SU1412823A1 - Actuator for transferring movable mass of tube cold rolling mill - Google Patents

Description

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The invention relates to pipe rolling equipment and can be used, in particular, in designing new and modernizing existing cold rolling mills.

The purpose of the invention is to increase the efficiency of balancing the moment from the inertia forces of the moving masses and decreasing the ratio of the halogen barriers.

FIG. 1 shows the kinematic diagram of the device; in fig. 2 - view A to FIG. one; in fig. 3 is a view B in FIG. one; in fig. 4 — graphs of the dynamic moment before and after M equilibration; in fig. 5 - graphs of the dynamic moment after equilibration of M and the moment of rolling Mir for mills with a stationary stand; in fig. 6 shows plots of the dynamic moment after equilibration of M and the rolling moment for mills with a moving stand; in fig. 7 is a kinematic diagram of a balancing device in the form of a double universal spindle; in fig. 8 is a view of B in FIG. 7; in fig. 9 is a view of FIG. 7

FIG. 2, 3, 8 and 9 are represented by dual devices in relation to mills with a moving stand. For mills with a stationary stand, single devices can be used, which are located in one direction from the rolling axis.

The drive includes connecting rods 1 mounted on the fingers of crank wheels 2 sitting on shafts 3 (Vedupkhi shaft), a fork 4 of a universal spindle connected to each shaft, its cross 5, a fork 6 rigidly connected to a driven shaft 7 mounted at an angle of p to drive shaft and carrying counterweight B, made in the form of a flywheel rigidly mounted on the b. Baom Ba. iy. The crank wheels are driven by drive gears 9. In the case of a double universal spindle (Fig. 7, 8, 9), the device additionally contains an intermediate shaft 10 with forks 11 and 12, rotated 90 ° relative to each other, and pivotally connected by a crosspiece 13.

The spindles are connected in series.

The axis of the hinges of the fork 4 of the driving shaft 3 is set at an angle a to the crankshafts OA of the drive of moving masses (Fig. 1, 7), the value of which is chosen in the region of 90--95 ° - when the yoke is turned off only by the moment of inertia of iodovodimennyh masses and parts of their drive, and at its simultaneous balancing with the moment of rolling in the area 78-82 for mills with a stationary stand and (i8 - 72 for mills with a moving stand.

The device is working in a smart way.

Uniform rotation of KpiiiiOHiHiniijix x forest 2 p) and the input of moving masses by means of a universal spindle and cross section with odonanrav, 1nosnos perennomnaya BpaHi.c- counterbalance 8 with alternating sections of H) on and braking p (n

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one for one revolution of cranks, corresponding to one double move of moving masses (stands - for HPT mills, a blank cartridge --- for HPPTS mills). In this case, the counterweight within one cycle has two alternating maxi.mu.ma and minimum angular velocity and, with its non-uniform rotation, develops an inertial moment MK - / sfs, creating a balancing moment on the shaft 3 of the crank.

Moo --- / 8 8 --- / 80J8 (f 8lf8,

where / 8, OJ8 and - the momentum inertia, angular velocity and acceleration of counterweights, o} -2 - angular speed of the crank, f in (1) 8 / (- 02 and1 | 8 8 / w | are analogues of the counterweight and acceleration .

The antiphase movement of the counterweight and the moving masses, therefore, of both the balancing MO and the balancing moments, is achieved by assigning an angle a between the crank OA and the axis of the fork 4 of the drive shaft 3 (Fig. 1, 7) in the proposed areas.

Assigning the angle a outside the specified areas violates the antiphase and instead of neutralizing the dynamic moment on the crank shaft (with or without rolling moment), the counterbalancing moment can be added to it.

The greatest degree of equilibration, in addition to providing antiphasing, is achieved by setting the moment of rotation of the counterweight to the proposal of the counterbalance. the dependencies below.

In presented on fi1. 1, 7, the counterweight devices are installed so that the axis of its movement is located with the axis of the shaft in the horizontal plane, containing the axis of rolling. If necessary (caused by, for example, constructive considerations), the axis of rotation of the counterweight together with the universal spindle without changing the relative position of its links can be rotated around the axis of rotation of the crank at any angle relative to the latter and set under this yr; ioM. In this case, to save achieved antiphase and the effect of equilibration, it is necessary to change the angle a in the same angle and in the same direction.

From us: yvi constant of kinetic energies, presented for two extreme positions of the system min / ,, - max (i, h and max LOj (c) g / max oij co.sp; uj., / MnH60g l / cos p ) defined. moment iner- luin npOT iHOBcca

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 -uiiMCHMOCTH FROM B, 1bra11; 1) d) the values of i - la - | between OS. Valo Univers./L- () ischiid.ch.

When it is possible to neglect the inertia of the connecting rods drive the moving masses. we have min / n O and max / paractl where r is the radius of the drive curvature of moving masses w.

In the case of a double universal spindle with forks of the intermediate shaft turned 90 °, we have (02 / max (, а) 2 / mino) 8 1 and the formula takes the form

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max / „- min / n (cosp) -cos p

To substantiate the validity of the dependencies to determine the moment of inertia of the counterweight and the proposed areas for selecting the angle a of the balancing device arrangement with a crank drive of moving masses on the EC-1022 computer, the drive of the HPPTS camp 90-160 was investigated using the following parameters of the drive central crank-slider mechanism: number double passages - l 90 dvh / min; dimensions of drive links, 5045 m, m; the distance from the rod center of gravity to the axis of its crank pin AS I, 22 m; drive unit weight Oz 11.5 t, Gn 1,341 t, G 10 t; the central moment of inertia of a rod - 1 $ 0,2136 tms

The graph of the dynamic moment variation MO () on the crank from the inertia forces of the connecting rod and the drive mechanism slider without balance is shown in FIG. 4. To balance this moment, a single universal spindle with an angle was used, and the moment of inertia of the counterweight was determined by the calculation formula. The optimal value of the arrangement angle between the crank and the axis of the lead viewer was established as a result of the resampling computer of the optimization problem:

minM (f, a) - hammock 2l a

equalizing and minimizing as a result of balancing the negative peaks of the total dynamic moment M. The graph M (l () for the found value is shown in Fig. 4. The value of the arrangement angle between the crank and the axis of the lead fork was determined by solving the problem in fb | l; 2l idling without rolling under the condition of the best adaptation of the total dynamic moment at site l) to neutralize the peak of the rolling moment in the case of a mill with a stationary stand. The graph M (f) for the value found is shown in FIG. five.

The value of the arrangement angle between the crank and the axis of the leading fork was determined by solving on a computer the problem of obtaining negative peaks

dynamic momentum M (nl plots npOKfiTKH on a rolling mill stand. The graph Af (f) for this case is shown in Fig. 6.

Such a constructive device allows the construction of a balancing counterweight actuator to be simplified, using a universal spindle for balancing; perform an effective balancing of the dynamic moment on the crankshafts of the moving mass drive (Fig. 4) by selecting the angle a in the proposed area of 90-95 ° and assigning the moment of inertia of the weighing weight according to the dependences connecting the inertial properties of the drive moving

from the masses to be equilibrated, with structurally acceptable values of the angle p between the shafts of the universal spindle. As the angle p increases, the degree of non-uniformity of rotation of the counterweight increases and its moment of inertia decreases.

0 In addition, it becomes possible to equalize and minimize the total torque on the crank shaft by selecting the value of the angle a in the region of 68-72 ° for mills with a moving cage and 78-82 ° C of mills with a stationary cage and significantly reduce, the energy intensity of the mill due to the combination of areas of negative (driving) dynamic moments with sections of rolling and the use of energy of moving masses and counterweight to remove the peaks of the rolling moment (see Fig. 5, 6), decrease in

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25 times the moment of inertia of the counterweight by using a double universal spindle with the Intermediate Shaft forks turned 90 °.

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Claims (2)

1 .. Drive movement of moving masses of a cold rolling mill tube containing a crank mechanism and a counterbalance mechanism in the form of a counterweight mounted on a shaft, kinematically connected to a curved shaft of a shaft, characterized in that, in order to increase the efficiency of counterbalance against inertial forces, the motive mass, the kinematic connection of the shafts, is made in the form of a universal spindle, the axis of which is set at an angle to the crank. 2. The drive according to claim 1, characterized in that, in order to reduce the dimensions, it is equipped with an additional universal spindle, connected in series with the main, and the forks of their common va.ch are rotated 90 ° while the two other spindle shafts are parallel. L FIG. G View 6 Fig.Z 15 ten 5 phage. 6 Phage.1 FIG. eight View g FIG. 9