses the rolls 4 and 5 of their inner surfaces against the necks of the gears of the rolls, displacing the axes of the rolls relative to the axes of the gears X in the direction of action of the resultant. Since the direction of the resultant forces developed by the hydraulic head gears of the gear head during its rotation remains approximately constant, the axis of the rolling head also maintains an approximately constant position in space. Under the action of frictional forces at the points of contact of the mill rolls and the necks of the gear rolls, the mill rolls are rotated in the same directions in which their gear shafts rotate.

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ki Thus, during the rotation of the gear rolls 1 and 2, the rolls 4 and 5 perform rotational movements of the opposing gears, and their axes maintain a approximately constant position in space. The rotation of the distribution ring with the help of an electric motor through a worm gear changes the average position of the resultant forces developed by the hydraulic cylinders of the gear wheel carrying the ring and the middle position of the axis of the mill roll sitting on this gear roll. As a result, the gap between the rolls changes.

The rolling process is carried out by rolling the workpiece between the rotating rolls A and 5. The installation of the necessary roll up before the rolling and its change in the rolling process are carried out by turning the distribution rings 6 and 7. During the rolling process, under the action of the rolling force, the axes of the rolling rolls which they occupy in the absence of metal between the rollers, and there is some increase in the (free) gap between the rollers set before rolling.

The displacement of the axis of the mill roll relative to the axis of the gear roll under the action of the resultant forces developed by the hydraulic cylinders of the brush roll is equal to the difference between the internal diameter of the roll roll and the outer diameter of the roll roll bearing neck.

The maximum possible change in the roll solution when turning both distributive rings is 2e. Such a change can be achieved if the sum of the outer diameter of the mill roll and the value 2e does not exceed the distance between the axes of the gear rolls. If this condition is not fulfilled, then the maximum possible change in roll solution is less than 2e.

To ensure that the roll solution required for adjusting the dimensions of the profile of the rolled strip and compensating for wear and regrinding rolls, the inside diameter of the mill roll should exceed the outer diameter of the cantilever neck of the gear roll carrying the mill roll, to half

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5th jc

Q 25

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it is the change in roll solution, and the sum of the outer diameter of the mill roll and the maximum required change in roll solution should be no more than the distance between the axes of the gear rolls.

In the course of the rotation of the rolls, the resultant forces developed by the cylindrical cylinders of the gear roll deviate from their average position by an angle, ve. Whose first term lies

g

within 1-, where o (, is the angular step

arrangement of hydraulic cylinders.

In this case, the displacement of the axis of the rolling mill from its middle position (the beating of the roll axis) lies within, and the change in the solution of the rolls caused by the beating of their axes lies within.

So that the change in the roll solution due to the beating of their axes does not exceed the specified allowable value + t, the angular spacing of the hydraulic cylinders oi should not exceed the value of / e. In other words, the number of hydraulic cylinders on one gear wheel should not be less than 2 / Ge / b. By increasing the smoothness of rotation of the rolls by increasing the number of hydraulic cylinders, the latter should be placed on the gear roll in two or more rows.

The displacement of the rolls' axes under the action of rolling force relative to the positions they occupy in the absence of metal between the rollers depends on the magnitudes of the resultant forces developed by the hydraulic cylinders and on the magnitude of the rolling force, increasing with increasing rolling force and decreasing with increasing forces developed by hydraulic cylinders.

The magnitude of the forces developed by the hydraulic cylinders under pressure, nL,; is taken in such a way that the displacement of the rolls' axes under the action of the rolling force does not exceed the permissible value.

The design of the cage provides its setting for rolling and the implementation of the process of rolling varietal profiles with the required accuracy.

By eliminating a double-sided ring gear that requires cutting internal teeth with a small pitch circle diameter and a large tooth length, the design of the proposed stand is simplified.

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From the pump

L. A

5.5

Fig.Z

Claims (1)

CART FOR ROLLING VARIETY PROFILES, comprising a bed, gear rolls with 'cantilever neck and rolling rolls in the form of rims mounted on cantilever neck of gear rolls from the non-drive side of the stand, characterized in that, in order to reduce the dimensions of the cage and its metal consumption, gear neck the rolls under the rims are equipped with radially located hydraulic cylinders, the rods of which abut against the working rolls installed with the clearance of the rim, and the opposite necks of the gear rolls are equipped with rotation of the distribution rings with two grooves located around the circumference on their inner surface, one of which is connected to the pump and the other to the drain line, while channels are connected in the body of the gear rolls connecting the hydraulic cylinders with the distribution ring grooves, and the rings are installed with the possibility of fixing relative to the bed.