JPS6034544A - Fluid-filled mount - Google Patents

Abstract

PURPOSE:To contrive to improve the vibration isolating effect by a structure wherein the wall rigidity of an elastic member is made variable and the wall rigidity is heightened under the condition that the displacement of a mount is large in order to make exert much larger damping in low frequency region. CONSTITUTION:Umbrella-shape elastic members 4 and 7 with a thin annular plate member 6 therebetween are mounted between a base member 2 and a mounting member 9. A stopper 5, which prevents the elastic member 4 from deflecting beyond the predetermined value by abutting against an orifice plate 11 when a mount 1 displaces largely, is formed at the inner peripheral part of an elastic member 4 near the base member 2. Due to the structure as mentioned above, the high wall rigidity determined only by the elastic member 7 emerges under the condition that the displacement of the mount is large, resulting in obtaining much larger damping in low frequency region.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fluid-filled mount that is designed to increase the wall rigidity of an elastic member during large displacements while suppressing damping in a low frequency range.

A mounting member connected to the vibration source and a base SI on which the vibration source is mounted are coupled with an elastic member to form a fluid chamber inside, and the fluid chamber is further divided into two chambers by an orifice plate to apply damping force. A fluid-filled mount is known in which, when the orifice size is constant, the wall stiffness (kM) of the elastic member forming the main fluid chamber and the stiffness of the diaphragm forming the auxiliary fluid chamber (kn) When the ratio kM/kD is large, the loss coefficient (t, ]JIδ) of the mount, that is, the damping becomes thick, and the peak frequency range shifts to the lower frequency side.

When such a mount is applied to an engine mount, for example, damping in the low frequency range is increased in order to fully suppress engine displacement when the vehicle starts, accelerates and decelerates, but this increases the dynamic spring constant. , the vibration damping effect in other frequency ranges decreases, and there is also a tendency for the damping effect to decrease due to insufficient damping against body vibrations during high-speed driving.

In other words, damping during large displacement due to high load 7:
If the orifice size is determined by increasing the wall rigidity of the elastic member, the dynamic spring constant in the normal region will increase, leading to insufficient damping at small displacements and reducing the vibration allocation and vibration isolation effects. The problem is that it does.

The present invention has been made in view of the above circumstances, and its purpose is to:
When the displacement is small, the semi-rigidity of the elastic part has low damping, and when the displacement is large, the wall material properties of the elastic member are completely variable, and the high rigidity provides even greater damping in the low frequency range. Therefore, when used as a vehicle engine mount, for example, it provides damping in the body vibration region during high-speed driving, and also provides damping for starting and
To provide a fluid-injected mount that can provide greater damping for engine vibrations during large displacements of the mount such as acceleration and deceleration, thereby providing superior vibration damping and vibration-proofing effects.

In order to achieve all of these objectives, the present invention has all the orifice plates arranged on the base member side, and all the hollow elastic members are stacked in two or more stages in series between the mounting member and the paulownia base part, and the orifice plate is further arranged on the mounting member side. Two or more bulges are formed in the mount, and during the contraction behavior of the mount, the inner circumferential side of the hollow elastic part closer to the base member comes into contact with the stepped surface of the orifice plate. shall be.

Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 shows a round 14 of the first embodiment, in which a thick annular plate-shaped base portion 2 has a female tapered surface 3 formed from the upper surface to the inner circumference, and the female tapered surface 3 may have a rubber phase. The T portion of the elastic member 4 which is hollow at the end and has an umbrella shape is baked, and a stopper 5 is integrally formed to hang down from the upper inner periphery of the elastic member 4. A thin ring plate member 6 is baked on the upper surface thereof, and an umbrella-shaped elastic part γ is baked on the upper surface of the ring plate part 6, and a thin disk-shaped attachment is attached to the upper part of the elastic part 7. Part 9 is baked.

In addition, on the lower surface of the base part 2, there is an outer peripheral part 1 of a thin disc-shaped orifice plate 11 formed with a central disc part 12 bulged in one step on the left side.
The orifice plate 11 and the diaphragm 16 are superimposed on each other, and the peripheral edge 1γ of the diaphragm 16 is superimposed on the lower surface of the outer peripheral portion 14, and the cover plate 18, which is bulged downward, is superimposed on the lower surface of this peripheral edge 17. The cover plate 1-18 is assembled by fastening bolts 19 to the lower surface of the entire base member 2 from below.

In this embodiment, the upper fluid chamber S1 and the lower diaphragm chamber S2 defined by the orifice plate 11 are filled with liquid.

In the above-described fluid-filled mount 1, the central disk portion 12 of the orifice plate 11, which is bulged in one step upwardly, that is, on the side of the mounting portion phase 9, is formed with a diameter that allows the stopper 5 to come into contact with it from above. In the free state, the central disc part 1
2 and the stopper 5 are sufficiently spaced apart from each other in the downward direction.

The effect when applied to the arrow engine mount will be described.

First, during normal small O displacement vibrations such as body vibrations during high-speed running, the stopper 5 is spaced upward from the central disk portion 12 of the orifice plate 11, and is stopped by the elastic members 4 and 7 stacked in two stages in series. Since its quasi-rigidity is low, J: redamping can be obtained in the damping force by the orifice 13, and good vibration damping and vibration isolation effects can be obtained.

On the other hand, during the large displacement vibration of the engine during starting, acceleration and deceleration of the vehicle in the low frequency range, the second
As shown in the figure, the stopper 5 first comes into pressure contact with the central disk portion 12 of the orifice plate 11, and in the further contraction process, the ring plate member 6
The lower elastic member 4 becomes almost rigid as it is pressed against it, and only the elastic member 1 forms the upper fluid fund, resulting in a high quasi-rigidity due only to the elastic part 7.1. Larger damping can be obtained in the lower frequency range, and engine displacement can be strongly suppressed.

Therefore, according to the mount of the present invention, it is possible to obtain greater damping during large displacements without increasing the quasi-rigidity of the elastic member itself as in the past, and at the same time, during normal small displacements, the two stages in series with the orifice 13 can be obtained. Elastic members 4, 7
Due to the low quasi-rigidity, the desired good damping can be sufficiently obtained, and vibration damping and vibration isolation effects can be obtained.

This? If expressed as a frequency (f)-loss coefficient (tan δ) characteristic diagram, it is as shown in FIG. In other words, characteristic A shows the characteristic when the displacement is large, and characteristic opening shows the characteristic when the displacement is small.From this characteristic diagram, the peak frequency range of characteristic A is in the low frequency range IUl+v.
It can be seen that the peak frequency range of the characteristic mouth is on the more delicious normal frequency range side, and the peak of the characteristic mouth is also larger than that of the characteristic mouth. Let me paraphrase! 1. The characteristic peak of the normal two-stage series elastic members 4 and 7 can be shifted to the lower frequency range side by the upper elastic member 7, and the peak value can be completely increased. .

In addition, the frequency (f) - dynamic spring constant (g) characteristic diagram is as shown in Figure 4, and the characteristic 2 only at the time of large displacement is large 1 without increasing the characteristic 2 at the time of normal small displacement. : I can understand.

The stopper 5 formed on the upper inner periphery of the lower elastic paulownia portion 4 may be provided in a continuous ring shape in the circumferential direction, or may be provided in a plurality intermittently.

Incidentally, in the above embodiment, the hollow elastic members are stacked in two stages, but it is also possible to stack them in three or more stages, as in the second embodiment shown in FIG. 5 as a half-cut section of the main part.

That is, the inner diameter of the hollow elastic part 42 is further reduced by interposing the monkey plate member 61 on the upper surface of the lower tier hollow elastic part 41 which has a stopper 51 formed on the inner periphery of the upper part. Laminated and glued? 1 (A stopper 52 is integrally formed on the inner periphery of the upper part of the sexual part 42, and an annular plate part 62 having a smaller inner diameter than the above is interposed on the upper surface of the elastic part 42, which includes the entire stop flange 52. Then, a hollow elastic part 43 with a smaller inner diameter 7 and a wider end 9 is stacked, and a stopper 53 is formed hanging integrally with the tray on the upper inner periphery of this elastic part 43, and a ring plate member 63 is formed in the same way. The uppermost hollow elastic member 71 is stacked.

The orifice plate 111 is formed to bulge out in three stages entirely above the center, with the first large-diameter annular step 121 facing below the bottom stopper 51, and the next annular step 122 in the same way. Let's look at the -F side of the stopper 52 on the tier, and then the orifice on the top tier? The central disc portion 123 facing below the third stage stopper 53.

In the second embodiment, in the free state of the mount, the clearance c1 between the first annular step 121 of the orifice plate 111 and the stopper 51, and the clearance c1 between the surface of the next annular step 122 and the stopper 52. The clearance C2 and the clearance c3 between the surface of the uppermost central disk portion 123 and the stopper 53 are set as C+<C2<C3, and the stopper 51 is configured to contact the orifice plate 111 side in order from the lower stopper 51.

If the elastic strips are stacked in series in three or more stages (four stages in this second embodiment) in this way, the wall material will have extremely low properties against normal minute displacements, and will exhibit shrinkage behavior due to large displacements. In the process,
The wall rigidity can be increased sequentially to 2 or more stages (3 stages in this embodiment) by contact with the stepped surface of the orifice plate.Also in the 6-section embodiment, a stopper is provided on the inner periphery of the elastic member. Of course, the general girder may be constructed so that the stepped surface of the orifice plate directly contacts the inner periphery of the elastic portion (2) to act as a stopper.

As is clear from the above description, according to the present invention, two or more stages of hollow elastic parts are stacked in series (ICs) between the mounting member and the base member, and the orifice plate arranged on the base member iM is connected to the mounting part similar to the other. The structure is such that the inner peripheral side of the hollow elastic member closer to the base comes into contact with the step surface of the A-rifice plate during the shrinking behavior of the mount. Without increasing the spring constant, it provides damping due to the low wall stiffness of the elastic part for small displacements, while increasing the wall stiffness of the elastic part for large displacements to achieve even greater damping in the lower frequency range. It has many advantages such as:

[Brief explanation of the drawing]

Fig. 1 is a central vertical cross-sectional view of the mount according to the first embodiment, Fig. 2 is a similar diagram showing its operation, Fig. 3 is a frequency-loss coefficient characteristic diagram, and Fig. 4 is a frequency-dynamic spring. The constant characteristic diagram and FIG. 5 are half-cut sectional views of essential parts of the mount according to the second embodiment. In the drawings, 1 is a fluid-filled mount, 2 is a base member, and 4.
γ, 41... and γ1 are hollow elastic members, 5°51.
. . . is a stopper, 6, 61 . S2 is a fluid chamber. Patent Applicant Honda Motor Co., Ltd. Agent Patent Attorney 2 1) Production Department Patent Attorney Kuni Ohashi Production Volume Patent Attorney Yu Koyama

Claims (1)

[Claims] A mounting member connected to the vibration source, a base member for mounting the vibration source, and an elastic member are combined to form a fluid chamber inside, and the fluid chamber is connected to the orifice plate! In a fluid control system consisting of 72 chambers, an orifice plate is arranged on the base member side, two or more hollow elastic members are stacked in series between the mounting member and the base member, and the contraction behavior of the cough mount is improved. A fluid-filled mount characterized in that, in the process, the inner peripheral side of the hollow elastic member closer to the base member is bulged in one or more steps toward the side of the entire orifice plate mounting area so that the inner peripheral side of the hollow elastic member closer to the base member comes into contact with the orifice plate.