JPH07238983A - Liquid sealed type engine mount - Google Patents

Abstract

PURPOSE:To reduce the extent of mass in a mass member as securing a damping effect to the vibratory input of a low frequency range to the full. CONSTITUTION:A lower end of a first mounting member 1 is connected to a second mounting member 2 through an elastic supporter 3, and a liquid chamber 4 inside is partitioned off into a pressure receiving chamber 4a at the elastic supporter side and a balance chamber 4b made possible to be expanded or contracted by a diaphragm 5 by a partitioner. In addition, a mass member 22 formed into a plate form by a material being larger in specific gravity than at least a liquid 6 is precipitated and set up in a nonsupporting state so as to be spread in a direction orthogonal with a cylinder shaft X, thereby eliminating the existence of a supporting spring. In succession, a through hole 22a is installed in the mass member and thereby any sticking to an inner surface 3b is prevented from occurring, while it is externally inserted into a guide pin 23 and any displacement in a direction orthogonal with it is regulated as making it freely displaceable only in the cylinder shaft X direction and thus any impact noise with an inner circumferential surface of the pressure receiving chamber is prevented from occurring.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a liquid filled engine mount having a mass member.

[0002]

2. Description of the Related Art Conventionally, as this type of liquid-sealed engine mount, there has been known one in which a part of a liquid chamber is defined by a mass member (for example, JP-A-64-46034).
(See the official gazette). In this one, a pair of support members 1
01 and 102 are connected to each other by an elastic support 103, and the inside is partitioned by a partition 104 into a pressure receiving chamber 105 on the elastic support 103 side and a balance chamber 107 that can be expanded and contracted by a diaphragm 106, and both chambers 105 and 107 are orifices. A liquid column resonance is made to communicate with each other via 108 and the liquid column resonance is used to attenuate the input vibration in the low frequency region. Then, the support rubber block 11 serving as a support spring for the plate-shaped mass member 109 is formed by the elastic bearing member.
It is arranged on the pressure receiving chamber side in a state of being elastically supported via 0, and the outer periphery of the mass member 109 is connected and supported by the supporting member 102 by an annular partition rubber 111 to form the pressure receiving chamber 105.
I try to define a part of it. In addition, the partition wall rubber 111 is made relatively thin so that the mass member 109 can be displaced and does not act as a support spring.

[0003]

However, in the above-mentioned conventional liquid-filled engine mount, the mass member 10 is used.
In order to define the pressure receiving chamber 105 by 9, the partition rubber 111 is arranged between the periphery of the mass member 109 and the support member 102, and the partition rubber 111 does not act as a support spring. It is made to be extremely flexible. Therefore, when the vibration in the low frequency range is input and the mass member 109 together with the elastic support 103 is displaced to the side of contracting the pressure receiving chamber 105, the liquid in the pressure receiving chamber 105 is pressurized, and the pressurized hydraulic pressure is applied. Is the partition rubber 11
The partition wall rubber 111 swells toward the side where the pressure receiving chamber 105 is enlarged by acting on 1. In this case, even if the partition rubber 111 is curved so as to project to the pressure receiving chamber 105 side in consideration of the influence of the liquid pressure, it is originally liable to be flexed, and therefore is accompanied by the input of the low frequency vibration. It deforms due to relatively large fluctuations in hydraulic pressure. As a result, the hydraulic pressure fluctuation due to the vibration input is absorbed by that amount, and the orifice 1
The amount of liquid flowing through 08 is reduced, and it becomes impossible to sufficiently obtain the vibration damping action due to the liquid column resonance of the orifice 108. That is, the partition rubber 111
As a result, the fluctuation of the hydraulic pressure is absorbed, so that there is a problem that the damping effect by the orifice 108 cannot be sufficiently obtained for the vibration input in the low frequency range.

Further, in order to suppress the vibration transmission at the time of inputting vibration in a high frequency range by using the mass member, there is also a demand to make the mass of the mass member as small as possible to make the engine mount compact.

The present invention has been made in view of the above circumstances, and an object thereof is to reduce the mass of the mass member while sufficiently ensuring the damping effect on the vibration input in the low frequency range. Is to try.

[0006]

In order to achieve the above object, the invention according to claim 1 connects a pair of mounting members which are arranged apart from each other in the vibration input direction and the pair of mounting members. An elastic support, a liquid chamber defined by the elastic support and containing a liquid, a pressure receiving chamber on the elastic support side, and at least a part of the liquid chamber defined by an elastic thin film member A partition that divides into a possible equilibrium chamber,
It is assumed that the pressure receiving chamber and the equilibrium chamber are provided with an orifice communicating with each other. In this, at least a mass member formed of a material having a specific gravity larger than that of the liquid is provided. Then, this mass member is formed in such a manner that it spreads in a direction orthogonal to the vibration input direction of the pressure receiving chamber, and the pressure receiving chamber is displaced in the vibration input direction, and is not supported in the liquid in the pressure receiving chamber. It is configured to be settled in the state.

According to a second aspect of the present invention, in the first aspect of the invention, the mass member is provided with a through hole penetrating in the vibration input direction.

According to a third aspect of the invention, in the invention of the first aspect, the guide member guides the mass member so as to be freely displaceable only in the vibration input direction and restricts the displacement in the direction orthogonal to the vibration input direction. Is provided.

According to a fourth aspect of the present invention, in the invention according to the third aspect, the guide member is constituted by a guide rod having the following constitution. That is, the guide rod is configured such that one end is connected to the mounting member on the pressure receiving chamber side and the other end is projected into the pressure receiving chamber in the vibration input direction and penetrates the mass member in a loosely fitted state.

According to a fifth aspect of the present invention, in addition to the third aspect of the invention, a bulky member having the following configuration is provided. That is, as the bulky member, one end is connected to the mounting member on the pressure-receiving chamber side and the other end is protruded toward the pressure-receiving chamber in the vibration input direction, and the vibration from the other end-side position of the supporting rod. It is provided with a bulge portion that expands in a direction orthogonal to the input direction. The guide member is composed of the support rod.

Further, the invention according to claim 6 is the same as claim 1.
In the invention described above, the elastic bearing members are arranged on the lower side and the elastic thin film members are arranged on the upper side, and the pressure receiving chamber is positioned on the lower side of the equilibrium chamber. Further, the mass member is arranged on the inner surface of the elastic support in a state of sinking.

[0012]

With the above construction, in the invention according to claim 1,
Since the mass member is placed in an unsupported state in the pressure receiving chamber, even if the elastic bearing flexes and the hydraulic pressure in the pressure receiving chamber fluctuates due to the input of low-frequency vibration, the mass member absorbs the fluctuation in hydraulic pressure. The amount of liquid corresponding to the fluctuation of the hydraulic pressure flows through the orifice without any movement. As a result, the input vibration in the predetermined low frequency range is damped by the orifice. In addition, as described above, since the mass member is in the unsupported state to eliminate the existence of the support spring, compared to the above-described conventional engine mount in which the mass member is elastically supported by the support spring, If the mass members have the same mass, the peak frequency of the dynamic spring constant is on the low frequency side because there is no support spring. Therefore, it is possible to reduce the mass of the mass member necessary for achieving the same peak frequency as that of the conventional one, and it is possible to reduce the mass of the mass member and reduce the number of parts, thereby achieving overall compactness and cost reduction.

According to the second aspect of the present invention, in addition to the function of the first aspect of the present invention, since the through hole is formed in the mass member so as to penetrate in the vibration input direction, the elastic bearing is supported by the load of the engine's own weight. Even if the mass member is settled and seated where the body is deformed and its inner surface becomes a flat state, for example, the flow of the liquid to the inner surface side of the elastic bearing body is ensured through the through hole. This prevents the mass member from sticking tightly to the inner surface of the elastic support member due to the action of the fluctuation of the hydraulic pressure, thus ensuring the free displacement of the mass member in the vibration input direction.

According to the third aspect of the invention, in addition to the action of the first aspect of the invention, since the movement of the mass member in the direction orthogonal to the vibration input direction is restricted by the guide member, the mass member is It is freely displaced only in the vibration input direction. Therefore, when vibration is input, displacement in the orthogonal direction and contact or collision with the inner peripheral surface of the pressure-receiving chamber are avoided, which causes abnormal noise such as collision noise that may occur without the above restrictions. Is prevented from occurring.

According to the invention described in claim 4, in addition to the operation according to the invention described in claim 3, the guide member is constituted by a guide rod penetrating the mass member in a vibration input direction in a loosely fitted state. Therefore, the movement restriction of the mass member can be reliably performed with a simple configuration.

In addition, in the invention described in claim 5, in addition to the action according to the invention described in claim 3, since the guide member is also used by the support rod of the bulky member, a special guide member is newly provided. Without restricting the displacement direction of the mass member. In addition, the vibration damping characteristics in a wider frequency range can be obtained by tuning the bulky member and the mass member.

Further, in the invention described in claim 6, in addition to the operation according to the invention described in claim 1, since the elastic bearing is arranged under the partition, the inner surface of the elastic bearing is provided in the pressure receiving chamber. Will be located at the bottom of. For this reason, the mass member normally sinks in the pressure receiving chamber and is seated on the inner surface of the elastic support body, so that noise is prevented from being generated due to collision with the inner surface during vibration input in the high frequency range. It

[0018]

Embodiments of the present invention will be described below with reference to the drawings.

<First Embodiment> FIG. 1 shows a liquid filled engine mount according to a first embodiment of the present invention, in which 1 is a cylinder shaft X in a vibration input direction (vertical direction in FIG. 1; Direction), a cylindrical first mounting member 2 arranged on the upper side, 2 a second mounting member arranged on the lower side, 3 an elastic support member for connecting both mounting members 1 and 2 to each other, A liquid chamber 7 is defined between the elastic support 3 and a diaphragm 5 which is an elastic thin film member and in which an incompressible liquid 6 is enclosed. Reference numeral 7 denotes the liquid chamber 4 on the elastic support 3 side. The partition member 8 partitions the pressure receiving chamber 4a on the side and the equilibrium chamber 4b on the side of the diaphragm 4, and 8 is a mass member arranged in the pressure receiving chamber 4a. The configuration of each component will be described below.

The first mounting member 1 is formed by integrally connecting a first support cylinder 11 that is opened vertically and a bottomed second support cylinder 12 that closes the upper end opening side of the first support cylinder 11. It has been configured. That is, a bent edge 12a bent in the outer peripheral direction is formed at the lower end of the second support cylinder 12, while the concave stepped portion 11a formed at the inner peripheral surface of the upper end of the first support cylinder 11 has the above-mentioned shape. A crimped portion 11b is formed so as to sandwich the bent edge 12a from above and below in a state where the bent edge 12a is fitted therein, and both 11 and 12 are integrated with each other. The mounting bolts 13 projecting upward from the second support cylinder 12 along the cylinder axis X are connected to a vibration generating source such as an engine.

The second mounting member 2 is formed by integrating a bottomed cylinder 14, a plate portion 15, and a mounting bolt 16 protruding downward from the plate portion 15 along the cylinder axis X. Yes, it is located on the lower end opening side of the first support cylinder 11 and on the cylinder axis X. The mounting bolt 16 is connected to a vibration receiving portion, for example, a bracket of a vehicle body.

The elastic support member 3 has the second mounting member 2
Further, it is integrally vulcanized and molded with the lower end portion of the first support cylinder 11 of the first mounting member 1 to connect the both 1, 2 to each other.
In addition, a thin rubber layer 3a that covers the inner peripheral surface of the upper end of the first support cylinder 11 up to the recessed step portion 11a is integrally vulcanized and bonded to the elastic support body 3. In addition to the bent edge 12a, the flange portion of the partition body 7 and the outer peripheral portion of the diaphragm 5 are overlapped with each other between the rubber thin layer 3a of the recessed step portion 11a and the caulked portion 11b. The partition body 7 and the diaphragm 5 are attached to the first attachment member 1 by being sandwiched between them.

The partition 7 is provided with a housing chamber 17 formed inside the central portion thereof, and a movable plate 1 made of rubber or synthetic resin housed in the housing chamber 17 so that it can be finely displaced vertically.
8 and an annular orifice 19 formed inside the outer peripheral portion
It has and. One end 19a of the orifice 19 is opened to the pressure receiving chamber 4a, and the other end 19b is opened to the equilibrium chamber 4b, so that the liquid 6 in the pressure receiving chamber 4a and the equilibrium chamber 4b can flow to each other through the orifice 19. The length and cross-sectional area of the orifice 19 are set so as to dampen vibrations in a predetermined low frequency range input in the vertical direction due to resonance of the liquid column when the liquid 6 flows. The accommodating chamber 17 is communicated with each of the pressure receiving chamber 4a and the equilibrium chamber 4b by a plurality of communication holes 21, 21, ... Penetrating the housing 20, and receives the fluctuation of the hydraulic pressure from the pressure receiving chamber 4a to receive the movable plate. The volume compensation of the pressure receiving chamber 4a is performed especially for medium to high frequency vibrations in which the orifice 19 is locked due to the clogging of the orifice 19 by causing a slight displacement of the pressure receiving chamber 4a. That is, the volume is changed. The orifice 19 is formed in the outer peripheral portion of the pair of vertically stacked plate-like members 7a and 7b in the range of C-shape in plan view, and the housing 20 is provided.
Are formed by being fitted into the through holes at the central portions of the pair of plate-shaped bodies 7a and 7b from above and below and coupled to each other.

The mass member 8 has a relatively thick circular plate shape having an outer diameter smaller than the inner diameter of the pressure receiving chamber 4a,
It is formed of a material such as metal having a specific gravity larger than that of the liquid 6. The mass member 8 is coaxial with the cylinder axis X and extends in a direction orthogonal to the cylinder axis X so as to expand.
It is placed in the liquid 6 in a in an unsupported state, and when it is stationary, it sinks in the liquid 6 and sits on the mortar-shaped inner surface 3b of the elastic support 3 that defines the bottom of the pressure receiving chamber 4a. There is. The mass of the mass member 8 is the same as that of the movable plate 18 described above.
It is determined that the dynamic damper function is exerted in the frequency range on the higher frequency side than the frequency of the volume compensation area of the pressure receiving chamber 4a. Further, a through hole 8a having a relatively large diameter is formed in the center of the mass member 8 so as not to be clogged by the input vibration in the frequency range received by the engine mount, and penetrates in the vertical direction. In the seated state, the free flow of the liquid 6 is ensured in the upper and lower portions of the pressure receiving chamber 4a with the mass member 8 interposed therebetween.

Next, the operation of the first embodiment having the above-mentioned structure,
The effect will be described.

When a low frequency vibration is input to the elastic support 3 in the vertical direction from the first mounting member 1 side, the elastic support 3
Is bent in the vertical direction, and the liquid 6 in the pressure receiving chamber 4a flows through the orifice 19 to the equilibrium chamber 4b. And
The liquid column resonance is caused by the flow of the liquid 6 through the orifice 19, and the liquid column resonance attenuates the vibration in the low frequency range. When the input vibration is on the higher frequency side and the orifice 19 locks in a clogged state in which the flow of the liquid 6 through the orifice 19 does not substantially occur, the pressure is received by the volume compensation due to the displacement of the movable plate 18. The increase of the internal pressure in the chamber 4a is suppressed, and the vibration transmissibility is reduced.

When the input vibration is on the higher frequency side, the mass member 8 is relatively displaced to the opposite phase side to the first mounting member 1 in the frequency region up to the set resonance frequency of the mass member 8, while the above-mentioned setting is made. When the resonance frequency is exceeded, the mass member 8 is displaced toward the same phase as the first mounting member 1, and the phase is inverted at the resonance point. Due to the relative displacement to the opposite phase side, the internal pressure rise in the pressure receiving chamber 4a is suppressed, and the vibration transmissibility is reduced.

In the liquid-filled engine mount which exhibits vibration damping characteristics over a wide range of frequency regions, since the mass member 8 is settled in the pressure receiving chamber in an unsupported state, the partition wall rubber as shown in FIG. 6 is used. Unlike the conventional engine mount in which the pressure receiving chamber 105 is defined by the mass member 109 connected by 111, even if the elastic support body bends and the hydraulic pressure in the pressure receiving chamber 4a fluctuates due to the input of low frequency vibration. The mass member 8 does not absorb the fluctuation of the hydraulic pressure. As a result, as a result of the amount of the liquid 6 flowing through the orifice 19 depending on the fluctuation of the hydraulic pressure, it is possible to surely attenuate the input vibration in the predetermined low frequency range by the orifice 19.

In addition, as described above, since the mass member 8 is unsupported to eliminate the existence of the support spring 110 and the like, the mass member 109 is supported by the support spring 110 as in the conventional engine mount described above. When the mass members 8 and 109 have the same mass, the peak frequency of the dynamic spring constant is on the low frequency side, as compared with the configuration in which the mass members 8 and 109 have the same mass. That is, the same shape (diameter 63,
9 mm, wall thickness 4 mm), the same mass (95 g) using the mass member of the present example and the conventional engine mount, as shown in the comparative test results of the relationship between the absolute spring constant and phase with respect to frequency Resonance point (peak frequency) A of absolute spring constant with respect to frequency in the embodiment
Is on the lower frequency side than the resonance point B of the conventional one, and the phase inversion angle (see the curve indicated by a in the figure) in the case of the present embodiment in the frequency region beyond the resonance point is -1 than the case of the thing (see the curve indicated by b in the figure)
Get closer to 80 degrees.

Regarding this point, further consideration is given as follows.
In the conventional structure shown in FIG. 6, the expansion spring constant of the elastic support 103 is K1, the support spring constant of the support rubber block 110 is K2, the spring constant of the partition rubber 111 is K3, the spring constant of the diaphragm 106 is K4, and the mass. Member 109
It is experimentally obtained that the peak frequency f1 of the dynamic spring constant of phase inversion can be approximately represented by the following equation (1), where m is the mass of

F1 = (1 / 2π) × √ {(K1 + K2 + K3 + K4) / m} (1) Here, the supporting rubber block 110 and the partition rubber 1
The peak frequency f2 when the respective spring constants K2 and K3 of 11 are removed is obtained by substituting K2 = K3 = 0 into the above equation (1), and f2 = (1 / 2π) × √ {(K1 + K4) / m} is represented by (2).

Therefore, when the mass member is in the unsupported state, its peak frequency f2 is K2 more than f1 when it is elastically supported by the supporting rubber block 110 or the like.
, K3 does not exist, so it can be set to the low frequency side. In other words, the peak frequency is the same as the conventional one (f1 = f
In the case of 2), the mass of the mass member necessary for the mass member 8 can be made smaller (lighter) than the conventional case.
The weight of the engine mount can be reduced, and the number of parts can be reduced by omitting the support rubber block 110 and the partition rubber 111 from the above-described conventional one, and the engine mount as a whole can be made compact and the cost can be reduced. .

Further, since the through hole 8a is formed in the mass member 8, the elastic support body 3 is deformed by the load of the engine's own weight on the side of the first mounting member 1 and the inner surface 3b thereof becomes flat, for example. Even if the entire lower surface of the mass member 8 comes into contact with the inner surface 3b or is sandwiched from both sides, the inner surface 3 of the elastic support body 3 is inserted through the through hole 8a.
Since the flow of the liquid 6 is ensured on the side of b and the hydraulic pressure acts, the mass member 8 is stuck to the inner surface 3b of the elastic support body 3 and sticks to the inner surface 3b of the elastic support body 3 to prevent its free displacement. It can be reliably prevented. Therefore, the effect of reducing the vibration transmissibility by the mass member 8 can be reliably obtained.

<Second Embodiment> FIG. 2 shows a liquid filled engine mount according to a second embodiment of the present invention. The second embodiment is provided with a guide member for allowing the displacement direction of the mass member only in a predetermined direction and restricting the displacement in other directions. In the figure, 22 is a mass member and 23 is this mass member. It is a guide pin (guide rod) as a guide member that regulates the displacement direction of the member 22.

The guide pin 23 is arranged such that the lower end portion 23a is fixed to the bottomed cylinder 14 of the second mounting member 2 and the upper end portion 23b projects upward in the pressure receiving chamber 4a along the cylinder axis X. ing.

Further, the mass member 22 is formed of a material having a specific gravity larger than that of the liquid 6 as in the case of the first embodiment 8, and the outer diameter of the guide pin 23 along the cylinder axis X is formed in the central portion. A through hole 22a having a larger inner diameter is formed. Then, the guide pin 2 is inserted into the through hole 22a.
The mass member 22 is externally inserted into the guide pin 23 from above so that 3 is inserted into the upper end portion 23 of the guide pin 23.
b is projected above the mass member 22 by a predetermined dimension. The through hole 22a has a diameter larger than the guide pin 22 by a predetermined dimension so that the liquid 6 can freely flow between the outer peripheral surface of the guide pin 22 and the inner peripheral surface of the through hole 22a. There is.

Further, the inner surface 3b of the elastic support 3 facing the lower surface of the mass member 22 has two or more protrusions 3c,
3c, ... Are integrally formed with the elastic support body 3, and the mass member 22 in a state of being settled in the pressure receiving chamber 4a is formed by each of the convex portions 3a.
It sits on the apex of c in a substantially point contact state.

Since the other construction of the liquid filled engine mount is the same as that of the first embodiment,
The same members are designated by the same reference numerals and the description thereof will be omitted.

In the case of the second embodiment, the effect of reducing the vibration transmissibility by the mass member 22 and the effect of the mass member 22 being provided in an unsupported state are the same as in the first embodiment. In addition to being able to obtain, the following actions and effects can be obtained. That is, since the displacement of the mass member 22 in the vertical direction is allowed by the guide pin 23 and the displacement in the direction orthogonal thereto (the direction orthogonal to the vibration input direction) is restricted, the orthogonal direction at the time of vibration input. It is possible to reliably avoid contact with or collide with the inner peripheral surface of the pressure receiving chamber 4a due to displacement to the above, thereby preventing generation of abnormal noise such as collision noise that may occur without the above regulation. can do. Moreover, the displacement direction regulation for preventing such abnormal noise generation can be easily and reliably achieved by a simple configuration in which the guide pin 23 is simply inserted into the through hole 22a.

<Third Embodiment> FIG. 3 shows a liquid filled engine mount according to a third embodiment. In the third embodiment, the mass member guide member is also used as a bulk member. In the figure, 24 is a bulk member arranged in the pressure receiving chamber 4a, and 25 is a bulk member 24. The mass member is provided so as to be vertically displaceable.

The bulky member 24 has a support rod portion 24a having a cylindrical shape with a bottom which is open upward, and a bulky portion 24 having a predetermined diameter which extends from the upper end of the support rod portion 24a in the direction orthogonal to the cylinder axis X.
b is integrally formed with the support rod 24
It is fixed to the bottomed cylinder 14 of the second mounting member 2 by a bolt 26 penetrating the bottom wall of a. And the above-mentioned umbrella part 24
b is arranged at a predetermined size above the elastic support 3'by the support rod 24a, and the pressure receiving chamber 4a is divided into an upper portion and a lower portion by the umbrella portion 24b.
Both portions are communicated with each other through an annular gap 27 having a predetermined width between the outer peripheral portion of the above-mentioned umbrella portion 24b and the inner peripheral surface of the pressure receiving chamber 4a.

The mass member 25 is made of the same material as that of the first embodiment, and has a through hole 25a having an inner diameter larger than the outer diameter of the support rod 24a formed along the cylinder axis X in the central portion. There is. Then, in a state of being externally inserted into the support rod portion 24a by the through hole 25a, a flat step portion 3d formed on the lower surface of the umbrella portion 24b and the inner surface of the elastic support body 3 '.
The mass member 25 is displaceable only in the vertical direction, and its displacement in the direction orthogonal thereto is restricted.

Since the other constructions of the liquid-filled engine mount are the same as those of the first embodiment,
The same members are designated by the same reference numerals and the description thereof will be omitted.

In the case of the third embodiment, the effect of reducing the vibration transmissibility by the mass member 25 and the effect of the mass member 25 being provided in an unsupported state are the same as in the first embodiment. Obtainable. In addition, since the displacement of the mass member 25 in the vertical direction is permitted by the support rod 24a of the bulky member 24 and the displacement in the direction orthogonal thereto is restricted, the mass member 2 is input at the time of vibration input.
It is possible to surely avoid a collision between the inner peripheral surface of the pressure receiving chamber 4a and the pressure sensor 5 and to prevent the generation of an abnormal noise such as the collision noise as in the second embodiment.

In addition, in this case, since the displacement direction of the mass member 25 is regulated by using the bulky member 24, the generation of abnormal noise is prevented without installing a special guide member and the mass member 25 is prevented. It is possible to regulate and guide the displacement direction. In addition, the bulky member 24 is relatively displaced in the vertical direction together with the elastic support 3 when the high frequency vibration is input to forcibly flow the liquid 6 in the pressure receiving chamber 4a through the annular gap 27, thereby reducing the vibration transmissibility. In addition to the effect, by tuning the bulky member 24 and the mass member 25 to different frequency regions even in the high frequency region, it is possible to obtain the vibration isolation characteristics in a wider frequency region.

<Fourth Embodiment> FIG. 4 shows a liquid filled engine mount according to a fourth embodiment. The fourth embodiment shows another mode in which the guide member of the mass member is shared with the bulky member similarly to the third embodiment, and in the figure, 28 is arranged in the pressure receiving chamber 4a. Made umbrella-shaped member, 2
Reference numeral 9 is a mass member provided on the bulky member 28 so as to be vertically displaceable.

The umbrella-shaped member 28 has a lower end fixed to the bottomed cylinder 18 of the second mounting member 2 and an upper end protruding upward along the cylinder axis X into the pressure receiving chamber 4a. When,
An umbrella member 31 fixed to the support rod member 30 and arranged in the pressure receiving chamber 4a at a position above the elastic support member 3 by a predetermined dimension.
It consists of and. The umbrella member 31 has a narrowed portion 31a formed at the lower end and an enlarged diameter portion 31 having a predetermined diameter at the upper end.
b is formed, and while the narrowed portion 31a is attached to the support rod member 30, the enlarged diameter portion 3 is formed.
The pressure receiving chamber 4a is divided into an upper portion and a lower portion by 1b, and both portions are communicated with each other through an annular gap 32 having a predetermined width between the outer peripheral portion of the expanded diameter portion 31b and the inner peripheral surface of the pressure receiving chamber 4a. ing.

The mass member 29 is formed of a material similar to that of the first embodiment so that the lower surface thereof has a shape corresponding to the inner surface shape of the above-mentioned umbrella member 31, and the supporting rod member along the cylinder axis X is formed in the central portion. A through hole 29a having an inner diameter larger than the outer diameter of 30 is formed. Then, in a state of being externally inserted into the support rod member 30 through the through hole 29a, the umbrella member 31 is formed.
It is placed on the inner surface of the seat. On the other hand, the support rod member 30 is set to have a length such that the upper end portion 30a of the support rod member 30 penetrates the through hole 29a of the mass member 29 upward and then projects by a predetermined dimension. It is possible to displace only at and the displacement in the direction orthogonal to it is restricted. Further, a rubber thin film 33 is vulcanized and adhered to the inner surface of the umbrella member 31 so as to prevent a collision noise when the mass member 29 is displaced in the vertical direction.

Since the other construction of the liquid-filled engine mount is the same as that of the first embodiment,
The same members are designated by the same reference numerals and the description thereof will be omitted.

In the case of the fourth embodiment, the effect of reducing the vibration transmissibility by the mass member 29 and the effect of the mass member 29 being provided in an unsupported state are the same as in the first embodiment. In addition to the above, the mass member 29 is freely displaced only in the vertical direction by the support rod member 30 of the bulky member 28, and the displacement in the direction orthogonal thereto is restricted. Mass member 2
It is possible to surely avoid a collision between the inner peripheral surface of the pressure receiving chamber 4a and the inner peripheral surface of the pressure receiving chamber 4a, and to prevent the generation of an abnormal noise such as a collision noise as in the second embodiment. In addition, since the displacement direction of the mass member 29 is regulated by using the umbrella member 28, the mass member is prevented from being generated without installing a special guide member as in the third embodiment. It is possible to provide guidance in the displacement direction of 29. Further, the effect of reducing the vibration transmissibility by the bulky member 28 and the vibration damping characteristics in a wider frequency range can be obtained as in the third embodiment.

<Other Embodiments> The present invention is based on the above first to third embodiments.
The present invention is not limited to the fourth embodiment and includes various other modified examples. That is, in the above embodiment, the first mounting member 1 is connected to the engine side and the second mounting member 2 is connected to the vehicle body side. However, the present invention is not limited to this. For example, in a type in which the engine is suspended and supported, the first mounting member is mounted. The member may be connected to the vehicle body side and the second mounting member may be connected to the engine side.

In the above embodiment, the first mounting member 1 is connected to the engine side and the second mounting member 2 is connected to the vehicle body side so that the elastic support body 3 and the pressure receiving chamber 4a are located on the lower side. However, the invention is not limited to this, and the elastic support 3 and the pressure receiving chamber 4a may be positioned upside down by reversing the top and bottom. In this case, the upper end portion 23b of the guide pin 23 of the second embodiment,
Alternatively, the upper end portion 30a of the support rod member 30 of the fourth embodiment.
May be further protruded by a predetermined dimension and a diameter-expanded portion may be provided at the protruding end to serve as a stopper portion that regulates the vertical movement range of the mass members 22 and 29.

Further, in the above embodiment, the orifice 19
Although the partition 7 is formed in the partition body 7 itself, the invention is not limited to this, and the orifice may be formed completely independently of the partition body, for example.

[0054]

As described above, according to the liquid-filled engine mount according to the first aspect of the present invention, the mass member is arranged in the pressure receiving chamber in a non-supported state. Even if the elastic support flexes and the hydraulic pressure in the pressure receiving chamber fluctuates, the aforementioned hydraulic pressure fluctuation in the engine mount arranged so as to define the pressure receiving chamber by connecting the conventional mass member with the rubber partition wall is absorbed. As a result of the flow of the liquid through the orifice in an amount corresponding to the fluctuation of the liquid pressure without causing the above adverse effect, it is possible to reliably obtain a predetermined low frequency vibration damping by the orifice. In addition, as described above, since the mass member is not supported and the existence of the support spring is eliminated, the mass member is supported by the support spring unlike the conventional engine mount described above. If the mass is the same, the peak frequency of the dynamic spring constant can be set to the low frequency side because there is no support spring, while the mass of the mass member required to make the peak frequency the same as the conventional one can be reduced. Therefore, the weight of the mass member and the reduction in the number of parts can reduce the overall size of the engine mount.

According to the second aspect of the present invention, in addition to the effect of the first aspect of the present invention, since the through hole penetrating the mass member in the vibration input direction is formed, Even if it sinks and sits in close contact with the bottom surface of the pressure receiving chamber or is sandwiched between elastic bearings, it is possible to ensure the flow of liquid to the bottom surface side of the pressure receiving chamber through the through hole,
Due to the action of the hydraulic pressure, the mass member is prevented from being fixed in position, and the free displacement in the vibration input direction can be reliably ensured. For example, when the mass member sinks and bottoms on the inner surface of the elastic bearing that is deformed into a flat state due to the load of the engine's own weight, etc., the mass member comes into close contact with the inner surface of the elastic bearing. It is possible to reliably prevent sticking.

According to the invention of claim 3, in addition to the effect of the invention of claim 1, the displacement direction of the mass member is restricted by the guide member so as not to displace in the direction orthogonal to the vibration input direction. Therefore, it is possible to prevent the mass member from coming into contact with or colliding with the inner peripheral surface of the pressure receiving chamber in the orthogonal direction at the time of inputting a vibration, and as a result, a collision noise that may occur without the above regulation. It is possible to reliably prevent the generation of noise such as.

According to the invention of claim 4, in addition to the effect of the invention of claim 3, the guide member is constituted by a guide rod penetrating the mass member in a vibration input direction in a loosely fitted state. Therefore, the displacement direction of the mass member can be regulated easily and reliably with a simple structure.

According to the invention described in claim 5, in addition to the effect of the invention described in claim 3, since the supporting rod of the bulky member also serves as a guide member, a special guide member is provided. It is possible to regulate the displacement direction of the mass member without newly providing. In addition, by tuning the bulk member and the mass member, it becomes possible to obtain vibration damping characteristics in a wider frequency range.

Further, according to the invention of claim 6, in addition to the effect of the invention of claim 1, an elastic bearing member is arranged below the partition member so that the inner surface of the elastic bearing member serves as a pressure receiving chamber. Since the bottom portion is defined, it is possible to prevent the occurrence of a collision noise when the mass member sinks in the pressure receiving chamber and sits on the inner surface of the elastic support.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a first embodiment of the present invention.

FIG. 2 is a vertical sectional view showing a second embodiment of the present invention.

FIG. 3 is a vertical sectional view showing a third embodiment of the present invention.

FIG. 4 is a vertical sectional view showing a fourth embodiment of the present invention.

FIG. 5 is a relationship diagram between frequency, absolute spring constant and phase,

FIG. 6 is a vertical sectional view of a conventional liquid-filled engine mount including a mass member.

[Explanation of symbols]

1 1st mounting member 2 2nd mounting member 3,3 'elastic support 3b inner surface of elastic support 3d flat part (inner surface of elastic support) 4 liquid chamber 4a pressure receiving chamber 4b equilibrium chamber 5 diaphragm (elastic thin film member) 6 Liquid 7 Partition Body (Vibration Plate) 8, 22, 25, 29 Mass Member 19 Orifice 22a, 25a, 29a Through Hole 23 Guide Pin (Guide Rod, Guide Member) 24, 28 Cavity Member 24a Support Rod (Support Rod) , Guide member) 24b umbrella portion 30 support rod member (support rod, guide member) 31 umbrella member (bulb portion)

Claims (6)

[Claims] 1. A pair of mounting members which are arranged apart from each other in a vibration input direction, an elastic support member which connects the pair of mounting members to each other, and a liquid which is defined by the elastic support member and contains a liquid. A chamber, a partitioning body for partitioning the liquid chamber into a pressure receiving chamber on the side of the elastic bearing and a balance chamber at least a part of which is defined by an elastic thin film member and is expandable and contractible, and the pressure receiving chamber and the equilibrium chamber. A control type vibration damping device having an orifice communicating with at least a mass member formed of a material having a specific gravity larger than that of the liquid, the mass member being in a direction orthogonal to the vibration input direction of the pressure receiving chamber. A liquid-filled engine machine, which is formed in a shape capable of being displaced in the vibration input direction in the pressure receiving chamber and is settled unsupported in the liquid in the pressure receiving chamber. Cement. 2. The liquid-filled engine mount according to claim 1, wherein the mass member has a through hole penetrating in the vibration input direction. 3. The liquid-filled engine mount according to claim 1, further comprising a guide member that guides the mass member so as to be freely displaceable only in a vibration input direction and restricts displacement in a direction orthogonal to the vibration input direction. . 4. The guide member according to claim 3, wherein one end of the guide member is connected to the mounting member on the pressure receiving chamber side, and the other end is projected into the pressure receiving chamber in the vibration input direction to penetrate the mass member in a loosely fitted state. Liquid-filled engine mount composed of rods. 5. The supporting rod according to claim 3, one end of which is connected to the mounting member on the pressure receiving chamber side and the other end of which is projected toward the pressure receiving chamber in the vibration input direction, and the other end side position of the supporting rod. To the vibration input direction, the liquid-filled engine mount is provided with a bulge-shaped member formed of a bulge portion that extends in a direction orthogonal to the vibration input direction, and the guide member includes the support rod. 6. The elastic supporting member according to claim 1, wherein the elastic thin film member is arranged on the lower side, the pressure receiving chamber is positioned on the lower side of the equilibrium chamber, and the mass member is an inner surface of the elastic supporting member. Liquid-filled engine mount that is placed in a settled state above.