JPH0457904B2 - - Google Patents

Description

Detailed Description of the Invention (Technical Field) The present invention relates to a mount device such as an automobile engine mount, and particularly to a fluid-filled mount device in which a predetermined fluid is sealed inside, the present invention relates to a mount device such as an engine mount for an automobile. The present invention relates to a technique for exhibiting a good vibration isolation effect against input vibration.

(Prior Art) Mounting devices such as automobile engine mounts have conventionally had a structure in which first and second support members, which are arranged to face each other with a predetermined distance apart, are elastically connected by a rubber elastic body. The vibration input between the supporting members is attenuated or blocked solely based on the elastic deformation of the rubber elastic body. However, conventional mounting devices with such a structure had the problem of not being able to obtain sufficient damping effect especially for large amplitudes in the low frequency range, so in recent years, a predetermined internal mounting device has been developed. So-called fluid-filled mound devices, which are filled with low-viscosity fluid and are designed to isolate (attenuate or block) input vibrations based on the flow of this low-viscosity fluid through a constriction passage, are now being used exclusively. I'm getting used to it. According to such a fluid-filled mounting device, the ratio between the cross-sectional area and the length of the throttle passage can be adjusted based on the flow action or inertial mass effect of the sealed fluid (low viscosity fluid) flowing through the throttle passage. Therefore, by setting (tuning) the cross-sectional area and length of the throttle passage corresponding to the low frequency range, it is possible to effectively dampen input vibration in the low frequency range.
Large amplitude vibrations in the low frequency range can be effectively damped.

Incidentally, such a fluid-filled mounting device generally includes (a) first and second support members arranged to face each other with a predetermined distance apart, and (b) the first and second support members. a rubber elastic body interposed between the support members to elastically connect them; and (c) a fluid storage space disposed on the second support member side and between the first support member. a partition wall member, at least a part of which is made of an elastic membrane, and (d) a partition wall member that is arranged in a fixed position with respect to the second support member, and that the fluid storage space is connected to the first partition wall member on the side of the rubber elastic body. (e) a predetermined low-viscosity fluid sealed in the first and second fluid chambers; and a throttle passage that allows the second fluid chambers to communicate with each other, and prevents vibrations input between the first and second support members based on the low viscosity fluid flowing through the throttle passage. However, as mentioned above, in such a fluid-filled mounting device,
By setting the cross-sectional area and length of the throttle passage to correspond to the low frequency range, it is possible to satisfactorily attenuate large-amplitude vibrations in that low frequency range. It is difficult to say that good anti-vibration function is necessarily obtained.
In particular, small amplitude vibrations in a frequency range higher than the tuning frequency range of the throttle passage are caused by the fact that low viscosity fluid becomes difficult to flow through the throttle passage.
On the contrary, there was a problem where the anti-vibration function (blocking function) deteriorated.

Therefore, in order to eliminate such problems, conventionally, as disclosed in Japanese Patent Application Laid-Open No. 57-9340, in the above-mentioned fluid-filled mounting device, (g) the first and second A movable member is provided that is displaced by a predetermined amount in a direction opposite to the fluid chambers in response to a fluid pressure difference within the fluid chambers.
If such a movable member is provided, based on the fact that the movable member is displaced in the opposite direction of the first and second fluid chambers, the tuning frequency range (first frequency range) of the throttle passage is higher than the tuning frequency range (first frequency range) of the throttle passage. It is possible to effectively dampen vibrations with smaller amplitudes in the frequency range (second frequency range), and it is possible to effectively dampen input vibrations in a wider frequency range than with a system that simply has a throttle passage. This makes it possible to prevent vibrations.

(Problem) However, even in a fluid-filled mounting device that includes such a movable member in addition to the throttle passage, as described above, two different frequency ranges (first and second frequency ranges) At best, a good vibration isolation function can be obtained for input vibrations in the range of frequencies, and the reality is that a good vibration isolation function has not yet been obtained for input vibrations in other frequency ranges.

(Solution) Against this background, the present invention provides a fluid-filled mount device that can exhibit a good vibration isolation effect against input vibrations in a wider frequency range than conventional ones. The gist of this is that (a) the first and second support members, (b) the rubber elastic body, (c) the partition member, and ( In addition to d) the partition member, (e) the low viscosity fluid, and (f) the throttle passage, the system further includes (g) a movable member as described above, and the low viscosity fluid flows through the throttle passage. Based on the fact that vibrations in the first frequency range inputted between the first and second support members are attenuated or blocked, and the movable member is displaced in the opposite direction of the first and second fluid chambers, In a fluid-filled mount device that damps or blocks vibrations in a second frequency range higher than the first frequency range that is input between the first and second support members, the first and second support members An annular rubber elastic membrane is disposed in a fluid-tight manner between both of the support members while straddling the support member, and the inside of the first fluid chamber is defined by the annular rubber elastic membrane. A third fluid chamber is formed, a predetermined high viscosity fluid is sealed in the third fluid chamber, and a predetermined high viscosity fluid is sealed in the third fluid chamber on one side of the first and second support members. A bottomed hole is provided that opens toward the side, and
A plunging member is disposed on the other side of the first and second support members to protrude into the bottomed hole and form a predetermined gap with the inner surface of the bottomed hole. When the second support member relatively moves in the opposite direction, the high viscosity fluid flows through the gap between the plunging member and the bottomed hole based on the plunger moving in and out of the bottomed hole. On the other hand,
A fluid pressure absorption mechanism is provided facing the space between the bottom of the bottomed hole and the plunger member, and absorbs fluid pressure fluctuations of a predetermined magnitude or less of the high viscosity fluid in the space. Fluid pressure fluctuations caused in the high viscosity fluid in the space by vibration input in the second frequency range are absorbed by the fluid pressure absorption mechanism.

Note that here, the high viscosity fluid sealed in the third fluid chamber is usually 1,000 centistokes or more, preferably 10,000 centistokes or more,
Preferably, a silicone oil having a kinematic viscosity of 100,000 to 1,000,000 centistokes will be used.

(Function/Effect) In this way, in the fluid-filled mount device, fluid pressure is absorbed for high viscosity fluid in the space between the bottom of the bottomed hole and the plunger member between the first and second support members. When large-amplitude vibrations that cause fluid pressure fluctuations that cannot be absorbed by the mechanism, that is, large-amplitude vibrations in a third frequency range that is lower than vibrations in the first frequency range, are input, the first and second support members Based on the relative movement, the highly viscous fluid sealed in the third fluid chamber is forced to flow actively through the gap between the inner surface of the bottomed hole and the plunger inserted into it. As a result, large-amplitude vibrations in the third frequency range, which is lower than the first frequency range, are effectively damped (damped) based on the viscous resistance caused when the high-viscosity fluid flows through the gap. ). In this case, since the throttle passage is tuned to the first frequency range which is higher than the third frequency range, it becomes difficult for the low viscosity fluid to flow through the throttle passage. The relative movement of the second supporting member is not obstructed, and therefore the viscous resistance caused by the relative movement of these supporting members, and the vibration isolation function (damping function) obtained based on the viscous resistance. ) will not be reduced.

On the other hand, when vibrations in the first and second frequency ranges whose amplitude is smaller than the vibrations in the third frequency range are input between the first and second support members,
Relative movement of the first and second support members is allowed based on fluid pressure fluctuations of the high viscosity fluid in the space being absorbed by the fluid pressure absorption mechanism;
The relative movement of the first and second support members is not inhibited by the viscous resistance of the highly viscous fluid flowing through the gap, and therefore, as in the conventional fluid-filled mounting device, one of the support members The vibration load input to the first fluid chamber is substantially transmitted to the other support member via the rubber elastic body and the low viscosity fluid sealed in the first fluid chamber. In other words, when vibrations in the first frequency range are input between the first and second support members, the vibration of the conventional fluid-filled Similar to the mounting device, since the low-viscosity fluid flows through the throttle passage, vibrations in the first frequency range can be effectively damped (attenuated or blocked), and the input vibration can be suppressed in the second frequency range. frequency range, the second frequency range is determined based on the displacement of the movable member in the opposite direction of the first and second fluid chambers, similarly to conventional fluid-filled mounting devices. It is possible to effectively isolate vibrations.

As described above, according to the fluid-filled mount device according to the present invention, based on the fact that the low viscosity fluid flows through the throttle passage and the movable member is displaced in the opposite direction of the first and second fluid chambers, Not only can a good vibration isolation function be obtained against input vibrations in two different frequency ranges (first and second frequency ranges), but also the high viscosity fluid sealed in the third fluid chamber has a bottom. Based on the flow in the gap between the hole and the plunger member, it is possible to obtain a good vibration isolation function even against input vibrations in a lower frequency range (third frequency range). This makes it possible to effectively dampen input vibrations in a wider frequency range than conventional fluid-filled mounting devices while maintaining a good damping function against low-frequency, large-amplitude input vibrations.

(Examples) Hereinafter, in order to clarify the present invention more specifically, some examples thereof will be described in detail based on the drawings.

First, FIG. 1 shows a longitudinal sectional view of an automobile engine mount, which is a fluid-filled mount device according to the present invention. In that figure, 10,
Reference numerals 12 denote first and second support fittings as first and second support members, respectively, which are arranged to face each other with a predetermined distance apart in the vibration input direction (up and down in the figure). There is.

The first support fitting 10 has a generally truncated cone shape with a relatively small diameter, and is arranged so that the top side of the truncated cone faces the second support fitting 12.
The second support fitting 12 has a relatively large-diameter bottomed cylindrical shape with a large-diameter caulked portion 14 at the opening, and is opened toward the first support fitting 10. It is arranged concentrically with the support fitting 10 of. Then, at the inner circumferential portion, the first support fitting 10
The annular rubber elastic body 16 is integrally vulcanized and bonded to the side surface of the rubber elastic body 16 and integrally crimped and fixed to the crimped part 14 of the second support fitting 12 at the outer periphery.
is arranged, which allows both support fittings 1
0 and 12 are elastically connected by the rubber elastic body 16.

In FIG. 1, reference numeral 18 denotes a metal fitting to be caulked which is integrally vulcanized and bonded to the outer circumference of the rubber elastic body 16, and the rubber elastic body 16 is attached to the metal fitting 18 to be caulked.
, the caulking portion 14 of the second support fitting 12
It is fluid-tightly caulked into place. Further, in the figure, reference numeral 20 denotes a tapered metal fitting embedded in the rubber elastic body 16 so as to divide the rubber elastic body 16 into two into inner and outer peripheral parts. Furthermore, in the same figure, 22, 24
are mounting bolts that are integrally attached to the first support metal fitting 10 and the second support metal fitting 12, respectively. It is attached to the vehicle body side or the engine side, and is attached to the engine side or the vehicle body side by the mounting bolt 24 of the second support fitting 12, so as to provide vibration-proof support for the engine or the power unit including the engine with respect to the vehicle body. It's summery.

The second supporting metal fitting 12 having a bottomed cylindrical shape includes a cylindrical metal fitting 28 in which the caulking part 14 is formed at one end and an outward annular caulking part 26 at the other end, and a central part. The mounting bolt 24 is integrally attached to the disk-shaped bottom metal fitting 32, and a cylindrical caulking part 30 is integrally formed on the outer periphery of the disk-shaped bottom metal fitting 32. It is integrally assembled by being crimped to the crimped portion 26 of 28. Then, by caulking the metal fittings 28, 32, the peripheral edges of the metal fittings 28, 32 are attached.
A diaphragm 34 as a partition member made of a rubber elastic membrane is disposed between the diaphragm 34 and the first support fitting 10 in a fluid-tight manner. A closed space is formed.

Note that the diaphragm 34 and the second support fitting 12
An air chamber 3 with a predetermined volume is provided between the bottom metal fitting 32 of the
6 is formed. In addition, as shown in FIG.
Both metal fittings 2 are attached via the outward flange portion 40 of
It is sandwiched between 8 and 32.

On the inner circumferential surface of the cylindrical metal fitting 28 of the second support fitting 12, an annular protrusion 4 is located at an intermediate portion in the axial direction.
2 is formed, and a partition mechanism 44 as a partition member is disposed with its peripheral edge sandwiched between the protrusion 42 and the spacer 38. As a result, the sealed space between the first support fitting 10 and the diaphragm 34 is partitioned into a first fluid chamber 46 on the rubber elastic body 16 side and a second fluid chamber 48 on the diaphragm 34 side. A predetermined low-viscosity fluid such as ethylene glycol, water, polyalkylene glycol, silicone oil, etc. is sealed in the first and second fluid chambers 46 and 48, which are partitioned by the partition mechanism 44, respectively. has been done.

Here, the partition mechanism 44 includes an annular member 50 disposed on the first fluid chamber 46 side and a disc-shaped member 52 superimposed on the annular member 50 on the second fluid chamber 48 side. There is. A throttle passage 54 having a predetermined cross-sectional area is located at the overlapping portion of the annular member 50 and the disc-shaped member 52, and communicates with one of the body chambers 46 and 48 at both ends thereof. It is formed to extend in length. Further, a through hole 56 having a predetermined cross-sectional area is formed to pass through the overlapping portion of both members 50 and 52 in the mount axis direction, and
Both fluid chambers 46,
A movable plate 58 as a movable member made of a predetermined material such as a rubber material is disposed so as to be movable over a small distance in a direction opposite to the movable plate 58 .

In this embodiment, the first and second fluid chambers 46, 4
The low viscosity fluid sealed in the cylindrical member 5
0 and the disc-shaped member 52 are allowed to mutually flow through a constriction passage 54 formed at the overlapping portion, and when a difference in fluid pressure occurs in the first and second fluid chambers 46, 48, , the movable plate 58 held in the through hole 56 can be displaced by a predetermined amount in the opposite direction of the fluid chambers 46 and 48 in accordance with the flow pressure difference.

Note that here, the ratio of the cross-sectional area and length of the throttle passage 54 is set (tuning) to correspond to a frequency _f1 in a relatively high frequency range corresponding to muffled sounds, etc.
Based on the flow action or inertial mass effect when a low viscosity fluid flows through the throttle passage 54, a comparison of muffled sounds, etc. corresponding to the tuning frequency _f1 of the throttle passage 54 is made. Input vibrations in a high frequency range (first frequency range) are effectively damped (attenuated or blocked). Moreover, here, the ratio of the cross-sectional area and length of the through hole 56 held in the movable plate 58 is set corresponding to the frequency: f ₂ which is higher than the frequency: f ₁ , thereby making the movable plate 58 movable. Based on the movement of the plate 58 in the opposite direction of both fluid chambers 46 and 48, the input of a high frequency range (second frequency range) such as engine transmitted sound corresponding to the tuning frequency of the through hole ₅₆ : f2. Vibration is well-isolated. Furthermore, here, the amount of movement (displacement) of the movable plate 58 is set to be sufficiently smaller than the amplitude of the input vibration in the first frequency range.

Incidentally, a cylinder block 60 is integrally fixed to the first support fitting 10 in a state that it projects into the first fluid chamber 46. The partition mechanism 44 is attached to this cylinder block 60.
A bottomed hole 62 with a circular cross section and a predetermined depth is opened toward the side, that is, the second support fitting 12 side.
is formed concentrically with the mount axis. Note that this cylinder block 60 is formed integrally with the mounting block 22, and the mounting bolt 2
The first support fitting 10 is connected to the non-threaded portion 64 at the proximal end of the second support fitting 10.
is press-fitted into the through hole 66 and fixed. Further, in FIG. 1, 68 is a seal member interposed between the first support fitting 10 and the cylinder block 60, and 69 is an annular seal member integrally formed on the outer circumference of the cylinder block 60. This is the protrusion.

On the other hand, when the first fluid chamber 46 is formed between the first support metal fitting 10 and the first support metal fitting 10 A piston member 70 having a predetermined size smaller in diameter than the diameter of the bottomed hole 62 is erected integrally or integrally in a state of protruding to the side. And the first and second support fittings 10,
Under an unloaded state where no load is applied between the piston member 70 and the bottom of the bottomed hole 62, as shown in the figure, the piston member 70 is inserted into the bottomed hole 62 in a state where a predetermined space 72 is formed between the piston member 70 and the bottom of the bottomed hole 62. 62 concentrically to a predetermined depth.

In this embodiment, as shown in the drawings, the proximal end of the piston member 70 and the outer circumference of the distal end side (opening side of the bottomed hole 62) of the cylinder block 60 have respective ends in the axial direction. A stepped cylindrical rubber elastic membrane 74 is disposed in a fluid-tight manner, thereby defining a third fluid chamber 76 defined by the rubber elastic membrane 74 within the first fluid chamber 46. is formed, and within the third fluid chamber 76,
A predetermined high viscosity fluid such as silicone oil is sealed.

When the first and second support fittings 10 and 12 move relative to each other in the opposite direction based on the elastic deformation of the rubber elastic body 16, the movement of the piston member 70 into and out of the bottomed hole 62 of the cylinder block 60 causes The high viscosity fluid is made to flow through the annular gap 78 between the inner surface of the bottom hole 62 and the piston member 70, and the high viscosity fluid is caused to flow through the gap 78. A predetermined viscous resistance is generated based on the shearing action. As is clear from this, in this embodiment, the piston member 70 constitutes the plunger member.

Here, the high viscosity fluid is generally 1,000 centistokes or more, preferably 10,000 centistokes or more, and preferably 100,000 to 100,000 centistokes.
A value of 1 million centistokes will be adopted.

Further, here, a cup-shaped rubber elastic membrane 80 is airtightly fixed to the distal end of the piston member 70 facing the space 72 at the opening periphery thereof, so that the rubber elastic membrane 80 defines an area. An air chamber 82 having a predetermined volume is formed. In this embodiment, based on the volume change of the air chamber 82, that is, the elastic deformation of the rubber elastic membrane 80, the tuning frequency of the throttle passage 54: f ₁
Fluid pressure fluctuations caused by the high viscosity fluid in the space 72 are effectively absorbed by small amplitude vibrations in the first frequency range corresponding to the first frequency range or a higher frequency range.

In other words, in this embodiment, when large amplitude vibration in a frequency range (third frequency range) lower than the first frequency range is input between the first and second support fittings 10 and 12, , based on the relative movement of the first and second support fittings 10 and 12 due to the vibration input, the high viscosity fluid is made to actively flow through the gap 78, thereby actively reducing the viscous resistance. However, when small amplitude vibrations in the first frequency range or a higher frequency range are input, fluid pressure fluctuations caused by the high viscosity fluid in the space 72 occur. The rubber elastic membrane 80
By absorbing the fluid through elastic deformation, the high viscosity fluid is prevented from flowing through the gap 78 while allowing relative movement of the first and second support fittings 10 and 12. It is,
As a result, the first and second support fittings 10, 1
This effectively prevents the relative movement of the two from being inhibited by the viscous resistance of the highly viscous fluid. Note that, as is clear from the above description, in this embodiment, the rubber elastic membrane 80 defining the air chamber 82 constitutes a fluid pressure absorption mechanism.

According to the engine mount with this structure,
When large amplitude vibration in a third frequency range such as shake, which is lower than vibration in the first frequency range, is input between the first and second support fittings 10 and 12, the high viscosity fluid flows into the gap 78. Based on the viscous resistance caused when the high viscosity fluid flows through the gap 78, the large amplitude vibration in the third frequency range is effectively damped (damped). ). In this case, as described above, the tuning frequency of the throttle passage 54: f ₁
is set to correspond to the first frequency range which is higher than the third frequency range, this makes it difficult for the low viscosity fluid to flow through the throttle passage 54. The relative movement of 10, 12 is not hindered, and therefore the viscous resistance caused by the relative movement and thus the vibration damping effect is not reduced.

On the other hand, if the vibrations input between the first and second support fittings 10 and 12 are in the first and second frequency ranges whose amplitude is smaller than that in the third frequency range, Based on the elastic deformation of the rubber elastic membrane 80, the relative movement of the first and second support fittings 10 and 12 is allowed almost without being hindered by the viscous resistance of the highly viscous fluid. The low viscosity fluid flows through the restricting passage 54 and the movable plate 58 moves through the first and second Based on the displacement according to the fluid pressure difference between the two fluid chambers 46 and 48, the throttle passages 54
The tuning frequency of the through hole 56: The input vibration of the first frequency range such as muffled sound corresponding to f ₁ , and the input vibration of the second frequency range such as engine transmitted sound corresponding to the tuning frequency of the through hole 56: f ₂ . Vibration can be isolated (attenuated or blocked).

That is, according to the engine mount according to this embodiment, input vibrations in the third frequency range corresponding to shake etc., input vibrations in the first frequency range corresponding to muffled sounds etc., and input vibrations in the first frequency range corresponding to engine transmitted sound etc. It is possible to effectively dampen input vibrations in three different frequency ranges, and therefore, while maintaining good damping function against low frequency large amplitude vibrations such as shake, it is possible to effectively dampen input vibrations in three different frequency ranges. It is possible to enjoy the effect of being able to effectively dampen input vibrations in a wider frequency range than with other types.

Although not specifically mentioned in this embodiment, the cross-sectional area of the annular gap 84 (see FIG. 1) between the protrusion 69 on the outer periphery of the cylinder block 60 and the wall surface of the first fluid chamber 46 and the ratio of the length to the frequency:
Frequency even higher than f ₂ : set corresponding to f ₃ ,
It is also possible to effectively dampen the input vibration in the frequency range corresponding to the frequency _f3 based on the flow action or inertial mass effect when the low viscosity fluid flows through the gap 84. It is. In this way, input vibrations in four different frequency ranges can be effectively damped, and the vibration damping function is further improved.

Further, in this embodiment, the rubber elastic membrane 80 as a fluid pressure absorption mechanism defining the air chamber 82 is provided on the side of the piston member 70, which is the plunger member.
It is also possible to provide such an air chamber 82 and rubber elastic membrane 80 on the cylinder block 60 side. Furthermore, it is also possible to seal a compressible fluid other than air within the space of the air chamber 82.

Next, another embodiment of this embodiment will be described based on FIG. 2. Note that this embodiment differs from the above embodiment only in the structure of the fluid pressure absorption mechanism that absorbs fluid pressure fluctuations of the high viscosity fluid in the space 72, so the structure of the fluid pressure absorption mechanism will be described below. Only the following will be explained in detail.

That is, as shown in FIG. 2, in this embodiment, the space 72 and the high viscosity fluid accommodation space outside the bottomed hole 62 are communicated with the piston member 70, and the gap 78 and Fluid passage 8 in parallel
6 is formed. And this fluid passage 86
The movable plate 9 is made of a predetermined material such as metal, resin, rubber, etc. (here, rubber material), with its peripheral edge held in an annular groove 88 formed on the inner surface of the movable plate 9.
0 is disposed so as to be movable a predetermined distance in the plate thickness direction according to the fluid pressure difference between the high viscosity fluids located on both sides thereof, and based on the movement (displacement) of this movable plate 90, as in the previous embodiment, Tuning frequency of the throttle passage 54: Fluid pressure fluctuations caused in the high viscosity fluid in the space 72 by input vibrations in the first frequency range corresponding to _f1 or in a higher frequency range are well absorbed. It is becoming more and more common. Even with an engine mount equipped with such a fluid pressure absorption mechanism, the same effects as in the above embodiment can be obtained.

In this embodiment, a rubber layer 92 of a predetermined thickness is disposed on the distal end surface of the piston member 70, and the annular groove 88 is formed between the rubber layer 92 and the piston member 70. The annular groove 88 may be formed using a metal member, a resin member, or the like instead of the layer 92.

Further, the fluid passage 86 can also be formed on the cylinder block 60 side.

In addition, here, the movable plate 90 constitutes the second movable member, but as the second movable member, the peripheral edge is held fluid-tightly on the inner circumferential surface of the fluid passage 86, and the second movable member is It is also possible to employ an elastic membrane that can be deformed by a certain amount in response to the fluid pressure difference of the high viscosity fluid in which it is located. Furthermore, such an elastic membrane is adopted as the second movable member,
If the fluid passage 86 is completely fluid-tightly blocked, it is also possible to form the fluid passage 86 so as to open into the space 72 and the first fluid chamber 46 .

Although several embodiments of the present invention have been described in detail above, 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 bottomed hole 62 was provided on the first support fitting 10 side, and the piston member 70, which is a plunger member, was provided on the second support fitting 12 side. The second support fitting 1
However, it is also possible to provide the piston member 70 on the first support fitting 10 side.

Further, in the above embodiment, the movable plate 58 was employed as the movable member, but the movable member is not necessarily limited to such a movable plate, and the movable member is not limited to the first and second movable members. It is also possible to employ as the movable member an elastic membrane that can be deformed by a certain amount in accordance with the fluid pressure difference between the two fluid chambers 46 and 48.

Furthermore, in the embodiment described above, an example was described in which the present invention was applied to an engine mount for an automobile, but the present invention can also be applied to a mounting device other than an engine mount for an automobile.

In addition, although it is omitted to list specific examples one by one, it goes without saying that the present invention can be practiced with various changes, modifications, improvements, etc. within the scope without departing from the spirit thereof.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view showing an example of an engine mount for an automobile according to the present invention, and FIG. 2 is a cross-sectional view showing essential parts of another embodiment of the present invention. 10: First support fitting (first support member), 1
2: Second support fitting (second support member), 16:
Rubber elastic body, 34: diaphragm (elastic membrane; partition member), 44: partition mechanism (partition member), 46: first fluid chamber, 48: second fluid chamber, 54: throttle passage, 58 movable plate (movable) member), 60: cylinder block, 62: bottomed hole, 70: piston member (pushing member), 72: space, 74: rubber elastic membrane (annular), 76: third fluid chamber, 78: gap,
80: rubber elastic membrane (fluid pressure absorption mechanism), 82: air chamber, 86: fluid passage, 90: movable plate (second movable member).

Claims (1)

[Claims] 1. (a) first and second support members arranged to face each other with a predetermined distance apart, and (b) interposed between the first and second support members. (c) at least a portion of the rubber elastic body that is disposed on the second support member side and forms a fluid accommodation space between the first support member and the second support member; (d) is arranged in a fixed position with respect to the second support member, and the fluid storage space is connected to the first fluid on the rubber elastic body side and the partition member. (e) a predetermined low-viscosity fluid sealed in the first and second fluid chambers; and (f) a partition member that partitions the first and second fluid chambers into the first and second fluid chambers; (g) a movable member disposed to be displaceable by a predetermined amount in opposite directions of the first and second fluid chambers in response to a fluid pressure difference in the first and second fluid chambers; Based on the viscous fluid flowing through the throttle passage, vibrations in the first frequency range inputted between the first and second support members are damped or blocked, and the movable member Based on the displacement of the second fluid chamber in the opposite direction, vibrations in a second frequency range higher than the first frequency range input between the first and second support members are damped or In the fluid-filled mounting device, an annular rubber elastic membrane is disposed in a fluid-tight manner with respect to the first and second supporting members in a state spanning the first and second supporting members, and A third fluid chamber defined by the annular rubber elastic membrane is formed inside the first fluid chamber, and a predetermined high-viscosity fluid is sealed in the third fluid chamber. and a bottomed hole opening toward the other side in the third fluid chamber is provided on one side of the second support member, and on the other side of the first and second support members, A plunging member that protrudes into the bottomed hole and forms a predetermined gap with the inner surface of the bottomed hole is provided, and the first and second support members are opposed to each other in opposing directions. When the plunging member moves in and out of the bottomed hole, the high viscosity fluid flows through the gap between the plunging member and the bottomed hole, while the bottomed hole A fluid pressure absorption mechanism is provided facing the space between the bottom of the hole and the plunger member for absorbing fluid pressure fluctuations of a predetermined magnitude or less of the high viscosity fluid in the space, and 1. A fluid-filled mount device, characterized in that the fluid pressure absorption mechanism absorbs fluid pressure fluctuations caused by a high viscosity fluid in the space due to vibration input in a frequency range. 2. The fluid-filled mounting device of claim 1, wherein the highly viscous fluid is silicone oil having a kinematic viscosity of at least 1,000 centistokes. 3. The fluid pressure absorption mechanism is an elastic membrane disposed to be deformable by a predetermined amount while separating a space between the bottom of the bottomed hole and the plunger member from a predetermined air chamber, and the fluid pressure absorption mechanism Fluid pressure fluctuations of the highly viscous fluid caused by the deformation of the elastic membrane are absorbed based on the deformation of the elastic membrane.
Fluid-filled mounting device as described in Section 1. 4 in a state in which the fluid pressure absorption mechanism blocks the fluid passage from a fluid passage formed in parallel with the gap between the inner surface of the bottomed hole and the plunge member;
and a second movable member disposed so as to be able to be displaced by a predetermined amount in response to a fluid pressure difference between the high viscosity fluid located on both sides of the fluid passage, the bottom of the bottomed hole and the plunger member. According to claim 1 or 2, fluid pressure fluctuations of the high viscosity fluid accommodated in the space between are absorbed based on the displacement of the second movable member. Fluid-filled mounting device.