JP3336945B2 - Anti-vibration support device and vehicle equipped with this device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention uses a damping force generated when a fluid passes through an orifice to obtain an anti-vibration effect and positively increases the volume of a fluid chamber defined by a supporting elastic body. The present invention relates to an anti-vibration support device capable of generating an active support force by changing the vibration control device, and a vehicle equipped with the device.

[0002]

2. Description of the Related Art An example of this type of prior art is disclosed in Japanese Patent Application Laid-Open No. 9-250590 previously proposed by the present applicant.

[0003] A vibration-damping support device disclosed in Japanese Patent Application Laid-Open No. 9-250590 will be described with reference to FIG. 4. This vibration-damping support device 1 is, for example, a flat fixing member fixed to a vibrating body such as an engine. On the upper surface of the fixing member 2, a bolt 2a for attachment to an engine is integrally provided. On the back surface of the fixing member 2, the center of the upper surface of the supporting elastic body 3 is vulcanized and adhered. Have been.

[0004] The support elastic body 3 has a hollow portion 3a having a mountain-shaped cross section formed on the inner surface thereof, with the central portion rising above the peripheral edge portion. The lower end of the support elastic body 3 having a thin shape is joined to the inner peripheral surface of the intermediate cylinder 4 by vulcanization bonding. The intermediate cylinder 4 is a member formed with a small-diameter cylindrical portion 4a and provided with an annular concave portion on the outer peripheral side.
c, an opening is formed, and the inside and outside of the intermediate cylinder 4 communicate with each other. The outer cylinder 5 fitted to the outside of the intermediate cylinder 4 has a diaphragm 6 coupled to an edge of an opening 5a formed on the peripheral surface, and the diaphragm 6 closes the opening 5a while closing the opening 5a. Bulges toward the annular concave portion.

The orifice constituting member 7 fitted inside the intermediate cylinder 4 includes a minimum-diameter cylinder 7a formed to have a smaller diameter than the small-diameter cylinder 4a of the intermediate cylinder 4, and an upper part of the minimum-diameter cylinder 7a. An annular upper flat portion 7b extending radially outward.
And an annular lower flat portion 7c extending radially outward from a lower portion of the minimum diameter cylindrical portion 7a. An annular space is defined between the lower flat portion 7c and the inner peripheral surface of the intermediate cylinder 4. Have been.

Then, an integral part of the support elastic body 3, the intermediate cylinder 4, the outer cylinder 5, the diaphragm 6, and the orifice constituting member 7 is inserted into the inside of the apparatus case 8 from the lower end opening thereof, and the intermediate cylinder 4 is inserted into the upper end caulking part 8a. It is arranged on the upper part of the device case 8 with the upper part of the outer cylinder 5 abutting.

A seal ring 9, a leaf spring 11 integrated with a movable member 10, a gap holding ring 12, an electromagnetic actuator 13, and a load sensor 14 are sequentially incorporated in a lower portion of the device case 8. After the assembly is completed, the lower end opening of the device case 8 is
The components are built into the device case 8 by closing the device case 8 and caulking the lower end of the device case 8 inward in the radial direction.

Further, a fluid such as oil is sealed in a communication passage from the cavity 3a of the support elastic body 3 to the space where the diaphragm 6 swells, but the orifice constituting member 7 extends from the cavity 3a of the support elastic body 3. Assuming that the communication path up to the annular space between the intermediate cylinder 4 and the main fluid chamber is a main fluid chamber, the vicinity of the opening formed in the intermediate cylinder 4 is an orifice, and a region surrounded by the diaphragm 6 and facing the opening is defined as an orifice. A fluid resonance system is formed as a sub-fluid chamber.

The vibration isolating support device 1 is provided in the orifice with respect to a relatively low frequency vibration input capable of moving fluid between the main fluid chamber and the sub fluid chamber through the orifice of the fluid resonance system. A fluid dynamic resonance provides a high dynamic spring constant and a high damping force, while a relatively high frequency vibration that makes it impossible to move the fluid through the orifice is input. A control signal for canceling the pressure fluctuation of the fluid is transmitted to the electromagnetic actuator 13.
To displace the movable member 10 to change the volume in the fluid chamber (without actually changing the volume), resulting in an anti-vibration support device with a low dynamic spring constant.

[0010]

By the way, when a large load (large excitation force) is input from the vibrating body to the anti-vibration support device 1 having the above structure, the supporting elastic body 3 moves toward the movable member 10 side. Deforms with excessive compression. At this time,
Although the cavity 3a side of the support elastic body 3 abuts on the orifice constituting member 7 and is greatly deformed, as shown in FIG. 4, it is locally limited only to the corner portion A between the minimum diameter cylindrical portion 7a and the upper flat portion 7b. Abut

As described above, when the support elastic member 3 is locally brought into contact with the orifice constituting member 7, the surface pressure of the contact portion is increased, and the spring constant in the support direction (direction for supporting the vibrator) is increased. However, since the supporting direction spring becomes the hard supporting elastic body 3, the vibration transmission rate is deteriorated.

When a large load is input, the supporting elastic body 3 comes into contact with the corner A of the orifice constituting member 7 with a small contact area, and a large stress is concentrated on the contacting portion. 3 has a problem in durability.

In view of this, it is conceivable that the support elastic member 3 is formed so as not to come into contact with the orifice constituting member 7 even if a large load is input. There is a problem that it is not preferable in terms of durability.

The present invention has been made in view of the unsolved problem of such a prior-art vibration isolating support device, and is capable of supporting the elastic member even if the elastic member is excessively compressed by a large load. It is an object of the present invention to provide an anti-vibration support device capable of obtaining a sufficient vibration reduction effect while improving the durability of a body, being small in size and inexpensive, and a vehicle equipped with this device.

[0015]

In order to achieve the above object, according to the first aspect of the present invention, a supporting elastic body is interposed between a vibrating body side and a supporting body side, and the supporting elastic body has a vibrating body having an axial center. A first cylindrical member facing the support direction and having a small-diameter cylindrical portion formed in a part of the axial direction is connected, and a second cylindrical member is connected inside the small-diameter cylindrical portion to form the first and second cylindrical members. A main fluid chamber is arranged in a space surrounded by the inside of the member and the inner surface of the support elastic body, and an annular space surrounded by an inner peripheral surface of the small-diameter cylindrical portion and an outer peripheral surface of the second cylindrical member. A movable member that arranges a sub-fluid chamber with variable volume and an orifice, forms a part of the partition wall of the main fluid chamber, and is displaceable in a direction that changes the volume of the fluid chamber; And an actuator for displacing in the direction, wherein the actuator is disposed in front of the second tubular member. A portion facing the supporting elastic body, an annular flat portion having a small area extending from the inside of the small-diameter cylindrical portion in a direction orthogonal to the axial direction; And an inclined portion formed with a downward inclined surface so as to gradually separate from the supporting elastic body as going toward.

According to a second aspect of the present invention, a supporting elastic body is interposed between the vibrating body side and the supporting body side, and the axis of the supporting elastic body is oriented in the vibrating body supporting direction and a small diameter is provided in a part of the axial direction. A first tubular member forming a tubular portion is joined, a second tubular member is joined inside the small-diameter tubular portion, and the inside of the first and second tubular members and the inner surface of the support elastic body are joined together. A main fluid chamber is arranged in the enclosed space, and a variable-volume sub-fluid chamber and an orifice are arranged in an annular space surrounded by an inner peripheral surface of the small-diameter cylindrical portion and an outer peripheral surface of the second cylindrical member. And a magnetizable movable member that forms a part of the partition wall of the main fluid chamber and is displaced in a direction that changes the volume of the fluid chamber, and generates an electromagnetic force that displaces the movable member according to a drive signal. And a vibration isolating support device comprising: An annular flat portion having a small area extending from the inside of the small-diameter cylindrical portion in a direction perpendicular to the axial direction, a portion facing the elastic body, and a continuous portion from the inside of the flat portion; And an inclined portion formed with a downward inclined surface so as to gradually separate from the supporting elastic body as going toward.

According to a third aspect of the present invention, in the anti-vibration support device according to the first or second aspect, an extension portion for extending the inclined portion provided on the second cylindrical member toward an axis is provided. Provided.

According to a fourth aspect of the present invention, there is provided the anti-vibration support device according to any one of the first to third aspects.
The boundary between the flat portion and the inclined portion of the tubular member was formed with roundness.

Further, a vehicle equipped with the anti-vibration support device according to claim 5 has a power including a horizontal engine in which the anti-vibration support device according to any one of the above 1 to 4 is mounted laterally with respect to the vehicle body. It was arranged in the longitudinal direction of the body of the plant.

[0020]

According to the first aspect of the present invention, when a large exciting force is input from the vibrating body side or the supporting body side, the supporting elastic body is excessively compressed and abuts on the second cylindrical member to be deformed.
At this time, the portion of the second cylindrical member facing the support elastic body of the present invention is an annular flat portion having a small area, and continuous from the flat portion to the inside, from the support elastic body toward the axis. Since it has a structure including an inclined portion formed with a downwardly inclined surface so as to be gradually separated, the contact portion of the supporting elastic body is concentrated on the inclined portion having a large area. As described above, when the supporting elastic body comes into contact with the inclined portion having a large area, the stress applied to the supporting elastic body gradually increases.
The spring constant can be prevented from suddenly increasing, and excessive elastic deformation of the supporting elastic body can be prevented to improve durability.

According to the invention of claim 2, according to claim 1,
The same effect as the invention can be obtained, and when a large excitation force is input from the vibrating body side or the supporting body side,
Because the support elastic body comes into contact with the slope with a large area,
The spring constant of the supporting elastic body in the supporting direction does not suddenly change to a large value. As a result, even if a large excitation force is input, the supporting direction spring does not rise suddenly, so that the vibration transmissibility does not deteriorate and a sufficient damping effect can be obtained without increasing the displacement of the movable member. Therefore, the size of the electromagnetic actuator can be reduced, and the cost can be reduced.

According to the third aspect of the present invention, since the inclined portion extends toward the axis, the area where the supporting elastic body can abut is increased, and the excessive elasticity of the supporting elastic body is increased by the increased area. Deformation can be prevented.

According to the fourth aspect of the present invention, since the boundary between the flat portion and the inclined portion is formed with a rounded shape, no stress concentration occurs in the supporting elastic body. Therefore, the durability of the support elastic body can be further improved.

According to the fifth aspect of the present invention, when a vehicle equipped with a power plant including a horizontally mounted engine mounted laterally with respect to the vehicle body suddenly starts, a protection device disposed on the rear side in the front-rear direction of the vehicle body. The vibrating support device is provided with a vibrating force that excessively compresses the supporting elastic body due to a torque reaction force from the power plant. With the anti-vibration support device described above, the anti-vibration support effect can be sufficiently obtained while the durability of the support elastic body is improved, and sufficient silence in the vehicle cabin can be obtained. Further, when the vehicle is decelerated by an engine brake or the like, an exciting force for excessively compressing the supporting elastic body acts on a vibration isolating support device disposed in the front in the vehicle longitudinal direction. When the vibration supporting device is the vibration isolating supporting device according to any one of claims 1 to 3, the above-described effects can be obtained.

[0025]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic side view of a vehicle to which an active vibration control device, which is an embodiment of a vibration isolation support device according to the present invention, is applied.

First, the construction will be described. An engine (vibrating body) 17 mounted horizontally is mounted on an active engine mount (hereinafter referred to as a vibration-proof support device) 20 disposed rearward in the vehicle longitudinal direction. It is supported by a vehicle body (support) 18 composed of a suspension member and the like. In addition,
Actually, a plurality of engine mounts that generate a passive support force according to the relative displacement between the engine 17 and the vehicle body 18 are interposed between the engine 17 and the vehicle body 18 in addition to the vibration isolating support device 20. . As a passive engine mount, for example, a normal engine mount that supports a load with a rubber-like elastic body, or a known fluid-filled mount in which a fluid is sealed inside a rubber-like elastic body so that a damping force can be generated. An insulator or the like can be applied.

Next, what is shown in FIG.
0 shows a specific configuration of the apparatus case 43. The outer case 34, the intermediate tube (first cylindrical member) 36, the orifice constituent member (second cylindrical member) 37, the support elastic body 32, and the like are mounted on the device case 43. An electromagnetic actuator 52 which contains components and displaces an elastically supported movable member 78 in a direction in which the volume of the fluid chamber 84 changes while forming a part of a partition of the fluid chamber 84 below the mount components; A load sensor 54 for detecting the vibration state of the member 28 is incorporated.

That is, the anti-vibration support device 20 of the present embodiment
Has an engine-side connecting member 30 with the connecting bolt 30a fixed upward. A hollow cylindrical body 30b having an inverted trapezoidal cross section is fixed to a lower portion of the engine-side connecting member 30.

The lower side of the engine side connecting member 30 and the hollow cylindrical body 30
The supporting elastic body 32 is fixed by vulcanization bonding so as to cover the periphery of b. The support elastic body 32 is a thick, substantially cylindrical elastic body that is gently inclined downward from the center to the outer periphery, and has a hollow section 32a having a mountain-shaped cross section on the inner surface. And the supporting elastic body 3 made thin
2 has a shaft center (hereinafter referred to as a mount shaft) P _1.
Are connected to the inner peripheral surface of the intermediate cylinder 36 coaxially with the hollow cylindrical body 30b in the vibrating body supporting direction (in this case, the vertical direction) by vulcanization bonding.

The intermediate cylinder 36 is a member in which a small-diameter cylindrical portion 36c is continuously formed between an upper cylindrical portion 36a and a lower cylindrical portion 36b having the same outer diameter, and has an annular concave portion on the outer circumference. Although not shown, an opening is formed in the small-diameter tube portion 36c, and the inside and the outside of the intermediate tube 36 communicate with each other through this opening.

An outer cylinder 34 is fitted on the outer side of the intermediate cylinder 36, and the outer cylinder 34 has an inner peripheral diameter of the upper end cylinder 3 of the intermediate cylinder 36.
This is a cylindrical member having the same dimensions as the outer diameters of the lower cylinder 6a and the lower cylinder 36b, and having the same axial length as the intermediate cylinder 36. An opening 34a is formed in the outer cylinder 34, and an outer periphery of a diaphragm 42 made of a rubber thin film elastic body is coupled to an opening edge of the opening 34a so as to close the opening 34a. It bulges toward the inside of the outer cylinder 34.

When the outer cylinder 34 having the above structure is fitted to the intermediate cylinder 36 so as to surround the annular recess, an annular space is defined in the circumferential direction between the outer cylinder 34 and the intermediate cylinder 36, and the annular space is formed in the annular space. The diaphragm 42 is provided in a swelled state. A cylindrical orifice component member 37 is fitted inside the intermediate cylinder 36.

The orifice component 37 is also shown in FIG.
As shown, the radial direction (mount axis P ₁Direction perpendicular to
And the area facing the support elastic body 32 is reduced.
An annular upper flat portion (flat portion) 37a and the upper flat portion
37a, it is continuous from the inside and
Form with a downward slope that gradually separates from the elastic body 32
The formed inclined portion 37b and the inclined portion 37b
P₁The extension 37e provided so as to extend toward
A small-diameter cylindrical portion 37c continuous from the lower part of the inclined wall portion 37b
Extending radially outward from the lower portion of the small-diameter cylindrical portion 37c.
And an annular lower flat portion 37d.
The boundary C between the tang portion 37a and the inclined portion 37b is rounded.
It is formed. Then, these upper flat portions 37a,
The inclined portion 37b, the small-diameter cylindrical portion 37c, and the lower flat portion 37d
An annular space is provided between the position surrounded by
ing. Also, one of the inclined wall portion 37b and the small-diameter cylindrical portion 37c is provided.
A second opening 37e is formed in the portion.

The device case 43 has an upper end caulking portion 43a having a circular opening having a diameter smaller than the outer diameter of the upper end cylindrical portion 36a at the upper end thereof, and a case body continuous with the upper end caulking portion 43a. Is a cylindrical member (the lower end opening is indicated by a broken line in FIG. 2) having the same inner diameter as the outer diameter of the outer cylinder 34 and continuing to the lower end opening. By caulking the lower end opening portion inward in the radial direction after the completion of assembling, the caulked portion shown by the solid line in FIG. 2 is formed.

Then, the outer cylinder 34 in which the support elastic body 32, the intermediate cylinder 36, the orifice constituting member 37 and the diaphragm 42 are integrated is fitted into the inside of the apparatus case 43 from the lower end opening thereof, and the lower surface of the upper end caulking part 43a is inserted. When the upper ends of the outer cylinder 34 and the intermediate cylinder 36 are brought into contact with each other, they are arranged at the upper part in the device case 43. At this time, the device case 4
An air chamber 42c is defined in a portion surrounded by the inner peripheral surface of the diaphragm 3 and the diaphragm 42. An air hole 43a is formed at a position facing the air chamber 42c, and air is passed through the air hole 43a. The chamber 42c communicates with the atmosphere.

A cylindrical spacer 70 is fitted in a lower portion of the device case 43, and a movable member 78 is disposed in an upper portion of the spacer 70, and an electromagnetic actuator 52 is disposed in a lower portion of the spacer 70. Have been.

The spacer 70 has a cylindrical upper cylinder 7.
0a, a cylindrical lower cylindrical body 70b, and a substantially cylindrical diaphragm 70c made of a rubber thin film elastic body bonded and vulcanized between the upper and lower ends of these cylindrical bodies.

The electromagnetic actuator 52 has an external cylindrical yoke 52a, an annular exciting coil 52b disposed on the upper end side of the yoke 52a, and a magnetic pole fixed vertically to the center of the upper surface of the yoke 52a. Permanent magnet 52c
It is composed of The yoke 52a has an annular first yoke member 53a and a permanent magnet 5 in a central cylindrical portion.
2c is fixed to the second yoke member 53b.

The upper and lower cylinders 70a, 70b
The intervening diaphragm 70c bulges toward a concave portion 52d formed on the outer periphery of the yoke 52a. In addition, a load sensor 64 is interposed between the lower surface of the yoke 52a and the lid member 62 having the vehicle body-side connection bolt 60 in order to detect residual vibration required for vibration reduction control. As the load sensor 64, a piezoelectric element, a magnetostrictive element, a strain gauge, or the like can be applied. As shown in FIG. 1, the detection result of this sensor is supplied to the controller 25 as a residual vibration signal e. I have.

On the other hand, above the electromagnetic actuator 52, a seal ring 72 for fixing a seal member, a support ring 74 for supporting an outer peripheral portion of a leaf spring 82 to be described later from below at a free end, and a permanent Magnet 52c
And a gap holding ring 76 for setting a gap H between the movable members 78. The outer diameters of the seal ring 72, the support ring 74, and the gap holding ring 76 are set to the same dimensions as the inner diameter of the upper cylinder 70a of the spacer 70 described above, and the upper cylinder projecting upward from the yoke 52a. A seal ring 72 in the body 70a;
All of the support ring 74 and the gap retaining ring 76 are fitted inside. A movable member 78 is arranged inside the seal ring 72, the support ring 74, and the gap holding ring 76 so as to be vertically displaceable.

The movable member 78 is a member composed of a partition wall forming member 78A having a disk shape in appearance and a magnetic path forming member 78B formed in a disk shape larger in diameter than the partition wall forming member 78A. A bolt hole 80a is formed in the axial center of the partition wall forming member 78A located farther from the electromagnetic actuator 52, and a magnetic path forming member 78B close to the electromagnetic actuator 52 is formed.
The partition wall forming member 78A and the magnetic path forming member 78B are integrally connected by screwing a movable member bolt 80 that passes through the bolt hole 80a into the bolt hole 80a.

The partition wall forming member 78A and the magnetic path forming member 78
A ring-shaped continuous constriction 79 is defined between B, and a plate spring 82 for elastically supporting the movable member 78 is accommodated in the constriction 79. That is, the leaf spring 82 is a disk-shaped member having a hole formed in the center, and the free end of the inner periphery of the leaf spring 82 is supported from below the rear center of the partition wall forming member 78A. 82 is supported at its free end from below by a spring support portion 74a of a support ring 74, whereby the movable member 78 is
3 is elastically supported via a leaf spring 82.

The partition wall forming member 78A is formed by reducing the thickness of the partition wall portion 80c facing the fluid chamber 84,
A member formed with an annular rib 80b protruding upward from the outer periphery of the member. A fluid chamber 84 is formed by the upper surface of the partition wall forming member 78, the lower surface of the support elastic body 32, and the inner peripheral surface of the orifice constituting member 37, and the fluid is sealed in the fluid chamber 84.

In order to prevent leakage of fluid from the fluid chamber 84 to the constricted portion 79 containing the leaf spring 82,
A ring-shaped seal member 86 made of a rubber-like elastic body is fixed between the outer periphery of the partition wall forming member 78A and the inner periphery of the seal ring 72. The elastic deformation of the seal member 86 causes the seal ring 7 or The relative displacement of the movable member 78 in the vertical direction with respect to the device case 43 is allowed.

Next, a brief description will be given of the vibration input damping action of the vibration isolating support device 20 of the present embodiment. In the anti-vibration support device 20 of the present embodiment, the hollow portion 32a of the support elastic body 32 communicates with the axial center space of the orifice member 37, and the axial center space of the orifice member 37 and the orifice member 37 and the intermediate cylinder 36. Between the second opening 3
7d, the annular space and the diaphragm 4
2 is communicated through an opening formed in the intermediate cylinder 36, and a communication passage from the cavity 32 a of the support elastic body 32 to the space in which the diaphragm 42 swells is provided. A fluid such as oil is enclosed.

If the communication path from the hollow portion 32a of the support elastic body 32 to the annular space between the orifice constituting member 37 and the intermediate cylinder 36 is the main fluid chamber 84, the vicinity of the opening formed in the intermediate cylinder 36 will be described. Is an orifice, and a fluid resonance system is formed in which a region surrounded by the diaphragm 42 while facing the opening is a sub-fluid chamber. The characteristics of the fluid resonance system, that is, the characteristics determined by the mass of the fluid in the orifice, the expansion direction spring of the support elastic body 32, and the expansion direction spring of the diaphragm 42 are determined when idle vibration occurs while the vehicle is stopped, that is, 20 to Engine mount 20A at 30Hz,
It is adjusted to show a high dynamic spring constant and a high damping force when 20B is vibrated.

On the other hand, the exciting coil 52b of the electromagnetic actuator 52 generates a predetermined electromagnetic force in accordance with a drive signal y which is a current supplied from the controller 25. The controller 25 includes a microcomputer, necessary interface circuits, an A / D converter, and a D / A
It is configured to include a converter, an amplifier, a storage medium such as a ROM and a RAM, and the like, so that an active supporting force capable of reducing vibration generated in the engine 17 is generated in the anti-vibration support device 20.
A drive signal y for the anti-vibration support device 20 is generated and output.

Also, as described above, the engine mount 2
0 has a built-in load sensor 64, which detects the vibration state of the vehicle body 18 in the form of a load and outputs it as a residual vibration signal e, and the residual vibration signal e is supplied to the controller 25 as a signal representing vibration after interference. Have been.

Here, the idle vibration and the muffled sound vibration generated by the engine 17 are, for example, in the case of a reciprocating four-cylinder engine, the engine vibration of the engine rotation secondary component is the vehicle body 1
The main reason is that the vibration is transmitted to the engine 8 and, if the drive signal y is generated and output in synchronization with the secondary component of the engine rotation, the vibration on the vehicle body side can be reduced. Therefore, in the present embodiment, an impulse signal synchronized with the rotation of the crankshaft of the engine 17 (for example, in the case of a reciprocating four-cylinder engine, one for every 180 ° rotation of the crankshaft) is generated, and the reference signal x Pulse signal generator 19 which outputs as
Is provided, and the reference signal x is supplied to the controller 25.

Then, based on the supplied residual vibration signal e and reference signal x, the controller 25 uses a synchronous filtered filter which is one of the successively updating adaptive algorithms.
By executing the -XLMS algorithm, a drive signal y for the anti-vibration support device 20 is calculated, and the drive signal y is output to the anti-vibration support device 20.

More specifically, the controller 25 has an adaptive digital filter W having a variable filter coefficient W _i (i = 0, 1, 2,..., I-1: I is the number of taps). At a predetermined sampling clock interval from the time when the reference signal x is input, the adaptive digital filter W
Of one of outputting a filter coefficient W _i in the order as the drive signal y, it is adapted to execute a process of appropriately updating the filter coefficient W _i of the adaptive digital filter W based on the reference signal x and the residual vibration signal e.

The updating equation of the adaptive digital filter W is expressed by F
The following equation (1) is obtained according to the filtered-X LMS algorithm. _{W i (n + 1) =} W i (n) -μR T e (n) ...... (1) where, indicates that the value in (n), (n + 1 ) term is attached is sampling time n, n + 1, μ is a convergence coefficient. The update reference signal R ^T is theoretically expressed as
The reference signal x is transmitted to the electromagnetic actuator 5 of the anti-vibration support device 1.
2 is a value obtained by filtering a transfer function C between the load sensor 64 and the load sensor 64 with a transfer function filter C ＾ modeled by a finite impulse response filter, but since the magnitude of the reference signal x is “1”, the transfer function When the impulse response of the filter C # is generated one after another in synchronization with the reference signal x, the impulse response coincides with the sum of the impulse response waveforms at the sampling time n. Also, theoretically, the reference signal x is filtered by the adaptive digital filter W to generate the drive signal y. However, since the size of the reference signal x is “1”, the filter coefficient W _i is sequentially changed. Output as the drive signal y, the result is the same as when the result of the filter processing is set as the drive signal y.

When an idle vibration frequency or higher frequency vibration (for example, muffled sound vibration) is input, a control vibration having the same cycle as the vibration and a phase opposite to that of the vibration is generated. 20 so that the transmission force of vibration to the vehicle body 18 becomes “0” (more specifically,
A drive signal y is generated and supplied to the excitation coil 52b so that the vibration force input to the vibration isolation support device 20 due to the vibration of the engine 17 is offset by the control force obtained by the electromagnetic force of the electromagnetic actuator 52). It is supposed to.

As a result, the drive signal y is supplied to the exciting coil 52b.
Is generated, but the magnetic path forming member 78B includes:
Since a constant magnetic force has already been applied by the permanent magnet 52c, the magnetic force of the exciting coil 52b is
It can be considered that it acts to increase or decrease the magnetic force of c. As described above, when the magnetic force of the permanent magnet 52c is increased or decreased, the movable member 78 is displaced in both the forward and reverse directions, and when the movable member 78 is displaced, the partition forming member 78A that forms a part of the partition of the fluid chamber 84 is formed. Is also displaced, thereby changing the volume of the fluid chamber 84, and the expansion spring of the support elastic body 32 is deformed by the change in the volume, so that an active supporting force in both the forward and reverse directions is generated in the vibration isolating support device 20. It is.

Next, the operation of the anti-vibration support device 20 of this embodiment will be described with reference to the drawings. When the vehicle starts abruptly, a large downward load (excitation force) is applied to the anti-vibration support device 20 disposed behind the horizontally mounted engine 17 in the vehicle longitudinal direction by a torque reaction force from the engine 17 side. ) F is input, and the support elastic body 32 is in an excessively compressed state. At this time, as shown in FIG. 3, the orifice constituting member 3
7 is largely deformed while abutting, but the abutting portion concentrates on the inclined portion 37 b of the orifice constituting member 37.
When the support elastic body 32 abuts on the inclined portion 37b having the large area, the support direction spring of the support elastic body 32 does not rapidly become hard.

That is, FIG. 6 shows a comparison between the present embodiment and a conventional device provided with the orifice constituting member 3 (see FIG. 5), showing the relationship between the vibration displacement x of the supporting elastic body and the reaction force f. I will try. Here, the vibration displacement x ₁ is the position where the supporting elastic body first contacts the orifice constituting member, and the vibration displacement x 1
₂ shows the displacement when the vehicle suddenly starts.

According to this, the conventional apparatus has a vibration displacement x ₂
Support since the elastic member 3 reaction force f ₂ are locally brought into contact with the orifice configuration member 7 is increased, the support direction of the spring constant k ₂ of the elastic support body _{3 (k 2 = ∂f 2 /} ∂x at ₂ ) Get up sharply.

On the other hand, in this embodiment, the vibration displacement x_TwoNoto
The support elastic body 32 comes into contact with the inclined portion 37b having a large area
The reaction force f₁Rises slowly, supporting bullets
Constant k in the supporting direction of the elastic body 32₁(K₁= ∂f₁/ ∂
x_Two) Is a small value (k ₁<K_Two).

The change in the spring constant is gradual when the orifice component member 37 is not provided, but the amount of vibration displacement becomes too large, and the durability of the support elastic body 32 is deteriorated. Thus, in this embodiment, the resilient support member 32 by entering a large excitation force when sudden start of the vehicle even in contact with the orifice component 37, without the spring constant k ₁ of the support direction rapidly rises characteristics Therefore, there is no fear that the vibration transmissibility suddenly deteriorates. Therefore, a sufficient damping effect can be obtained without increasing the displacement amount of the movable member 78, so that the size of the electromagnetic actuator 13 can be reduced and the cost can be reduced.

Further, an extension portion 37e is provided to
Since the area of the support elastic body 37 is in contact with the inclined portion 37b, the support elastic body 32 can be prevented from being excessively displaced while the support elastic body 37 is in contact with the inclined portion 37b. Excessive displacement of the elastic body 32 can be restricted.

FIG. 7 is a graph showing the operation under the condition of the same load F.
Added to the elastic support when abutting the orifice component
The stress was compared between the conventional device and the present embodiment.
According to this figure, in the conventional device, the support elastic body 3 has an orifice.
Small area S of the component 7 ₁Abuts corner A of
Therefore, the stress increases.
Has a large surface on the inclined portion 37b of the orifice constituting member 37.
Product S_TwoThe contact is small, so the stress is small. Also, the present embodiment
Upper flat portion 37a and inclined portion of orifice constituting member 37
The boundary C with 37b is formed with roundness
Thus, stress concentration does not occur in the support elastic body 37. But
Therefore, the device of the present embodiment increases the durability of the support elastic body 37.
It can be greatly improved.

As described above, for a vehicle having a large torque reaction force at the time of sudden start, a sufficient anti-vibration support effect can be obtained while the durability of the support elastic body 32 is improved, and sufficient quietness in the vehicle interior is obtained. Can be obtained.

When the vehicle is decelerated by an engine brake or the like, a large downward load (excitation force) is input to an engine mount disposed in front of the engine 17 in the vehicle longitudinal direction. When the anti-vibration support device 20 of the embodiment is arranged, the above-described effects can be obtained.

The application of the present invention is not limited to a vehicle. The present invention can be applied to a vibration isolating support device for reducing vibrations generated by components other than the engine 17. Regardless of the above, the same operation and effect as those of the above embodiments can be obtained. For example, the present invention is applicable to an anti-vibration support device that reduces vibration transmitted from a machine tool to a floor or a room.

In each of the above embodiments, the drive signal y
Synchronous Filtered as an algorithm for generating
Although the -X LMS algorithm is applied, the applicable algorithm is not limited to this, and may be, for example, a normal Filtered-X LMS algorithm or the like.

[Brief description of the drawings]

FIG. 1 is a schematic side view of a vehicle.

FIG. 2 is a cross-sectional view illustrating a configuration of a vibration isolation support device of the present invention.

FIG. 3 is a view showing a shape of an orifice constituting member according to the present invention and a state in which an elastic support is deformed by input of a large excitation force.

FIG. 4 is a cross-sectional view showing a configuration of a preceding vibration isolation support device.

FIG. 5 is a view showing a state in which the elastic support is deformed by the input of a large excitation force in the preceding vibration isolating support device.

FIG. 6 is a table showing the relationship between the reaction force of the supporting elastic body and the vibration displacement between the apparatus of the present invention and the preceding apparatus.

FIG. 7 is a table comparing the stress applied to the supporting elastic body by the input of a large excitation force between the apparatus of the present invention and the preceding apparatus.

[Explanation of symbols]

 Reference Signs List 17 engine (vibration body) 18 body (support) 20 anti-vibration support device 32 support elastic body 36 intermediate cylinder (first cylindrical member) 36c small-diameter cylindrical portion 36c 37 orifice constituent member (second cylindrical member) 37a Flat upper part Part (flat part) 37b Inclined part 37c Small diameter cylindrical part 37d Lower flat part 37e Extension part 42 Diaphragm 52 Electromagnetic actuator 52a Yoke 52b Exciting coil 52c Permanent magnet 78 Movable member 84 Main fluid chamber C Boundary part between upper flat part and inclined part

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Kazushige Aoki 2 Takaracho, Kanagawa-ku, Yokohama-shi, Kanagawa Prefecture Inside Nissan Motor Co., Ltd. (56) References JP-A-9-250590 (JP, A) JP-A Sho62 −292942 (JP, A) JP-A-60-34544 (JP, A) JP-A-2-34843 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16F 13/18 F16F 13/26

Claims (5)

(57) [Claims] A first cylinder in which a support elastic body is interposed between a vibrating body side and a support body side, and a small-diameter cylindrical portion is formed on the support elastic body with an axis oriented in the vibrating body support direction and partially in the axial direction. The second fluid member is coupled to the inside of the small-diameter tubular portion, and the main fluid chamber is formed in a space surrounded by the inside of the first and second cylindrical members and the inner surface of the support elastic body. Are arranged, and in the annular space surrounded by the inner peripheral surface of the small-diameter cylindrical portion and the outer peripheral surface of the second cylindrical member, a variable-volume sub-fluid chamber and an orifice are arranged. A vibration isolating support device, comprising: a movable member forming a part of a partition wall and displaceable in a direction for changing the volume of the fluid chamber; and an actuator for displacing the movable member in the direction. A portion of the member facing the support elastic body,
An annular flat portion having a small area extending from the inside of the small-diameter cylindrical portion in a direction perpendicular to the axial direction, and continuing from the flat portion to the inside, gradually from the support elastic body toward the axis; And an inclined portion formed by attaching a downward inclined surface so as to be separated from the supporting member. 2. A first cylinder in which a supporting elastic body is interposed between the vibrating body side and the supporting body side, and a small-diameter cylindrical portion is formed on the supporting elastic body with an axis oriented in the supporting direction of the vibrating body and partly in the axial direction. The second fluid member is coupled to the inside of the small-diameter tubular portion, and the main fluid chamber is formed in a space surrounded by the inside of the first and second cylindrical members and the inner surface of the support elastic body. Are arranged, and in the annular space surrounded by the inner peripheral surface of the small-diameter cylindrical portion and the outer peripheral surface of the second cylindrical member, a variable-volume sub-fluid chamber and an orifice are arranged. A magnetizable movable member that forms a part of a partition wall and is displaced in a direction that changes the volume of the fluid chamber, and an electromagnetic actuator that generates an electromagnetic force that displaces the movable member in response to a drive signal In the vibration support device, a portion of the second cylindrical member facing the support elastic body is
An annular flat portion having a small area extending from the inside of the small-diameter cylindrical portion in a direction orthogonal to the axial direction, and continuous from the inside of the flat portion, gradually from the support elastic body toward the axis. And an inclined portion formed by attaching a downward inclined surface so as to be separated from the support member. 3. An anti-vibration support device according to claim 1, wherein an extension is provided to extend the inclined portion provided on the second cylindrical member toward an axis. 4. The anti-vibration support device according to claim 1, wherein a boundary between the flat portion and the inclined portion of the second cylindrical member is formed round. 5. The anti-vibration support device according to claim 1, wherein the anti-vibration support device is disposed in a vehicle front-rear direction of a power plant including a horizontally mounted engine mounted laterally to the vehicle body. A vehicle equipped with a support device.