JPS5920049B2 - Torsional vibration damping device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a device for suppressing the resonance magnification of torsional vibration of a rotating machine.

A plan view of a conventionally known device of this type is shown in FIG. 1, and a sectional view thereof is shown in FIG.

In the figure, 1 is a lid, 2 is a guide ring fitted to the inertia ring to regulate the inertia ring, 3 is a casing that supports the whole, 4 is an inertia ring that contributes to suppressing torsional vibration, and 5 is an inertia ring. The gap between the casing 3 and the inertia ring 4 is filled with a viscous fluid that similarly contributes to vibration suppression.

Next, the operation of this conventional device will be explained.

FIG. 3 is a simulation of a torsional vibration system equipped with a suppressor.

Here, 6 is an inertial body of the vibration allocation device, 7 is a damped body, 8 is a spring exhibiting torsional rigidity, and 9 is a foundation having infinite rigidity.

When the inertial body 6 having viscosity is attached to the object I to be damped shown in FIG. 3, the relationship between the amplitude multiplier M and the frequency ratio γ of the object T to be damped becomes as shown in FIG.

Note that U is a damping ratio and uopt is an optimal damping ratio.

That is, in relation to the damping ratio U, there exists a value at which the amplitude magnification M is the smallest.

At this time, the following relationship holds true.

Here, Id is the amount of inertia of the inertia ring 6, and Ie is the amount of inertia of the damped body 7.

On the other hand, the amount of vibration energy absorbed by the allocator is at its maximum when:

C=Idω0 Here, C is the viscosity coefficient and ω0 is the uniform frequency.

Therefore, the damping effect of a certain damped object is determined by the inertia of the damping device and the viscosity coefficient commensurate with its uniform frequency.

However, conventionally, the viscosity coefficient is adjusted by fitting the inertia ring 4 to the casing 3 with an appropriate spacing as shown in FIG.

Further, in order to maintain a constant gap, a guide ring 2 is fitted into the inner diameter side of the inertia ring 4, and precision machining is finished to maintain a minute gap.

In these conventional devices, it is necessary to increase the machining accuracy of each part, and the guide link 2 has the disadvantage of causing a galling phenomenon during sudden acceleration and deceleration, which changes the characteristics. There were problems in terms of price and manufacturing.

This invention was made with the aim of solving the above-mentioned conventional drawbacks, and by enclosing a fragmented inertial body together with a viscous fluid in a casing attached to a to-be-assigned body using a lid. The aim is to achieve the desired vibration damping effect by achieving stable characteristics and extending the service life without the need to increase machining accuracy (and without causing galling).

An embodiment of the present invention will be described below with reference to the drawings.

In Fig. 5, 1 is a lid, 3 is a casing, 5 is a viscous fluid, and 10 is an inertial body made into pieces (small balls in the figure), and there is no space between it and the casing 3 together with the viscous fluid 5. The lid 1 is bolted or welded to the casing 3 to seal them.

By attaching this damping device to the object to be damped, the casing 3 vibrates, but the inertial body 10 receives the vibration force only through the viscous fluid 5 filling the casing.

Therefore, energy related to the amount of inertia between the casing 3 and the inertial body 10 and the viscosity of the viscous fluid 5 is consumed.

This has a damping effect, but since the inertial body 10 is divided into pieces, the mass of each piece is small, so a galling phenomenon occurs between the inertial body 10 and the casing 3, which affects the damping effect. There is no possibility that it will cause any harm.

Determine the ratio of the inertia of the damping device to the magnitude of the inertia of the damped body, and select the viscous fluid 5 having a viscosity coefficient adjusted from the damping frequency to the inertia of the damping device. By doing so, the desired vibration damping effect can be achieved.

As described above, according to the present invention, the rotating casing 3
The viscous fluid 5 having a predetermined viscosity coefficient and the fragmented inertial body 10 are filled in the inside so that there are no voids, so even if the casing 3 vibrates due to rotation, the inertial body 1
0 does not receive vibration force through the viscous fluid 5 filling the casing, and the inertia and the energy corresponding to the viscosity of the viscous fluid 5 are consumed between the casing 3 and the inertial body 10 and the vibration is suppressed. Since the oscillation was made to take place, the inertial body 10
Furthermore, there is no galling phenomenon between the viscous fluid 5 and the casing 3, which not only provides a smooth vibration damping effect, but also stabilizes the characteristics and extends the life of the product.

[Brief explanation of the drawing]

Figure 1 is a plan view of a conventional vibration damping device, Figure 2 is a side sectional view thereof, Figure 3 is a diagram explaining its torsional vibration system, Figure 4 is its resonance curve diagram, and Figure 5 is the invention. FIG. 3 is a side sectional view showing one embodiment of the invention. In the figure, 1 is a lid, 3 is a casing, 5 is a viscous fluid, and 10 is a solid piece. Note that the same reference numerals in the figures indicate the same or corresponding parts.

Claims (1)

[Scope of Claims] 1. A torsional vibration damping device characterized in that a rotating casing is filled with a viscous fluid having a predetermined viscosity coefficient and a fragmented inertial body so that there are no voids. 2. The viscosity coefficient of the viscous fluid is adjusted by calculating the ratio of the inertia of the vibration damping device to the magnitude of the inertia of the damped body, and from the uniform frequency to the inertia of the vibration damping device. A torsional vibration damping device according to claim 1, characterized in that: