JPS596449A - Torsional vibration damping eraser - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] The present invention relates to a screw υ vibration damping and canceling device.

This torsional vibration damping and canceling device consists of a resonant annular body formed in a two-part casing for containing a damping medium, and a rotary body that transmits screw vibration to a rotating body to be damped. A futsunjibonu mechanism for performing the combination,
It has a viscoelastic element that is connected to the flexible body mechanism described above at a certain resonant frequency.

This kind of torsional damper or screw or vibration damping canceler is a screw or vibration damping canceler in one secondary system, where the inertial body can be the only damping system element or the damping system element. Via the elastic system elements (both of which belong to the above-mentioned secondary system), the resonant screw vibration of the primary inertial body is damped or compressed to a desired degree for the primary inertial body that performs torsional vibration. are adjusted and connected.
.

Torsional dampers or screw vibration damping cancelers of the type must very often be used in conjunction with piston reciprocating devices; When the frequency of vibration due to the torque fluctuation due to the force due to the vibration and the gas force coincides with the natural screw vibration frequency of the primary system, the irreducible lll1! This is to rotate the width resonance. Therefore, torsional vibration dampers or torsional vibration damping cancelers are often coupled to the free end of the crankshaft in internal combustion engines.

The laws that should be applied to calculations to adjust the Yuzu damper or vibration canceling device N to the best condition according to each usage situation have already been known through research and development over the past several decades. There is. however,
My damper or vibration canceling device can be used at low cost.
It remains difficult to utilize a given space as efficiently as possible or to have absolute reliability of operation.

Conventionally, various so-called viscous dampers have been known, in which a ring-shaped secondary inertial body is movable within an annular closed casing connected to a primary inertial body. The gap around the secondary inertial body is filled with a damping medium, i.e. silicone oil, which is
Since it also produces alternating return torque,
In the end, this viscous (elastic) screw vibration damper cannot be called a pure damper, but rather belongs to the category of a screw vibration damping and canceling device.)
. Now, this viscous damper has the following drawbacks.

That is, this viscous damper cannot function unless it is constantly adjusted ηh, and its lifespan is limited to such an extent that it cannot be accurately predicted. This is because wear cannot be avoided within the sleeve bearing of the ring within the casing. A relatively large casing inertia that resonates with the primary inertia also has an adverse effect.

In new dampers of this type, part or all of the secondary inertial body is a casing. In this case, however, an elastic packing made of a viscoelastic material must be provided between the flange of the primary body and the casing in order to ensure that the silicone oil is enclosed within the gap. . In such cases,
The viscoelastic packing element has already reduced the secondary inertial body to 1
The dimensions are large enough to serve the purpose of elastically connecting the second inertial body. In one known example, a viscoelastic membrane l-1 of this type is provided with a disk loaded with shear stress on one side of the cake and a central bar formed as an extension of the fixed flange. will be installed between.

It is an object of the present invention to provide a multi-vibration damping canceler for a particularly wide viscoelastic element in the case where the secondary inertial body is as large as possible, the viscoelastic element having a sealing effect as well as a and has excellent elasticity.

According to the present invention, the above object is achieved as follows. That is, a viscoelastic element with a thin wall relative to its width does not essentially form a disk-like structure in the radial plane, but rather a hollow cylinder or sleeve-like structure that is cascaded from both sides in the axial direction. It is formed in
Therefore, it is advantageous to utilize a given damping structure, usually limited for space reasons, by approximately doubling its width and making its radius as small as possible due to its substantially rectangular cross-section. can be achieved by an axially extending viscoelastic element. Furthermore, in the annular inertial body, as many parts of the cross-sectional area element as possible, which increase outwardly to the sixth power, remain in a given space.

The screw vibration damping device according to the invention eliminates the drawbacks of known viscous screw vibration dampers mentioned above. For torsional vibration damping dampers (including torsional vibration dampers), if the space in the structure is limited to a given size, then the space can be used for the purpose of installing a secondary inertial body. It is especially important that it be used as widely and as extensively as possible. The secondary inertial body determines, first of all, to what extent the amplitude in the resonance course of the primary inertial body is reduced by the screw vibration damping canceler (this has also been recently (This is also the reason why we try to avoid the use of unnecessary casing inertia bodies that resonate with the primary inertia body as much as possible during research and development.) An area element of a certain size, for example, a unit area element in a cross-sectional area limited for reasons of nuvene, is
It contributes to the total moment of inertia fffx'pdv of the secondary inertia body by the cube of its radius. In contrast, for a given shape and given material, the energy absorption capacity of a spring depends only on its volume. Therefore, if we take into account that the secondary inertial body is made as large as possible, if a part of the 91I elastic element or elastic element is formed in an appropriate shape, It is advantageous to install the rotor as close as possible to the shaft (as far as the dimensions of the flange given by the rotor to be used allow). Viscoelastic elements loaded with shear stress, which in addition to the sealing effect also have a good elastic effect,
It has a large width compared to its thickness. The present invention takes advantage of such a situation.

Referring now to the drawings, FIGS. 1 and 2 show sleeve-shaped viscoelastic elements 5.6 that are combined with one another and act in parallel. The outer viscoelastic element 6 is thicker than the viscoelastic element 5 because its average radius is larger than that of the viscoelastic element 5. Therefore, the secondary inertial body 1.2 and the primary inertial body 3
As a result of the relative vibration between the viscoelastic element 5.
The alternating shear stress applied to 6 is maintained at the same value that is considered to be acceptable.

The hollow cylindrical or generally axially extending sleeve-like form of the viscoelastic element has further advantages according to the invention. That is, the stiffness of these elements in the radial direction, i.e. the secondary inertia body 1.2 and 1.
(#) is larger in the axial direction than in the axial direction with respect to the 7-bunshi 3 of the next inertial body. However, the tensile and compressive stiffness is considerably higher). In the case of disc-shaped rubber elements, the relationship between radial stiffness and axial stiffness is reversed. The same applies to the accuracy of the centering of the secondary inertial body 1.2 relative to the primary inertial body 6, which accuracy depends on the tolerance of the intervening viscoelastic element 5.6 determined during the manufacturing stage.

A high stiffness in the radial direction is required when the annular secondary inertia body 1.2 vibrates transversely with respect to the primary inertia body 3, or when the degree of unbalance is further increased under unbalanced conditions. The resonant rotational speed when increasing and dislocating in the radial direction is
This is to ensure that the maximum rotational speed of the rotor to be damped is as high as possible.

In order for viscoelastic elements, such as rubber (natural rubber) or Vuitton, to be bonded to adjacent metal parts in a fatigue-resistant and hermetically sealed manner, their free, unbonded surfaces must be Advantageously, it is easily accessible by the forming tool. Therefore, in the present invention, the secondary system is provided within the component so that it can be easily accessed with a tool or the like from both sides in order to facilitate the joining of the free surface of the viscoelastic element with an adjacent metal surface, e.g. by vulcanization. It is distributed as possible.

In the embodiment shown in FIGS. 1 and 2, during the joining of the annular parts which are not yet joined on the outside in FIG. Even when they are combined with each other in a shape, it is possible to apply them perpendicularly to the surface of the combined viscoelastic elements.

[Brief explanation of drawings]

The drawings show embodiments of the present invention, and FIG. 1 is an overall side view in cross section of the lower half of the torsional vibration damping and canceling device of the present invention, and FIG. 2 is the upper half of the device shown in FIG. 1. FIG. 1.2... Inertial body 6... Flange-boss mechanism 4... Coupling ring 5.6... Viscoelastic element 7... Damping medium

Claims (3)

[Claims] (1) resonant and annular, 2 for accommodating a damping medium;
an inertial body made in a casing that is partially parallel to the casing; a flange-boss mechanism for coupling to the rotor whose screw vibrations are to be damped; A screw vibration damping and canceling device having a viscoelastic element connected with a screw, the viscoelastic element having a thin wall compared to its width,
Substantially not in the form of a disc in the radial plane, but in the axial direction, hollow cylinders or sleeves assembled from two sides in a cascade manner, and thus
The use of a given damping medium, which is usually limited for space reasons, by approximately doubling its width and making its radius as small as possible makes it possible to reduce its substantially rectangular shape. The cross section is formed by a viscoelastic element extending in the axial direction, and the annular inertial body 1.2 has an outwardly extending 5
A screw vibration damping and canceling device characterized in that as many parts as possible of the mass action of the cross-sectional area element increasing by the power are retained in a given space. (2) No combination of separate components, two of which transmit mass and elastic effects through one inertial body and one viscoelastic element, respectively, while the other The main function of the two components 7 or another group of components is to transmit a damping effect, and in distributing and arranging the components, in each of the two (first-mentioned) components, 2. A device as claimed in claim 1, characterized in that the free surfaces on both sides of the viscoelastic element are readily accessible to forming instruments during the manufacturing process. (3) In the two individual elements 1.3.5i2.4.6, the viscoelastic elements combined with each other ensure that during the assembly process the stresses increased by the key effect are The torsional vibration according to any one of paragraphs 1 and 2 of the patent anti-icing range, characterized in that it is shaped so as to be applied vertically to the surface of these viscoelastic elements in a bonded UK. Attenuation canceler.