JP3438507B2 - Anti-vibration support device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an anti-vibration support device for isolating and supporting a vibrating body, such as an engine of a vehicle, which periodically oscillates, on a supporting body such as a vehicle body, and more particularly to a fluid An electromagnetic actuator that generates a displacement force on a magnetizable movable member that changes the volume of the chamber, and a load sensor that is disposed between the yoke of the electromagnetic actuator and the support body and detects residual vibration on the support body side are provided. Anti-vibration support device.

[0002]

2. Description of the Related Art An engine mount, which is a vibration isolating support device generally used for supporting a power unit of a vehicle, mainly has good antivibration against idle vibration, engine shake, muffled noise vibration and noise vibration during acceleration. The vibration damping function is required to be exhibited, but among these various vibrations, the characteristics required for the vibration isolation support device in order to reduce engine shake, which is a vibration with a relatively large amplitude of about 5 to 15 Hz, are: , While having a high dynamic spring constant and high damping, idle vibration which is a relatively large amplitude vibration of about 20 to 30 Hz, and muffled sound vibration which is a relatively small and medium amplitude vibration of about 80 to 800 Hz The characteristics required of the vibration-proof support device to reduce noise and vibration during acceleration are low dynamic spring constant and low damping. Therefore, it is difficult to prevent all vibrations with an ordinary engine mount made of an 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, the prior application described in Japanese Patent Application No. 8-68055 previously filed by the present applicant. There is technology.

In this prior art, a vibrating body that generates periodic vibrations and a supporting elastic body interposed between supporting bodies that support the vibrating body, and a main fluid chamber defined by the supporting elastic body and having a fluid enclosed therein are provided. A variable volume sub-fluid chamber that communicates with the main fluid chamber via an orifice, a movable member that forms a part of the partition wall of the fluid chamber and is displaceable in a direction that changes the volume of the fluid chamber, and the movable member. An electromagnetic actuator capable of generating a displacement force that displaces a member in the direction, a pulse signal generator that detects a vibration generation state in the vibrating body and generates a reference signal, and a residual vibration on the support side is detected. A load sensor that outputs a residual vibration signal, and a controller that outputs a drive signal to the electromagnetic actuator based on the residual vibration signal and the reference signal to generate a displacement force in the electromagnetic actuator. A vibration-damping support device provided.

When vibration is input from the engine side, the pulse generator generates a reference signal corresponding to the reference vibration and outputs it to the controller. When residual vibration occurs on the vehicle body side member, the load sensor causes the vehicle body side member to detect the residual vibration. The vibration status of is detected in the form of load 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 vehicle body member to be "0". . Further, since the main fluid chamber has a structure in which it communicates with the sub fluid chamber through the orifice, when the supporting elastic body is deformed by the vibration input from the engine side and the main fluid chamber changes in volume, The fluid enclosed in the chamber and the liquid enclosed in the sub-fluid chamber move with each other through the orifices to generate a damping force, so that a passive fluid-filled vibration damping support device can be obtained.

[0006]

FIG. 6 shows the lower structure of the vibration-damping support device 2 attached to the vehicle body-side member 1. The movable member 4 and the electromagnetic member are arranged in this order from the top in the device case 3. The actuator 5 and the load sensor 6 are arranged coaxially, and the load sensor 6 is built in while applying a preload by a lid member 7 fixed by caulking to the opening end of the device case 3.

The movable member 4 is a disk-shaped leaf spring 4a.
And a magnetic path member 4a fixed to the central portion of the leaf spring 4a. The leaf spring 4a is provided between the annular seal ring 8a and the gap retaining ring 8b arranged in the tubular device case 4. The outer periphery of the yoke 5a of the electromagnetic actuator 5 is in contact with the lower end of the gap retaining ring 8b.

Further, the electromagnetic actuator 5 has a cylindrical yoke 5a, an exciting coil 5c embedded in an annular groove-shaped coil housing recess 5b formed on the upper surface of the yoke 5a, and
The yoke 5a is provided with a permanent magnet 5d fixed to the central portion of the upper surface thereof, and the central portion of the lower surface of the yoke 5a is provided with a sensor housing recess 5e having a circular shape with a diameter smaller than the inner peripheral diameter of the coil housing recess 5b. Has been done. The upper part of the load sensor 6 is housed with the pressure receiving surface in contact with the lower surface of the sensor housing recess 5e.

Further, the lid member 7 has a bottom lid 7b for fixing the connecting bolt 7a connected to the vehicle body-side member 1 and covering the load sensor 4, and an engaging portion 7c for engaging with the caulking portion 3a of the device case 3. , A thick walled cylindrical portion 7d that connects the bottom lid 7a and the locking portion 7c.

By the way, when a vibration force is input to the anti-vibration support device 2 from the vibrating body side, the seal ring 8a and the gap holding ring are passed through the supporting spring of the supporting elastic body (not shown) as shown by the broken line arrow in FIG. Excitation force is input to the outer peripheral surface of the upper surface of the yoke 5a from the path of the main fluid chamber 9, the leaf spring 4a, and the gap retaining ring 8a through the path of 8b and the expansion spring of the support elastic body.

Here, the yoke 5a is the recess 5 for storing the coil.
Since the wall thickness between b and the sensor housing recess 5e (the portion indicated by the dimension H ₁ in FIG. 6) is thin, when an external force is applied to the outer peripheral side of the upper surface, the lower surface side with which the load sensor 6 is in contact is As the fulcrum, the outer peripheral side moves to the lower side (support 1 side) and is likely to be deformed in an upward convex arc shape. That is, the rigidity of the yoke 5a is low with respect to the external force directed downward from the outer peripheral side of the upper surface.
Note that it is difficult to form the yoke 52a in which the wall thickness between the coil housing recess 5b and the sensor housing recess 5e is significantly increased due to the restrictions of the layout of the device (height restriction, outer diameter restriction, etc.).

Further, since the lid member 7 is provided with the thick-walled expanded portion 7d even if an external force directed downward from the engaging portion 7c is applied, the lid member 7 is not easily deformed and has a high rigidity. .
In a structure including such a yoke 5a and a lid member 7, when a vibration force is input from the outer peripheral side of the upper surface of the yoke 52a,
Most of the exciting force passes through the yoke 5a having low rigidity and is transmitted to the support body 1 side through the lid member 7 having high rigidity, and the exciting force is not input to the load sensor 54.
Therefore, the residual vibration transmitted to the side of the support 1 cannot be accurately detected.

The present invention has been made in view of the above problems, and it is possible to prevent the vibration on the support side in the entire frequency range by the load sensor accurately detecting the residual vibration on the support side. The purpose is to provide a support device.

[0014]

In order to solve the above-mentioned problems, a vibration-damping support device according to a first aspect of the present invention defines a vibrating body and a supporting elastic body interposed between the supporting bodies and the supporting elastic body. Fluid chamber, a fluid enclosed in the fluid chamber, a magnetizable movable member that forms a part of the partition of the fluid chamber, an electromagnetic actuator that displaces the movable member, and residual vibration on the support side. A load sensor for detecting
A controller that generates and outputs a control signal to the electromagnetic actuator according to the detection result of the load sensor, and an apparatus case is interposed between the support elastic body and the support body, and the support in the apparatus case is provided. On the support body side from the elastic body, an annular support member that supports the movable member,
The supporting member is brought into contact with the outer peripheral edge of the surface of the yoke facing the supporting elastic body, the electromagnetic actuator is disposed, and the load sensor is provided at the center of the surface of the yoke facing the supporting body and the center of the lid member. And the outer peripheral engagement portion of the lid member is in contact with the outer peripheral edge of the surface of the yoke facing the support body side, and is secured to the opening end of the device case by caulking. In the vibration support device, when the vibration force is transmitted from the vibrating body side through the supporting elastic body to the outer peripheral side of the yoke and the supporting body side through the lid member ,
The yoke is rigid so that it is not easily deformed by the excitation force.
So that it can be easily deformed by the excitation force.
The rigidity of the lid member is reduced and the electromagnetic actuation is performed.
Use a solid cylindrical yoke and the
Coil storage formed as an annular groove on the surface facing the moving member
Recess and excitation coil embedded in this coil housing recess
And a surface facing the movable member surrounded by the exciting coil
The permanent magnet fixed to the
A circular hole with a diameter smaller than the inner peripheral diameter of the coil housing recess
Sensor storage recess formed to accommodate the load sensor
And is closest to the sensor housing recess.
The inner corner of the coil housing recess and the sensor housing
The corners of the recess should be rounded or curved with a curved surface.
The attached shape was used.

According to a second aspect of the present invention, there is provided the vibration-damping support device according to the first aspect, wherein the coil storage recess is embedded.
The corners of the exciting coil to be installed are
Be in non-contact with the inner corner of the coil housing recess
The inner corner of the coil housing recess to the corner of the exciting coil.
Rounded or large radius of curvature with respect to the side corner
It has a shape with a slope.

The invention according to claim 3 is the same as claim 1 or
The vibration-isolating support device according to 2, wherein the sensor storage recess is
The corners of the load sensor housed in the
So that it is not in contact with the corner of the sensor housing recess.
The corner of the load sensor to the corner of the sensor storage recess.
With a large radius of curvature or a large slope
It has a digit shape.

The invention according to claim 4 is the same as claim 1.
The anti-vibration support device according to any one of 3 to 3, wherein the lid portion
A lid body that contacts the load sensor, and the device case.
An outer peripheral locking portion that is caulked and fixed to the open end of the base,
Expanding diameter that connects to the outer peripheral locking part while expanding the diameter from the lid body
A structure including a tubular portion, wherein the enlarged diameter tubular portion is provided with the lid main body.
Deforms easily when the excitation force is transmitted by making the wall thickness thinner
Was formed.

Further, the invention of claim 5 is the same as that of claim 4.
In the vibration-damping support device described above,
Formed in a substantially bowl shape that curves toward the side of the base or the side of the support
did.

[0019]

[0020]

When the anti-vibration supporting device according to the present invention is arranged between the vibrating body and the supporting body, the path through which the exciting force generated on the vibrating body side is transmitted to the supporting body side is the supporting spring of the supporting elastic body. the passing <br/> Ji and supporting member, the yoke, the path for transmitting the support side through the lid member, extension spring resilient support bodies, the movable member through the fluid chamber, the support member, the yoke, supported by the lid member There is a route to the body side. The exciting force passing through these paths acts as a force that deforms the yoke into a convex arc shape toward the support elastic body side with the portion where the load sensor is in contact as a fulcrum.

According to the vibration-damping support device of the first aspect, however, the rigidity of the yoke is increased so that the yoke is not easily deformed by the vibration force, and the yoke is easily deformed by the vibration force. > Since the lid member has a structure with low rigidity, most of the excitation force is input to the load sensor. Therefore, most of the vibration transmitted from the vibrating body side to the supporting body side is input to the load sensor, so that the load sensor can accurately detect the residual vibration on the supporting body side.

Further, when the coil housing recess is formed in the yoke for embedding the exciting coil and the sensor housing recess is formed for housing the load sensor, the space between the coil housing recess and the sensor housing recess is formed. There is a problem in terms of yoke rigidity when the vibrating force described above is applied because the thick portion becomes thin. Although it is conceivable to increase the thickness of the thick portion described above, it becomes a large-sized yoke, which is not possible due to the layout constraint of the device.

Therefore, in the vibration-damping support device according to the first aspect,
According to this, the corners on the inner peripheral side of the coil housing recess closest to the sensor housing recess and the corners of the sensor housing recess are rounded with a curved surface or beveled. In this way, the wall thickness increases only at the inner peripheral side corners of the coil storage recess and the corners of the sensor storage recess, which are rounded or beveled, so that they can be easily deformed even when the above-mentioned vibration force is applied. It was not rigid able to provide a significantly yoke, load
The heavy sensor can accurately detect the residual vibration on the support side.
it can.

Further, when the adhesive for fixing the exciting coil is poured into the coil housing recess, the adhesive smoothly flows along the roundness or the slope formed at the corner of the coil housing recess. The pouring work can be easily performed.

According to the vibration isolating support device of the second aspect , in addition to the effect of the first aspect , the corner of the exciting coil does not come into contact with the corner of the coil accommodating recess, so that the coil accommodating recess is provided in the coil accommodating recess. Since the exciting coil can be embedded closely, almost no air is trapped in the coil housing recess, and it is possible to prevent moisture from being generated due to thermal expansion and contraction of air and destruction of the seal structure.

According to the vibration-damping support device of the third aspect , in addition to the effect of the second aspect , the corner of the load sensor does not come into contact with the corner of the sensor accommodating recess, and the pressure-receiving surface of the load sensor. Can be reliably brought into contact with the surface of the sensor accommodating recess, so that the load sensor can perform good sensing.

According to the vibration-damping support device of the fourth aspect, the effect of any one of the first aspect to the third aspect can be obtained, and at the same time, the outer peripheral lock is caulked and fixed to the opening end of the device case. Thinner than the lid body between the section and the lid body
The lid member is a member having a low rigidity because the diameter-expanding tubular portion is provided so that it is easily deformed when the vibration force is transmitted .
Thus, the above-mentioned vibration force is not transmitted to the support body side through the lid member, and most of the vibration force is input to the load sensor, so that the load sensor can accurately detect the residual vibration on the support body side. .

Further, according to the vibration isolating support device of the fifth aspect, since the diameter-enlarged tubular portion having a reduced wall thickness is formed in a substantially bowl shape which curves toward the yoke side or the support body side, it is further reduced. It becomes a rigid member. Therefore, the load sensor can detect the residual vibration on the support side more accurately.

[0029]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows 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 supporting body. It is applied to). An engine mount denoted by reference numeral 20 in FIG. 1 is disposed on the rear side of the vehicle body of an engine 22 mounted horizontally, and an upper portion thereof is fixed to a bracket 24 and a lower portion thereof is fixed to a vehicle body 26, which serves as a support member 28. Is attached to.

The engine mount 20 incorporates mount components such as an outer cylinder 34, an orifice component 36, a support elastic body 32 defining a main fluid chamber, etc. inside the device case 43, and below the mount components. An electromagnetic actuator 52 as an actuator for displacing a movable member elastically supported while forming a part of a partition wall of the main fluid chamber in a direction in which the volume of the main fluid chamber changes, and a load sensor 54 for detecting a vibration state of the member 28. It is a device with and built in.

That is, the engine mount 20 is
The engine-side connecting member 30 is provided with the connecting bolt 30a fixed upward. This engine side connecting member 30
A hollow cylindrical body 30b having an inverted trapezoidal cross section is fixed to the lower part of the.

On the lower surface side of the engine side connecting member 30, the lower side of the engine side connecting member 30 and the hollow cylindrical body 3 are provided.
The support elastic body 32 is fixed by vulcanization adhesion so as to cover the periphery of 0b.

The support elastic body 32 is a thick-walled, substantially cylindrical elastic body that gently inclines downward from the central portion toward the outer peripheral portion, and has a hollow portion 32a having a mountain-shaped cross section formed on the inner surface. There is. The lower end portion 32b of the thin support elastic body 32 has a shaft center (hereinafter referred to as a mount shaft) P ₁
Is bonded by vulcanization adhesion to the inner peripheral surface of the orifice constituting member 36 that is coaxial with the hollow cylindrical body 30b and faces the vibrating body supporting direction (in this case, the vertical direction).

The orifice-constituting member 36 is a member in which a small-diameter tubular portion 36c is continuously formed between an upper-end tubular portion 36a and a lower-end tubular portion 36b having the same outer diameter, and an annular recess is provided on the outer periphery. . Further, an opening hole 36d is formed in the small diameter cylinder portion 36c. The lower end portion 32b of the support elastic body 32 is connected to the inner peripheral surface of the orifice component member 36, but the lower end portion 32b does not close the opening hole 36d, and the orifice component member 36 is provided through the opening portion 36d. The inside and outside of the are communicating.

The outer cylinder 3 is provided in the orifice component member 36.
4 is externally fitted, and the inner peripheral surface of the outer cylinder 34 surrounds the annular recess of the orifice forming member 36 to define an annular space in the circumferential direction. The diaphragm 42 is arranged in this annular space.

That is, the inner peripheral diameter of the outer cylinder 34 is the same as the outer peripheral diameters of the upper end cylinder portion 36a and the lower end cylinder portion 36b of the orifice constituting member 36, and the axial length thereof is the same as that of the orifice constituting member 36. It is a cylindrical member set to. A slit-shaped opening 34a facing the annular recess other than the position where the opening hole 36d is formed is formed in the outer cylinder 34 in the circumferential direction.

The diaphragm 42 is a thin film elastic body made of rubber, is connected to the entire circumference of the opening edge portion of the opening portion 34a to close the opening portion 34a, and bulges toward the annular concave portion of the orifice component member 36. It is arranged in a closed state. The outer cylinder 34 is fitted inside the upper part of the device case 43.

The device case 43 has an upper end crimped portion 43a having a circular opening having a diameter smaller than the outer diameter of the upper end tubular portion 36a at the upper end thereof, and the shape of the case body continuous with the upper end crimped portion 43a. Is a member having a cylindrical shape in which the inner peripheral diameter is the same as the outer peripheral diameter of the outer cylinder 34 and continues to the lower end opening (the lower end opening is shown by the broken line in FIG. 1).

Then, the outer cylinder 34 in which the support elastic body 32, the orifice component 36 and the diaphragm 42 are integrated is fitted into the inside of the lower end opening of the device case 43, and the outer cylinder 34 is placed on the lower surface of the upper end crimped portion 43a. The upper end portion of the orifice component member 36 and the orifice component member 36 come into contact with each other, so that they are arranged in the upper portion of the device case 43. Here, an air chamber 42a is defined in a portion surrounded by the inner peripheral surface of the device case 43 and the diaphragm 42, and an air hole 42b is formed at a position facing the air chamber 42a. The air chamber 42a communicates with the atmosphere via 42b.

Further, in the lower part of the device case 43, the leaf spring 4 integrated with the seal ring 44 and the magnetic path member 46 is provided.
8, gap retaining ring 50, electromagnetic actuator 5
2, the load sensor 54, and the lid member 57 are sequentially assembled, and after the assembly of these parts is completed, the device case 4
By caulking the lower end portion of 3 toward the inner side in the radial direction, the lower end caulking portion 43c is formed as shown by the solid line in FIG. Here, in the present embodiment, the magnetic path member 46 and the leaf spring 48 constitute a movable member.

The seal ring 44 is the device case 43.
The outer peripheral diameter is the same as the inner peripheral diameter of
Is an annular member having an inner diameter smaller than that of the lower end tubular portion 36b. The upper surface of the seal ring 44 is disposed in contact with the lower end of the outer cylinder 34.

The leaf spring 48 is a disc member whose outer diameter is slightly smaller than the inner diameter of the device case 43. A magnetizable metal such as iron is attached to the lower center of the leaf spring 48. The magnetic path member 46 composed of is fixed coaxially with the mount axis P ₁ . Then, the gap retaining ring 50 is arranged in a state where the upper peripheral portion of the leaf spring 48 is in contact with the lower surface of the seal ring 44. The gap retaining ring 50 is
The axial length is set to be the axial length from the lower surface of the leaf spring 48 to the lower surface of the magnetic path member 46 so that a predetermined gap is provided between the lower surface of the magnetic path member 46 and the upper surface of the electromagnetic actuator 52. It is an annular member set to a length obtained by adding the dimension of the gap to.

The electromagnetic actuator 52 that abuts the lower surface of the gap retaining ring 50 is surrounded by a cylindrical yoke 52a, an exciting coil 52b coaxially embedded in the upper end surface of the yoke 52a, and an exciting coil 52b. The permanent magnet 52c has a magnetic pole fixed in the vertical direction within the upper surface of the yoke 52a.

That is, a continuous coil housing recess 52d is formed as an annular groove on the upper surface side of the yoke 52. The coil housing recess 52d, as shown in FIG. 3, is formed a corner portion 52d ₁ of the bottom inner peripheral side rounded with a curvature surface of the radius R _1. The corner 52d ₂ on the outer peripheral side of the bottom surface of the coil housing recess 52d is also formed by being rounded with a radius of curvature R ₁ (see FIG. 5).

The exciting coil 52b embedded in the coil housing recess 52d is, as shown in FIG.
The corner 52b ₁ facing the corner 52d ₁ is formed with a rounded shape having a curvature surface with a radius R ₂ (R ₂ > R ₁ ) larger than the radius R ₁ described above. . Incidentally, the corners of the exciting coil 52b that faces the corner portion 52d ₂ of the bottom outer peripheral side of the coil housing recess 52d also rounded with a curvature surface of the radius R ₁ is greater than radius R ₂ of the above-mentioned (R _2> R ₁₎ It is formed by attaching. The exciting coil 52b is embedded after the adhesive is poured into the coil housing recess 52d.

Further, as shown in FIG.
A circular sensor storage recess 52e is formed in the center of the lower surface.
Has been done. The sensor storage recess 52e is shown in FIG.
So that its upper surface corner 52e₁Is radius R₃With curvature surface
It is formed with roundness. And sensor storage
The lower surface of the yoke 52b with the upper part housed in the recess 52e.
A load sensor 54 is provided in the. Here, shown in FIG.
As shown in FIG.₁To
The corners 54a of the load sensor 54 facing each other are provided with sensor storage recesses.
Top corner 52e of the portion 52e₁Radius of₃Larger radius
R_Four(R_Four> R ₃) With a rounded surface
Has been done.

A lid member 57 is arranged so as to cover the load sensor 54 from the lower side.
As shown in FIG. 2, a disk-shaped bottom lid 58, a diameter-expanding tubular portion 59 that rises from the outer peripheral edge of the bottom lid 58 toward the yoke 52a side while rising in diameter, and the diameter-expanding tubular portion 59. And an outer peripheral engaging portion 60 that extends annularly outward from the upper edge of the outer peripheral edge of the outer peripheral locking portion. A plurality of press-fitting holes 58 a are formed on the outer peripheral side of the bottom lid 58.
The vehicle body side connecting bolt 56 is press-fitted in a.

Here, the enlarged diameter cylindrical portion 59 formed between the bottom lid 58 and the outer peripheral locking portion 60 is set to have a smaller wall thickness than the bottom lid 58 and has a predetermined curvature toward the lower side. It is formed in a substantially bowl shape that bends at.

Then, the lower surface of the load sensor 54 is brought into contact with the central portion of the upper surface of the lid member 57, and the lower end caulking portion 43c of the device case 43 shown by the solid line in FIG.
When 0 is caulked and fixed, the bottom lid 58 is moved to the load sensor 54.
The lid member 57 is integrated with the device case 43 while pressing the yoke 52a toward the yoke 52a side and applying a predetermined preload thereto. The above-mentioned preload is a load that is applied in advance to give an initial load to the load sensor 54.

By the way, the cavity 32 of the support elastic body 32
a, a space surrounded by the outer peripheral surface of the orifice forming member 36 and the leaf spring 48 is defined as a main fluid chamber 66.
A fluid such as oil is sealed in the communication passage from the space through the opening 36d to the space where the diaphragm 42 bulges.

The internal space near the diaphragm 42 is used as a sub-fluid chamber 67, and the sub-fluid chamber 67 and the main fluid chamber 6
An orifice 68 is used as a communication path between the six fluid chambers 6, and when the volume of the main fluid chamber 66 fluctuates, a fluid resonance occurs due to the sub fluid chamber 67 and the orifice 68.

Here, the characteristics of the fluid resonance system, which is determined by the mass of the fluid in the orifice 68 and the shape of the flow path in the expansion direction of the support elastic body 32, are the characteristics when the engine shake occurs during running, that is, at 5 to 15 Hz. The engine mount 20 is adjusted so as to exhibit a high dynamic spring constant and a high damping force when the engine mount 20 is vibrated.

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.
According to the above, 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, an amplifier, etc., and is a vibration in a frequency band in which the fluid cannot move between the main fluid chamber 66 and the sub fluid chamber 67 through the orifice 68, that is, a vibration of a higher frequency than the engine shake described above. When idle vibration, muffled sound vibration, or vibration during acceleration is input, control vibration having the same cycle as the vibration is generated in the engine mount 20, and the transmission force of the vibration to the member 28 becomes “0”. As described above (more specifically, the excitation force input to the engine mount 20 by the vibration of the engine 22 side is canceled by the control force obtained by the electromagnetic force of the electromagnetic actuator 52), the drive signal y Generating and exciting coil 52b
It is designed to be supplied to.

Here, idle vibration and muffled sound vibration are
For example, in the case of a reciprocating 4-cylinder engine, the engine rotation 2
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 of the crankshaft of the engine 22 is synchronized (for example, in the case of a reciprocating 4-cylinder engine,
A pulse signal generator 76 is provided which generates an impulse signal and outputs it as a reference signal x each time the crankshaft rotates by 180 degrees.
Is supplied to the controller 74 as a signal indicating the generation state of the vibration.

The load sensor 54 detects the vibration state of the member 28 in the form of a load and outputs it as a residual vibration signal e. The residual vibration signal e is supplied to the controller 74 as a signal representing the vibration after the interference. Has been done.
Then, the controller 74 generates and outputs the drive signal y based on the reference signal x and the residual vibration signal e according to the Filtered-X LMS algorithm which is one of the successive update adaptive algorithms.

Next, the engine mount 20 of this embodiment
The operation of the anti-vibration mechanism will be described. When the engine 22 is started and the vibration is input to the engine mount 20, the controller 74 executes a predetermined calculation process, outputs the drive signal y to the electromagnetic actuator 52, and reduces the vibration to the engine mount 20. Generate active control force to get.

That is, the filter coefficient of the adaptive digital filter W is applied 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 and the residual vibration signal e are input. Are sequentially supplied as the drive signal y. As a result, a magnetic force corresponding to the drive signal y is generated in the exciting coil 52b, but since the magnetic path member 46 is already given a constant magnetic force by the permanent magnet 52c, the magnetic force by the exciting coil 52b is the permanent magnet. It can be considered to act to strengthen or weaken the magnetic force of 52c. That is, in the 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 in which the elastic supporting force of the leaf spring 48 and the magnetic force of the permanent magnet 52c are balanced. . When the driving signal y is supplied to the exciting coil 52b in this neutral state, if the magnetic force generated in the exciting coil 52b by the driving signal y is in the opposite direction to the magnetic force of the permanent magnet 52c, the magnetic path member 4 is formed.
6 is displaced in a direction in which the clearance with the electromagnetic actuator 52 increases. On the contrary, if the magnetic force generated in the exciting coil 52b is in the same direction as the magnetic force of the permanent magnet 52c, 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, and if the leaf spring 48 is displaced up and down, the main fluid chamber 66 can be moved.
Of the supporting elastic body 32 due to the change in the volume of
Expansion spring (considering the dynamic model, the supporting elastic body 32
The support spring and the expansion spring are interposed in parallel. ) Is deformed, an active supporting force is generated in the engine mount 20 in both forward and reverse directions. Then, each filter coefficient W of the adaptive digital filter W that becomes the drive signal y
_{Since 1} is sequentially updated according to the synchronous Filtered-X LMS algorithm, after a certain amount of time has passed and the filter coefficients W _i of the adaptive digital filter W have converged to the optimum values, the drive signal y is changed to the engine mount 2
By being supplied to 0, idle vibration and muffled sound vibration transmitted from the engine 22 to the member 28 side via the engine mount 20 are reduced.

Here, considering the main transmission path of the exciting force input from the engine 22 side to the engine mount 20,
As shown in FIG. 5, the engine 22 receives an input to the orifice component 36 through the support spring of the support elastic body 32, and then reaches the member 28 through the seal ring 44, the gap retaining ring 50, the electromagnetic actuator, and the lid member 57. The fluid in the main fluid chamber 66 is input from the engine 22 through the first path (the path indicated by the dashed arrow A _{1 in} FIG. 5) and the expansion spring of the support elastic body 32, and from there, the leaf spring, the gap retaining ring 50, and the electromagnetic field. A _second path (broken line arrow A _{2 in} FIG. 5) to the member 28 via the actuator and the lid member 57.
Path) and a permanent magnet 52c that gives a magnetic force to the magnetic path member 46, and inputs it as a reaction force to the axial center portion of the yoke 52a, and from there to the member 28 via the load sensor 54 and the lid member 57. Route 3 (route of dashed arrow A _{3 in} FIG. 5)
Can be considered.

The exciting force passing through the first path A ₁ and the exciting force passing through the second path A ₂ are
a on the outer peripheral side of the upper surface of a.
The vibrating force that is overlapped on the outer peripheral side of the upper surface of a is passed through the path toward the load sensor 54 and the outer peripheral side of the yoke 52a, and the lid member
7 and the route (route indicated by the one-dot chain line arrow B in FIG. 5) to be input to No.

The load sensor 5 is attached to the yoke 52a.
When a vibration force is applied from the outer peripheral side (in the direction of the one-dot chain line arrow B) with the lower surface side on which 4 abuts as a fulcrum, the coil storage recess 52d and the sensor storage recess 52e, which have the smallest wall thickness, are formed.
A force is applied so that the outer peripheral side moves downward (toward the member 28) from the space so that the outer peripheral side is deformed into a convex arc shape.

However, the yoke 52a of this embodiment is
Corner 52d of coil housing recess 52d ₁And sensor storage recess
Corner 52e of part 52e₁Together with roundness
And a corner portion of a conventional yoke (see FIGS. 3 and 4).
Compared to the corners shown by the broken line), as shown in FIG.
52d corner₁, 52e₁By minimum wall thickness
Dimension H₂Is increasing (H₂> H₁: H₁Is traditional
Dimension of minimum wall thickness of yoke). Thus, the coil
Minimum thickness part between the storage recess 52d and the sensor storage recess 52e
Dimension H₂The yoke 52a with increased
A yaw with increased rigidity that does not easily deform even when force is applied.
KU 52a.

Therefore, most of the vibration forces of the first path A ₁ and the second path A ₂ which are overlapped on the outer peripheral side of the upper surface of the yoke 52a are input to the load sensor 54 from the yoke 52a having a large rigidity. That is, most of the vibration transmitted from the engine 22 to the member 28 is input to the load sensor 54 via the yoke 52a, so that it cannot be canceled by the active control force described above, and the member 28 cannot be canceled.
The residual vibration transmitted to the side can be accurately detected by the load sensor 54.

Further, the exciting force, which is superposed on the outer peripheral side of the upper surface of the yoke 52a, passes through the outer peripheral side of the yoke 52a and the lid member 5
Considering the path input to 7, the yoke 5
The outer peripheral engaging portion 6 of the lid member 57 in order from the outer peripheral side of the lower surface of 2a.
0, a diameter-expanding cylinder portion 59, and a bottom lid 58 are present, and the diameter-increasing cylinder portion 59 in these transmission members is formed to have a thin wall thickness and is curved to a lower side with a predetermined curvature. Since it is bowl-shaped, it is a member with reduced rigidity that is easily deformed.

Therefore, from the yoke 52a to the lid member 57.
Vibrations to the member 28 side via the yoke are blocked by the expanded diameter cylindrical portion 59 having a reduced rigidity, and all the exciting force is applied to the yoke 5.
Since it is input to the load sensor 54 via 2a, it is possible to detect the residual vibration by the load sensor 54 more accurately.

Although the exciting coil 52b is embedded after the adhesive is poured into the coil housing recess 52d, the adhesive smoothly flows along the curved surfaces of the rounded coil housing corners 52d ₁ and 52d _2. Therefore, the operation of pouring the adhesive can be easily performed.

Further, as shown in FIG. 3, the exciting coil 5
Since the corner 52b _{1 of} 2b is formed with a larger roundness than the coil housing corners 52d ₁ and 52d ₂ of the coil housing recess 52d, the corners of the exciting coil and the coil housing recess are formed at right angles to each other. Compared with the structure of the device, the outer surface of the exciting coil 52b other than the corners is provided with the coil housing recess 52.
It can be embedded in close contact with the inner surface of d. As a result, almost no air is generated in the coil housing portion 52d, and it is possible to prevent the generation of water due to the thermal expansion and contraction of air, the destruction of the seal portion, and the like.

Further, as shown in FIG. 4, the load sensor 5
The corner 54a of No. 4 is also the corner 52e of the sensor housing recess 52e.
Since it is formed with a radius larger than _1, the pressure receiving surface (upper surface) of the load sensor 54 can be reliably brought into contact with the lower surface of the sensor housing recess 52e. As a result, the load sensor 5 is provided on the lower surface of the yoke 52a as compared with the conventional device in which the corners of the load sensor and the sensor housing recess are formed at right angles to each other.
4 can be arranged normally.

In the above embodiment, coil storage
Coil storage corner 52d of recess 52d ₁, 52d₂Predetermined
Formed with a rounded surface with a radius of curvature,
It is the gist of the present invention to provide a structure with no corners, and examples
For example, a chamfered coil storage corner 52d with a slope
₁, 52d₂Even if it is, it is possible to obtain the same effect.
it can. Also, the coil storage corner 52d₁, 52d₂Against
Corner 52b of exciting coil 52b facing₁Rounded
Not only the shape but also the chamfered shape with the above-mentioned slope.
However, the same effect can be obtained.

The corner 52e of the sensor housing recess 52e
Also, the shape is not limited to the rounded shape. For example, a chamfered shape with an inclined surface can also obtain the same effect. Further, the corner portion 54a of the load sensor 54, which faces the corner portion 52e of the sensor housing recess 52e, is not limited to the rounded shape, but the same operational effect can be obtained even if the chamfered shape with the above-described slope is formed. You can

Further, in the above-mentioned embodiment, the enlarged diameter cylindrical portion 59 of the lid member 54 is formed in a substantially bowl shape that curves downward, but, conversely, it is formed in a substantially bowl shape that curves upward. Even
The same effect can be obtained.

Further, in the above embodiment, the engine 22
Although the present invention is applied to the engine mount 20 that supports the engine mount, the application target of the vibration isolation support device according to the present invention is not limited to the engine mount 20. For example, the vibration isolation support device of a machine tool accompanied by vibrations. And so on.

[Brief description of drawings]

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

FIG. 2 is a view showing a cross section along the axial center direction of the anti-vibration support device of the present invention.

FIG. 3 is a diagram showing a coil housing recess and an exciting coil according to the present invention.

FIG. 4 is a diagram showing a sensor housing recess and a load sensor according to the present invention.

FIG. 5 is a diagram showing a structure on a support body side of the anti-vibration support device according to the present invention.

FIG. 6 is a view showing a structure of a conventional anti-vibration support device on a support body side.

[Explanation of symbols]

20 engine mount (anti-vibration support device) 22 engine (vibration body) 28 member (support body) 32 support elastic body 43 device case 44 seal ring (support member) 46 magnetic path member (movable member) 48 leaf spring (movable member) 50 Gap retaining ring (support member) 52 Electromagnetic actuator (actuator) 52a Yoke 52b Excitation coil 52b ₁ Excitation coil corner 52c Permanent magnet 52d Coil storage recesses 52d ₁ and 52d ₂ Coil storage recess corner 52e Sensor storage recess 52e ₁ Corner 54 of sensor housing recess 54 Load sensor 57 Lid member 58 Bottom lid (lid main body) 59 Expanding tubular portion 60 Outer peripheral locking portion 66 Main fluid chamber (fluid chamber) 67 Sub-fluid chamber (fluid chamber) 68 Orifice (fluid chamber) )

─────────────────────────────────────────────────── ─── Continuation of the front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) F16F 13/00 B60K 5/12

Claims (5)

(57) [Claims] 1. A support elastic body interposed between a vibrating body and a support body, a fluid chamber defined by the support elastic body, a fluid enclosed in the fluid chamber, and a part of a partition wall of the fluid chamber. , A magnetizable movable member, an electromagnetic actuator that displaces the movable member, a load sensor that detects residual vibration on the support side, and a control signal for the electromagnetic actuator that is generated according to the detection result of the load sensor. An annular support member for supporting the movable member on the support body side of the support elastic body in the device case, with a device case interposed between the support elastic body and the support body. The support member is brought into contact with the outer peripheral edge of the surface of the yoke facing the support elastic body, the electromagnetic actuator is disposed, and the load sensor faces the support side of the yoke. The device case is disposed so as to be sandwiched between the central portion of the surface and the central portion of the lid member, and the outer peripheral locking portion of the lid member is in contact with the outer peripheral edge of the surface of the yoke facing the support body side. In the anti-vibration support device that is caulked and fixed to the opening end of the, the excitation force is transmitted from the vibrating body side through the supporting elastic body to the outer peripheral side of the yoke, and through the lid member to the supporting body side.
Once reached, it will not be easily deformed by this excitation force.
To increase the rigidity of the yoke and
In order to make it easier to shape, lowering the rigidity of the lid member
In the electromagnetic actuator, a solid cylindrical yoke and
Formed as an annular groove on the surface of the yoke facing the movable member side
The coil storage recess and the coil storage recess
Excitation coil and the movable body surrounded by the excitation coil
The permanent magnet fixed to the surface facing the member, and the yoke of the yoke.
Smaller than the inner diameter of the coil housing recess on the surface facing the support
It is formed as a circular hole with a diameter and is used to store the load sensor.
Sensor storage recess, and the sensor storage recess is provided.
And a corner on the inner peripheral side of the coil housing recess closest to
The corner of the sensor housing recess is rounded with a curved surface,
Alternatively , an anti-vibration support device having a shape with a slope . 2. An excitation that is embedded in the coil housing recess.
The corner of the coil has the coil storage recess facing the corner.
Excitation so that it is in non-contact with the inner corner of the
Match the corner of the coil to the corner on the inner peripheral side of the coil housing recess.
With a large radius of curvature or a large slope
The anti-vibration support device according to claim 1 , wherein the anti-vibration support device has a shape.
Place 3. The load stored in the sensor storage recess.
The sensor storage in which the corners of the heavy sensor face each other.
The load sensor so that it is not in contact with the corner of the recess.
The radius of curvature of the corner of the
Large roundness or a shape with a large slope
The anti-vibration support device according to claim 1 or 2. 4. The cover member is brought into contact with the load sensor.
The main body of the lid and the open end of the device case.
The outer peripheral locking part and the outer part while expanding the diameter from the lid body.
A structure including a diameter-enlarging cylinder part connected to the peripheral locking part,
The diameter expansion tube is made thinner than the lid body, and
Characterized by being formed so that it easily deforms when transmitted
The anti-vibration support device according to any one of claims 1 to 3. 5. The expanded cylinder portion is provided on the yoke side or the
Characterized by being formed in a substantially bowl shape that curves toward the support side
The anti-vibration support device according to claim 4.