JPS6361536B2 - - Google Patents

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, structures in which a rubber block is interposed between two mounting brackets have been used as vibration-proof supports for automobile body mounts, cab mounts, tension rods, strut bar cushions, etc. 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 can be sufficiently achieved. I couldn't satisfy it. 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 such demands, an elastic support body having a structure that utilizes the elasticity of rubber and the flow resistance of fluid has been proposed in Japanese Patent Application Laid-open No. 5376/1983. 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. With this, it was 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 vibrations in the direction perpendicular to that were limited. 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. This made its installation difficult, and its damping effect was also insufficient. In addition,
Such a fluid-filled elastic support body also has the problem that the spring constant ratio (lateral spring constant/vertical spring constant) cannot be kept large.

The present invention has been made in view of the above circumstances, and its main purpose is to improve a vibration isolation support that uses a fluid medium and has high damping characteristics. It is in.

Another object of the present invention is to utilize a fluid medium and its flow resistance between two chambers to
The object of the present invention is to provide a vibration-proof support that simultaneously exhibits low dynamic spring characteristics and high damping characteristics, while also being able to exhibit such performance in two orthogonal directions.

In order to achieve these objects, the present invention includes: (a) an inner cylindrical metal fitting having a flange portion extending laterally at one end in the axial direction, into which a predetermined mounting shaft is inserted; b) An outer cylinder having a flange portion which is arranged concentrically outside the inner cylinder metal fitting, and which is on the same side as the flange portion of the inner cylinder metal fitting and faces a predetermined distance in the axial direction. metal fittings and (c)
(d) an annular first elastic member disposed between the flange portion of the inner tube fitting and the flange portion of the outer tube fitting; and (d) opposing cylindrical portions of the inner tube fitting and the outer tube fitting. (e) a second elastic member disposed in between; and (e) located inside the annular shape of the first elastic member, mainly the first elastic member, the inner cylinder fitting, and the second elastic member. (f) a plurality of second chambers formed in the circumferential direction within the second elastic member; (g) the first chamber and the second chamber; and (h) a predetermined incompressible fluid sealed in the first chamber and the second chamber.

Therefore, in the case of a vibration-proof support with such a structure,
An effective damping effect can be exerted against the vibration in the axial direction by the elasticity of the first elastic member and the flow resistance of the fluid in the first chamber and the second space. In addition, vibrations applied from a direction perpendicular to the axis are handled by the elasticity of the second elastic member and the resistance to fluid flow between the plurality of second chambers communicated by the communication mechanism. As a result, an effective damping effect can be exerted. Furthermore, in addition to the damping effect on vibrations in two orthogonal directions, a damping effect in a composite direction of these two directions can also be naturally achieved. Since the spring constant can be made different by changing the material, the spring constant ratio (spring constant in the direction perpendicular to the axis/spring constant in the axis direction) is different from that of conventional fluid-filled vibration isolation supports. It became possible to make it larger than the body.

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, FIGS. 1 and 2 show an example of a cab mount which is a vibration-proof support according to the present invention. An inner cylindrical metal fitting 10 into which a bolt is inserted, and an outer cylindrical metal fitting 12 arranged outside the inner cylindrical metal fitting 10 at a predetermined distance apart.
, a rubber ring 14 as a first elastic member and a rubber sleeve unit 16 constituting a second elastic member, which are respectively arranged between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12, and the inner cylindrical metal fitting. 10 and the outer cylindrical fitting 12, from a predetermined incompressible fluid 22 filled in a first chamber 18 and a second chamber 20 formed by the rubber ring 14 and the rubber sleeve unit 16. , substantially consisting of.

More specifically, as shown in FIG. 3, the inner cylinder metal fitting 10 constituting the innermost cylinder of the cab mount is a cylinder body provided 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, and the large diameter portion 2
6, a medium diameter portion 28 extends toward the end opposite to the end where the flange portion 24 is provided, and a position slightly away from the large diameter portion 26 is provided in this medium diameter portion 28. A small diameter portion 30 having a predetermined length: 1 is provided at. In addition, the outer cylinder fitting 12
As shown in FIGS. 4 and 5, the is provided with a flange portion 32 extending laterally at one end in the axial direction thereof, and at a position slightly away from the flange portion 32, the outer circumferential surface of the A mounting bracket 34 is fixed 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.
A ring-shaped caulking metal fitting 38 is fixed to the end surface of 4 by vulcanization adhesive or the like. Further, an outer cylindrical ring 40 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, as shown in FIGS. 6 and 9, the rubber sleeve unit 16 consists of two divided bodies 16a and 16b that are axially divided into two parts, and both of these divided bodies have the same diameter. cylindrical rubber half parts 42a, 42b, inner cylinder half parts 44a, 44b and outer cylinder half parts 46a, 4 fixed to the inside and outside thereof by vulcanization adhesive or the like, respectively.
6b. Note that the inner cylindrical half portion 4 of one of the divided bodies 16a shown in FIG.
4a has a plurality of notches 4 at both ends in the axial direction, as shown in FIGS. 7 and 8.
8,50 are provided. In addition, each divided body 16
A plurality of second chamber halves 20a, 20b having approximately the same phase difference are provided at corresponding positions in the circumferential direction of the rubber halves 42a, 42b of the rubber halves 42a, 16b. Inside the rubber 42 (42a+42b) which becomes the second elastic member when the end faces in the axial direction are connected and are connected, there is a circumference surrounded in the radial direction by the inner cylinder 44 and the outer cylinder 46. A plurality of sealed second chambers 20 are formed separately in the direction.

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 the components shown in FIGS. 6 to 10 are assembled. The two divided bodies 16a and 16b form an outer cylindrical metal fitting that constitutes the component shown in FIGS. 4 and 5 in an incompressible fluid 22 such as water, polyalkylene glycol, silicone oil, or a low molecular weight polymer. The divided body 16a is press-fitted into the 12 cylindrical portions so that it is located on the flange portion 32 side, and then the other divided body 16b is inserted into the second chamber half portion 20a, which has an opening in each divided body.
20b are brought together and press-fitted. By this press-fitting operation, the second chamber half 2
0a and 20b 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 and 16b are each filled with an incompressible fluid 22.

Next, with respect to the divided bodies 16a and 16b press-fitted into the outer cylindrical fitting 12, the inner cylindrical fitting 10 shown in FIG. In this way, it is press-fitted. That is, the inner cylinder fitting 1
The middle diameter portion 28 of 0 is press-fitted into the inner cylindrical half portions 44a, 44b of each divided body 16a, 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 the communicating circumferential groove 52 is formed therein by the first inner cylindrical half 44a. It will be formed as shown in the figure and FIG. Further, the flange portion 24 of the inner cylinder metal fitting 10 is abutted on and accommodated in a caulking metal fitting 38, and the flange portion 24 is held liquid-tight by the caulking metal fitting 38 by caulking the caulking metal fitting 38. , the first chamber 18 is connected to the large diameter portion 26 of the inner cylindrical fitting 10 by the inner cylindrical fitting 10, the rubber ring 14, the divided body 16a, and the outer cylindrical fitting 12.
The first chamber 18, like the second chamber 20, is filled with an incompressible fluid 22 by being press-fitted in an incompressible fluid formed around the first chamber 18. Further, the first chamber 18 and the plurality of second chambers 20 formed in this way are provided in the divided body 16a, respectively, with respect to the communication circumferential groove 52 formed around the cylindrical part of the inner cylinder fitting 10. They are communicated by cutouts 48 and 50 at both ends. Therefore, the first 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.

Therefore, in the case of the cab mount having such a structure, when vibration as a load W is applied in the axial direction, the incompressible fluid 22 in the first chamber 18 is moved to the inner cylinder half as shown in FIG. Notch 48 of 44a
(first communication part), a communication circumferential groove 52 formed on the outer peripheral surface of the inner cylinder fitting 10, and a notch 50 (second communication part) in the inner cylinder half part 44a to move into the second chamber 20. The flow resistance during this movement effectively damps such vibrations, that is, vibrations in the low frequency range.
Here, since the outer cylindrical ring 40 is provided on the outer periphery of the rubber ring 14, outward deformation of the rubber ring 14 is effectively suppressed, and the first chamber 18 located inside thereof is effectively suppressed. It is now possible to effectively transform the Furthermore, with respect to 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, vibration noise in that region can be effectively reduced. is possible.

On the other hand, when vibration is applied in a direction perpendicular to the axial direction, that is, when a load W as shown by the arrow in FIG. 12 is applied, the second chamber 20 on the side to which the load is applied is deformed. The incompressible fluid 22 filled in the inner cylinder half 44a of the divided body 16a passes through the notch 50 of the inner cylinder half 44a, the communication circumferential groove 52, and again through the notch 50 of the inner cylinder half 44a to the other second chamber. 20
As a result, the low frequency vibrations W are effectively attenuated. Furthermore, when high frequency vibration is applied, the rubber sleeve unit 16 interposed between the inner cylinder 10 and the outer cylinder 12
(divided body 16a + divided body 16b) is damped by the elasticity of the rubber 42, a, b, and therefore, by selecting a rubber material that can withstand such high frequency vibration, the vibration noise can be reduced. It is possible to achieve a reduction in

In the cab mount having such a configuration, high-frequency vibrations and low-frequency vibrations in the axial direction are transmitted to both the flange portions 2 of the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12.
4, 32, as well as the elasticity of the rubber ring 14 provided between the first chamber 18 and the second chamber 2.
2 can be moved effectively through the notch 48, the communication 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. Furthermore, the vibration damping effect in two directions is further enhanced by the fact that each rubber part and each chamber attenuate the component forces of high-frequency vibrations and low-frequency vibrations from these combined directions.
As a whole, an effective damping effect can be exerted. 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. It has also become possible to increase the spring constant in the direction perpendicular to the center direction/spring constant in the axial direction.

In the above example, 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 may be provided. However, it is also possible to simply provide two second chambers 20, as shown in FIGS. 13 and 14, for example. 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. This 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 cab mount is actually attached to an automobile, in which a cab mount 6 according to the present invention is shown.
0 is assembled between the body member 62 and the frame member 64. That is, it is fixed to the frame member 64 via the mounting bracket 34 fixed to the outer peripheral surface of the outer cylinder metal fitting 12 constituting the cab mount 60, while the body member 62 is fixed to the body member 62. A penetrating mounting bolt 66 is inserted into the inner cylinder fitting 10 of the cab mount 60, and the stop member 6
It is assembled by tightening with a nut 70 via the screw 8. In addition, 72 in the figure
7 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;
4 is Watsusha.

Further, FIGS. 16 and 17 show an example in which the present invention is applied to a cushion used for attaching a tension rod to a suspension of an automobile, in which the cushion 76 according to the present invention is, as is known, In order to attach the tip of the tension rod 80 to a bracket 78 attached to a side member or cross member of the vehicle body, the two tension rods are combined and used as a pair. That is, as shown in FIG. 16, the tension rod 80 is inserted into the inner cylindrical fitting of each cushion 76 with its distal end portion touching the second chamber side end of each cushion 76. Natsuto 82
It is attached by tightening it. In addition, the cushion 76 illustrated here
Since this has the same structure as the cab mount shown earlier, similar parts will be given the same reference numerals and detailed explanation will be omitted. Of course, even with the cushion 76 having such a structure, the main load in the axial direction of the cushion 76 applied from the tension rod 80 can be effectively attenuated by the movement of fluid between the first chamber and the second chamber. ,
In addition to being able to significantly improve its damping characteristics, it is also possible to exhibit effective damping performance against vibrations in a direction perpendicular to the axial direction, as well as vibrations in a combination of these two 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 communicate 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, although it is desirable to install the outer cylindrical ring 40 disposed on the outer periphery of the rubber ring 14 as the first elastic material disposed between the flange portions of the inner cylindrical metal fitting and the outer cylindrical metal fitting, In some cases, the rubber ring 14 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. Furthermore, in the specific example illustrated, the flange portion 24 is fixed to one end of the inner cylinder fitting 10, and an integrally formed structure is adopted, but instead of this, the flange portion 24 is A structure that is separate from the inner cylindrical fitting 10, for example, a structure in which a flange forming member is attached to one end of the inner cylindrical fitting by caulking, fitting, etc., may also be adopted as appropriate. Needless to say.

[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 in the figure. Figures 3 to 1
Figure 0 shows the components of the cab mount shown in Figure 1, Figure 3 is a half-cut front view of the cylindrical metal fitting, and Figure 4 shows the outer cylinder metal fitting, rubber ring, bracket, and outer cylinder ring. A plan view of the included parts, FIG. 5 is a half-cut front view thereof, FIG. 6 is a longitudinal cross-sectional view of one of the divided bodies forming the rubber sleeve unit, FIG. 7 is a bottom view thereof, and FIG. 8 is used therein. A perspective view of a half of the inner cylindrical body, FIG. 9 is a longitudinal section of another divided body forming the rubber sleeve unit, FIG. 10 is a plan view thereof, and FIG. 11 is a diagram when vibration is applied in the axial direction. A cross-sectional half view corresponding to FIG. 1 for explaining the flow of incompressible fluid in
FIG. 12 is a diagram corresponding to FIG. 2 for explaining the flow of incompressible fluid when vibration is applied in a direction perpendicular to the axial direction, and FIG. 13 is a diagram corresponding to another embodiment of the present invention. Figure 1 corresponding to Figure 2 according to the embodiment
4 is a diagram for explaining the movement of the incompressible fluid in the embodiment of FIG. 13, and FIG. 15 is a diagram for explaining the movement of the incompressible fluid in the embodiment of FIG.
FIG. 16 is a cross-sectional view showing the mounted state of the cab mount shown in the figure, and FIG.
FIG. 17 is a cross-sectional view showing the attachment state of the cushion of the tension rod as an example, and FIG. 17 is a cross-sectional view taken 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: first chamber, 20: second chamber,
20a, 20b: second chamber half part, 22: incompressible fluid, 24: flange part, 26: large diameter part, 28: medium diameter part, 30: small diameter part, 32: flange part, 34:
Mounting bracket, 38: Caulking metal fittings, 40: Outer cylinder ring, 42, a, b: Rubber (half part), 44,
a, b: Interior cylinder (half part), 46, a, b: Exterior cylinder (half part), 48, 50: Notch, 52: Communication circumferential groove, 60: Cab mount, 62: Body member, 64: Frame member, 66: Mounting bolt, 7
6: Cushion, 78: Bracket, 80: Tension rod.

Claims (1)

[Scope of Claims] 1. An inner cylindrical metal fitting having a flange portion extending laterally at one end in the axial direction, into which a predetermined mounting shaft is inserted, and concentrically arranged on the outside of the inner cylindrical metal fitting. is,
and an outer cylindrical metal fitting having a flange part on the same side as the flange part of the inner cylindrical metal fitting and facing each other at a predetermined distance in the axial direction; a flange part of the inner cylindrical metal fitting and a flange part of the outer cylinder metal fitting; a second elastic member disposed between opposing cylindrical portions of the inner cylindrical fitting and the outer cylindrical fitting; and the first elastic member. a first chamber located inside the annular shape of and mainly surrounded by the first elastic member, the inner cylindrical fitting, and the second elastic member; and a first chamber formed within the second elastic member. , a plurality of separate second chambers arranged in the circumferential direction thereof, and a communication mechanism that allows the first chamber and the second chamber to communicate with each other, and allows the plurality of second chambers to communicate 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 metal fitting, a first communication portion that allows communication between the communication circumferential groove and the first chamber, and a communication circumferential groove and the first chamber. and a second communication portion that communicates with each of the second chambers, and the first chamber and all of the plurality of second chambers are simultaneously communicated with each other via the communication circumferential groove. The anti-vibration support according to scope 1. 3. A patent claim in which 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 that are respectively fixed to the outer circumferential surface and inner circumferential surface of the second elastic member. The anti-vibration support according to item 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. An axial length that is shorter than an inner cylindrical body portion of the divided body is provided on the outer circumferential surface portion of the inner cylindrical metal fitting where the divided body of the second elastic member that is press-fitted and placed on the first chamber side is located. wherein a small diameter portion is provided, a communication circumferential groove is formed by the small diameter portion and the inner cylinder portion, and a first communication portion that communicates the communication circumferential groove with the first chamber; A second communication portion is provided that communicates the communication circumferential groove with each of the second chambers, and the communication mechanism is formed by the communication circumferential groove and the first and second communication portions. A vibration-proof support according to claim 4, characterized in that: 6. Claims 1 to 5, characterized in that a member capable of preventing outward deformation of the first elastic member is provided on the outer periphery of the first elastic member.
The anti-vibration support described in any of paragraphs.