JPS645144Y2 - - Google Patents

Description

[Detailed Description of the Invention] This invention relates to a vibration-proof support used for mounting vibrating machines such as vehicle engines, general machines, and construction machines.

Generally, machines that generate vibrations, such as vehicle engines, are attached to the attached member via a vibration-proof support in order to prevent the vibrations of the machine from being transmitted to the attached member, such as a board. . As shown in FIG. 4, for example, this type of vibration-proof support has a metal bushing c fixed in the center hole b of a cylindrical body a made of an elastic material, and a metal bush c fixed in the axial direction of the body a. There is one in which an annular outer wall d and an annular inner wall e are provided coaxially on one side, and an annular reinforcing member f made of a plate material is fixed (see, for example, Japanese Utility Model Application Publication No. 124639/1983). Two of the vibration isolating supports are used as a set.

By the way, in the structure described above, since the annular deep circumferential groove g is formed between the outer wall d and the inner wall e, stress is concentrated near the bottom of the circumferential deep groove g during use, and the bottom part There was a problem that cracks appeared in the vicinity, shortening the life of the vibration-proof support.

Regarding this point, if the groove width of the circumferential deep groove g is increased, the above problem will be solved, but on the other hand, a new problem as described below will arise.

That is, as the groove width of the circumferential deep groove g increases, the outer diameter of the main body a inevitably increases due to the design, and as a result, the relationship between the deflection and the load in the direction perpendicular to the axis of the vibration isolating support increases in linearity. If the amount of displacement in the direction perpendicular to the axis is increased during an impact and it is used, for example, for mounting an engine, problems such as the engine swinging greatly and contacting peripheral equipment may occur.

Additionally, if the outer diameter of main body a is large, the spring constant in the axial direction of the anti-vibration support will increase, leading to a decrease in anti-vibration performance, so to compensate for this, the height of main body a in the axial direction is increased Therefore, it is necessary to increase the volume of the main body a and keep the spring constant small. However, if the volume of main body a is increased in this way,
Inevitably, the shape of the vibration isolating support becomes larger, further reducing stability.

The present invention has been made in view of such conventional problems, and it increases the groove width of the circumferential deep groove to reduce the stress generated near the bottom of the circumferential deep groove, which is the stress concentration area, and The purpose of the present invention is to provide a vibration-isolating support that has good vibration-isolating performance and stability despite an increase in the outer diameter of the main body due to an increase in the groove width.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The configuration of the present invention will be described below with reference to the drawings.

The anti-vibration support device according to the present invention is shown in FIG. 1, and the anti-vibration support device 1 is used as a set of two.
A cylindrical main body 2 made of an elastic material such as anti-vibration rubber,
It is composed of a metal bush 3 and an annular reinforcing member 4 made of a metal plate.

The bush 3 is fixed to the center hole 5 of the main body 2, and has a function as a spacer in the attached state, which will be described later. Further, on one side (lower side in FIG. 1) of the main body 2 in the axial direction, an annular external wall 6 is provided.
and an inner wall 7 are provided coaxially, the inner wall 7
is thinner than the outer wall 6, and the tip surface 9 of the inner wall 7 is substantially flush with the end surface 10 on one side of the bush 3, and is located more inward than the tip surface 11 of the outer wall 6 (see FIG. It is arranged so that it is located above the Note that the other end surface 12 of the bush 3
is substantially flush with the end surface 13 on the other side of the main body 2. Furthermore, the groove width l of the annular circumferential deep groove 14 formed between the outer wall 6 and the inner wall 7 and the size of the bottom portion 15 of the circumferential deep groove 14 in the solid line circle are determined by The settings are made so that stress will not concentrate and cracks will not occur.

The reinforcing member 4 is fixed to an end surface 16 on one side of the main body 2, and the reinforcing member 4 has an outer flange portion 4a fixed to the outer peripheral edge 17 of the main body 2 so as to protrude outward (in the direction perpendicular to the axis), and an outer wall. a cylindrical portion 4b fixed to the outer circumferential surface 18 of the outer wall 6; and an inner flange portion 4c fixed to the distal end surface 11 of the outer wall 6 so as to protrude inwardly (in the direction perpendicular to the axis).
It consists of In addition, the outer flange portion 4a and the cylindrical portion 4
The connecting portion with b has a substantially U-shaped cross section.

Note that the parts of the bush 3 and the reinforcing member 4 inside the dotted circle in FIG. . Moreover, the cylindrical part 4b
The ratio d/D of the cylinder diameter d and the outer diameter D of the main body 2 is 0.6 ~
It is set within the range of 0.85, with the optimum value being 0.65 to 0.75.

Next, a method for mounting a vehicle engine using the vibration-proofing support 1 will be described (see FIG. 2).

(i) Insert the external walls 6, 6 of the anti-vibration supports 1, 1 into the mounting holes 20 drilled in the mounting member (mounting board) 19 from the upper and lower sides, respectively, and insert the outer walls 6, 6 of the vibration isolating supports 1, 1, respectively, into the mounting holes 20 drilled in the mounting member (mounting board) 19. , 4 are brought into contact with each other.

(ii) Install the engine mounting stand 2 on the upper anti-vibration support 1.
1, the mounting base 21 and the vibration-proof supports 1, 1 are temporarily tightened with tightening bolts 22 and nuts 23. In this temporarily tightened state, only the inner flange portions 4c, 4c of the reinforcing members 4, 4 are in contact with each other, and the tip surfaces 9, 9 of the inner walls 7, 7 are separated from each other. In addition, 24, 25
is Watsiya.

(iii) Finally, tighten the tightening bolt 22 and nut 23.
are fully tightened until the end surfaces 9, 9 of the inner walls 7, 7, that is, the end surfaces 10, 10 of the bushes 3, 3 are in contact with each other. Leave it in a compressed state.

Next, FIG. 3 shows the relationship between the deflection of the vibration isolating support 1 according to the present invention (the product of the present invention) against static loads in the axial direction and the direction perpendicular to the axis (radial direction) in comparison with the conventional product shown in FIG. Shown below.

As is clear from Figure 3, the product of this invention is more
Compared to conventional products, it is softer and has a larger displacement near the rated load point, and has a smaller displacement at large load points.
This is the size of the bottom vicinity 15 of the circumferential deep groove 14,
In other words, the rubber wall thickness is larger than that of conventional products, and the projected surface area in the direction perpendicular to the axis of the main body 2 (tube diameter d and attached member 1
9) is larger than the conventional product, and despite the increased volume of the main body 2, the reinforcing member 4, especially the inner flange portion 4c, makes the main body 2
This is because the displacement is regulated at a large load point.
The effect of regulating the displacement of the main body 2 by the reinforcing member 4 is particularly excellent against displacement in the direction perpendicular to the axis (radial direction).

As detailed above, in the present invention, a reinforcing member is fixed to one side of a main body made of an elastic material, and the reinforcing member has an outer flange part fixed to the outer peripheral edge of the main body so as to protrude outward; Since it is composed of a cylindrical part fixed to the outer circumferential surface of the outer wall and an inner flange part fixed to the distal end surface of the outer wall so as to protrude inward, the function of regulating the displacement of the main body by the reinforcing member,
In particular, it has an excellent effect of regulating displacement in the direction perpendicular to the axis, and can increase the size of the vicinity of the bottom of the circumferential deep groove, which is the stress concentration part of the main body, and increase the projected surface area of the main body in the direction perpendicular to the axis. This provides various excellent effects as listed below.

(a) By increasing the size near the bottom, the life of the main body can be significantly improved. In other words, according to experiments, it is possible to reduce the local stress generated near the bottom, so the local shear strain in this area can be reduced by about 20% compared to the conventional one, and the fatigue life estimation formula below shows that the life expectancy is It turned out to be about 3 times as much.

N=(1000/γ) ⁵ {N: Fatigue life (Number of repeated cycles of load application (times) γ: Shear strain (%)} (b) The improvement in fatigue life mentioned above is based on the projection plane in the direction perpendicular to the axis of the main body. This can also be achieved by increasing the area of the reinforcing member 4. For example, in FIG.
If the cylinder diameter d of b is made 1.15 to 1.25 times that of the conventional product and the above projected surface area is increased by the same percentage, the stress in the direction perpendicular to the axis can be reduced by 13 to 20% compared to the conventional product.
Experiments have shown that this can be reduced.

(c) From the characteristics shown in Figure 3, a low-rigidity anti-vibration support can be obtained which has a small amount of displacement when a large external impact occurs and has good anti-vibration performance.

(d) Since the thickness of the external wall, that is, the radial thickness of the main body part that is inserted into the mounting hole of the mounted member can be increased, the axial height of the vibration isolating support can be made relatively low. , the stability when supporting an engine or the like can be increased.

[Brief explanation of drawings]

Embodiments of the present invention are illustrated in FIGS. 1 to 3, in which FIG. 1 is a longitudinal sectional view of a vibration isolating support, FIG. 2 is a longitudinal sectional view showing the installed state of the vibration isolating support, and FIG. The figure is a diagram showing the relationship between the static load and deflection of the vibration isolating support in the same installed state, and FIG. 4 is a longitudinal sectional view of the conventional vibration isolating support. DESCRIPTION OF SYMBOLS 1... Anti-vibration support, 2... Main body, 3... Bush, 4... Reinforcing member, 5... Center hole, 6... External wall, 7... Internal wall, 9... Tip surface (internal wall),
11... Tip face (external wall), 16... End face (main body), 17... Outer peripheral edge (main body), 18... Outer peripheral surface (external wall), 4a... Outer flange part, 4b... Cylindrical part , 4c...inner flange part.

Claims (1)

[Scope of utility model registration request] A metal bush is fitted into the center hole of a cylindrical body made of an elastic material, and an annular outer wall and an inner wall are coaxially provided on one side in the axial direction of the body,
The front end surface of the inner wall is substantially flush with the end surface on one side of the bush, and is located inwardly than the front end surface of the outer wall. A reinforcing member is fixed to the main body, and the reinforcing member includes an outer flange part fixed to the outer peripheral edge of the main body so as to extend outwardly, a cylindrical part fixed to the outer peripheral surface of the outer wall, and a tip end of the outer wall. A vibration-proof support comprising an inner flange portion which extends inwardly and is fixed to a surface.