RU170555U1 - Combined vibration isolator - Google Patents

Abstract

The utility model relates to transport engineering and can be used for vibration isolation and suppression of dangerous vibration of units, assemblies, devices, etc. in all areas of technology where increased vibration protection is required. A combined vibration isolator consisting of a rotor shaft, a package of corrugated plates, an outer and inner ring and an elastic hysteresis element made in the form of a zig-shaped, double-curved hollow wire strand infinitely folded into the ring, inside filled with hemp base and placed between cylindrical pockets made in the inner ring from the side of the package of corrugated plates and hollows of the corrugation of the package, characterized in that in addition a fixed copper winding, which is located in the support housing, a magnet, which is located directly on the rotor shaft, and a speed sensor, which is mounted on the support and regulates the voltage supply, are connected with the fixed copper winding, creating a magnetic field that pushes the magnet, and creates a longitudinal force applied along the rotor shaft. The proposed combined vibration isolator allows to increase the vibration isolation resource and the possibility of its adjustment.

Description

The utility model relates to transport engineering and can be used for vibration isolation and suppression of dangerous vibration of units, assemblies, devices, etc. in any areas of technology where increased vibration protection is required.

It is known a damping device comprising a housing, a vibrator and a package of corrugated plates installed between the housing and the vibrator, characterized in that, in order to improve the damping of vibrations, the device is equipped with an additional package of corrugated plates mounted on the vibrator, and an intermediate ring, the inner diameter of which is larger the outer diameter of the vibrator, and the width is less than the width of the latter and interacts with the main package of corrugated plates, and the gaps between the case and packages are selected from tions:

where A _max - the maximum working amplitude of the vibration of the rotor in the support;

Y ₁ - the gap between the housing and an additional package of corrugated plates;

Y ₂ - the gap between the body and the main package of corrugated plates;

Y ₃ - the gap between the vibrator and the intermediate ring;

[a.s. RF №778399, IPC F16F 7/00, publ. 03/20/2001, authors Ponomarev Yu.Kh., Antipov V.A. and etc.]

The disadvantages of this invention are the complexity of the design, an abrupt change in stiffness, which is, in fact, an impact load for a vibration-insulated object. Therefore, the efficiency of vibration suppression at small amplitudes is less than it could be.

Known combined vibration isolator, consisting of a package of corrugated plates, the outer and inner rings and an elastic hysteresis cable element, characterized in that the elastic hysteresis element made in the form of a zig-shaped, infinite, twisted into a ring double-curved cable strand, and the strand is made hollow from the inside, or filled with hemp placed between cylindrical pockets, which, in turn, are made in the inner ring from the side of the package of corrugated plates, and the hollows of the corrugations of the pack that one. [RF patent for utility model No. 38374, IPC F16F 7/00, publ. 06/10/2004. Combined vibration isolator. / Antipov V.A., Kovtunov A.V., Ponomarev Yu.K., Duletsky V.A., Vershinin P.V., Gunin V.A., Shatrov V.G.)

The disadvantage of this vibration isolator is the inability to regulate the quality of vibration isolation at various types of load.

This technical solution is selected as a prototype.

The technical result is to increase the reliability and quality of vibration isolation by changing the stiffness of the rotor during acceleration-stopping.

The technical result is achieved by changing the natural frequency of the system, creating a force applied along the rotor shaft, on which the magnet is located, using a fixed copper winding, which is placed in the support housing, the moment of which the voltage supply is canceled is regulated by an inertial speed sensor, which is mounted on the support, when it reaches a rotation speed exceeding the resonant frequency of rotation of the rotor, not loaded with a longitudinal force.

To implement the proposed utility model, the rotor 1 (Fig. 1) is hollow, with a magnet 4 inserted, and fixed by the bearing assemblies 2 with a combined vibration isolator 3. An inertial-type sensor 5 is mounted in the support housing, which is connected to the winding 6.

In FIG. 2 shows the amplitude-frequency characteristics of the rotor-housing systems with vibration suppression: curve 8 - for the rotor with rigid supports; curve 9 - vibration suppression in the supports; 10 - vibration suppression by an elastic-damper system; curve 11 - characterizing the rotor-body system under the action of longitudinal force; curve 12 - characteristic, when implementing a combined vibration isolator.

In FIG. 1 shows a diagram of a device.

In FIG. 2 shows the amplitude-frequency curves of the rotor-housing systems.

A magnet 3 is mounted on the rotor shaft 1, fixed by the bearing assembly 2, a combined vibration isolator 4 is installed next to it, a sensor 5 is installed in the support housing, which is connected to a winding 6 installed in the support housing 7.

Combined vibration isolator works as follows.

On the rotor shaft of EU 1 with a magnet 3 located on it, the shaft is fixed with the help of the bearing assembly 2. When the rotor is untwisted to ω = ωav (Fig. 2), voltage is applied to the winding 6. In this case, the rotor has a rigidity C2 and a resonant frequency ωр2 (Fig. 2), and the amplitude of movement of the rotor 1 in the bearing units 2 is characterized by the left branch of curve 12 (Fig. 2). When the rotor reaches the frequency ω = ωcp (Fig. 2), a sensor 5 of inertial speed is activated, connected with the winding 6, which ceases to create a magnetic field. In this case, the rotor stiffness abruptly changes to the value C1 at ω = ωp1 (Fig. 2), and with a further set of revolutions, the displacement amplitude is determined by the right branch of curve 8 (Fig. 2).

When the rotor stops, the response of the elements of the system occurs in the reverse order.

The proposed combined vibration isolator allows to increase vibration protection by adjusting the amplitude-frequency characteristics of the rotor shaft, which increases the reliability of the bearings and their durability, thereby increasing the resource of the supports by 10%.

Claims (1)

A combined vibration isolator consisting of a rotor shaft, a package of corrugated plates, an outer and inner ring, and an elastic hysteresis element made in the form of a zig-shaped double-curved cable hollow endlessly turned into a ring, inside filled with a hemp base and placed between cylindrical pockets made in the inner ring from the side plates, and hollows of the corrugations of the package, characterized in that it additionally introduced a stationary copper winding, which is placed in the housing about Orae magnet disposed on the rotor shaft, and a speed sensor which is mounted on a support and controls the supply voltage, the latter being connected to a fixed copper coil that creates a magnetic field which pushes the magnet and generates a longitudinal force applied along the rotor shaft.

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