JPH06346942A - Liquid sealed type engine mount - Google Patents

Abstract

PURPOSE:To damp by an orifice by way of positioning and fixing a partition body against low frequency oscillation, to prevent jumping of a dynamic spring by liquid-operated control by way of easily relatively displacing the partition body without providing a special driving means against high frequency oscillation and to reduce energy required for relative displacement of the partition body. CONSTITUTION:The upper end part of a support cylindrical body 10 and an installation member 3 are connected to each other by an elastic bearing body 4. By fixing a diaphragm 5 on a lower part inner peripheral surface of the support cylindrical body 10, a liquid cell 12 is formed between the diaphragm 5 and the elastic bearing body. By partitioning the liquid cell 12 into a pressure cell 13 and a balancing cell 14 by a partition body 6, an orifice 7 to communicate both of the cells 13, 14 through to each other is formed elastically supported by sandwiching it from above and below by a first elastic member 8 and a second elastic member 9 respectively made in a pre-compressed state, and spring constant of the second elastic member 9 is made smaller than that of the first elastic member 8. Additionally, a driving means to forcibly excite the partition body can be provided.

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 used as a mount for an automobile engine.

[0002]

2. Description of the Related Art Conventionally, as a liquid-filled engine mount of this type, a liquid chamber is defined inside a supporting cylinder having an elastic support member attached to one end, and a part of the liquid chamber is defined. So that the plate body is connected to the support cylinder through an elastic member so that the plate body can be displaced relative to the liquid chamber side, and the relative displacement of the plate body increases the hydraulic pressure. There are known ones that have been attempted to be suppressed (for example, JP-A-3-
24338). In this device, a metal plate body is reciprocally moved by using a combination of a permanent magnet and an electromagnet, and this reciprocating motion is performed when high frequency vibration is input. Then, the spring constant of the elastic member is set to be larger than the spring constant of the elastic bearing body so that the plate body does not cause relative displacement when a low frequency vibration is input. That is, even if the elastic support body is deformed when the low frequency vibration is input, the elastic member is prevented from being deformed following this deformation.

[0003]

However, in the above-mentioned conventional liquid-filled engine mount, since the plate is supported by using a single elastic member, the plate is resistant to low frequency vibration. In order to fix the position so that relative displacement does not occur, set the whole elastic member to a fairly high spring constant,
In other words, it has to be fairly hard. in this case,
If the elastic member is made quite hard, the position fixing is satisfied, but in order to reciprocate at the time of high frequency vibration input, a considerably large driving energy corresponding to the spring constant of the elastic member multiplied by the displacement amount. Are required in the above electromagnet. Since a relatively large number of engine mounts are mounted on one vehicle, the electric energy required to operate the electromagnets of all engine mounts is extremely large. On the other hand, if the driving energy is made relatively small, the amount of forced displacement of the plate body correspondingly becomes small, and as a result, it becomes impossible to sufficiently reduce the dynamic spring constant by the hydraulic pressure control.

Further, since the plate member is supported by such an elastic member, in order to displace the plate member, a special compulsory driving means such as the above-mentioned electromagnet is required, and the above-mentioned conventional liquid is used. Enclosed engine mounts add complexity to the configuration.

The present invention has been made in view of such circumstances, and an object of the present invention is to fix low-frequency vibration by positioning a partition member to attenuate it by an orifice, thereby reducing high-frequency vibration. On the other hand, it is to prevent the sudden increase of the dynamic spring constant (dynamic spring jump) due to the hydraulic pressure control by easily displacing the partition body without providing a special drive means. In addition, it is intended to reduce the energy required for the relative displacement regardless of the presence or absence of the driving means for forcibly making the relative displacement of the partition body.

[0006]

In order to achieve the above-mentioned object, the invention according to claim 1 is arranged so that one end is directed toward the vibration source side and the other end is directed toward the vibration receiving part. A supporting cylinder, a mounting member arranged on the one end side of the supporting cylinder and connected to the vibration source side, and the mounting member and one end of the supporting cylinder. An annular elastic support member that is connected to each other, an elastic partition member that is connected to the inner peripheral surface of the support cylinder and forms a liquid chamber in which liquid is sealed between the elastic support member, and the liquid chamber A partition body is provided for partitioning the pressure receiving chamber on the elastic bearing side and the equilibrium chamber on the elastic partition member side, and an orifice formed in the partition body for communicating the pressure receiving chamber and the equilibrium chamber with each other. And, the partition body,
The partition body is supported by the support cylinder through a pair of independent elastic members sandwiching the partition body from both sides in the vibration input direction. In addition, the pair of elastic members are respectively interposed in a pre-compressed state so as to exert a compression restoring force from both sides in the vibration input direction toward the partition body.

According to a second aspect of the present invention, in addition to the first aspect of the invention, a drive means for forcibly exciting the partition body in the vibration input direction according to the input vibration is provided.

Further, the invention according to claim 3 is the same as claim 1.
Alternatively, in the invention of claim 2, the elastic member of the pair of elastic members, which is resistant to relative displacement of the partition body in the direction of expanding the pressure receiving chamber, is set to have a smaller spring constant than the elastic members of the other side. It is configured to do.

[0009]

With the above construction, in the invention according to claim 1,
The elastic support body is bent by the input of the low-frequency vibration from the mounting member side and the pressure receiving chamber side is contracted, so that hydraulic pressure acts on the partition body from the pressure receiving chamber side. At this time, the partition body having the orifice is sandwiched by a pair of elastic members from both sides in the vibration input direction, and the elastic members are pre-compressed so that compression restoring forces in different directions are applied to the partition body. Since the partition body is supported in the actuated state, movement of the partition body in the vibration input direction is restricted and the position is substantially fixed. Therefore, the flow of the liquid from the pressure receiving chamber to the equilibrium chamber is ensured through the orifice, and the liquid column resonance through the orifice resulting from the flow of the liquid causes
Attenuation of the low frequency vibration is achieved.

On the other hand, when high-frequency vibration is input from the mounting member side and the orifice is in a so-called clogging state, the hydraulic pressure in the pressure receiving chamber rises. And that hydraulic pressure
When the pre-compression load of the elastic member on one side exerting the compression restoring force in the direction opposite to the acting direction of the hydraulic pressure is exceeded, the partition body expands the pressure receiving chamber against the elastic member on the one side. Relative displacement in the direction. Therefore, the hydraulic pressure is prevented from further increasing in the pressure receiving chamber, and the jump of the dynamic spring is prevented. At this time, the relative displacement of the partition body occurs because a force exceeding the compression restoring force of only one side of the pair of elastic members elastically supporting the partition body acts, so that the partition body is supported. The energy required for the relative displacement of the partition body can be reduced as compared with the conventional case where the relative displacement is performed against the spring elastic force of the entire elastic member.

Further, in the invention described in claim 2, in addition to the operation according to the invention described in claim 1, since the drive means for forcibly exciting the partition body in the vibration input direction is provided, the high frequency vibration input is provided. At this time, by forcibly displacing the partition body in the direction in which the pressure receiving chamber is expanded in response to the input in the direction in which the hydraulic pressure in the pressure receiving chamber rises, a sudden increase in hydraulic pressure in the pressure receiving chamber is reliably prevented. The jump of the dynamic spring is surely prevented. At this time, since the driving energy required to relatively displace the partition body has a force that opposes only one side of the pair of elastic members elastically supporting the partition body, the partition body is supported. The drive energy of the drive means can be reduced as compared with the conventional case in which the elastic member is relatively displaced against the entire elastic member.

Further, in the invention described in claim 3, in addition to the operation according to the invention described in claim 1 or 2,
Of the pair of elastic members, the elastic member on the side that resists relative displacement of the partition body in the direction of expanding the pressure receiving chamber has a smaller spring constant than the elastic members on the other side, so the orifice is locked. When such a high-frequency vibration is input, relative displacement of the partition body in the direction of expanding the pressure receiving chamber occurs with a relatively small force corresponding to the small spring constant. As a result, the energy required to control the hydraulic pressure due to the relative displacement of the partition body can be further reduced.

[0013]

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

FIG. 1 shows a liquid-sealed engine mount according to a first embodiment of the present invention, in which a cylinder axis X is oriented in a vibration input direction (vertical direction in FIG. 1, hereinafter simply referred to as vertical direction). A support cylinder member, 2 is a cup-shaped member that closes the lower end opening side of the support cylinder member 1, and 3 is a mounting member that is located on the upper end opening side of the support cylinder member 1 and is arranged on the cylinder axis X, Reference numeral 4 denotes an annular elastic support for connecting the mounting member 3 and the support cylinder member 1 to each other, 5 a doughnut-shaped diaphragm made of a rubber thin film which is an elastic partition member, 6 a partition, and 7
Is an annular orifice formed in the partition body 6, and 8 and 9 are first and second elastic members for supporting the partition body 6.

The support cylinder member 1 and the cup-shaped member 2 are
Caulked portion 1a constituted by the lower end edge of the support cylinder member 1
Are connected to each other, and the support cylinder 10 having a bottomed cylindrical shape is constituted by the both 1 and 2. The caulking portion 1a has the outer peripheral edge of the cup-shaped member 2, the outer peripheral edge of the diaphragm 5, and the lower peripheral edge 11a of the holding cylinder member 11 for holding the first elastic member 8 fixedly positioned. The liquid L is enclosed in a sealed space defined by the diaphragm 5, the elastic support 4 and the support cylinder member 1 to form a liquid chamber 12. The liquid chamber 12 is divided into two by the partition body 6, the pressure receiving chamber 13 is formed on the upper side of the partition body 6, and the equilibrium chamber 14 is formed on the lower side. Further, the support cylinder member 1 or the cup-shaped member 2 is fitted into a bracket (not shown) and is held by the caulking portion 1a at a portion projecting to the outer peripheral side, whereby the vibration receiving portion, for example, the vehicle body side is connected. It is supposed to be done.

The mounting member 3 includes a plate member 3a, a connecting bolt 3b protruding upward from the plate member 3a along the cylinder axis X, and a bottomed cylindrical member 3c protruding downward from the plate member 3a. It consists of The mounting member 3 is connected to the vibration source side, for example, the engine side, via the connecting bolt 3b. Further, the elastic support body 4 is formed in a truncated cone shape by integral vulcanization molding of rubber between the outer peripheral surface of the cylindrical member 3c and the inner peripheral surface of the upper opening edge 1b of the support cylindrical body 1,
The mounting member 3 is elastically supported on the support cylinder 10 by the elastic body support body 4.

The partition 6 is formed by vertically stacking a pair of hat-shaped plate-shaped members 15 and 16, and the annular orifice 7 is constituted by an annular passage formed inside the outer peripheral portion. ing. This annular orifice 7
Has one end opened to the pressure receiving chamber 13 and the other end opening to the equilibrium chamber 14, respectively.
The length and cross-sectional area of the liquid L of No. 4 are set so as to attenuate vibrations in a predetermined low frequency range input in the vertical direction by liquid column resonance when the liquids L of No. 4 flow through each other through the orifice 7. . A head portion 17a of a rod 17 is fixed to the central portion of the pair of plate-shaped members 15 and 16 in a penetrating state, and a shaft portion 17b of the rod 17 penetrates the diaphragm 5 and extends along the cylinder axis X. A seat portion 17c extending downward and extending outward in the radial direction is integrally formed at the lower end portion.

A first portion is provided between the upper surface of the outer peripheral edge 15a of the plate member 15 which is bent outward in the radial direction and the lower surface of the inner peripheral edge 11b of the holding cylinder member 11 which is bent inward in the radial direction. The elastic member 8 is interposed in a predetermined pre-compression state, while the second elastic member 9 is in a predetermined pre-compression state between the lower surface of the seat portion 17c of the rod 17 and the upper surface 2a of the cup-shaped member 2. It is installed in the state. The first elastic member 8 is formed in an annular shape, and its upper surface is attached to the inner surface of the inner peripheral edge 11b of the holding cylinder member 11 by means such as adhesion. The second elastic member 9 is formed in a hollow shape, and its lower surface is attached to the upper surface of the cup member 2 by means such as adhesion. That is, the partition body 6 applies a downward compressive restoring force from the first elastic member 8 to the second elastic member 8.
The elastic member 9 is sandwiched from above and below by the elastic members 8 and 9 in the state of receiving the upward compressive restoring force,
As a result, the partition 6 is elastically supported in the vertical direction with respect to the support cylinder 10.

As shown in FIG. 2, the first and second elastic members 8 and 9 have a predetermined spring constant K1 of the first elastic member 8 which is relatively large as shown by a chain line in FIG. The spring constant K2 of the second elastic member 9 is set to a relatively small predetermined value as shown by the chain double-dashed line in FIG. That is, the first elastic member 8 is set to be hard and the second elastic member 9 is set to be soft, and the first elastic member 8 is contracted by d1 and the second elastic member 9 is contracted by d2. 6 is set in a neutral state in which it is stationary at a predetermined position. The partition body 6 supported by the first and second elastic members 8 and 9 in such a pre-compressed state increases the hydraulic pressure in the pressure receiving chamber 13 due to the vibration input, as shown by the solid line in FIG. The pressing load acting on the partition 6 is limited to a slight downward displacement between 0 and the critical load F1 by the vibration input, while the orifice 7 is in a clogging state (orifice lock state) in a predetermined high frequency vibration input. At the time when the pushing-down load to the partition body 6 due to the increase in the liquid pressure due to the above exceeds the critical load F1, the first elastic member 8 and the outer peripheral edge 15a are separated from each other, and the partition body 6 is the second elastic member. The displacement of 9-the load gradient only governs the displacement.

That is, by supporting the partition body 6 by sandwiching it by the two elastic members 8 and 9 in the pre-compressed state, a non-linear elastic support characteristic is exhibited in the support mode of the partition body 6. Specifically, for vibration input in the low frequency range, the partition body 6 is maintained in a substantially neutral state and the flow of the liquid L from the pressure receiving chamber 13 to the equilibrium chamber 14 is ensured via the orifice 7. However, the liquid column resonance caused by the flow of the liquid exerts a damping force. On the other hand, the orifice 7 becomes clogged with respect to the vibration input in the high frequency range, and the partition body The pushing-down load to 6 exceeds the critical load F1, and the partition 6 is positively displaced downward to cancel the increase in the hydraulic pressure in the pressure receiving chamber 13.

Reference numerals 5a and 5b in FIG. 1 denote core members embedded in the inner and outer peripheral positions of the diaphragm 5, and the outer peripheral edge of the diaphragm 5 is surrounded by the outer peripheral core member 5a.
In addition, the inner peripheral side core member 5b securely fixes the inner peripheral edge of the diaphragm 5 to the outer peripheral surface of the rod 14 at a predetermined position. There is.

Next, the operation and effect of the first embodiment having the above structure will be described.

Mounting member 3 mounted on the side of the vibration source
When vertical low frequency vibration is input from the elastic support 4 and the mounting member 3 is displaced downward, the pressure receiving chamber 13
Is reduced and the internal liquid L flows through the orifice 7 to the equilibrium chamber 14 side. At this time, since the liquid L can flow through the orifice 7 in the low frequency range,
The pressing load to the partition 6 due to the increase in the hydraulic pressure of the pressure receiving chamber 13 remains within the range of the pre-compression load (compression restoring force) of the elastic members 8 and 9, so that the partition in which the orifice 7 is formed is formed. It is possible to limit the relative movement in the vertical direction by keeping 6 in the substantially neutral state. As a result, liquid column resonance can be effectively generated through the orifice 7 associated with the flow of the liquid L, and the liquid column resonance can attenuate the input vibration in the low frequency range.

On the other hand, when the vibration input from the mounting member 3 is on the higher frequency side and the orifice 7 is in the locked state, the hydraulic pressure in the pressure receiving chamber 13 increased as the mounting member 3 is displaced downward. Acts to push down the partition body 6. Then, when this pushing-down load exceeds the pre-compression load of the second elastic member 9, the partition body 6 has a relatively soft second
The elastic member 9 is rapidly displaced downward corresponding to the load-displacement characteristic. For this reason, the volume of the pressure receiving chamber 13 is suddenly expanded to prevent the hydraulic pressure from further increasing, and it is possible to prevent the dynamic spring jump. In this case, the first elastic member 8 is separated from the partition body 6, only the second elastic member 9 is involved in the relative displacement of the partition body 6, and the second elastic member 9 is set to a relatively small spring constant. Therefore, the energy for displacing the partition 6 downward when the high-frequency vibration is input is relatively small, and thus the energy required for the hydraulic pressure control by the movement of the partition 6 can be reduced.

That is, according to the first embodiment, when the low frequency vibration is input, the partition body 6 is substantially fixed in position by the precompression load of the two elastic members 8 and 9, and the partition body 6 passes through the orifice 7. While the damping of the low-frequency vibration due to the liquid column resonance can be ensured, the partition 6 is set when the high-frequency vibration is input, that is, when the orifice 7 is locked and a downward load equal to or greater than the precompression load acts. It is possible to easily displace the pressure receiving chamber 13 to the side to be enlarged and to displace it with a comparatively small force, and it is possible to avoid a dynamic spring jump and prevent an increase in load transmissibility. In addition, the two elastic members 8 and 9
By changing the setting of the respective spring constants and the setting of the precompression to change the critical load F1 in FIG. 2, it is possible to change the frequency of the high frequency at which it is desired to avoid the dynamic spring jump.

FIG. 3 is the same as that of the first embodiment, but omits the first and second elastic members 8 and 9 in the first embodiment, and the partition body 6 is the same as the neutral state of the first embodiment. The result of having performed the comparative test with what was fixed in a position (comparative example) is shown. In the figure, the broken line indicated by tan δ is the first
With respect to the damping characteristics in the examples and the comparative examples, the solid line indicated by Kd indicates the dynamic spring constant according to the first embodiment, and the alternate long and short dash line indicated by Kd0 indicates the dynamic spring constant according to the comparative example. The spring constants of the first and second elastic members 8 and 9 in the first embodiment used in this comparative test are set as shown in FIG. That is, the spring constant K1 of the first elastic member 8 is set to 25 kgf / mm, and the spring constant K2 of the second elastic member 9 is set to 2.5 kgf / mm. Also, the critical load F1 is set to 1.0 kgf, and 1.0 kgf is set by pre-compression of both elastic members 8 and 9.
While the relative displacement of the partition 6 is regulated by the following loads,
When the pushing load exceeds 1.0 gkf, the partition body 6 is relatively displaced downward.

According to the test results, regarding the attenuation of the low frequency vibration, the peak of the attenuation is generated in the low frequency region which is almost the same between the first embodiment and the comparative example. Partition 6 by pre-compression of both elastic members 8 and 9
The position is fixed effectively. Regarding the dynamic spring jump due to the rise in hydraulic pressure after the orifice lock due to the high frequency vibration input, the comparative example has a sharp increase of ΔKd0, while the first example has a considerably small value of ΔKd. ing.

FIG. 5 shows a liquid-sealed engine mount according to a second embodiment of the present invention, in which 18 is a coil spring as a second elastic member and 19 is an upper surface 2a of the cup-shaped member 2.
The electrode member 20 is fixed in position while being insulated from the cup-shaped member 2, and 20 is an electromagnetic coil provided on the electrode member 19. The partition member 6 is forcibly applied by the electrode member 19 and the electromagnetic coil 20. The driving means 21 for shaking is configured.

The coil spring 18 is interposed between the cup-shaped member 2 and the seat portion 17b of the rod 17 in a state of being pre-compressed by a predetermined amount, and the partition body 6 is vertically moved together with the first elastic member 8. It is sandwiched and elastically supported. The spring constant of the coil spring 18 is set to be the same value as the spring constant K2 of the second elastic member 9 in the first embodiment, so that, as in the first embodiment, the spring constant is set via the orifice 7. The partition body 6 is substantially fixed in position while the liquid L is flowing, and after the orifice 7 is locked, the partition body 6 is based on only the bending characteristic of the coil spring 18.
Non-linear elastic support characteristics are exerted so as to relatively displace the lower part.

The upper surface of the electrode member 19 and the lower surface of the seat portion 17b are positioned so that a predetermined amount of gap 22 exists between the partition member 6 and the electromagnetic coil 20 when the partition member 6 is in the neutral state. By turning on and off, the seat 17b can be converted into a state in which the seat 17b is attracted to the electrode member 19 and brought into close contact therewith, and a state in which only the gap 22 is separated. That is, when the partition body 6 is relatively displaced downward from the neutral state by the gap 22 by the ON state, the partition body 6 is restored to the original neutral state by the compression restoring force of the coil spring 18 when it is OFF. There is. Then, this ON / OFF is automatically and repeatedly controlled according to the direction of the input vibration so as to reciprocate the partition body 6 in the vertical direction, and is turned ON at the time of the vibration input on the side for displacing the mounting member 3 downward, On the contrary, it is turned off when the vibration of the side to be displaced upward is input. In addition, this ON / OFF control is started at the time of high frequency vibration input that locks the orifice 7.

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 ON / OFF control is not performed at the time of inputting the low frequency vibration, and the partition body 6 is sandwiched by the first elastic member 8 and the coil spring 18 in the pre-compression state and is in a substantially neutral state. Held in. Therefore, it is possible to ensure the flow of the liquid L through the orifice 7 formed in the partition body 6, and as a result of the flow of the liquid L, liquid column resonance occurs through the orifice 7, The liquid column resonance can reduce the low frequency vibration.

On the other hand, at the time of high frequency vibration input, ON / OFF control of the current to the electromagnetic coil 20 is performed, and the partition body 6 is forcibly reciprocated in the vertical direction according to the direction of the vibration input. As a result, when the vibration input in the direction in which the hydraulic pressure in the pressure receiving chamber 13 increases, the partition 6 is forcibly displaced downward and the pressure receiving chamber 13 is expanded, so that the hydraulic pressure in the pressure receiving chamber 13 is prevented from rising. Therefore, it is possible to positively reduce the dynamic spring when high frequency vibration is input. At this time, the suction force of the seat portion 17b due to the current ON may be equal to or larger than the compression restoring force of the coil spring 18 whose spring constant is set low, whereby the fluid pressure can be controlled by the forced displacement of the partition body 6. It can be performed with relatively small driving energy, that is, with relatively little electric energy.

FIG. 6 shows a liquid-sealed engine mount according to the third embodiment of the present invention, in which 23 is a ring-shaped first elastic member attached to the lower surface of the inner peripheral edge 11b of the first holding member 11 by means such as adhesion. Member, 24 is an annular second holding member, 2
Reference numeral 5 is an annular second elastic member attached to the second holding member 24 by means such as adhesion.

The second holding member 24 has an outer peripheral edge 24.
a is held by the caulked portion 1a of the support tubular member 1 together with the outer peripheral edge 11a of the first holding member 11 and is fixed to the support tubular body 1, and its inner peripheral edge 24b is a predetermined outer peripheral edge 15a of the partition body 6. It is located in the lower position. The upper surface of the inner peripheral edge 24b of the second holding member 24 and the partition 6
The second elastic member 25 is interposed between the outer peripheral edge 15a and the outer peripheral edge 15a to be in a predetermined pre-compression state.

On the other hand, the first elastic member 23 has an inner peripheral edge 11b of the first holding member 11 and an outer peripheral edge 15a of the partition body 6.
And a predetermined pre-compression state. Then, the partition body 6 receives the downward compression restoring force from the first elastic member 23 and the upward compression restoring force from the second elastic member 25, and then the first and second elastic members. It is sandwiched by the members 23 and 25 from above and below and is held in a predetermined neutral state.

As shown in FIG. 7, the first and second elastic members 23 and 25 are set to have the same spring constants K1 and K2.
Are pre-compressed until they have the same compression displacement amount. The partition member 6 is supplied when a predetermined low-frequency vibration is input so that the flow of the liquid L through the orifice 7 is ensured.
In the range of the load (hydraulic pressure) that acts on the partition body 6, the partition body 6 is substantially positionally fixed in the neutral state by the precompression, while the range of the load that acts on the partition body 6 when the orifice 7 is locked. Then, the partition body 6 is relatively displaced based on only the bending characteristic of one of the first elastic member 23 and the second elastic member 25.

Since the other construction of the liquid-filled engine mount is the same as that of the second 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 ON / OFF control to the electromagnetic coil 20 is not performed at the time of inputting the low frequency vibration,
The partition body 6 is sandwiched by both elastic members 23 and 25 in the pre-compressed state and is held in a substantially neutral state, whereby the liquid column resonance through the orifice 7 causes low-frequency vibration as in the second embodiment. Can be attenuated.

On the other hand, at the time of high frequency vibration input, ON / OFF control of the current to the electromagnetic coil 20 is performed, and the partition 6 is forcibly reciprocated in the vertical direction according to the direction of the vibration input. Similarly to the second embodiment, the partition body 6 is forcibly displaced downward to prevent the hydraulic pressure in the pressure receiving chamber 13 from rising, and a low dynamic spring at the time of high frequency vibration input can be achieved. . At this time, the suction force of the seat portion 17b due to the current ON may be equal to or greater than the compression restoring force of one of the pair of elastic members 23 and 25, and thereby the hydraulic pressure control by the forced displacement of the partition body 6 is performed. In comparison with the case where the partition body is elastically supported by a single elastic member, it is possible to carry out with a small driving energy, that is, with relatively little electric energy.

Moreover, in the case of the third embodiment, the partition body 6, the first and second holding members 11 and 24, and the first and second holding members are formed.
The second elastic members 23 and 25 can be assembled in a predetermined state in advance before being assembled to the support cylindrical body 10. By fixing the integrated one with the caulking portion 1a, a pair of elastic members can be obtained. The partition body 6 elastically supported by being sandwiched by 23 and 25 can be easily assembled to the support cylindrical body 10.

The present invention is not limited to the above embodiment, but includes various other modifications. That is, in the above embodiment, the drive means 21 is constituted by the electromagnets 19 and 20, but the invention is not limited to this.
For example, an electromagnetic actuator or a piezoelectric actuator may be used.

[0043]

As described above, according to the liquid-filled engine mount of the first aspect of the invention, the partition body is sandwiched by the pair of elastic members from above and below, and the pair of elastic members is in the pre-compressed state. As a result, the partition body is supported in a state in which compression restoring forces act in opposite directions, so that relative displacement in the vibration input direction of the partition body in which the orifice is formed within the range up to the precompression load. Can be restricted to substantially fix the position of the orifice with respect to the vibration input direction. Therefore, it is possible to secure the flow of the liquid from the pressure receiving chamber to the equilibrium chamber side through the orifice with respect to the low frequency vibration input from the mounting member side, and the liquid column resonance generated as a result of the flow causes the low frequency vibration. Vibration can be damped.

On the other hand, when high-frequency vibration is input from the side of the mounting member and the orifice is clogged, the hydraulic pressure in the pressure receiving chamber rises and is one side of the pair of elastic members. By exceeding the precompression load of the elastic member on the side of the equilibrium chamber, it is possible to relatively displace the partition body in the direction of enlarging the pressure receiving chamber against the elastic member on the one side by its hydraulic pressure. Therefore, it is possible to prevent the hydraulic pressure from further increasing in the pressure receiving chamber, and it is possible to prevent the dynamic spring jump.

For this reason, both low frequency vibration damping and dynamic spring jump prevention at high frequency vibrations can be achieved without providing special drive means for fixing the position of the partition body or forcibly making relative displacement. Can be planned.

Moreover, the partition body can be relatively displaced by applying a force exceeding the compression restoring force of only one side of the pair of elastic members elastically supporting the partition body, so that the plate body can be made into a single plate. It is possible to reduce the energy required for the hydraulic pressure control by the relative displacement of the partition body, as compared with the conventional case in which the elastic member is supported and the relative displacement is performed against the spring elastic force of the single elastic member.

According to the second aspect of the present invention, in addition to the effect of the first aspect of the present invention, a driving means for forcibly exciting the partition body in the vibration input direction is provided, so that high frequency At the time of vibration input, by forcibly displacing the partition body in the direction of expanding the pressure receiving chamber with respect to the input in the direction in which the hydraulic pressure of the pressure receiving chamber rises, a sudden increase in hydraulic pressure in the pressure receiving chamber is ensured. Therefore, the jump of the dynamic spring can be surely prevented. Moreover, the drive energy required to relatively displace the partition body only needs to have a force that opposes only one side of the pair of elastic members elastically supporting the partition body, so that the plate body The driving energy of the driving means can be reduced as compared with the conventional case in which the elastic member is supported and relatively displaced against the entire single elastic member.

Furthermore, according to the invention of claim 3, in addition to the effect of the invention of claim 1 or claim 2, among the pair of elastic members, the partition body in the direction of expanding the pressure receiving chamber is formed. The spring constant of the elastic member on the side that resists relative displacement is
Since it is set smaller than the spring constant of the elastic member on the other side, the relative displacement of the partition body in the direction in which the pressure-receiving chamber expands in response to the input of high-frequency vibration that locks the orifice, is set to the small spring constant. Can be generated with a relatively small force. As a result, it is possible to further reduce the energy required for hydraulic pressure control at the time of high frequency vibration input due to the relative displacement of the partition body.

[Brief description of drawings]

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

FIG. 2 is a relationship diagram of load and displacement of a pair of elastic members and a partition body according to the first embodiment.

FIG. 3 is a relationship diagram of a frequency, a dynamic spring constant, and a damping characteristic in a comparative test.

FIG. 4 is a relationship diagram of load and displacement of a pair of elastic members and a partition body in a comparative test.

FIG. 5 is a vertical sectional view showing a second embodiment.

FIG. 6 is a vertical sectional view showing a third embodiment.

FIG. 7 is a relationship diagram of load and displacement of a pair of elastic members and a partition body according to the third embodiment.

[Explanation of symbols]

 3 Mounting member 4 Elastic support member 5 Diaphragm (elastic partition member) 6 Partition member 7 Orifice 8,23 First elastic member 9,25 Second elastic member 10 Support cylinder 12 Liquid chamber 13 Pressure receiving chamber 14 Balance chamber 18 Coil spring ( Second elastic member) 21 Drive means

Claims (3)

[Claims] 1. A support cylinder body having one side end portion facing the vibration source side and the other side end portion facing the vibration receiving portion side, and the one side end portion side of the support cylinder body. And a ring-shaped elastic support that connects the mounting member and one end of the support cylinder to each other, and a mounting member that is connected to the vibration source side, and is connected to the inner peripheral surface of the support cylinder. And an elastic partition member that forms a liquid chamber in which a liquid is sealed between the elastic support member and a partition member that partitions the liquid chamber into a pressure receiving chamber on the elastic support member side and an equilibrium chamber on the elastic partition member side. And an orifice that is formed in the partition body and connects the pressure receiving chamber and the equilibrium chamber to each other, and the partition body includes a pair of independent elastic members that sandwich the partition body from both sides in the vibration input direction. Is supported by the support cylinder through the pair of elastic members facing the partition body. Fluid-filled engine mount, characterized in that are interposed respectively pre-compressed state to exert a compressive restoring force from the vibration input direction on both sides. 2. The liquid-filled engine mount according to claim 1, further comprising drive means for forcibly exciting the partition body in a vibration input direction in response to input vibration. 3. The elastic member according to claim 1 or 2, wherein the elastic member on the side that resists relative displacement of the partition body in the direction of enlarging the pressure receiving chamber is more elastic than the elastic members on the other side. A liquid filled engine mount configured to have a low spring constant.