SU554532A1 - Device to eliminate backlash in the gearbox - Google Patents

Description

one

The invention relates to elements of automatic control systems and can be used to build precision servo drives in various sectors of the national economy.

Executive mechanisms are known that represent a closed kinematic kinetour of two gears with forced pa BOipOTOM them in one direction: positive sides due to spring 1 or elastic element 2.

However, these known mechanisms are characterized by the direct dependence of the output character on the moment of loading.

Also known is an operating mechanism with a device for sampling a gap, which contains two gearboxes, the input axes of which are interconnected through a torsion, and the output axes are coaxial and rigidly interconnected 3.

However, this mechanism is also characterized by a significant dependence of the accuracy of the mechanisms on the moments of the load, due to the fact that the total mechanicism of the mechanism, consisting of the two components of the gap bz and the elastic deformation, depends on the moment My, created by the elastic element, and has the minimum value of lisch at a certain value of My: Alyopt, which most often cannot be maintained, since My elastic element is chosen "e

only on the basis of the minimum value of 6s, but also on the condition of ensuring operation at the maximum possible load moment. The purpose of the invention is to improve the accuracy of the device.

For this purpose, a differential, a worm pair, an adder, an amplifier, a torque motor, and angle sensors, each of which is set to

input axes of the gearboxes and is connected to an adder, which is connected via a successively connected amplifier, a torque motor and a worm gear pair with a differential, the differential

mounted on one of the input axles of the gearboxes and kinematically connected with the torsion wheel.

The drawing shows a structural-directional. An electrical circuit diagram of the device.

The device for eliminating backlash in the gearbox contains two gearboxes 1 and 2, torsion bar 3, angle sensors 4 and 5, an adder 6, an amplifier 7, a correction torque 8, a pair 9, a differential 10.

The device works as follows.

In the initial non-working state, twisting is reported to the torsion bar, optionally not to change its value at half the load torque on the output axis of the mechanism: ma. With action. this load and feed

The input of the cisx signal is transmitted by the Circassian gearbox 1 or 2, the gaps 6h in which are selected by the action of the moment My Torsion 3. The elastic deformation in this case is only half of their maximum value at max. maximally possible load moment MnPri the combined effect of n signals from angle sensors 4 and 5 and the reference signal UQ signal at the input of amplifier 7 in this case is zero. The 8-point correction torque motor does not develop. And does not create an additional negative or positive torsion bar 3.

When the deviation of the moment Mn from the polynomial value under its action of torioi 3 is deformed relative to the initial spin. The signal from sensors 4 and 5 becomes different from the L / o signal. Under the action of a differential sipnal of one or another Ziak, of one value or another, selected in adder 6 and amplified by amplifier 7, engine 8 returns torsion 3 in (The initial oscillation and informs the additional moment through the worm gear pair 9 and differential 10 to the input of gearbox | groove 1 and 2 to recreate the total My moment needed to select the gaps.

The proposed actuator has an increased accuracy of signal transmission Ovx, since it has less elastic deformations than in the prototype. They are now variable depending on the load moment Mn, and reach the 31 witnesses observed in the prototype, only at the acceptably possible moment Mn, i.e., the smaller the moment M n, the smaller the elastic deformations developed (In the mechanism.

Claims (3)

1. Mushtaev, A.F. Willow gaps in the drive elements for smooth movement of machine tool tables, Machine Tools and Tools, 1960, No. 8. 2. Rozovsky, MS. Power Calculation of Gear Gearboxes with Preliminary Pressure, “Bulletin of Machine-Building Industry, 1963, No. 2. 3. Kozhevnikov G. B. Non-luffing gearboxes with a closed kinematic contour. Production technical bulletin. M., House of Technology, 1959, No. 11 (prototype).