JPS63195442A - Fluid sealed type vibro-isolating bush - Google Patents

Abstract

PURPOSE:To satisfactorily damp a low-frequency and large-amplitude vibration input in the diametric direction, by providing a protruding member in the first fluid chamber while a flange part forms a predetermined clearance between wall surfaces of the corresponding fluid chambers. CONSTITUTION:A mount eccentrically arranges an inner cylinder metal fixture 10 and an outer cylinder metal fixture 12 by a predetermined distance in the diametric direction of the mount to be elastically connected by a circular arc- shaped rubber elastic unit 14 mounted interposing between these inner and outer cylinder metal fixtures. While the mount, which forms a pocket part 20 inside, seals fluid chambers 34, 36 containing non-compressible fluid. And if a low-frequency vibration is input in the opposed direction of the fluid chamber 34 to space 16, the mount, in which the fluid in the fluid chambers 34, 36 communicates through an orifice passage 38, damps the input vibration of low frequency and large amplitude corresponding to a tuning frequency of the orifice passage 38.

Description

Detailed Description of the Invention (Technical Field) The present invention relates to a fluid-filled anti-vibration bushing, particularly in the radial direction (
The present invention relates to a fluid-filled vibration-isolating bushing that can exhibit good vibration-isolating effects against both low-frequency vibrations and high-frequency vibrations that are input in the axially perpendicular direction.

(Prior art) A bushing-type vibration-proofing support (vibration-proofing bushing) that is installed in a vibration system of an automobile, etc. is designed to attenuate or block vibrations that are mainly input in the radial direction. There is something I did. Examples include suspension bushings for automobiles and cylindrical engine mounts for FF (front engine/front drive) cars.

By the way, such a vibration-proof bushing is required to exhibit good damping characteristics against low-frequency, large-amplitude vibrations that are input in the radial direction, while it is also required to exhibit good damping characteristics against high-frequency, small-amplitude vibrations. However, in conventional anti-vibration bushings, the anti-vibration function against these input vibrations was obtained solely based on the elastic deformation of the rubber elastic body. Therefore, it is difficult to satisfy these requirements at the same time, and there is a problem in that a sufficient damping effect cannot be obtained particularly for low frequency and large amplitude vibrations.

On the other hand, in recent years, (a) an inner cylinder member, and (b)
an outer cylinder member disposed concentrically or eccentrically on the outside of the inner cylinder member; (c) a rubber elastic body interposed between the inner cylinder member and the outer cylinder member to connect them; (
d) a first fluid chamber formed by fluid-tightly closing an opening of a pocket provided in the rubber elastic body with the outer cylinder member, and the first fluid chamber and a predetermined throttle passage; and a second fluid chamber communicated through the inner cylinder member and the outer cylinder member, based on which a predetermined incompressible fluid sealed in the fluid chambers flows mutually through the throttle passage. a fluid flow mechanism that damps or blocks vibrations in the radial direction of the bushing input between the bushings;
So-called fluid-filled anti-vibration bushings have been proposed.

According to such a fluid-filled vibration-damping bushing, the incompressible fluid sealed in the first and second fluid chambers of the fluid flow mechanism mutually flows through the throttle passage, so that the flow of the throttle passage is reduced. It is possible to effectively attenuate or block input vibrations in a frequency range corresponding to the ratio of the cross-sectional area and length. Therefore, the cross-sectional area and length can be set (tuned) to correspond to vibrations in the low frequency range. ), it is possible to obtain good damping characteristics against human vibration in the low frequency range.

(Problem) However, although such conventional fluid-filled vibration-isolating bushings can obtain good vibration-isolating characteristics against input vibration in the frequency range corresponding to the tuning frequency of the throttle passage, It is difficult to say that good vibration isolation characteristics are necessarily obtained for input vibrations in the frequency range of There was such a problem. Therefore, as described above, if the throttle passage is set to correspond to low frequencies and is designed to effectively attenuate low-frequency, large-amplitude input vibrations, the blocking performance against high-frequency, small-amplitude input vibrations will be improved. There was a tendency to decrease.

(Solution Means) Against this background, the present invention provides a fluid-filled type that can exhibit good vibration isolation effects against both low-frequency, large-amplitude vibrations and high-frequency, small-amplitude vibrations that are input in the radial direction. This was done to provide an anti-vibration bushing.
The gist of this is that, as described above, the fluid-filled vibration damping system includes (a) an inner cylinder member, (b) an outer cylinder member, (c) a rubber elastic body, and (d) a fluid flow mechanism. In the bushing, a predetermined protruding member is provided in at least the first fluid chamber of the fluid flow mechanism in a state extending from the outer cylinder member side toward the inner cylinder member side, and a predetermined protruding member is provided in the at least first fluid chamber of the fluid flow mechanism, and a predetermined protruding member is provided in a state that extends from the outer cylinder member side toward the inner cylinder member side. The flange is provided with a flange that protrudes to form a predetermined gap with the wall surface of the corresponding fluid chamber.

(Function/Effect) According to such a fluid-filled vibration-isolating bushing, as with conventional fluid-filled vibration-damping bushings, by tuning the throttle passage of the fluid flow mechanism (setting the cross-sectional area and length), the non-compressible Based on the sexual fluid flowing through its constricted passage,
Low-frequency, large-amplitude vibrations input in the radial direction can be favorably damped.

On the other hand, in the present invention, the protrusion member is provided in at least the first fluid chamber in a state extending from the outer cylinder member side to the inner cylinder member side, and the protrusion member protrudes laterally from the tip side portion of the protrusion member. Since a flange portion is formed in the state and a predetermined gap is formed between the flange portion and the wall surface of the fluid chamber, when vibration is input in the radial direction of the bushing, at least the first fluid chamber In this case, the incompressible fluid is caused to flow in the bushing radial direction through the gap formed between the flange of the protruding member and the fluid chamber wall, and the incompressible fluid flows in the bushing radial direction through the gap. Based on this, vibrations in a frequency range depending on the shape (cross-sectional area and length) of the gap are effectively attenuated or blocked. In other words, if the shape of the gap is set (tuned) to correspond to high frequencies, high frequency, small amplitude input vibrations can be effectively blocked.

As described above, according to the fluid-filled vibration-proof bushing according to the present invention, low frequency It is possible to obtain good damping characteristics against large-amplitude vibrations, as well as good isolation characteristics against high-frequency and small-amplitude vibrations. can be significantly improved.

(Example) Hereinafter, in order to clarify the present invention more specifically,
Some embodiments thereof will be described in detail based on the drawings.

In the following, a case where the present invention is applied to a cylindrical engine mount for a front-wheel drive vehicle will be explained.
Of course, the invention can also be applied to anti-vibration bushings other than car engine mounts.

First, FIGS. 1 and 2 show an example of a cylindrical engine mount for a front-wheel drive vehicle according to the present invention. In those figures, 10 and 12 are an inner cylinder metal fitting as an inner cylinder member and an outer cylinder metal fitting as an outer cylinder member, respectively, which are arranged eccentrically by a predetermined amount in the radial direction of the mount (radial direction of the bush). , are elastically connected by a substantially arc-shaped rubber elastic body 14 interposed therebetween. and,
The engine mount of this embodiment is attached to an inner cylinder fitting 10 by being fitted onto a mounting shaft on the side of a power unit including an engine and a transmission or on a vehicle body side, and a cylindrical holding part on the side of a vehicle body or a power unit in an outer cylinder fitting 12. The power unit is inserted into and attached to the vehicle body, thereby providing anti-vibration support for the power unit against the vehicle body.

Note that the rubber elastic body 14 is connected to the inner cylinder fitting 10 and the outer cylinder fitting 12.
It is integrally vulcanized and bonded to the inner cylindrical metal fitting 10 on the side having a larger distance in the eccentric direction from the inner cylindrical fitting 10. As a result, a space 16 having an arc-shaped cross section penetrating in the axial direction of the mount is formed on the side where the eccentric distance between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12 is smaller.

Further, as shown in the figure, this rubber elastic body 14 is usually
It is formed integrally with the rubber layer 17 of a predetermined thickness that extends around the cavity 16 side.

Further, in the engine mount of this embodiment, normally, the eccentric direction of the inner cylinder metal fitting 10 and the outer cylinder metal fitting 12 is set to the vibration input direction, and the rubber elastic body 14 is arranged so that the inner cylinder metal fitting 10 and the outer cylinder metal fitting 12 are connected to each other by the weight of the power unit. It is used by being interposed between the vehicle body and the power unit so that it is compressed and deformed with the cylindrical metal fitting 12.

Here, the rubber elastic body 14 includes
As shown in the figure, a groove 18 of a constant width and a constant depth is formed in the circumferential direction in an open state on the outer circumferential surface, and the vacant space 18 is opened in the groove 18.
A pocket portion 20 having the same width and a predetermined depth as the groove portion 18 is formed so as to face the groove portion 6 with the inner cylinder fitting 10 interposed therebetween.

Then, a pair of metal sealing sleeves 22° 22 are integrally vulcanized and molded with respect to the outer peripheral surface of both ends of the rubber elastic body 14 in the direction of the mount axis, with the opening edge of the groove 18 being defined. It is being

On the other hand, the cavities 16 of these sealing sleeves 22.22
In the area facing the rubber elastic body 1, the window portion 24 defined by the seal sleeves 22, 22 and both ends of the rubber elastic body 14 in the circumferential direction is fluid-tightly closed from the inside.
A bag-shaped rubber elastic membrane 26 having a substantially U-shaped cross section is integrally formed with the rubber elastic membrane 4 and is vulcanized and bonded together.
A recess 28 having the window 24 as an opening is formed separated from the cavity 16 by the rubber elastic membrane 26.

In this embodiment, as shown in FIGS. 1 and 2, such an integrally vulcanized product of the rubber elastic body 14 is fitted into the groove 18 of the rubber elastic body 14. A pair of semi-cylindrical orifice member segments 32.
32 are assembled, thereby forming first and second fluid chambers 34, 36 that use the pocket portion 20 and the recess 28 as fluid storage spaces, respectively. Further, the outer cylindrical fitting 12 is fitted to the integrally vulcanized product of the rubber elastic body 14 to which the orifice member divided bodies 32 and 32 are assembled, so that the outer cylindrical fitting 12 and the orifice member divided Four orifice passages 38 of equal cross-sectional area and length are formed in the circumferential direction between the body 32.32 and the first and second fluid chambers 34.36 to communicate with each other. There is.

More specifically, as shown in FIGS. 5 and 6, each orifice member divided body 32 and 32 has two orifice grooves extending in the circumferential direction with openings on the respective outer peripheral surfaces. 40, 40, and through holes 42, 42 located in the corresponding bottom walls of the orifice grooves 40, 40, respectively, as shown in FIGS. 1 and 2. Then, the pocket 20 and the recess 28 are assembled by being press-fitted into the groove 18 of the rubber elastic body 14 from opposing directions. And orifice member divided body 32.3
2 thereby closes the openings of the pocket 20 and the recess 28 and closes the openings of the first and second fluid chambers 34,36.
is formed, and the through hole 4 is formed on its outer peripheral surface.
Four orifice grooves (4o
) is formed. Note that each seal sleeve 22 of the integrally vulcanized product of the rubber elastic body 14 is subjected to a predetermined drawing process prior to the assembly operation of the orifice member divided body 32, 32, so that the rubber elastic body 14 A predetermined precompression is applied to the orifice member, and the outer diameter of the orifice member divided body 32 is approximately the same as the outer diameter when assembled.

Then, as shown in FIGS. 1 and 2, a predetermined thickness is applied to the inner peripheral surface of the integrally vulcanized product of the rubber elastic body 14 in which the orifice member divided bodies 32 and 32 are assembled in this way. An outer cylinder fitting 1 integrally equipped with a sealing rubber layer 44 of
2 is press-fitted, and both ends in the axial direction are roll caulked to fit the four orifice grooves (40 ) are fluid-tightly closed to form the four orifice passages 38.

Incidentally, the assembling operation of the orifice member divided bodies 32, 32 and the fitting operation of the outer cylinder fitting 12 are normally performed in a predetermined incompressible fluid. As a result, each fluid chamber 3
At the same time as the fluid chambers 34, 36 are formed, a predetermined incompressible fluid such as water, polyalkylene glycol, silicone oil, etc. is sealed in the fluid chambers 34, 36.

Further, the shape (cross-sectional area and length) of the four orifice passages 38 is set (tuned) corresponding to a low frequency, and the first and second fluid chambers 34.3
Based on the fact that the incompressible fluid sealed in the incompressible fluid flows through the four orifice passages 38, vibrations such as engine shake corresponding to the tuning frequency are effectively damped. As is clear from this, in this embodiment, the four orifice passages 38 constitute a throttle passage, and the orifice passages 38 and each fluid chamber 34, 36 form a fluid flow mechanism. It is composed of Note that the throttle passage may be constructed in a form other than this example, for example, a single orifice passage, if necessary.

Further, although not shown, annular seal lips are formed on the inner circumferential surfaces of both ends of the seal rubber layer 44 in the axial direction, and these seal lips are sandwiched between the seal sleeves 22 and 22. The pressure ensures fluid tightness of the fluid chambers 34, 36 and each orifice passage 38. As is clear from this, each fluid chamber 34, 36 is substantially formed by fluid-tightly closing the openings of the pocket portion 20 and the recess 28 with the outer cylindrical fitting 12. It is.

By the way, the orifice member number 32 that closes the opening of the pocket portion 20 to form the first fluid chamber 34 is
A block 46 having a substantially rectangular parallelepiped shape is integrally fixed to the inner circumferential surface of the first fluid chamber 34 so as to protrude at a predetermined height into the first fluid chamber 34 . A rectangular stopper plate 48 having a predetermined thickness is integrally fixed to each side of the block 46, with its peripheral edge protruding by a predetermined distance. And with this, 1. Such a stopper plate 48 and the first fluid chamber 34
An annular gap 50 with a predetermined cross-sectional area between the corresponding wall surface of
is formed, and when the inner cylindrical fitting 10 and the outer cylindrical fitting 12 are moved relative to each other in the eccentric direction of both fittings 10 and 12 by input vibration, the incompressible fluid sealed in the first fluid chamber 34 The fluid can flow in the radial direction of the mount through the gap 50, and the stopper plate 48 abuts the bottom wall of the first fluid chamber 34 (pocket 20), so that Excessive displacement of the rubber elastic body 14 between the metal fitting 10 and the outer cylinder metal fitting 12 in the compression direction is prevented.

In this embodiment, as shown in FIGS. 1 and 2, the wall surface of the first fluid chamber 34 (pocket portion 20 (inner wall surfaces) are formed to extend in the eccentric direction of the inner cylindrical fitting 10 and the outer cylindrical fitting 12, respectively, and when both fittings 10° 12 are relatively moved in the eccentric direction by input vibration. , the cross-sectional area of the gap 50 is always maintained at a substantially constant size. In this embodiment, the shape (length and cross-sectional area) of the gap 50 is set to correspond to a relatively high frequency, and when the incompressible fluid flows in the radial direction of the mount through the gap 50, Based on the flow action or inertial mass effect of the incompressible fluid flowing through the gap 50, vibrations in a relatively high frequency range such as muffled sound and engine transmitted sound corresponding to the tuning frequency of the gap 50 are suppressed. It is now blocked by

Further, as shown in FIGS. 1 and 2, the block 46 and the stopper plate 48 are fixed to the orifice member segment 32 by bolts 52 here.

Furthermore, as shown in FIGS. 1 and 2, in this embodiment, a rubber elastic membrane 26 is located at the center of the rubber elastic membrane 26 as a partition wall separating the cavity 16 and the second fluid chamber 36. Based on the fact that a rubber block 54 of a predetermined thickness is integrally formed, and the rubber block 54 is compressed between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12 (rubber layer 17 and orifice member divided body 32). This prevents excessive displacement of both metal fittings 10 and 12 in the direction in which the rubber elastic body 14 is pulled.

In an engine mount having such a structure, the inner cylinder fitting 10
When vibration is input in the opposite direction between the first fluid chamber 34 and the cavity 16, which is the eccentric direction of the outer cylindrical fitting 12, the orifice which makes the first and second fluid chambers 34 and 36 communicate with each other. Since the passage 38 is tuned to correspond to a low frequency as described above, when the input vibration is in a low frequency range, the second fluid chamber 36 due to elastic deformation of the rubber elastic membrane 26 Due to the change in volume, incompressible fluid is forced to flow through the orifice passage 38 between the two fluid chambers 34,36.

In other words, when vibration in the low frequency range is input in the opposite direction between the first fluid chamber 34 and the cavity 16, the incompressible fluid sealed in the first and second fluid chambers 34 and 36 flows into the orifice passage. 38 and thus an incompressible fluid flows through the orifice passages 38.
Low-frequency, large-amplitude input vibrations such as engine shake corresponding to the tuning frequency of 8 are effectively damped.

On the other hand, if the vibration input in the opposite direction between the first fluid chamber 34 and the recess 16 is in a high frequency range such as muffled sound or engine transmitted sound, the orifice passage 38 is tuned to a low frequency. As a result, the incompressible fluid is inhibited from flowing through the orifice passage 38, but in this case, as described above, the gap 50 in the first fluid chamber 34 has a high frequency Since the setting corresponds to Since the fluid flows in the radial direction of the mount through the gap 50, input vibrations in the high frequency range are effectively blocked.

In other words, the engine mount of this embodiment not only provides good damping characteristics against low frequency, large amplitude input vibrations, but also provides good isolation characteristics against high frequency, small amplitude input vibrations. Compared to conventional fluid-filled engine mounts, it can exhibit superior vibration damping effects.

In this embodiment, as described above, the inner wall surface of the pocket portion 20 facing the peripheral edge of the stopper plate 48 is formed to extend in the eccentric direction of the inner cylindrical fitting 10 and the outer cylindrical fitting 12, respectively. When both metal fittings 10 and 12 are moved relative to each other in their eccentric directions due to input vibration, the cross-sectional area of the gap 50 is always maintained at a substantially constant size. Because an incompressible fluid flows through the incompressible fluid, there is an advantage that stable isolation characteristics can always be obtained against vibrations in the frequency range targeted for vibration isolation.

゛ Furthermore, as is clear from the above description, in this embodiment, the block 4 including a part of the stopper plate 48
6 constitutes a protruding member, and the protruding portion of the stopper plate 48 that protrudes laterally from the block 46 constitutes a flange portion.

Next, another example of the cylindrical engine mount according to the present invention will be explained based on FIGS. 7 and 8. Here, only the parts that are different from the embodiment described above will be described in detail, and the parts similar to the embodiment described above will be given the same reference numerals as those of the embodiment described above, and detailed explanation thereof will be omitted.

That is, in the engine mount of this embodiment, unlike the previous embodiment, the block 46 is connected to the orifice member segment 3.
2, and is not held fixedly with respect to the orifice member divided body 32, and is elastically held through a pair of rubber elastic bodies 58 and 58 as elastic members, with a predetermined gap 56 being formed between the orifice member divided body 32. is maintained. This allows the block 46 (including the stopper plate 48) to function as a dynamic damper against input vibrations.

According to such an engine mount, it is possible to obtain the same anti-vibration function as in the above-mentioned embodiment against input vibration.
Based on the damper function of the block 46, it is possible to obtain good vibration damping characteristics even with vibrations in a frequency range different from those (for example, muffled sound of about 50 to 80 Hz), and it is better than that of the previous embodiment. This makes it possible to further improve vibration damping characteristics.

In this embodiment, both ends of the stopper plate 48 in the circumferential direction are connected to the pocket portion 20 that constitutes the first fluid chamber 34.
It is bent into a shape that corresponds to the bottom wall of the. Further, the shapes of the cavity 16 and the second fluid chamber 36 are also slightly different from those of the previous embodiment. Furthermore, in this embodiment, the stopper plate 48 is fixed to the block 46 with bolts 60.

Although a few embodiments of the present invention have been described above in detail, these are literal illustrations, and it goes without saying that the present invention should not be interpreted as being limited to these specific examples.

For example, in the embodiment described above, the block 46 and the stopper plate 48 were configured as separate members, but it is also possible to configure them as an integral member, and the block 46 is When mounted in a fixed position, the block 46 and the orifice member segment 32 can also be configured as an integral member. In addition, as the constituent members of the block 46, stopper plate 48, and orifice member segment 32, metal, synthetic resin, or other suitable material can be adopted as necessary. Furthermore, in the embodiment described above, the protruding member (block 46, stopper plate 48) had a function as a stopper for regulating excessive displacement between the inner cylindrical fitting 10 and the outer cylindrical fitting 12, but the protruding member does not necessarily have to have such a stopper function.

Further, in the embodiment, the second fluid chamber 36 is communicated with the first fluid chamber 34 through the orifice passage 38,
Although the change in the volume of the first fluid chamber 34 was allowed based on the change in the volume of the second fluid chamber 36, a third fluid chamber was provided separately from the second fluid chamber (36). , this third fluid chamber is connected to the first fluid chamber (34) through a predetermined throttle passage.
) so that a change in the volume of the first fluid chamber is allowed based on a change in the volume of both the second and third fluid chambers.

Further, in the embodiment, the second fluid chamber 36 is located in the cavity 16.
The second fluid chamber 36 is separated by a rubber elastic membrane 26, and the elastic deformation of the rubber elastic membrane 26 allows a change in the volume of the second fluid chamber 36 and, by extension, a change in the volume of the first fluid chamber 34. Similarly to the first fluid chamber (34), the second fluid chamber (36) is a pocket portion (2) formed in the rubber elastic body (14).
0) with an outer cylinder member (12), and the first and second fluid chambers are formed by closing the inner cylinder member (12) with the inner cylinder member (12).
10), it is possible to achieve the object of the present invention even if they are made to face each other with the parts 10) in between. In addition, when the second fluid chamber is formed in such a state, it is possible to provide a protruding member with a flange portion on the second fluid chamber side, and in this way, the second fluid chamber can be When a protruding member with a flange is provided on the fluid chamber side as well, by tuning the gap formed between the flange and the fluid chamber wall to a frequency different from that in the first fluid chamber. , it becomes possible to satisfactorily isolate input vibrations in a wider frequency range than in the embodiments described above. Further, when the second fluid chamber 36 is formed in such a state, the inner cylinder member and the outer cylinder member are generally arranged concentrically.

In addition, in the embodiment, the orifice passage 38 as the throttle passage is formed in the orifice groove 40 of the orifice member segment 32 disposed between the rubber elastic body 14 and the outer cylinder fitting 12.
However, depending on the formation form of the fluid chamber of the fluid flow mechanism, etc., the throttle passage may be formed on the inner peripheral side of the rubber elastic body (14). It is also possible.

Although not listed here, various other modifications may be made without departing from the spirit of the present invention.

It goes without saying that the present invention can be implemented with modifications, improvements, etc.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view (II--I cross-sectional view in FIG. 2) showing an example of a cylindrical engine mount for an FF vehicle according to the present invention, and FIG. 2 is a cross-sectional view taken along the line ■--■ in FIG. It is. FIG. 3 is a cross-sectional view corresponding to FIG. 1 (mm-m cross-sectional view in FIG. 4) showing an integrally vulcanized product of the rubber elastic body in the engine mount of FIG. Third
It is a TV-IV sectional view in the figure. Figures 5 and 6
The figures are a plan view and a front view, respectively, showing an orifice member division in the engine mount of FIG. 1. FIG. 7 is a cross-sectional view corresponding to FIG. 1 showing another embodiment of the present invention (cross-sectional view taken along the line ■-■ in FIG. 8), and FIG. 8 is a cross-sectional view taken along the line ■-■ in FIG. It is. lO: Inner cylinder metal fitting (inner cylinder member) 12: Outer cylinder metal fitting (outer cylinder member) 14: Rubber elastic body 16: Hole 20: Pocket hole 22: Seal sleeve 26 = Rubber elastic membrane (partition wall) 28: Recess 32 Niorifice member divided body 34: First fluid chamber 36: Second fluid chamber 38 Niorifice passage (throttle passage) 46: Block 48 Niston Pave plate 50: Gap portion 56: Gap 58: Rubber elastic body (elastic member)

Claims (6)

[Claims] (1) (a) an inner cylinder member; (b) an outer cylinder member disposed concentrically or eccentrically on the outside of the inner cylinder member; (c)
(d) a rubber elastic body interposed between the inner cylinder member and the outer cylinder member to connect them; and (d) an opening of a pocket provided in the rubber elastic body that is fluid-tight with the outer cylinder member. and a second fluid chamber communicated with the first fluid chamber through a predetermined throttle passage, and a predetermined fluid chamber sealed in the fluid chamber. A fluid flow mechanism that damps or blocks vibrations in the bush radial direction input between the inner cylinder member and the outer cylinder member based on the incompressible fluid mutually flowing through the throttle passage. In the fluid-filled vibration damping bushing, a predetermined projecting member is provided in at least the first fluid chamber in a state extending from the outer cylinder member side toward the inner cylinder member side, and 1. A fluid-filled vibration isolating bushing comprising: a flange projecting laterally from a tip side portion of a projecting member and forming a predetermined gap with a wall surface of a corresponding fluid chamber. (2) The fluid-filled vibration damping bushing according to claim 1, wherein the protruding member is arranged in a fixed position with respect to the outer cylinder member. (3) The fluid-filled anti-vibration bushing according to claim 1, wherein the protruding member is arranged to be elastically connected to the outer cylindrical member via a predetermined elastic member. . (4) Any one of claims 1 to 3, wherein the inner wall surface of the pocket portion of the rubber elastic body constituting the first fluid chamber is formed to extend parallel to the vibration input direction. Fluid-filled anti-vibration bushing described in . (5) The fluid according to any one of claims 1 to 4, wherein the orifice means is formed to extend in the circumferential direction between the rubber elastic body and the outer cylinder member. Enclosed anti-vibration bushing. (6) A cavity is formed that passes through the bush in the axial direction so as to face the first fluid chamber with the inner cylindrical member in between, and the second fluid chamber is located in the cavity. and at least a portion thereof are separated by a partition wall made of a predetermined elastic membrane, and a change in volume of the second fluid chamber is allowed by elastic deformation of the elastic film of the partition wall. A fluid-filled vibration damping bushing according to any one of claims 1 to 5.