JPS5937349A - Vibration preventing support - Google Patents

Abstract

PURPOSE:To provide an effective damping effect by elasticity of a first elastic member and flow resistance of fluid between a first chamber and a second chamber and elasticity of a second elastic member and flow resistance of fluid between a plurality of second chambers. CONSTITUTION:When vibration as a load W is applied axially, non-compressive fluid 22 in a first chamber 18 moves into a second chamber 20 through a notch 48, a communicating peripheral groove 52 and a notch 50 so that the vibration in low frequency region is effectively damped by flow resistance in the movement of the fluid. When vibration in the direction perpendicular to the axial direction, i.e., a load W is applied, the second chamber 20 at the side to which the load is applied is deformed and the non-compressive fluid 22 moves into another second chamber 20 so that the low frequency vibration W is satisfactorily damped.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibration-isolating support, which can exhibit effective damping characteristics at the same time, particularly against low-frequency vibrations and high-frequency vibrations; The present invention relates to a vibration isolating support that can also be exerted in a direction perpendicular to the axial direction.

Conventionally, a structure in which a rubber block is interposed between two mounting brackets has been used as a vibration-proof support for automobile body mounts, cab mounts, tension rods, strut bar cushions, etc. However, when rubber with a low dynamic spring constant is used to reduce vibration noise in the high frequency range, the loss coefficient of the rubber is small, so the damping coefficient becomes small, and therefore the characteristics required for such a vibration isolating support are reduced. could not be fully satisfied.

This is because such a vibration-proof support is required to have high damping characteristics to reduce vibration in the low frequency range and low dynamic spring characteristics to reduce noise in the high frequency range. .

On the other hand, in order to meet this demand, an elastic support body with a structure that utilizes the elasticity of rubber and the flow resistance of fluid was developed in Japanese Patent Laid-Open No.
This method has been proposed in Publication No. 5376 and the like. This fluid-filled elastic support has damping properties due to the damping effect due to the elasticity of the rubber as well as the flow resistance effect caused by the fluid passing through the small holes that communicate two separately formed spaces. This made it possible to achieve low dynamic spring characteristics and high damping characteristics, but due to its structure, the damping characteristics were limited to one direction, and the damping characteristics were limited to vibrations in a direction perpendicular to that direction. However, there was a major problem in that the damping effect was insufficient. Therefore, in order to exert a damping effect in two orthogonal directions using such fluid-filled elastic supports, it is necessary to use two of them as a set and arrange them at an angle. 5. Installation was difficult, and its damping effect was insufficient. In addition, in such a fluid-filled elastic support, the spring constant ratio (lateral spring constant/
There is also the inherent problem that the vertical spring constant cannot be made large.

The present invention has been made in view of the above circumstances, and its main purpose is to provide a vibration isolation support having high damping characteristics using a fluid medium.
The aim is to improve this.

Another object of the present invention is to simultaneously exhibit low dynamic spring characteristics and high damping characteristics by using a fluid medium and utilizing the flow resistance in its two spaces, while also achieving such performance by orthogonally spaced two spaces. It is an object of the present invention to provide a vibration-proof support that can exhibit vibration in various directions.

In order to achieve these objects, the present invention includes: (a) an inner cylindrical metal fitting having an extended hill flange portion on the side at one end in the axial direction, into which a predetermined mounting shaft is inserted; (1)) Located on the outside of the inner cylindrical metal fitting and arranged concentrically, the eye is located on the same side as the flange part of the inner cylindrical metal fitting and is opposed to it at a predetermined distance in the axial direction. (c) an annular first elastic member disposed between the flange portion of the inner tube fitting and the flange portion of the outer tube fitting; a second elastic member disposed between the cylindrical fitting and the opposing cylindrical portions of the outer cylindrical fitting, and (e) the first elastic member 4', located inside the annular shape of A, and a first chamber surrounded by a second elastic member, the inner cylindrical fitting, and the second elastic part H;
(f) a plurality of second chambers formed in the circumferential direction of the second elastic member; (g) a communication mechanism that allows the first chamber and the second chamber to communicate with each other; ))) The vibration isolating support is configured to include a predetermined incompressible fluid sealed in the first chamber and the second chamber.

Therefore, in the vibration-proof support having such a structure, vibrations in the axial direction can be prevented by the elasticity of the first elastic member and the fluid flow resistance between the first chamber and the second chamber. Therefore, an effective damping effect can be exerted, and the elasticity of the second elastic member and the plurality of elastic members connected by the communication mechanism are effective against vibrations applied from the direction perpendicular to the axis. An effective damping effect can be exerted by the fluid flow resistance between the second chambers.

Furthermore, in addition to the damping effect of damping vibrations in two orthogonal directions, a damping effect in a composite direction of these two directions can also be naturally achieved. The spring constant ratio (spring constant in the direction perpendicular to the center/
It has become possible to make the spring constant (center direction spring constant) smaller than that of the conventional fluid-filled vibration isolating support.

EMBODIMENT OF THE INVENTION Hereinafter, in order to clarify the present invention more specifically, several embodiments according to the present invention will be described in detail based on the drawings.

First, FIG. 1 and FIG. 2 show an example of a cab mount which is a vibration-proof support according to the present invention. , an inner cylindrical metal fitting 1o into which the mounting bolt is inserted, an outer cylindrical metal fitting 12 disposed outside thereof at a predetermined distance, and an inner cylindrical metal fitting 10 disposed between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12, respectively. A rubber ring 14 as a first elastic member, a rubber sleeve unit 16 as a second elastic member, an inner cylindrical fitting 10 and an outer cylindrical fitting 12.
between the rubber ring 14 and the rubber sleeve unit 1.
6 and a predetermined incompressible fluid 22 filled in the second chamber 20.

More specifically, as shown in FIG. 3, the inner cylinder metal fitting 10 constituting the innermost cylinder of the cab mount is a cylinder equipped with a flange portion 24 extending laterally at one end in the axial direction. A large diameter portion 26 is provided with a predetermined length on the flange portion 24 side in the cylindrical outer peripheral portion thereof, and an end portion following the large diameter portion 26 and provided with the flange portion 24. A medium diameter portion 28 extends toward the opposite end, and a small diameter portion 30 having a predetermined length l is provided in this medium diameter portion 28 at a position slightly apart from the large diameter portion 26. ing. Further, as shown in FIGS. 9-4 and 5, the outer cylindrical fitting 12 is provided with a flange portion 32 extending laterally at one end in the axial direction, and the flange portion 32 is slightly spaced apart from the flange portion 32. At this position, a mounting bracket 34 is fixed to the outer peripheral surface by welding or the like.

Note that a suitable number of mounting bolt holes 36 are provided through the bracket 34. A rubber ring 14 of a predetermined thickness is fixed concentrically to the outer surface of the end flange portion 32 of the outer cylinder fitting 12 by vulcanization adhesive or the like, and a ring-shaped caulking is further attached to the end surface of the rubber ring 14. Metal fittings 38
is fixed by vulcanization adhesive or the like. Further, an outer cylindrical ring 4o is embedded in the outer peripheral portion of the rubber ring 14, and is configured to prevent the rubber ring 14 from deforming outward.

Furthermore, the rubber sleeve unit 16 is shown in FIGS.
As shown in the figure, it consists of two divided bodies 16a and 16b divided into two in the axial direction, and each of these divided bodies has a cylindrical rubber half part 42a and 42b of the same diameter, and an inner side thereof. and an inner cylindrical body half 4 fixed to the outside by vulcanization adhesive or the like.
4a, 4411 and an exterior cylindrical half portion 46a, 461). Note that the inner cylindrical half portion 44a of one of the divided bodies 16a shown in FIG. 6, that is, the one located on the side of the flange portion 24 of the inner cylindrical fitting 10 and the flange portion 32 of the outer cylindrical fitting 12, is shown in FIG. As shown in FIG. 8, a plurality of notches 48.degree. 50 are provided at both ends in the axial direction. In addition, each divided body 16a
.

A plurality of second chamber halves 20a, 201) having approximately equal phase differences are provided at corresponding positions in the circumferential direction of the rubber halves 42a, 4211 of 16b, and these divided bodies 16a, 161) Rubber 42 (42a+4
2b), a plurality of separately sealed second chambers 20 are formed in the circumferential direction and are surrounded in the radial direction by the inner cylinder 44 and the outer cylinder 46.

When assembling the cab mount according to the present invention as shown in FIGS. 1 and 2 using the components shown in FIGS. 3 to 10, first, assemble the cab mount shown in FIGS. 6 to 10. The two divided bodies 16a, , 1G+), which are separated from each other in FIG.
The divided body 16a is press-fitted into the cylindrical part of the outer cylindrical metal fitting 12 constituting the component shown in FIG.
b is the second chamber half 20a with the opening of each divided body.

201] and press them together. By this press-fitting operation, the second chamber halves 2Qa, 2Q
b are combined to form one second chamber 20, and this second chamber 20 is formed with a predetermined phase difference in the circumferential direction. The three second chambers 20 formed by press-fitting the divided bodies 16a, 161) are each filled with an incompressible fluid 22.

Next, the divided body 16a is press-fitted into the outer cylinder fitting 12.
, 16b, the inner cylinder fitting 10 shown in FIG.
However, the flange 24 is connected to the flange portion 3 of the outer cylinder fitting 12.
It will be press-fitted so that it is located on the 2nd side and then it will be wetted. That is, the middle diameter portion 28 of the inner cylinder fitting 10 is divided into each divided body 16a,
It is press-fitted into the inner cylindrical half portions 44a, 441) of 16b. By press-fitting the inner cylindrical fitting 10, the outside of the small diameter portion 30 of the inner cylindrical fitting 10 is surrounded by the inner cylindrical half portion 44a of the divided body 16a, and a communicating circumferential groove 52 is formed therein as shown in FIGS. It will be formed as shown in the figure. Further, the flange portion 24 of the inner cylinder metal fitting 10 is in contact with and accommodated in the caulking metal fitting 38, and this caulking metal fitting 3
8 is caulked and the flange portion 24 is attached to the caulking metal fitting 38.
By holding the inner cylindrical fitting 10 liquid-tightly,
A first chamber 18 is formed around the large diameter portion 26 of the inner tube fitting 10 by the rubber ring 14, the divided body 16a, and the outer tube fitting 12, and the inside of the first chamber 18 is formed by press fitting in an incompressible fluid. Similarly to the second chamber 20, the chamber is filled with an incompressible fluid 22. Moreover, the second chamber 18 and the plurality of second chambers 20 formed in this way are each divided into separate bodies with respect to the communication circumferential groove 52 formed around the cylindrical -13= part of the inner cylindrical fitting 10. Notches 48.5 at both ends provided in 16a
They are connected by 0.

Therefore, the second chamber 18 is communicated with each of the second chambers 20 via the communication circumferential groove 52, and a plurality of (three in this case) second chambers 20 are also communicated with each other through the communication circumferential groove 52.
They are communicated via 2.

Therefore, in a cab mount having such a configuration, the first
As shown in FIG. 1, when a vibration as a load W is applied in the axial direction, the incompressible fluid 22 in the first chamber 18 moves through the notch 48 (first communication section) of the inner cylinder half 44a, The second chamber 2 is connected to the second chamber 2 through the communication circumferential groove 52 formed on the outer peripheral surface of the inner cylinder fitting 10 and the notch 50 (second communication part) of the inner cylinder half part 44a.
0, and due to the flow resistance during this movement, such vibrations, that is, vibrations in the low frequency range, are effectively damped.

Here, since the outer cylindrical ring 40 is provided on the outer periphery of the rubber ring 14, the outward deformation of the rubber ring 14 is effectively suppressed, and The deformation of the chamber 18 can now be carried out effectively. Furthermore, for high-frequency vibrations in the axial direction, by using a rubber material having an appropriate dynamic spring constant as the rubber material constituting the rubber ring 14, it is possible to effectively reduce vibration noise in that region. It is.

On the other hand, the vibration in the direction perpendicular to the axial direction, that is, the 12th
When a load W as shown by the arrow in the figure is applied, the second chamber 20 on the side to which the load is applied is deformed, and the incompressible fluid 22 filled therein is transferred to the inner cylinder of the divided body 16a. It moves into the other second chamber 20 through the notch 50 of the body half 44a, the communication circumferential groove 52, and again through the notch 50 of the inner cylindrical body half 44a, whereby the low frequency vibration (W) is well suppressed. This results in attenuation. Furthermore, when high-frequency vibration is applied, the elasticity of the rubber 42 (a, I) constituting the rubber sleeve unit 16 (divided body 16a and fully divided body 16b) interposed between the inner cylinder 10 and the outer cylinder 12 Therefore, by selecting a rubber material that is resistant to such high-frequency vibrations, it is possible to reduce the vibration noise.

In this way, in a cab mount with such a configuration,
High-frequency vibrations and low-frequency vibrations in the axial direction cause the inner cylinder metal fitting 10 to
Together with the elasticity of the rubber ring 14 provided between the 7 flange portions 24 and 32 of the outer cylinder fitting 12, the movement of the compressible fluid 22 between the first chamber 18 and the second chamber This can be carried out effectively through the circumferential groove 52 and the notch 50 with a predetermined flow resistance.
In addition, in the direction perpendicular to the axis, the high-frequency vibrations and low-frequency vibrations are caused by the elasticity of the rubber 42 in the rubber sleeve unit 16, as well as by the notches 50 between the plurality of second chambers 20 and the communication circumferential grooves. 52 and the notch 50, the flow resistance of the incompressible fluid 22 can be effectively damped. Moreover, the vibration damping effect in these two directions is also effective as a whole, as each rubber part and each chamber attenuate their respective component forces against high-frequency vibrations and low-frequency vibrations from those combined directions. It is possible to exert a damping effect. In addition,
Since the rubber materials of the rubber ring 14 and the rubber sleeve unit 16 can be provided separately, the dynamic spring constants of these rubber materials can be appropriately selected. This also made it possible to increase the spring constant in the perpendicular direction/spring constant in the axial direction.

In addition, on the upper side, the number of second chambers 20 provided in the rubber sleeve unit 16 is three, but the present invention is by no means limited to this, and generally a plurality of second chambers 20 are provided. However, for example, FIGS. 13 and 14
As shown in the figure, it is also possible to provide only two second chambers 20.

In addition, in the case where there are two second chambers 20, unlike the case where there are three second chambers 20 as in the previous example, where vibrations from all directions perpendicular to the axis are damped, the vibrations are simply damped as shown in FIG. 17-, which becomes effective only when vibration is applied as a load W in the direction of the arrow.

Further, FIG. 15 shows a state in which the above-mentioned exemplary cab mount is actually attached to an automobile, in which a cab mount 60 according to the present invention is assembled between a body member 62 and a frame member 64. It is.

That is, it is fixed to the frame member 64 via the bracket 34 fixed to the outer peripheral surface of the outer cylindrical metal fitting 12 constituting the cab mount 60, while the body member 62 is fixed to the body member 62. A mounting bolt 66 passing through the hole 62 is inserted into the inner cylindrical metal fitting 10 of the cab mount 60, and then the nut 70 is inserted through the stopper member 68.
It is assembled by tightening it. In addition, in the figure, 72 is a stopper fixed to and formed on the stopper member 68 so as to face the end surface of the outer cylinder fitting 12, and 74 is a washer.

Further, FIGS. 16 and 17 show an example in which the present invention is applied to a cushion used when attaching a tension rod of an automobile suspension, and the cushion 76 according to the present invention is used in a well-known manner. 1. In order to attach the tip of the tension rod 80 to the bracket 78 attached to the side member or cross member of the vehicle body, two of the tension rods 80 are combined and used as a pair. That is, as shown in FIG. 16, each cushion 76 is disposed such that the tip end of the tension rod 80 abuts the second chamber side end of each cushion 76.
It is inserted into the inner cylindrical metal fitting of the cylindrical member and is attached by tightening with a nut 82. In addition,
Since the cushion 76 illustrated here has a similar structure to the cab mount shown above, similar parts will be denoted by the same reference numerals and detailed explanation will be omitted. Of course, even if the cushion 76 has such a structure, the cushion 76 applied from the tension rod 80
The main axial load of the is effectively damped by the movement of fluid between the first and second chambers, and its damping characteristics can be significantly improved, as well as vibrations in the direction perpendicular to the axis. Furthermore, it is possible to exhibit effective damping performance against vibrations from those two joining directions.

Although various embodiments of the vibration isolation support according to the present invention have been described above, the present invention is by no means limited to only these illustrative embodiments, and the present invention It goes without saying that various changes and modifications can be made to the.

For example, in the previous example, the structure is such that the first chamber and the second chamber as well as a plurality of second chambers are communicated with each other at the same time via the communication circumferential groove, but the communication between the first chamber and the second chamber and the It is also possible to provide communication between the two chambers separately, and the communication circumferential groove can be provided not only on the inner cylindrical metal fitting but also on the outer cylindrical metal fitting side. Further, an outer cylinder ring 4 is arranged on the outer periphery of a rubber ring 14 as a first elastic material arranged between the seven rungs of the inner cylinder metal fitting and the outer cylinder metal fitting.
Although it is desirable to install the rubber ring 0, there are cases where it is not provided, and it is also possible to have a structure in which it is in contact with the outer peripheral surface of the rubber ring 14 as a belt-like band.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of a cab mount according to an example of the vibration-proof support according to the present invention, and FIG.
■It is a sectional view. 3 to 10 each show the components of the cab mount shown in FIG. 1,
Fig. 3 is a half-cut front view of the cylindrical fitting, Fig. 4 is a plan view of parts including the outer cylindrical fitting, rubber ring, bracket, and outer cylindrical ring, Fig. 5 is a half-cut front view thereof, and Fig. 6 is a A longitudinal sectional view of one of the divided bodies forming the rubber sleeve unit,
Fig. 7 is a bottom view thereof, Fig. 8 is a perspective view of a half of the inner cylindrical body used therein, Fig. 9 is a vertical sectional view of another divided body forming the rubber three-7'' unit, and Fig. 10. is a plan view of the same, Fig. 11 is a half-section cross section corresponding to Fig. 1 for explaining the flow of incompressible fluid when vibration is applied in the axial direction, and Fig. 12 is a cross-sectional view in the axial direction. 13 is a diagram corresponding to FIG. 21 for explaining the flow of an incompressible fluid when vibration in a right angle direction is applied, and FIG. 13 is a diagram corresponding to FIG. 2 according to another embodiment of the present invention. Figure 14 corresponds to Figure 13.
FIG. 15 is a cross-sectional view showing how the cab mount shown in FIG. 1 is attached, and FIG. 16 is a vibration-proof 17 is a cross-sectional view showing a state in which a cushion of a tension rod, which is an example of a support body, is attached, and FIG. 17 is a cross-sectional view taken along the line ■-X■ in FIG. 16. 10: Inner cylinder metal fitting 12: Outer cylinder metal fitting 14: Rubber ring 16: Rubber sleeve unit 16a, 16b: Divided body 18: -th chamber, 20: Second chamber 2OA, 20b: Second chamber and a half! 22: Incompressible fluid 24: Flange portion 26: Large diameter portion
28: Medium diameter part 30: Small diameter part 32: Flange part 34: Mounting bracket 38: Caulking metal fittings 40: Outer cylinder ring 22- 42 (a, b): Rubber (half part) 44 (a, b): Inner cylinder Body (half part) 46 (11, b): Exterior cylinder body (half part) 48.50: Notch 52: Communication circumferential groove 60: Gab mount 62: Body member 64: Frame member
66: Mounting bolt 76: Cushion 78 Bracket 80: Tension rod Applicant Tokai Rubber Industries Co., Ltd. 23- Figure 5 Figure 13 Figure 14 Figure 4a Figure 15

Claims (6)

[Claims] (1) An inner cylindrical metal fitting having seven rungs extending laterally at one end in the axial direction, into which a predetermined mounting shaft is inserted; , and an outer cylindrical metal fitting having a 7-rung portion on the same side as the 7-rung portion of the inner cylindrical metal fitting and facing each other at a predetermined distance in the axial direction; and the 7-lung portion of the inner cylindrical metal fitting and the outer cylinder. a first annular elastic member disposed between the seven rung portions of the metal fitting; a second elastic member disposed between opposing cylindrical portions of the inner cylindrical fitting and the outer cylindrical fitting; a first chamber located inside the annular shape of the first elastic member and mainly surrounded by the second elastic member, the inner cylindrical fitting, and the second elastic member; A plurality of separate second chambers formed within the member and disposed in the circumferential direction thereof, the first chamber and the second chamber being in communication with each other, and the plurality of second chambers being arranged in the circumferential direction thereof. A vibration isolating support comprising: a communication mechanism that communicates with each other; and a predetermined incompressible fluid sealed in the first chamber and the second chamber. (2) The communication mechanism includes a communication circumferential groove formed on the outer circumferential surface of the inner cylindrical fitting, a first communication portion that communicates the communication circumferential groove with the first chamber, and a communication circumferential groove. A patent that includes a second communication portion that communicates with each of the second chambers, and allows the first chamber and all of the plurality of second chambers to communicate with each other at the same time via the communication circumferential groove. A vibration-proof support according to claim 1. (3) The second elastic member is press-fitted between the outer cylindrical metal fitting and the inner cylindrical metal fitting via an outer cylindrical body and an inner cylindrical body fixed to the outer circumferential surface and inner circumferential surface of the second elastic member, respectively. A vibration-proof support according to claim 1. (4) The second elastic member having the outer cylindrical body and the inner cylindrical body has a structure in which it is divided into two in the axial direction, and the plurality of second chambers are connected to the second elastic member by connecting the divided parts. 4. The vibration isolating support according to claim 3, which is surrounded in the radial direction by the outer cylindrical body and the inner cylindrical body and formed separately in the circumferential direction within the elastic member. (5) On the outer circumferential surface portion of the inner cylindrical fitting where the divided body of the second elastic member that is press-fitted and arranged on the first chamber side is located, an axial direction shorter than the inner cylindrical body portion of the divided body is provided. A first communication portion is provided in the length, and a communication circumferential groove is formed by the small diameter portion and the inner cylindrical body portion, and a first communication portion that communicates the communication circumferential groove with the first chamber; A second communication portion is provided for communicating the communication circumferential groove and each of the second chambers, and the communication mechanism is formed by the communication circumferential groove and the first and second communication portions. The vibration isolating support according to claim 4. (6) A member capable of preventing outward deformation of the first elastic member is provided on the outer periphery of the second elastic member. The anti-vibration support according to any of Item 5.