JPH0219644Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibration isolating device that prevents vibrations of a part of a structure or an object installed on the structure.

For example, stays are used to dampen the vibrations of main engines and auxiliary machinery installed on ship structures, but if the stays have sufficient axial rigidity, their lateral rigidity is not large. Good too. On the other hand, if it is too large, damage will occur due to some type of forced displacement external force.

An example of a conventional vibration isolator is explained with reference to FIG. 1. When a structure b installed on a base a is vibrating in the direction of the arrow, a stay (support rod ) is often attached to structure d to provide vibration isolation. And generally this stage c
should work effectively only against that lateral force.
However, in actual structure b, not only the axial direction but also
Some vibrations often occur in other directions as well.
Also, a relative displacement may occur between the bases a and d. In such a case, if the stay is a fixed type stay e as shown in FIG. 2, damage will occur due to bending of the stay e. Therefore, in order to prevent stress from occurring even if the stay is bent, the stay h using a hinge f or g as shown in Figures 3 and 4, for example.
Or i is adopted. However, in this method, it is difficult to minimize the clearance of the pins constituting the hinge f or g, and it is not possible to effectively deal with minute vibrations. Further, even if the clearance is made small, the pin portion will wear out due to repeated loads, causing backlash and becoming ineffective against vibrations.

In view of the above points, the present invention adopts two orthogonal thin plates as part of the stay, so that the base a,
The purpose of this design is to provide a vibration isolator that can reduce the stress level caused by forced displacement between the two plates, eliminate damage, and maintain its original function. The cross-sectional shape of the intersecting portion is formed in a cross shape by intersecting and fixing each other, and the dimension in the direction parallel to the plane of the tip of each plate gradually decreases toward the tip.

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

FIG. 5 shows an embodiment of the vibration isolating device of the present invention,
Thin plates 1 and 2 are orthogonally crossed and fixed to each other by welding,
When plate 1 bends due to forced displacement in the vertical direction, plate 2
In order to smoothly continue the in-plane deformation of the plate 1 and the out-of-plane deformation of the plate 1, the dimension of the plate 2 tip 2a in the direction parallel to the plane of the plate 2 is shaped to gradually become smaller toward the tip side. Plate 1 is designed so that when plate 2 bends, the in-plane deformation of plate 1 and the out-of-plane deformation of plate 2 smoothly continue.
The dimension of the distal end portion 1a in the direction parallel to the surface of the plate 1 is made into a shape that gradually decreases toward the distal end side.
This shape may be curved as shown in FIG. 5, or it may be straight. Also, by reducing the thickness of plates 1 and 2, the axial spring constant, that is, the cross-sectional area, which is the original purpose of the vibration isolator, must not become smaller.
This problem was solved by widening the board width.

A structure 4 is placed on the base 3, and one end of the vibration isolator A having the above structure is fixed to the base 5, and the other end of the vibration isolator A having the above structure is fixed to the upper end of the structure 4. The vibration isolator A may be attached to both sides of the structure 4 as shown in FIG. 6, or may be attached only to one side.

When the structure 4 vibrates in the vertical or longitudinal direction,
Even if the vibration is not large enough to cause a problem, the vibration isolator A
Forcible vertical or longitudinal displacement acts on the. For example, in response to vibrations in the X direction in Figure 5, the stress against forced displacement type external forces can be lowered by bending plate 1, and in response to vibrations in the Y direction, bending deformation of plate 2 can reduce stress. Therefore, the stress caused by forced displacement type external force can be reduced. In other words, even if bending stress is generated in the plate due to vibration, by making the plate thickness of plates 1 and 2 sufficiently thin, the stress against external force of the forced displacement type can be lowered, and damage to the vibration isolator due to this can be prevented. Can be done. In addition, the dimensions of the distal ends 1a and 2a of the plates 1 and 2 in the direction parallel to the surfaces of the plates 1 and 2 gradually decrease toward the distal ends, so that the dimensions of the distal ends 1a and 2a of the plates 1 and 2 gradually decrease as they move toward the distal ends. During forced displacement, stress concentration does not occur at the intersection of the two plates, making it possible to more effectively prevent damage to the vibration isolator.

Figures 7 to 10 are examples of other embodiments of the present invention used in the main engine of a ship. In the figure, 6 is the main engine, 7 is the hull structure, and a bracket 8 is attached to the main engine 6.
plate 1 and bracket 8 of vibration isolator A are sandwiched from left and right by plate 9, plates 1 and 9 are fixed with bolts 10, and bracket 8 and plate 9 are connected via friction plate 11. It is fixed with bolts 12. With this configuration, vibration of the main engine 6 can be prevented.

In addition, in the embodiment of the present invention, a case has been described in which thin plates are intersected and fixed at approximately right angles and no ribs are provided. The shape of the tip of the plate may be any shape as long as the stress concentration is small, the two plates that intersect may have different thicknesses, and the structure other than the thin plate part that intersects may be of any shape. It goes without saying that the present invention can be implemented as a structure, and that various other changes can be made without departing from the gist of the present invention.

According to the vibration isolator of the present invention, () the rigidity can be made sufficiently small to reduce stress against forced displacement type lateral bending, so damage to the plates constituting the vibration isolator can be prevented. Therefore, the safety of the structure against vibrations is improved. () Unlike the pin hinge type, there is no need to reduce the clearance, and there is no wear of the pin due to rotation, so there is no need to increase machining accuracy, and machining is easy. () With the pin hinge type, it is necessary to replace the part whenever play occurs, but with this method, replacement is not necessary. Therefore, no maintenance is required. () It has a simple structure of just two thin plates intersecting each other, so it is easy to manufacture and the manufacturing cost is low. () The tip of the plate is parallel to the surface of the plate. Since the dimension in the direction gradually decreases toward the distal end, even if forced displacement occurs in the intersecting plates, stress concentration can be prevented from occurring at the intersection of the plates. It can have excellent effects.

[Brief explanation of the drawing]

Figures 1 to 4 are explanatory diagrams of a conventional vibration isolator, Figure 5 is an explanatory diagram of an embodiment of the vibration isolator of the present invention, and Figure 6 is an illustration of the operation of the vibration isolator shown in Figure 5. Explanatory diagrams, FIGS. 7 to 10 show other embodiments of the vibration isolator of the present invention, FIG. 7 is an explanatory diagram when the vibration isolator is used for vibration isolation of a ship's main engine, and FIG. Fig. 7 is an explanatory diagram of the vibration isolating device, Fig. 9 is a - direction arrow view of Fig. 8,
FIG. 10 shows a - direction arrow view of FIG. In the figure, A indicates a vibration isolator, and 1 and 2 indicate thin plates.

Claims (1)

[Scope of utility model registration request] The tips of the two plates were crossed and fixed together to form a cross-sectional cross-section of the intersection, and the dimension of the tip of each plate in the direction parallel to the plane gradually decreased toward the tip. A vibration isolating device characterized by: