JPH09242809A - Vibrationproof support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a vibration resistant characteristic over a wide frequency range by actively changing the capacity of fluid chamber defined by a support elastic member by use of damping force generating when fluid passes through an orifice. SOLUTION: In an engine mount 20, a case 43 incorporating therein engine mount parts such as a support elastic member 32 forming a main fluid chamber, orifice and auxiliary fluid chamber, inner cylinder 34, first orifice component 36, an outer cylindrical member 38, and below the mount parts an electromagnetic actuator 52 is incorporated which displaces a movable member elastically supported to form part of partitioning wall of the main fluid chamber in the direction to change the capacity of the main fluid chamber. Inside the member 32, a hollow part 32b is formed and the first orifice component 36 is fitted as a second cylindrical member in the inner cylinder 34 so that it is positioned below the hollow part 32b. Accordingly over a wide frequency range an excellent vibration resistant characteristic is obtained.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for supporting a vibrating body such as an engine of a vehicle on the side of a supporting body such as a vehicle body while isolating the same, and is particularly generated when a fluid passes through an orifice. The present invention relates to an anti-vibration support device that can obtain an anti-vibration effect by utilizing a damping force, and can actively generate an active support force by positively changing the volume of a fluid chamber defined by a support elastic body.

[0002]

2. Description of the Related Art In general, an engine mount, which is an anti-vibration support device used to support a power unit of a vehicle, mainly has a good anti-vibration function against idle vibration, muffled sound vibration, noise vibration during acceleration, and the like. It is required to be exerted, but among these various vibrations, 20 to 30
In order to reduce the idle vibration, which is a vibration with a relatively large amplitude of about Hz, the characteristics required of the anti-vibration support device are a high dynamic spring constant and a high damping, whereas a characteristic of 80-800 Hz is relatively high. The characteristics required for the anti-vibration support device in order to reduce the muffled noise vibration and the noise noise during acceleration, which are small and medium amplitude vibrations, are a low dynamic spring constant and a low damping. Therefore, it is difficult to prevent all vibrations with an engine mount including only a normal elastic body or a conventional liquid-filled engine mount.

Therefore, as an anti-vibration support device capable of actively damping and supporting a vibrating body such as an automobile engine, for example, Japanese Unexamined Patent Publication No. 5-60168 (hereinafter referred to as "prior art 1"), A technique disclosed in Japanese Patent Laid-Open No. 7-223444 (hereinafter, referred to as Prior Art 2) is known.

That is, in the vibration isolating support device of the prior art 1, a support is fixed to the vehicle body side of an automobile, and an outer shell is arranged above the support at a predetermined interval, and the outer shell and the aforesaid A supporting elastic body (referred to as an expansion spring in the publication) made of a rubber-like elastic body having a hollow conical shape is connected between the supporting body and the outer shell so as to cover an outer lower portion of the supporting elastic body. A bellows is provided between the support and a magnetizable diaphragm supported by a leaf spring provided on the upper portion of the outer shell, and the bellows is connected to the upper portion of the outer shell to face the upper surface of the diaphragm. As described above, the bearing member is fixed to the engine side of the automobile, the permanent magnet is provided on the bearing member so as to face the diaphragm, and the magnet body made of an electromagnet is provided around the permanent magnet. A closed main fluid chamber (referred to as a working chamber in the publication) is formed between the upper surface of the expansion spring and the lower surface of the diaphragm, and the lower surface of the support elastic body and the upper surface of the bellows are formed. A sub-fluid chamber (referred to as a pressure-regulating chamber in the publication) sealed between them is formed, liquid is sealed in the main fluid chamber and the sub-fluid chamber, and the space between the main fluid chamber and the sub-fluid chamber is The structure is such that they communicate with each other through a buffer hole formed in the outer shell.

In the prior art 1, when the diaphragm vibrates due to the electromagnetic force generated by the electromagnet, a volume change occurs in the main fluid chamber, and the volume change acts on the elastic support body to generate an active support force there. Since the vibration is generated, the vibration plate is appropriately vibrated according to the vibration generation state to reduce the vibration transmitted to the support body side. Further, the main fluid chamber communicates with the sub fluid chamber through the buffer hole, and when the supporting elastic body is deformed by the vibration input from the vibrating body side and a volume change occurs in the main fluid chamber, Since the liquid enclosed in the body chamber and the liquid enclosed in the sub-fluid chamber move with each other through the buffer holes to generate a damping force, the action of a passive fluid-filled type vibration damping support device can also be obtained. You can

Further, in the vibration isolation support device of the prior art 2, a supporting elastic body interposed between the vibrating body side and the supporting body side, a main fluid chamber defined by the supporting elastic body, and a vibrating body of the main fluid chamber. One side in the support direction (here, the upper part on the vibrating body side)
A variable-volume auxiliary fluid chamber communicating through an orifice disposed in the main fluid chamber, the fluid enclosed in the main fluid chamber, the auxiliary fluid chamber, and the orifice, and a magnetic path forming a part of the partition wall of the main fluid chamber. Member, a leaf spring that exhibits non-linear spring characteristics while elastically supporting the magnetic path member in a direction that changes the volume of the main fluid chamber, and a displacement force that displaces the magnetic path member in the direction. And an actuator to operate. In addition, a diaphragm should be placed on the upper side of the vibrating body, the space above this diaphragm should communicate with atmospheric pressure, and the orifice structure should be placed in the space below this diaphragm (the other side in the vibrating body supporting direction). This forms a sub fluid chamber between the diaphragm and the orifice structure. Then, in the prior art 2, a pulse generator that detects a vibration generation state of the vibrating body and generates a reference signal, an acceleration sensor that detects the residual vibration on the support side and outputs the residual vibration signal, and the residual vibration signal. And a controller that outputs a drive signal to the actuator based on the reference signal to generate a displacement force in the actuator.

According to the prior art 2, when vibration is input from the vibrating body side, the pulse generator generates a reference signal according to the reference vibration and outputs the reference signal to the controller. When residual vibration occurs on the support body side, the acceleration sensor operates. The vibration status of the body member is detected in the form of acceleration and output to the controller as a residual signal. Then, the controller outputs a control signal to the electromagnetic actuator to appropriately vibrate the magnetic path member and changes the volume of the main fluid chamber to control the vibration transmission force to the support side to be "0". .

[0008]

However, in the vibration isolating support device of the prior art 1 described above, the bellows, which are arranged so as to be exposed toward the vehicle body side of the automobile, vibrate when vibration is input. Large displacement in the body support direction,
There is a problem in terms of durability of the bellows because it may be damaged by flying stones.

Further, in the vibration isolating support device of the prior art 2, in order to generate the fluid resonance effective for vibration reduction, it is necessary to provide the sub-fluid chamber and the orifice having a large volume. Since they are provided in series in the supporting direction of the vibrating body, increasing the volume of these leads to an increase in the size of the device. For this reason, there is also a problem that it is difficult to apply a fluid-filled type vibration-damping support device capable of generating a large damping force to a vehicle or the like having a large mounting space restriction.

Further, at the time of braking, a shake vibration having a larger amplitude (frequency of 20 Hz or less) than the idle vibration may occur, but in order to provide a good vibration damping function against this shake vibration, further An auxiliary fluid chamber having a large volume and an orifice must be provided to provide a vibration damping support device having a high dynamic spring constant and high damping. However, the prior arts 1 and 2 lead to an increase in the size of the entire apparatus if the sub-fluid chamber and the orifice having a large volume are provided as described above. It is impossible.

The present invention has been made by paying attention to the problems to be solved by such a conventional technique, and it is possible to achieve miniaturization and to prevent muffled sound vibration from vibration of large amplitude such as shake vibration. An object of the present invention is to provide a fluid-filled type vibration-damping support device that can obtain good vibration-damping characteristics over a wide frequency band up to small-amplitude vibrations such as noise vibrations during acceleration.

[0012]

In order to achieve the above object, the invention according to claim 1 provides a supporting elastic body interposed between a vibrating body side and a supporting body side, and a main fluid defined by the supporting elastic body. A chamber, a variable volume sub-fluid chamber communicating with the main fluid chamber through an orifice, a fluid enclosed in the main fluid chamber, the sub-fluid chamber and the orifice, and a part of the partition wall of the main fluid chamber. In a vibration-damping support device including a movable member elastically supported to form, and an actuator that displaces the movable member in a direction in which the volume of the main fluid chamber changes, one of the vibrating body side or the supporting body side and the The support elastic body is coupled to the support elastic body through a first tubular member whose axial center faces the vibrating body support direction and a small diameter portion is formed in a part of the axial direction, and a second cylinder is provided inside the small diameter portion. The first member and the second member together. 2 A main fluid chamber is arranged in a space surrounded by the inner side of the tubular member and the inner surface of the supporting elastic body, and an annular shape surrounded by the inner peripheral surface of the small diameter portion and the outer peripheral surface of the second tubular member. The first sub-fluid chamber and the first orifice are arranged in the space, and the second sub-fluid chamber and the second orifice are arranged on the outer peripheral side of the small diameter portion of the first tubular member.

According to a second aspect of the present invention, in the vibration-damping support device according to the first aspect, the main fluid chamber is formed in a space from the second tubular member to the inner surface of the support elastic body,
A third orifice was formed on the inner peripheral surface side of the second tubular member, and a third sub-fluid chamber was formed in the space from the second tubular member to the movable member.

According to a third aspect of the present invention, in the vibration-isolating support device according to the first or second aspect, an opening hole is formed in a part of the small diameter portion, and the opening hole is closed by the first diaphragm. The annular space near the first diaphragm is the first sub-fluid chamber, and the annular space other than the first sub-fluid chamber is the first orifice.

According to a fourth aspect of the present invention, in the vibration isolating support device according to any one of the first to third aspects, the first aspect is provided.
The tubular member is externally fitted with the third tubular member to form an annular space between the outer peripheral surface of the small diameter portion and the inner peripheral surface of the third tubular member, and a part of the annular space is surrounded. A second diaphragm is disposed in the direction, and a second orifice component is disposed in the remaining annular space due to the disposition of the second diaphragm,
A second sub-fluid chamber was formed between the second orifice component and the second diaphragm.

Further, the invention according to claim 5 is the invention according to claim 4.
In the vibration-damping support device described above, the second orifice component has a first communication hole that communicates with the main fluid chamber side, and a second communication hole that communicates with one circumferential end of the second diaphragm. In addition, a fluid passage, which is connected to the first communication hole and the second communication hole and is longer than the circumferential length of the second orifice component member, is formed inside.

[0017]

According to the invention described in claim 1, as a result of forming the small diameter portion in the first tubular member, a space can be provided on the outer peripheral side of the first tubular member. Even if the second sub-fluid chamber and the second orifice having a relatively large capacity are arranged on the outer peripheral side of the member, it is possible to avoid the second sub-fluid chamber and the second orifice from being largely projected outward. It is possible to reduce the size of the vibration isolation device.

Further, since the tubular member is interposed between one of the vibrating body side or the supporting body side and the supporting elastic body, vibration on the vibrating body side is supported through the supporting elastic body and the first tubular member in series. It is transmitted to the body side. When the supporting elastic body is elastically deformed by the vibration, the volume of the main fluid chamber changes. At this time, if the vibration frequency of the vibrating body is lower than, for example, the frequency at which the fluid in the first orifice is in a stick state, the vibration frequency of the main fluid chamber and the first fluid flow through the first orifice according to the volume change of the main fluid chamber. Since the fluid moves between the first sub-fluid chambers, a damping force is generated by the fluid resonance system constituted by the first orifice and the first sub-fluid chamber. On the other hand, if the vibration frequency of the vibrating body is higher than the frequency at which the fluid in the first orifice is in a stick state, for example, the first
Since the movement of the fluid through the orifice does not occur, the volume fluctuation of the main fluid chamber is transmitted to the second sub fluid chamber. At this time, if the fluid in the second orifice is not in a stick state, movement of the fluid occurs between the main fluid chamber and the second sub-fluid chamber via the second orifice. A damping force is generated by the fluid resonance system configured by the sub-fluid chamber. As described above, the anti-vibration support device of the present invention can obtain good anti-vibration characteristics over a wide frequency band by the two fluid resonance systems.

Further, the invention according to claim 2 can obtain the effect according to claim 1, and the third orifice formed on the inner peripheral surface side of the second tubular member and the movable member are diaphragms. A third fluid resonance system is configured with the third sub-fluid chamber. Then, for example, if the vibration frequency of the vibrating body is higher than the frequency at which the fluid in the second orifice is in the stick state, the movement of the fluid through the second orifice does not occur, so that the volume fluctuation of the main fluid chamber is caused by the third sub-fluid. Transmitted to the room. At this time, if the fluid in the third orifice is not in a stick state, the fluid moves between the main fluid chamber and the third sub-fluid chamber via the third orifice, so this third fluid resonance system As a result, a damping force is generated, and good vibration damping characteristics can be obtained over a wide frequency band.

The invention according to claim 3 is the same as that of claim 1,
In addition to the effect described in 2, it is possible to easily adjust the fluid resonance system including the first sub-fluid chamber and the first orifice and to reduce the manufacturing cost because of the simple structure. Further, the first diaphragm does not have a structure that is largely displaced and is not damaged by flying stones or the like, so that it is possible to provide a vibration-proof support device having excellent durability.

The invention according to claim 4 is the same as that of claim 1,
The effects described in 2 and 3 can be obtained, and since the structure is simple, the fluid resonance system including the second sub-fluid chamber and the second orifice can be easily adjusted, and
Manufacturing costs can be reduced. Further, since the second diaphragm does not have a structure that is largely displaced and is not damaged by flying stones or the like, it is possible to provide an anti-vibration support device having excellent durability.

Further, the invention according to claim 5 is the invention according to claim 4.
In addition to being able to obtain the effects described, the second diaphragm is configured to extend in the circumferential direction, and the fluid passage through which the fluid flows is formed in a passage longer than the circumferential length of the second orifice component member. A sub-fluid chamber and an orifice having a large volume can be provided. When these volumes are large, a large-amplitude control force can be generated, so that a damping force that cancels a large-amplitude vibration such as a shake vibration that occurs during braking of the vehicle can be generated.

[0023]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a perspective view showing a so-called active engine mount (hereinafter simply referred to as an engine mount) that actively reduces vibration transmitted from an engine side as a vibrating body to a vehicle body-side member as a support. ).

The engine mount designated by the reference numeral 20 in FIG. 1 is provided as a support body which is disposed on the rear side of the vehicle body of the engine 22 mounted horizontally and whose upper portion is fixed to the engine side bracket 24 and whose lower portion is fixed to the vehicle body 26. Is attached to the member 28.

2 to 7 show a concrete structure of the engine mount 20.
In the case 43, mounting components such as a support elastic body 32 that forms a main fluid chamber, a plurality of orifices and a sub fluid chamber, an inner cylinder 34, a first orifice component 36, an outer cylinder 38, and the like are built in. , At the bottom of these mounting parts,
A built-in electromagnetic actuator 52 that displaces a movable member elastically supported so as to form a part of the partition wall of the main fluid chamber in a direction in which the volume of the main fluid chamber changes.

That is, the engine mount 20 is
Two engine side mounting bolts 30 that are spaced parallel to each other
It is provided with a connecting member 30 in which a is fixed upward,
A hollow cylindrical portion 30b having an inverted trapezoidal cross section is fixed to the lower portion of the connecting member 30. A support elastic body 32 is fixed to the lower surface side of the connecting member 30 by vulcanization adhesion so as to cover the periphery of the connecting member 30 and the hollow cylindrical portion 30b.

The support elastic body 32 is a substantially cylindrical elastic body having a wall thickness which is gently inclined downward from the central portion toward the outer peripheral portion, and the outer peripheral surface thereof has a hollow cylindrical portion 30b as an axial center. It is coupled by vulcanization adhesion to the inner peripheral surface of the inner cylinder 34 as the first cylindrical member that is coaxially oriented in the vibrating body supporting direction (in this case, the vertical direction).

As shown in FIG. 2, the inner cylinder 34 is gradually reduced in diameter from the upper end cylinder portion 34a to form an inclined portion 34b, and an inclined portion 34b is formed downward from the lower end portion of the inclined surface 34b. A small diameter portion 34c having a diameter smaller than that of the tubular portion 34a is formed. An annular portion 34d is formed radially outward from the lower end of the small diameter portion 34c, and the upper end cylinder portion 34a is formed downward from the outer peripheral end of the annular portion 34d.
It is a member in which a lower end cylindrical portion 34e having the same outer peripheral diameter as that of is formed. The small diameter portion 34c is provided with a first opening hole (opening hole) 34f and a second opening hole 34g at positions symmetrical to each other with respect to the axis.

A thin film elastic body 32a continuous from the lower side of the support elastic body 32 is joined to the inner peripheral surfaces of the inclined portion 34b and the small diameter portion 34c of the inner cylinder 34, and the thin film elastic body 32a is Further, it extends to the annular portion 34d side and the lower end tubular portion 34e side, and is coupled to the inner peripheral surfaces of the annular portion 34d and the lower end tubular portion 34e. Here, the lower end portion of the thin film elastic body 32a has a thickened shape.

Here, the thin film elastic body 32a has the first opening 3
4f is closed to form the first diaphragm 32c. Further, the second opening hole 34g is opened without being blocked by the thin film elastic body 32a.

A hollow portion 32b having a mountain-shaped cross section is formed inside the support elastic body 32. The hollow portion 32b is formed.
A first orifice constituting member 36 as a second tubular member is fitted in the inner cylinder 34 so as to be located in the lower part of the.

The first orifice forming member 36 has a minimum diameter cylindrical portion 3 formed to have a smaller diameter than the small diameter portion 34c of the inner cylinder 34.
6a, which is a tubular member in which annular portions 36b and 36c are formed radially outward in the upper and lower ends of the minimum diameter tubular portion 36a. The outer peripheral diameter of the annular portion 36b on the upper side is the inner cylinder 34.
The diameter is slightly smaller than the small diameter portion 34c. The annular portion 36c of the lower side, with has a smaller diameter than the lower cylindrical portion 34e of the inner cylinder 34, the cylindrical end portion 36c ₁ is formed downward from the outer peripheral edge. Furthermore, in the minimum diameter cylindrical portion 36a, the third opening hole 3 is provided at a position facing the second opening hole 34g formed in the inner cylinder 34.
6d are formed.

Here, the lower end portion of the thin film elastic body 32a having the increased thickness as described above has a lower end tubular portion 34e of the inner cylinder 34.
By being sandwiched between the first orifice component member 36 and the tubular end portion 36c ₁ , the first orifice component member 36 is slightly compressed downward in the radial direction while being compressed.

On the other hand, an outer cylinder 38 as a third cylindrical member is externally fitted to the inner cylinder 34, and between the inner cylinder 34 and the outer cylinder 38, the inclined portion 4b, the small diameter portion 34c and the annular shape. Part 3
An annular space is defined in the circumferential direction by surrounding the recess formed by the outer peripheral surface of 4d with the inner peripheral surface of the outer cylinder 38. And
In this annular space, the second orifice component 40 and the second orifice
A diaphragm 42 is provided.

That is, the outer cylinder 38 is a cylindrical member having an inner peripheral diameter the same as the outer peripheral diameter of the inner cylinder 34 and an axial length the same as the inner cylinder 34. A thin liquid-tight sealing material 38a made of an elastic body is joined to the. Then, in the outer cylinder 38, approximately 1 of the recess is formed.
So that it is possible to face the part of / 3 from the outer peripheral side,
A slit-shaped opening 38b whose longitudinal direction extends in the circumferential direction is formed.

The second diaphragm 42 is a rubber-like thin film elastic body, and as shown in FIG. 5, it is connected to the entire circumference of the opening edge portion of the opening portion 38b to close the opening portion 38b, and It is arranged in a state of bulging toward the approximately 1/3 portion.

The second orifice-constituting member 40 has a remaining annular space (small annular space corresponding to approximately ⅔ of the concave portion) which has become a small space by disposing the second diaphragm 42.
As shown in FIGS. 5 and 6, the partition wall member 40a and the passage forming member 40b are made of an elastic material.

The partition member 40a includes the second diaphragm 42.
Is disposed in an annular space near the one end portion 42a in the longitudinal direction thereof while being fitted between the inner cylinder 34 and the outer cylinder 38 forming the annular space, and the partition wall member 40a forms the passage forming member 40b. Side to the second diaphragm 42 side is blocked.

The passage forming member 40b is the partition member 4
0a to a position close to the other end portion 42b of the second diaphragm in the longitudinal direction, and an annular space is continuously formed, and one end opening portion 40b as a first communication hole is formed.
₃ extending along the second opening hole 34g and communication with the circumferential direction of the inner cylinder 34, the first passage 40b ₁ to the other end opening is open towards the partition wall member 40a, the first passage 40b ₁ As a different passage at the upper part of the first passage 40b ₁ extending in the circumferential direction with a length approximately twice that of the first passage 40b ₁ , one end opening toward the partition member 40a, and the other end opening 40b as the second communication hole. ₄ is second
Second opening to the other end 42b of the diaphragm 42
And a passage 40b ₂ . The upper side of the case 43 is fitted onto the outer cylinder 38. Here, in the present embodiment, the first passage 40b ₁ and the second passage 4
A fluid passage is constituted by 0b ₂ .

The case 43 has an inner cylinder 34 at the upper end thereof.
Upper end caulking portion 4 having a circular opening with a diameter smaller than the outer diameter of
2a is formed and the upper end caulking portion 42 is formed.
In the case main body which is continuous with a, the inner peripheral diameter is the same as the outer peripheral diameter of the outer cylinder 38 and has a cylindrical shape continuous to the lower end opening (the lower end opening is shown by the broken line in FIG. 2). is there. Then, the outer cylinder 38 integrated with the support elastic body 32 and the inner cylinder 34 is fitted into the inside of the lower end opening of the case 43, and the upper ends of the outer cylinder 38 and the inner cylinder 34 are attached to the lower surface of the upper end caulking portion 42a. By abutting the parts, they are arranged in the upper part of the case 43. Here, FIG. 2 and FIG.
As shown in FIG. 4, an air chamber 42c is defined in a portion surrounded by the inner peripheral surface of the case 43 and the first diaphragm 32c. An air hole 42d is formed at a position facing the air chamber 42c. The air chamber 42c communicates with the atmosphere via the hole 42d. Further, a plurality of actuator parts such as the electromagnetic actuator 52 are sequentially arranged in the lower part of the case 43, and after all parts are arranged, the lower end of the case 43 is deformed inward in the radial direction, As shown by the solid line in FIG. 2, a lower end caulking portion 42d is formed.

That is, the seal ring 44, the leaf spring 48 integrated with the magnetic path member 46, the gap holding ring 50, the electromagnetic actuator 52, the load sensor 54, and the vehicle body side connecting member 56 are provided below the outer cylinder 38. They are sequentially arranged from the lower opening of the case 43. Here, in the present embodiment, the magnetic path member 46 and the leaf spring 48 constitute a movable member.

That is, as shown in FIG. 7, the sealing member 44 has the same outer diameter as the inner diameter of the case 43, and has an inner diameter smaller than that of the lower annular portion 36c of the first orifice component 36. An O-ring 44a is attached to the lower surface of the annular member in a ring groove formed in a circumferential direction with a predetermined radius. The seal member 44 is arranged with its upper surface in contact with the lower end of the outer cylinder 38.

The leaf spring 48 is a disc member whose outer diameter is slightly smaller than the inner diameter of the case 43. The lower portion of the leaf spring 48 is made of magnetizable metal such as iron. The magnetic path member 46 is coaxially fixed. Then, after the peripheral edge of the upper surface of the leaf spring 48 is brought into contact with the lower surface of the seal ring 44, the gap holding ring 50 is arranged in the state of being brought into contact with the peripheral edge of the lower surface of the leaf spring 48.

The gap retaining ring 50 includes the magnetic path member 46.
The axial length is set so that a predetermined gap is provided between the lower surface of the plate spring and the upper surface of the electromagnetic actuator 52.
The annular member is set to a value obtained by adding the dimension of the gap to the axial length from the lower surface to the lower surface of the magnetic path member 46.

The electromagnetic actuator 52 disposed in contact with the lower surface of the gap retaining ring 50 has a cylindrical yoke 52a and an excitation coil wound around the upper end surface of the yoke 52a with the axial direction being the vertical direction. Coil 52b
And a permanent magnet 52c whose magnetic pole is fixed in the vertical direction on the upper surface of the yoke 52a within the range surrounded by the exciting coil 52b.

Below the electromagnetic actuator 52, there is disposed a substantially disk-shaped vehicle body side connecting member 56 having two vehicle body side mounting bolts 56a spaced apart from each other and fixed downward. The load sensor 54 is arranged between the upper surface of the vehicle body side connecting member 56 and the lower surface of the yoke 52a.

When the lower end caulking portion 42d is formed at the lower end portion of the case 43 as described above, the peripheral portion of the vehicle body side connecting member 56 is fixed in a state of being covered from the outside. At this time, since the electromagnetic actuator 52 is pushed toward the outer cylinder 38 side, the lower end portion of the thin film elastic body 32a sandwiched between the lower end tubular portion 34e and the tubular end portion 36c ₁ is the upper surface of the seal ring 44. It is pressed upward by the and becomes a compressed state. The O-ring 44a mounted on the lower surface of the seal member 44 is also pressed upward by the leaf spring 48 and deformed over the entire circumference. The gap retaining ring 5
Since the upper and lower surfaces of 0 contact the lower surface of the leaf spring 48 and the upper surface of the yoke 52a, a predetermined gap is provided between the lower surface of the magnetic path member 46 and the upper surface of the electromagnetic actuator 52.

Further, a rebound stopper 60 is fixed to the upper part of the case 43. As shown in FIGS. 3 to 4, the bound stopper 60 includes two engine-side mounting bolts 30 that extend upward from the connecting member 30.
The stopper main body 60a extending in a direction orthogonal to the line connecting the bolts and the stopper portion 60a.
Is a member provided with a pair of stopper legs 60b which are gradually lowered from both ends and are joined to the outer periphery of the case 43. When the supporting elastic body 32 is excessively elastically deformed upward due to the rebound operation of the engine mount 20, the coupling member 30 comes into contact with the lower surface of the stopper portion 60a, so that the supporting elastic body 32 is excessively deformed. It is supposed to be prevented.

By the way, the engine mount 20 according to the present embodiment is provided with the first orifice component member 36 on the outer peripheral side and the first orifice member 36.
The inside of the orifice forming member 36 communicates with each other through the third opening hole 36d, and the inside of the first orifice forming member 26 and the first passage 40b ₁ of the second orifice forming member 40 pass through the second opening hole 34g. The second passage 4 communicates with the space where the second diaphragm 42 bulges from the first passage 40b ₁ .
It is connected via 0b ₂ .

When a portion defined by the hollow portion 32b of the support elastic body 32 and the upper outer peripheral surface of the first orifice constituting member 36 is defined as a main fluid chamber 66, the above-mentioned second diaphragm is separated from the main fluid chamber 66. A fluid such as oil is enclosed in the communication passage up to the space where 42 swells. And
By the above-described first and second orifice component members 36 and 40 and the first and second diaphragms 32c and 42c,
Three first to third orifices 68A, 70A, 72A that generate fluid resonance when the volume of the main fluid chamber 66 changes
Also, the first to third sub-fluid chambers 68B, 70B, 72B are formed.

That is, the first orifice 68A is shown in FIG.
As shown in FIG. 5, the first sub-fluid chamber 68B is an internal space surrounded by the minimum diameter cylindrical portion 36a of the first orifice component 36 and the small diameter portion 34c of the inner cylinder 34.
It is the internal space of the first orifice component 36 near c. As shown in FIGS. 5 and 6, the second orifice 70A is a space from the first passage 40b ₁ to the position where the second diaphragm 42 bulges inward through the second passage 40b ₂ . The second sub-fluid chamber 70B is a space in which the second diaphragm 42 bulges inward. Further, the third orifice 72A is a space on the inner peripheral side of the minimum diameter tubular portion 36a, and the third sub-fluid chamber 72B is a space from the lower end surface of the minimum diameter tubular portion 36a to the leaf spring 48. The characteristic of the fluid resonance system configured by the one orifice 68A and the first sub-fluid chamber 68B is that the damping peak frequency (the frequency at which the damping is maximum) is at the frequency of idle vibration (about 20 to 30 Hz) generated while the vehicle is stopped. It has been adjusted to match. In addition, the second orifice 70A and the second
The characteristics of the fluid resonance system configured by the sub-fluid chamber 70B are adjusted so that the attenuation peak frequency matches the frequency of shake vibration (20 Hz or less) generated during braking. Furthermore, the third orifice 72A and the third sub-fluid chamber 7
The characteristic of the fluid resonance system configured by 2B is that the damping peak frequency is such that muffled sound vibration in the passenger compartment / noise vibration at acceleration (80 to 8
The frequency is adjusted to match the frequency of 00 Hz or more).

The exciting coil 52b of the electromagnetic actuator 52 is connected to the controller 74 via a harness, and as shown in the block diagram of FIG. 1, a drive signal y as a drive current supplied from the controller 74.
, A predetermined electromagnetic force is generated.

The controller 74 is a microcomputer, a necessary interface circuit, an A / D converter, a D / A.
It is configured to include a converter, amplifier, etc., and when high-frequency vibration of idle vibration frequency or higher (for example, muffled sound vibration) is input, control vibration of the same cycle as the vibration is input to the engine mount. 20 so that the transmission force of the vibration to the member 28 becomes “0” (more specifically, the exciting force input to the engine mount 20 by the vibration of the engine 22 side is applied to the electromagnetic actuator 5).
The driving signal y is generated and supplied to the exciting coil 52b so as to be canceled by the control force obtained by the electromagnetic force of 2).

Here, the idle vibration and the muffled sound vibration are as follows.
For example, in the case of a reciprocating four-cylinder engine,
The main cause is that the engine vibration of the next component is transmitted to the member 28 via the engine mount 20, so if the drive signal y is generated and output in synchronization with the secondary component of the engine rotation, the vibration transmission rate. Can be reduced. Therefore,
In the present embodiment, the rotation is synchronized with the rotation of the crankshaft of the engine 22 (for example, in the case of a reciprocating four-cylinder engine,
A pulse signal generator 76 is provided for generating an impulse signal (each time the crankshaft rotates 180 degrees) and outputting the impulse signal as a reference signal x.
Is supplied to the controller 74 as a signal indicating the state of occurrence of the vibration at.

On the other hand, as described above, the engine mount 2
0 has a built-in load sensor 54, detects the vibration state of the member 28 in the form of a load, outputs it as a residual vibration signal e, and supplies the residual vibration signal e to the controller 74 as a signal representing the vibration after interference. Has been done.

Then, the controller 74, based on the reference signal x and the residual vibration signal e, is a Filtered-X LM which is one of the adaptive algorithms of the successive update type.
The drive signal y is generated and output according to the S algorithm.

Next, the operation of this embodiment will be described. That is, the engine 22 is in the starting state and the engine mount 2
When the vibration is input to 0, the controller 74
Executes a predetermined calculation process, and the electromagnetic actuator 52
The drive signal y is output to the engine mount 20 to generate an active control force capable of reducing vibration.

That is, the filter coefficient of the adaptive digital filter W is sequentially output to the electromagnetic actuator 52 of the engine mount 22 from the controller 74 at a predetermined sampling clock interval from the time when the reference signal x is input. supplied as y. As a result,
A magnetic force corresponding to the drive signal y is generated in the exciting coil 52b, but since a constant magnetic force is already applied to the magnetic path member 46 by the permanent magnet 52c, the magnetic force of the exciting coil 52b is the magnetic force of the permanent magnet 52c. Can be considered to act to strengthen or weaken. That is, in a state where the drive signal y is not supplied to the exciting coil 52b, the magnetic path member 46 is displaced to a neutral position where the elastic supporting force of the leaf spring 48 and the magnetic force of the permanent magnet 52c are balanced. . Then, in this neutral state, the exciting coil 52b
When the drive signal y is supplied to the magnetic field member 46, if the magnetic force generated in the exciting coil 52b by the drive signal y is in the opposite direction to the magnetic force of the permanent magnet 52c, the magnetic path member 46 increases the clearance with the electromagnetic actuator 52. Is displaced to. Conversely, the magnetic force generated in the exciting coil 52b is
If it is in the same direction as the magnetic force of, the magnetic path member 46 is displaced in the direction in which the clearance with the electromagnetic actuator 52 decreases.

As described above, the leaf spring 48 can be displaced in both up and down directions by the magnetic force generated by the electromagnetic actuator 52.
Of the supporting elastic body 32 due to the change in volume.
, The active support force in both the forward and reverse directions is generated in the engine mount 20. Then, each filter coefficient W ₁ of the adaptive digital filter W that becomes the drive signal y is a synchronous Filtered-X
Since the sequentially updated according to the LMS algorithm, after converged to optimum values each filter coefficient W _i of the adaptive digital filter W has passed a certain time, the drive signal y
Is supplied to the engine mount 20, so that the member 2 is moved from the engine 22 through the engine mount 20.
Idle vibrations and muffled sound vibrations transmitted to the side 8 are reduced.

Here, if the frequency of the vibration input from the engine 22 side to the engine mount 20 is near the shake vibration frequency during braking, in the present embodiment, the main fluid chamber 66 is set to the second orifice 70A. Second through
Since it is communicated with the sub-fluid chamber 70B and the resonance frequency of the fluid resonance system is made to coincide with the shake vibration frequency, when the volume of the main fluid chamber 66 changes, the main fluid chamber 66 and the second fluid chamber 66 and the second fluid flow through the second orifice 70A. Fluid resonance occurs due to fluid movement between the sub fluid chambers 70B. As a result, a high damping force can be applied to the shake vibration, and a good vibration damping effect can be obtained.

When the frequency of the vibration input from the engine 22 side to the engine mount 20 becomes close to the idle vibration frequency while the vehicle is stopped, even if the volume of the main fluid chamber 66 changes at that frequency, the second orifice is generated. Since the fluid in 70A cannot follow the idle vibration frequency and is in a stick state, the fluid does not move between the main fluid chamber 66 and the second auxiliary fluid chamber 70B via the second orifice 70A. Therefore, the volume fluctuation in the main fluid chamber 66 is transmitted to the first sub fluid chamber 68B via the first orifice 68A. Since the resonance frequency of this fluid resonance system matches the idle vibration frequency, the main flow Even if the volume of the body chamber 66 changes periodically at that frequency, the fluid in the first orifice 68A does not become a stick state, and the main flow occurs via the first orifice 68A to which the pressure change in the main fluid chamber 66 directly acts. The fluid moves between the body chamber 66 and the first sub-fluid chamber 68B. As a result, fluid resonance occurs between the main fluid chamber 66 and the second sub fluid chamber 68B through the first orifice 68A, so that a larger control force can be generated by the same electromagnetic actuator 52. In particular, the control vibration having a large amplitude can be superimposed on the idle vibration having a large amplitude generated on the engine 22 side, and a good vibration damping effect can be obtained.

Further, when the frequency of the vibration input from the engine 22 side to the engine mount 20 becomes close to the frequencies of muffled sound vibration and noise vibration during acceleration, even if the volume of the main fluid chamber 66 changes at that frequency. First orifice 68
Since the fluid in A cannot follow the muffled sound vibration frequency and is in a stick state, the fluid does not move between the main fluid chamber 66 and the second auxiliary fluid chamber 68B via the first orifice 68A. Therefore, the volume variation in the main fluid chamber 66 is caused by the third auxiliary fluid chamber 72B via the third orifice 72A.
However, since the resonance frequency of this fluid resonance system matches the frequencies of muffled sound vibration and noise vibration during acceleration, even if the volume of the main fluid chamber 66 changes periodically at that frequency, The fluid in the orifice 72A does not become a stick state, and when the volume of the main fluid chamber 66 changes, the main fluid chamber 66 and the third sub-fluid chamber 72B pass through the third orifice 72A.
Fluid resonance occurs between the same electromagnetic actuator 52
Can generate a greater control force.

Therefore, in the engine mount 20 of the present embodiment, the first to third orifices 68A, 70 at three locations where fluid resonance occurs when the volume of the main fluid chamber 66 changes.
A, 72A and first to third sub-fluid chambers 68B, 70B, 7
Since 2B is provided, good vibration damping characteristics can be obtained over a wide frequency band such as shake vibration, idle vibration, muffled sound vibration, acceleration noise, and the like.

Further, as a result of forming the small diameter portion 34c in the inner cylinder 34, a space can be provided on the outer peripheral side of the inner cylinder 34, so that the second sub-fluid chamber having a relatively large capacity on the outer peripheral side of the inner cylinder 34. Even if 70B and the second orifice 70A are arranged,
It is possible to avoid the second sub-fluid chamber 70B and the second orifice 70A from protruding to the outside, and it is possible to reduce the size of the vibration isolator. Further, it is very advantageous for the engine mount 20 of the vehicle, which has a large restriction on the mounting space.

Further, after the first opening hole 34f is formed in the small diameter portion 23c, the first hole opening hole 34f is formed in the thin film elastic body 32.
By forming the first diaphragm 32c by closing e, the space near the first diaphragm 32c becomes the first sub-fluid chamber 68A, and the minimum diameter tubular portion of the first orifice component member 36 excluding this space. 36a and the small diameter portion 34c of the inner cylinder 34, the first orifice 68A
Because of the simple structure, the first sub-fluid chamber 68B and the first sub-fluid chamber 68B
The fluid resonance system including the orifice 68A can be easily adjusted, and the manufacturing cost can be reduced. Further, the first diaphragm 32c does not have a structure that is largely displaced in the vibrating body supporting direction unlike the conventional device, and is not damaged by a flying stone or the like, so that it is possible to provide a vibration-proof supporting device having excellent durability. it can.

Further, the inner cylinder 34 and the outer cylinder 38 define an annular space, and the second orifice component 40 is formed in this annular space.
Since the second sub-fluid chamber 70B and the second orifice 70A are formed by disposing the second diaphragm 42 and the second diaphragm 42, the second sub-fluid chamber 70B and the second orifice 7 are formed.
The fluid resonance system of 0 A can be easily adjusted, and the manufacturing cost can be reduced. Further, like the above-described first diaphragm 32c, the second diaphragm 42 does not have a structure that is largely displaced in the vibration body supporting direction, and is not damaged by flying stones or the like.
It is possible to provide a vibration damping support device having excellent durability.

Further, the second diaphragm 42 is structured to extend in the circumferential direction, and the fluid passage (first
Since the passage 40b ₁ and the second passage 40b ₂ ) are formed so as to be longer than the circumferential length of the second orifice constituting member 40, the auxiliary fluid chamber and the orifice having a large volume can be provided. By increasing the volume of these, it is possible to sufficiently generate a damping force that cancels the shake vibration generated during braking.

In the above embodiment, the vibration isolating support device according to the present invention is applied to the engine mount 20 that supports the engine 22. However, the vibration isolating support device according to the present invention is applicable. The present invention is not limited to the engine mount 20, and may be, for example, an anti-vibration support device for a machine tool that vibrates.

The small diameter portion 34c is formed by forming the inner cylinder 34 into a U-shaped cross section.
The shape is not limited to this, and any other shape may be used as long as the third orifice 72A is formed on the inner peripheral side thereof.

Further, the first passage 40 forming a fluid passage
The b ₁ and the second passage 40b ₂ are formed as different passages in the axial direction, but the present invention is not limited to this and may be formed as a long passage, for example, as a meandering passage. .

[Brief description of drawings]

FIG. 1 is an overall configuration diagram showing an arrangement state of a vibration isolation support device of the present invention.

FIG. 2 is a view showing a cross section along an axial direction of a vibration isolation support device.

FIG. 3 is a plan view of the anti-vibration support device.

FIG. 4 is a diagram showing a side surface of a vibration isolation support device with a part thereof as a cross section.

FIG. 5 is a view showing a cross section of a vibration isolation support device cut in a direction orthogonal to the axial direction.

FIG. 6 is a perspective view showing a main part of a second orifice constituent member which is a constituent member of the vibration-damping support device.

FIG. 7 is a first cylindrical member that is a constituent member of the anti-vibration support device,
It is the figure which expanded the cross section of the 2nd cylindrical member.

[Explanation of symbols]

20 engine mount (anti-vibration support device) 22 engine (vibration body) 28 member (support body) 32 support elastic body 32c first diaphragm 34 inner cylinder (first cylindrical member) 34c small diameter portion 34f first opening hole (opening hole) ) 36 first orifice constituting member (second tubular member) 38 outer cylinder (third tubular member) 40 second orifice constituting member 40b ₃ first communicating hole 40b ₄ second communicating hole 40b ₁ , 40b ₂ fluid passage 42 Second diaphragm 46 Magnetic path member 48 Leaf spring 52 Electromagnetic actuator (actuator) 66 Main fluid chamber 68A First orifice 68B First sub-fluid chamber 70A Second orifice 70B Second sub-fluid chamber 72B Third sub-fluid chamber 72A Third orifice

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Kazushige Aoki 2 Takara-cho, Kanagawa-ku, Yokohama, Kanagawa Nissan Motor Co., Ltd. (72) Inventor Tsutomu Hamabe 2 Takara-cho, Kanagawa, Yokohama, Japan Nissan Motor Co., Ltd.

Claims (5)

[Claims] 1. A support elastic body interposed between a vibrating body side and a support body side, a main fluid chamber defined by the support elastic body, and a variable volume sub-fluid chamber communicating with the main fluid chamber via an orifice. A fluid enclosed in the main fluid chamber, the sub-fluid chamber and the orifice, a movable member elastically supported so as to form a part of the partition wall of the main fluid chamber, and the movable member being the main fluid chamber. In a vibration-damping support device including an actuator that displaces in a direction in which the volume changes, a shaft center faces a vibrator support direction and an axial direction between one of the vibrator side or the support side and the support elastic body. A first tubular member having a small diameter portion formed in a part thereof, a second tubular member joined to the inside of the small diameter portion, and the inside of the first and second tubular members and Mainstream in the space surrounded by the inner surface of the supporting elastic body A chamber is arranged, and a first sub-fluid chamber and a first orifice are arranged in an annular space surrounded by an inner peripheral surface of the small diameter portion and an outer peripheral surface of the second cylindrical member, An anti-vibration support device, wherein a second sub-fluid chamber and a second orifice are arranged on the outer peripheral side of the small diameter portion. 2. The main fluid chamber is formed in the space from the second tubular member to the inner surface of the support elastic body, and the third orifice is formed on the inner peripheral surface side of the second tubular member. The anti-vibration support device according to claim 1, wherein a third sub-fluid chamber is formed in a space from the second tubular member to the movable member. 3. An opening hole is formed in a part of the small-diameter portion, the opening hole is closed by a first diaphragm, and the annular space near the first diaphragm serves as the first sub-fluid chamber. 3. The annular space other than the first sub-fluid chamber is used as the first orifice.
The anti-vibration support device according to the above. 4. The first tubular member is externally fitted with a third tubular member to form an annular space between the outer peripheral surface of the small diameter portion and the inner peripheral surface of the third tubular member, A second diaphragm is arranged in a circumferential direction of a part of the annular space, and a second orifice constituting member is arranged in the remaining annular space due to the arrangement of the second diaphragm. The anti-vibration support device according to any one of claims 1 to 3, wherein a second sub-fluid chamber is formed between the second diaphragms. 5. The second orifice constituting member is formed with a first communication hole that communicates with the main fluid chamber side and a second communication hole that communicates with one circumferential end of the second diaphragm. At the same time, a vibration passage, which is connected to the first communication hole and the second communication hole and is longer than the circumferential length of the second orifice component, is formed inside. Support device.