SU1724970A1 - Method and apparatus for balancing dynamic moment on input shaft of reciprocate masses drive - Google Patents

Abstract

The invention relates to rolling production and can be used in balancing the moving masses of cold rolling mills with a moving and stationary stand for balancing the dynamic moment on the drive shaft. The purpose of the invention is to increase the efficiency of balancing. A counterbalance force is applied to the crank pin, which rotates freely on the pin relative to the crank at double speed, and rotates the counterweight in the direction of rotation of the crank. 2 sec. f-ly, 10 ill. w YO VI you 4 YO VI O

Description

The invention relates to rolling production and can be used in cold tube rolling mills (HPT) for balancing the dynamic moment on the input shaft of the drive of the reciprocating masses of working stands of the HPT mill.

The purpose of the invention is to increase the efficiency of balancing.

Fig. 1 shows the rotation scheme of the crank, the counterweight, the relative position of the trajectories of the crank pin and the centers of the weight of the counterweight and moving masses; figure 2 - the proposed device, top view; on fig.Z - section aa in figure 2; figure 4 - section bb in fig.Z; figure 5 is a view In figure 2; Figure 6 is the same; figure 7 is a view of the figure 6; on

Fig.8 is a graph of the dynamic moment; figure 9 is a graph of the horizontal dynamic force acting on the base; in fig. 10 is a graph of the variation in the vertical dynamic force acting on the base.

Balancing the moment from the inertia forces by the proposed method is carried out as follows.

In the initial - left extreme position In the driven mass (V2 0) the center of gravity of the satellite counterweight is as far as possible away from the axis of rotation of the crank, located in the middle of the So branch of the double-vertex epicycloid (Fig. 1) and has a maximum speed of max Vs 3 6o ( rs + Ra / 3) and maximum kinetic energy. In the B0Bi section of acceleration of the driven mass Va, the speed of the center of gravity of the satellite counterweight decreases from max Vs to a minimum value of min / 5 (g5-Pz / 3) at the Si top of the epicycloid, and energy is exchanged between the driven mass and the counterweight (kinetic counterweight energy is given to the driven mass for acceleration reporting). With the subsequent movement of the driven mass, its speed decreases from max Va to zero, and the center of gravity of the satellite-counterweight weight increases from the minimum value (at the point Si) to max VB at position $ 2. and energy, given by the driven mass, goes to accelerate the balances. During the reverse course of the driven mass, the energy exchange cycle is repeated.

The device implementing the method contains a carrier made integral with the crank 1 of a drive of movable masses 2 (stands for rolling mills, a mandrel, a workpiece and its cartridge for stations with a stationary stand) are rotatably mounted on additional crank pins 3 by means of bearings 4 satellite counterweights 5 and a fixedly mounted in the housing 6 block gears 7, introduced into engagement with the satellites. Satellites 5 compared with fixed gears have half the number of teeth.

The crank drive of the moving mass 2 is made in the form of crank gears 1, rigidly interconnected by means of the crank shaft 8 and mounted on bearings 9 in the housing. On the crank gears, the main crank fingers 10 are rigidly mounted

bearings 11 with connecting rods 12 drive movable masses. The crank gears are engaged with gears 13 and 14, rigidly mounted on the drive shaft 15.

In another embodiment, the device is additionally equipped with a wide parasitic gear 16, which is brought into engagement simultaneously with the drive gear and its crank gear 1 (Fig.6 and 7). In this case, one (or both) of the crank gear on the shaft 8 is installed with the possibility of rotation, and the latter is rigidly connected with a stationary gear wheel. The presence of a parasitic gear 16 in the chain leads to a mismatch of the directions of rotation of the crank gears 1, and therefore of the connecting rods 12, the counterweights 5, to the balancing of the vertical components of the inertial forces of these links and the unloading of the foundation bolts.

In order to maximize the degree of balancing of the dynamic moment on the cranks, the mass of each of the two satellite counterweights 5 is set according to

GP5G5 (0.16-0.17) mR2io / Rs,

where ms and iz-mass, satellite counterweight and the distance of their common center of gravity from the axis of the satellite;

Rio and Ra are the distances between the axis of the crank shaft 8 and the axes of the main 10 and an additional 3 fingers;

m is the calculated value of the reciprocating masses, equal to the sum of the masses of the mandrel, the workpiece and its cartridge for mills with a stationary stand, and the sum m m + J / Ruj of the mass hp2 of stand 2 and the equivalent mass of the roller group with a total moment of inertia J, taking into account the dynamic moment of the latter in their reciprocating motion relative to the stand, realized by the leading gear wheels of radius RUJ of the initial circle.

To balance the horizontal inertial forces and unload the basement in the horizontal direction, the centers of gravity Si of the crank gears are moved beyond their axis by a value of 0.2-0.3 of the crank length OA Cs (Fig. 5).

The device works as follows.

When rotating from the drive gears 13 and 14 of the crank gears 1 last by means of additional crank pins 3 carry

counterweights 5 with satellites (portable movement), which run around the fixed wheels 7, rotate relative to the crank gears with double angular velocity, as shown in figure 1 (relative movement). As a result, the absolute angular velocity of rotation of the satellite (around the engagement pole with the fixed wheel) is three times the angular velocity of rotation of the crank crank 1. In this case, due to the adopted ratio (Zy: Zs 2), the center of gravity S of the counterweight 5 moves along two - a vertex elongated epicycloid (Fig. 1) with a variable speed equal to max Vs at the positions S0 and Ss of their maximum distance from the axis O of rotation of the cranks, and min Vs at the positions of Si and Zz to their maximum approximation to this axis. As a result of uneven movement of the center of gravity of counterweights, antiphase to the reciprocating movement of the driven mass 2, the tangential components of the inertia forces of the counterweights and their gravity on the input cranks 1 create a moment that effectively balances the dynamic moment caused by the inertia forces of the driven mass 2 and rods 12.

The dynamic moment on the crank gears is balanced by combining the extreme positions of the reciprocating mass 2 (figure 1) with the positions of the maximum speed of the centers of gravity of the counterweights. This leads to the fact that the accelerated movement of the driven mass 2 corresponds to the slow motion of the centers of gravity of counterweights and vice versa, and this ensures a constant energy exchange between them and unloading both the engine and all parts of the transmission mechanism between the engines and cranks.

The balancing of the horizontal component inertia forces is performed by placing additional crank pins 3 diametrically opposite to the main crank pins 10 and placing the common center of gravity Si of the crank links between the axes of the cranks 1 and their additional fingers 3 (Fig. 5). However, these measures lead to an increase in the vertical component of the total inertia force compared to the unbalanced initial drive mechanism (Fig. 10). In the second design (FIGS. 6 and 7), the presence of a parasitic gear 16 leads to the fact that the movements of the crank gears 1, the connecting rods 12 and the counterweights 5 of the two branches are oppositely directed, and this, in turn, ensures complete mutual balancing of the vertical forces (curve 8 in FIG. 10), prc maintaining the result of balancing horizontal forces. Here, the tilting moment created by the vertical components of the inertia forces of the counterweights 5 and the crank gears 1 relative to the horizontal axis X (Figures 6 and 7) is opposed to the tilting moment from the connecting rods 12 of the inertia forces of the connecting rods 12 and is balanced by it.

The application of the balancing method and device for its implementation allows reducing the level of dynamic moment on the cranks of the drive mechanisms by more than 4-5 times, the level of dynamic forces acting on the base of the drive in the horizontal direction by more than 2 times, and completely balancing the dynamic forces acting on the base in the vertical direction, as well as the tilting moment, which in turn reduces the drive's vibroactivity, improves the balancing efficiency and unloading as an the engine and the elements between the latter and the crank with a significantly smaller mass of counterweights, performing a plane-parallel motion, with a constant angular velocity of rotation,

Claims (2)

1. The method of balancing the dynamic moment on the input shaft of the drive of reciprocating masses, mainly drives cold-rolling mills, providing for the crank of the counterbalance counterbalance force on the finger relative to the crank with a doubled speed, which is different in order to increase balancing efficiency, the counterweight relative to the crank is rotated in the direction of rotation of the latter. 2. A device for balancing the dynamic moment on the input shaft of the drive of reciprocating masses containing two identical crank gears located inside the bearings installed in the housing, each of which is equipped with main and additional crank pins, two connecting rods pivotally connected to the cage and main crank pins , and two identical balancing counterweight, characterized in that it is equipped with a block of external gearing gears, fixedly fixed — twice as many numbers The teeth are made in the housing coaxially with the crank shaft together with the counterweights and the hinged scrap, which are rigidly connected to each other by means of the crank gears mounted on the additional crank gears and the spiked fingers with maximum removal from the fixed gear teeth of their 5 centers. the sheet metal from the axis of the crank by the forests with two identical satellites fell in the extreme positions of the cage. QPig eight