JPH11166576A - Vibration isolating support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration isolating support device that can perform vibration isolating control with high accuracy dulling the sensitivity of a load sensor to exciting force in the case of the exciting force being inputted from the direction offset the axis of the device due to rolling vibration or the like generated at a power unit. SOLUTION: A load sensor is arranged adjacently to a yoke positioned closest to the vibration body member side of an electromagnetic actuator, and an opening part of a device case opened to the vehicle body member side from the load sensor is closed with a cover member 57. In a vibration isolating support device of such constitution, the cover member 57 is so formed that the wall thickness of front and rear side parts 59b, facing the longitudinal direction of a vehicle body, of a diameter enlarged cylinder part 59 is formed to be thick so as to set the body longitudinal rigidity of the diameter enlarged cylinder part 59 large. Accordingly, even if exciting force in the body longitudinal direction offset from the axis of the device is inputted during rolling vibration of a power unit including a horizontally mounted engine, the elastic deformation of the diameter enlarged cylinder part 59 in the body longitudinal direction is hardly generated so as to be able to dull the sensitivity of the load sensor to exciting force.

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 supporting a power unit including an engine which generates a periodic vibration on a vehicle body while damping the power unit. In particular, the present invention relates to a load sensor for detecting residual vibration on a support side. The present invention relates to an anti-vibration support device interposed between a component located closest to a vehicle body in an apparatus case and a lid member.

[0002]

2. Description of the Related Art In general, an engine mount, which is an anti-vibration support device used to support a power unit of a vehicle, mainly has good anti-vibration against idle vibration, engine shake, muffled sound vibration, noise vibration during acceleration, and the like. It is required that the vibration-proof function is exhibited. Among these various vibrations, the characteristics required of the vibration-proof support device in order to reduce the engine shake which is a vibration having a relatively large amplitude of about 5 to 15 Hz are as follows. Idle vibration, which has a relatively large amplitude of about 20 to 30 Hz while having a high dynamic spring constant and high damping, 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 isolation support device to reduce the noise and vibration during acceleration are a low dynamic spring constant and low attenuation. Therefore, it is difficult to prevent all vibrations with an engine mount composed of only a normal elastic body or a conventional liquid-filled engine mount.

[0003] In view of the above, an anti-vibration support device capable of actively damping and supporting a vibrating body such as an engine of an automobile has been disclosed in Japanese Patent Application Laid-Open No. 8-145114 filed earlier by the present applicant. There is technology.

In this prior art, as shown in FIG. 11, a vibrating body 1 and a supporting elastic body 3 interposed between the vibrating body 1 and a supporting body 2 are provided.
And a fluid chamber 4 defined by the support elastic body 3,
A movable member 5 comprising a fluid sealed in the fluid chamber 4, a leaf spring 5a forming a part of a partition of the fluid chamber 4, and a magnetizable magnetic path member 5b fixed at the lower center of the leaf spring 5a. An electromagnetic actuator 6 for displacing the movable member 5, a pulse signal generator 7 for detecting a state of generation of vibration in the vibrating body 1 and generating a reference signal, and a residual vibration signal for detecting residual vibration on the support 2 side. And a controller 9 that outputs a drive signal to the electromagnetic actuator 6 based on the reference signal and the residual vibration signal. In this vibration-proof support device, an actuator case 10 is interposed between the support elastic body 3 and the support 2, and the electromagnetic actuator 6 is disposed in the actuator case 10, and the load sensor 8 is The upper surface and the lower surface are sandwiched between the yoke 6A of the electromagnetic actuator 6 and the case member 10a disposed on the support 2 side in the actuator case 10 so as to be in contact therewith.

[0005] When vibration is input from the vibrating body 1 side in the axial direction of the anti-vibration support device, the pulse generator 5 generates a reference signal corresponding to the reference signal and outputs the reference signal to the controller 9. When the residual vibration occurs in 2, the load sensor 8 outputs the residual vibration to the controller 9. Then, the controller 9 sends the drive signal to the electromagnetic actuator 4.
And the electromagnetic actuator 4 appropriately displaces the movable member 5 so that the volume of the fluid chamber 4 changes and the vibration transmission force to the support 2 side is controlled to be “0”.

Meanwhile, in a power unit including a laterally mounted engine, which is often used in a front-wheel-drive vehicle, since the crankshaft of the horizontally mounted engine is oriented in the left-right direction with respect to the vehicle body, the power unit is moved in front, rear, left and right with respect to the vehicle body. When the vehicle is supported on the vehicle body via the engine mount at the four positions, the two engine mounts disposed at the left and right positions are relatively close to the roll inertia main shaft, and the engine mounts disposed at the front and rear two positions are relatively the roll inertia main shaft. Away from you. When the engine is running at a low speed, such as at idle, a torque fluctuation input of the engine causes a roll vibration around the roll inertia main shaft in the power unit,
It is known that vertical vibration occurs in the power unit when the engine rotates at a high speed, and the vibration input by the roll vibration is relatively large in the engine mounts at two front and rear positions far from the roll inertia main shaft. Therefore, if the anti-vibration support device shown in FIG. 11 is disposed as an engine mount at two positions in front and rear distant from the roll inertia main shaft, a support force is actively generated, so that the anti-vibration reduction effect on the vehicle body can be enhanced.

[0007]

Here, if the overall thickness of the actuator case 10 is reduced to form a case structure having low rigidity, the sensitivity of the load sensor 8 to vibration input from the power unit can be improved. .

However, if the rigidity of the entire actuator case 10 is reduced, the sensitivity of the load sensor 8 can be increased with respect to vibration input along the axis of the vibration isolator, but roll vibration occurs in the power unit. The load sensor 8 also picks up the exciting force at that time, which may adversely affect the anti-vibration control.

That is, when the rotational force at the time of roll vibration is input to the anti-vibration support device as an oblique vibration force that is inclined in the front-rear direction of the vehicle body and does not coincide with the axis of the anti-vibration support device, the oblique vibration is applied. The force is also transmitted to the load sensor 8 and may be output as a detected value of a large residual vibration that is erroneously recognized.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problem, and is capable of receiving an exciting force in an oblique direction deviated from the axis of the apparatus due to a roll vibration or the like generated by a power unit. It is an object of the present invention to provide an anti-vibration support device that can reduce the sensitivity of a load sensor to a vibration force and can perform anti-vibration control with high accuracy.

[0011]

According to a first aspect of the present invention, there is provided an anti-vibration support device arranged to support vibration of a power unit in a vertical direction and in a roll direction. An anti-vibration support device, in which a support elastic body and a part of a partition of a fluid chamber are formed in a cylindrical device case whose axis is oriented in the support direction of the power unit, and the volume of the fluid chamber is changed. A movable member displaceable in the supporting direction and an electromagnetic actuator capable of generating a displacement force for displacing the movable member in the supporting direction are coaxially arranged, and a yoke of the electromagnetic actuator positioned closest to the vehicle body member A load sensor is disposed adjacently and coaxially, and an opening of the device case, which opens from the load sensor to the vehicle body member, is closed with a lid member. In an anti-vibration support device in which an outer peripheral portion of a member is caulked and fixed to an opening end of the device case, an outer peripheral portion of the lid member has a large rigidity against a vibration force input in a width direction of the power unit, The structure has a small rigidity with respect to the exciting force input along the axial direction.

According to a second aspect of the present invention, in the anti-vibration support device according to the first aspect, the outer peripheral portion of the lid member is directed toward the yoke from the outer peripheral portion of the sensor fixing portion with which the load sensor contacts. An enlarged-diameter cylinder portion that rises while increasing the diameter, and an outer-circumference locking portion that extends annularly outward in the radial direction from an upper peripheral edge of the enlarged-diameter cylinder portion and is caulked and fixed to an opening end of the device case. The thickness of the portion of the enlarged diameter cylindrical portion facing the width direction of the power unit is increased, and the thickness of the portion of the enlarged diameter cylindrical portion facing the roll axis direction of the power unit is reduced.

According to a third aspect of the present invention, in the anti-vibration support device of the first aspect, the outer peripheral portion of the lid member is directed toward the yoke from the outer peripheral portion of the sensor fixing portion with which the load sensor contacts. An enlarged-diameter cylinder portion that rises while increasing the diameter, and an outer-circumference locking portion that extends annularly outward in the radial direction from an upper peripheral edge of the enlarged-diameter cylinder portion and is caulked and fixed to an opening end of the device case. In addition to increasing the thickness of the entire circumference of the enlarged diameter cylindrical portion, a long hole extending in the width direction of the power unit is formed at a portion of the enlarged diameter cylindrical portion facing the roll axis direction of the power unit. .

According to a fourth aspect of the present invention, in the anti-vibration support device of the first aspect, the outer peripheral portion of the lid member is directed toward the yoke from the outer peripheral portion of the sensor fixing portion with which the load sensor contacts. An enlarged-diameter cylinder portion that rises while increasing the diameter, and an outer-circumference locking portion that extends annularly outward in the radial direction from an upper peripheral edge of the enlarged-diameter cylinder portion and is caulked and fixed to an opening end of the device case. The thickness of the enlarged diameter cylindrical portion is increased over the entire circumference, and the portion of the outer peripheral locking portion facing the roll axis direction of the power unit is cut out.

Further, the invention according to claim 5 is the invention according to claim 1.
In the anti-vibration support device according to the above, the outer peripheral portion of the lid member,
A diameter-enlarging cylindrical portion that rises while increasing in diameter toward the yoke from the outer periphery of the sensor fixing portion with which the load sensor contacts,
An outer periphery locking portion extending annularly outward from the upper end periphery of the enlarged diameter cylindrical portion in the radial direction and being caulked and fixed to the open end of the apparatus case; In addition to increasing the thickness of the circumference, the portions of the enlarged diameter cylindrical portion and the outer peripheral locking portion facing the roll axis direction of the power unit are cut out.

[0016]

According to the vibration isolating support device of the first aspect,
When the engine is running at low speeds, such as when idling, roll fluctuations occur in the power unit due to the input of torque fluctuations in the engine, and an oblique excitation force that does not match the axial direction of the anti-vibration support device is input, adversely affecting the sensing performance of the load sensor. May be given.

However, the present invention has a structure in which the outer peripheral portion of the lid member has a large rigidity with respect to the exciting force input in the width direction of the power unit. Is hardly elastically deformed in the front-rear direction of the vehicle body, so that the sensitivity of the load sensor to the exciting force can be reduced. Further, in the present invention, the outer peripheral portion of the lid member has a structure having a small rigidity with respect to the exciting force input along the axial direction of the device, and when the exciting force is input from the power unit along the axial center, The outer peripheral portion is elastically deformed in the axial direction to reliably transmit the exciting force in the axial direction to the load sensor.
Therefore, according to the present invention, even when an oblique excitation force is input due to a roll vibration or the like generated by the power unit, the sensitivity of the load sensor to the oblique excitation force is reduced, and the vibration isolation control can be performed with high accuracy. An anti-vibration support device can be provided.

According to the vibration isolating support device of the second aspect, the portion of the enlarged diameter cylindrical portion facing the width direction of the power unit is formed thick, and the roll axis direction of the power unit of the enlarged diameter cylindrical portion is adjusted. The required rigidity of the outer peripheral portion of the lid member can be easily achieved by a simple structure in which the thickness of the facing portion is made thin.

According to the vibration isolating support device of the third aspect, the wall thickness of the entire diameter of the enlarged diameter cylindrical portion is increased, and the power unit of the power unit is located at a position facing the roll axis direction of the power unit of the enlarged diameter cylindrical portion. The required rigidity of the outer peripheral portion of the lid member can be easily achieved by the simple structure of forming the elongated hole extending in the width direction.

According to the vibration-damping support device of the fourth aspect, the wall thickness of the entire circumference of the enlarged-diameter cylindrical portion is increased, and the portion of the outer peripheral locking portion facing the roll axis direction of the power unit is cut out. With this simple structure, the required rigidity of the outer peripheral portion of the lid member can be easily achieved.

Further, according to the vibration isolating support device of the fifth aspect, the thickness of the entire circumference of the enlarged-diameter tube portion is increased, and the power-unit of the enlarged-diameter tube portion and the outer peripheral locking portion faces the roll axis direction of the power unit. The required rigidity of the outer peripheral portion of the lid member can be easily achieved by the simple structure of notching the portion where the cover member is formed.

[0022]

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) in which an anti-vibration support device according to the present invention is used to actively reduce vibration transmitted from a power unit including an engine to a vehicle body-side member as a support. It is applied to The engine mount according to the first embodiment indicated by reference numerals 20A and 20B in FIG. 1 is disposed in the vehicle longitudinal direction of an engine 22 mounted horizontally, and an upper portion thereof is provided on a bracket 24 and a lower portion thereof is provided on the vehicle body 2.
It is attached to a vehicle body member 28 fixed to 6.

These engine mounts 20A, 20B
As shown in FIG. 2, the outer cylinder 3 is provided inside the device case 43.
4. A movable part which has built-in mounting components such as an orifice constituting member 36 and a support elastic body 32 defining a main fluid chamber, and is elastically supported while forming a part of a partition of the main fluid chamber below these mounting components. This device incorporates an electromagnetic actuator 52 as an actuator for displacing a member 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 vehicle body member 28.

That is, the engine mounts 20A, 20A
B includes an engine-side connecting member 30 to which the connecting bolt 30a is fixed facing 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 cylinder 3
The supporting elastic body 32 is fixed by vulcanization bonding so as to cover the periphery of Ob.

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 formed on the inner surface. I have. A lower end portion 32b of the resilient support member 32 which is a thin shape, the axis (hereinafter, referred to as the mounting shaft) P ₁
Is connected to the inner peripheral surface of the orifice component member 36 facing the vibrating body supporting direction (in this case, the vertical direction) coaxially with the hollow cylindrical body 30b by vulcanization bonding.

The orifice constituting member 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 an annular concave portion is provided on the outer circumference. . An opening 36d is formed in the small-diameter cylindrical portion 36c. The lower end 32b of the support elastic body 32 is connected to the inner peripheral surface of the orifice constituting member 36, but this lower end 32b does not close the opening 36d, and the orifice constituting member 36 is not closed through the opening 36d. Inside and outside communicate with each other.

The orifice component 36 has an outer cylinder 3
4 is externally fitted, and the annular concave portion of the orifice constituting member 36 is surrounded by the inner peripheral surface of the outer cylinder 34, thereby defining an annular space in the circumferential direction. A diaphragm 42 is provided in the annular space.

That is, the inner diameter of the outer cylinder 34 is the same as the outer diameter of the upper cylindrical portion 36a and the lower cylindrical portion 36b of the orifice component 36, and the axial length is the same as that of the orifice component 36. Is a cylindrical member set to. The outer cylinder 34 is formed with a slit-shaped opening 34a facing the annular concave portion other than the position where the opening 36d is formed in the circumferential direction.

The diaphragm 42 is a rubber-made thin film elastic body, and is connected to the entire periphery of the opening edge of the opening 34a to close the opening 34a and bulges toward the annular recess of the orifice constituting member 36. It is arranged in the state where it did. The outer cylinder 34 is fitted inside the upper part of the device case 43.

The device case 43 has an upper end caulking portion 43a having a circular opening having a diameter smaller than the outer peripheral diameter of the upper end cylindrical portion 36a at the upper end thereof, and the shape of the case body connected to the upper end caulking portion 43a. Is a cylindrical member having the same inner diameter as the outer diameter of the outer cylinder 34 and continuous to the lower end opening (the lower end opening is indicated by a broken line in FIG. 2).

Then, the outer cylinder 34 in which the supporting elastic body 32, the orifice constituting member 36 and the diaphragm 42 are integrated is fitted into the inside of the apparatus case 43 from the lower end opening thereof, and the outer cylinder 34 is attached to the lower surface of the upper end caulking part 43a. When the upper ends of the orifice components 36 come into contact with each other, they are disposed in the upper part 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 the air chamber 42b.

Further, a leaf spring 4 integrated with a seal ring 44 and a magnetic path member 46 is provided at a lower portion in the apparatus case 43.
8, gap retaining ring 50, electromagnetic actuator 5
2. The load sensor 54 is sequentially incorporated, and after the incorporation of these components is completed, the opening of the device case 43 is closed with the lid member 57 so that the lower end of the device case 43 is directed radially inward. By tightening, a lower end caulking portion 43c is formed as shown by a solid line in FIG.

That is, the seal ring 44 is an annular member having the same outer diameter as the inner diameter of the device case 43 and an inner diameter smaller than the lower end cylindrical portion 36b of the orifice constituting member 36. The upper surface of the seal ring 44 is
It is arranged in contact with the lower end of the.

The leaf spring 48 is a disk member whose outer diameter is slightly reduced from the inner diameter of the device case 43. A magnetizable metal such as iron is provided at the lower center of the leaf spring 48. magnetic path member 46 made of is fixed to the mounting shaft P ₁ coaxially. In the present embodiment, a movable member is configured by the magnetic path member 46 and the leaf spring 48.

Then, the gap holding ring 50 is provided in a state where the peripheral edge of the upper surface of the leaf spring 48 is in contact with the lower surface of the seal ring 44. This gap retaining ring 50
In order to provide a predetermined gap between the lower surface of the magnetic path member 46 and the upper surface of the electromagnetic actuator 52, the axial length is set to the axial length from the lower surface of the leaf spring 48 to the lower surface of the magnetic path member 46. It is an annular member set to a length obtained by adding the size of the gap to.

The electromagnetic actuator 52 abutting on the lower surface of the gap retaining ring 50 is surrounded by a cylindrical yoke 52a, an exciting coil 52b coaxially embedded on the upper end side of the yoke 52a, and an exciting coil 52b. And a permanent magnet 52c having a magnetic pole fixed vertically in the upper surface range of the yoke 52a. In the center of the lower surface of the yoke 52a, a circular sensor housing recess 5 is provided.
2e is formed, and the load sensor 54 is disposed in a state where the upper part is stored in the sensor storage recess 52a.

In the load sensor 54, an upper pressure receiving plate 54a and a lower pressure receiving plate 54b are layered on the upper and lower surfaces of a ring-shaped piezoelectric element (not shown) via electrodes and insulating plates (not shown). It has a structure.

The lid member 57 that covers the load sensor 54 from below has a disc-shaped bottom lid (sensor fixing portion) 58 having a flat surface that comes into contact with the load sensor 54, and an outer peripheral edge of the bottom lid 58. It has an enlarged-diameter tube portion 59 that rises while increasing the diameter toward the yoke 52a side, and an outer-peripheral locking portion 60 that extends annularly outward from the upper peripheral edge of the enlarged-diameter tube portion 59 in the radial direction. . A plurality of press-fit holes 58a are formed on the outer peripheral side of the bottom cover 58, and the vehicle-body-side connecting bolt 56 is press-fitted into these press-fit holes 58a.

Here, as shown in FIGS. 3 and 4, the enlarged-diameter cylindrical portion 29 of the lid member 57 has a different thickness at positions toward the front, rear, right and left directions of the vehicle body. That is, the thickness of the right and left side portions 59a of the enlarged diameter cylindrical portion facing the left and right direction of the vehicle body is reduced, and
9b is formed thick.

The upper pressure receiving plate 54 of the load sensor 54
a in the sensor receiving recess 52e of the yoke 52a,
When the lid member 57 is provided below the load sensor 54 and the outer periphery locking portion 60 is swaged and fixed by forming the lower end swaging portion 43c of the device case 43 shown by a solid line in FIG.
The cover member 57 is integrated with the device case 43 while the load sensor 8 presses the load sensor 54 toward the yoke 52a and applies a predetermined preload.

By the way, the cavity 32 of the support elastic body 32
Assuming that the space surrounded by the outer peripheral surface of the orifice component member 36 and the leaf spring 48 is a main fluid chamber 66, the main fluid chamber 66
A fluid such as oil is sealed in a communication path from the space through the opening 36d to the space where the diaphragm 42 is bulged. An internal space near the diaphragm 42 is defined as a sub-fluid chamber 67, and a communication passage between the sub-fluid chamber 67 and the main fluid chamber 66 is defined as an orifice 68. When the volume of the main fluid chamber 66 fluctuates, the sub-fluid chamber 67 and the orifice 68 causes fluid resonance.

Here, the characteristics of the fluid resonance system determined by the mass of the fluid in the orifice 68 and the shape of the flow path in the extending direction of the support elastic body 32 are such that when the engine shakes during running, that is, 5 to 15 Hz. Engine mount 20A, 20
It is adjusted so as to exhibit a high dynamic spring constant and a high damping force when B is excited.

Then, each engine mount 20A, 20
The excitation coil 52b of the B electromagnetic actuator 52 is connected to the controller 71 via a harness.
As shown in the block diagram, a predetermined electromagnetic force is generated according to the drive signals y ₁ and y ₂ as the drive current supplied from the controller 71.

The controller 71 includes a microcomputer, necessary interface circuits, an A / D converter, and a D / A
It is configured to include a converter, an amplifier and the like, and is a vibration in a frequency band in which fluid cannot move between the main fluid chamber 66 and the sub-fluid chamber 67 through the orifice 68, that is, a vibration higher in frequency than the engine shake described above. When the idle vibration, the muffled sound vibration, and the vibration at the time of acceleration are input, the 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 vehicle body member 28 becomes “0”. Drive signal y so that the excitation force input to the engine mount 20 due to the vibration on the engine 22 side is offset by the control force obtained by the electromagnetic force of the electromagnetic actuator 52. ₁ and y ₂ are generated and supplied to the exciting coil 52b.

Here, the idle vibration and the muffled sound vibration are as follows.
For example, in the case of a reciprocating four-cylinder engine,
The next component of the engine vibration is the engine mount 20A, 20
The main cause is transmission to the vehicle body member 28 via B. If the drive signal y is generated and output in synchronization with the engine rotation secondary component, the vibration transmission rate can be reduced. Therefore, in the present embodiment, an impulse signal synchronized with the rotation of the crankshaft of the engine 22 (for example, in the case of a reciprocating four-cylinder engine, one for each rotation of the crankshaft by 180 degrees) is generated and used as the reference signal x. The output pulse signal generator 76 is provided, and the reference signal x
Is supplied to the controller 71 as a signal indicating the state of occurrence of vibration in the engine 22.

The load sensor 54 detects the vibration state of the vehicle body member 28 in the form of a load and outputs it as residual vibration signals e ₁ and e ₂ , and the residual vibration signals e ₁ and e ₂
Is the signal representing the vibration after the interference.
1 is supplied. Then, based on the reference signal x and the residual vibration signals e ₁ and e ₂ , the controller 71
Filter, one of the successively updated adaptive algorithms
A drive signal y is generated and output according to the red-X LMS algorithm.

Next, the engine mount 20 of the present embodiment will be described.
The effects of A and 20B will be described. When the engine 22 is started and vibrations are input to the engine mounts 20A and 20B, the controller 71 executes a predetermined calculation process and sends a drive signal y to the electromagnetic actuator 52.
₁ y ₂ is output, and an active control force capable of reducing vibration is generated in the engine mounts 20A and 20B.

That is, from the controller 71 to the electromagnetic actuator 52 of the engine mount 20A,
In the reference signal x and the residual vibration signal from the time the e ₁ is input in a predetermined sampling clock interval, the filter coefficients of the adaptive digital filter W is supplied as the drive signal y ₁ in order. As a result, although the magnetic force is generated in response to the drive signal y ₁ to the excitation coil 52b, because certain force is applied by the already permanent magnets 52c in the magnetic path member 46, magnetic forces caused by the excitation coil 52b is permanent Magnet 52
It can be considered that it acts to increase or decrease the magnetic force of c. That is, the drive signal y ₁ is supplied to the exciting coil 52b.
Is not supplied, the magnetic path member 46 is displaced to a neutral position where the elastic supporting force of the leaf spring 48 and the magnetic force of the permanent magnet 52c are balanced. When a driving signal y ₁ to the excitation coil 52b in the state of the neutral is supplied, the excitation coil 52b by the drive signal y ₁
Is generated in the direction opposite to the magnetic force of the permanent magnet 52c, the magnetic path member 46 is displaced in a direction to increase the clearance with the electromagnetic actuator 52. Conversely, the exciting coil 5
If the magnetic force generated in 2b 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 up and down by the magnetic force generated by the electromagnetic actuator 52. When the leaf spring 48 is displaced up and down, the main fluid chamber 66 is displaced.
Of the supporting elastic body 32 due to the change in volume.
Expansion spring (considering a dynamic model, the supporting elastic body 32
Are interposed in parallel. ) Is deformed, an active supporting force in both the forward and reverse directions is generated on the engine mount 20A. Then, since each filter coefficient W ₁ of the adaptive digital filter W serving as the drive signal y is sequentially updated according to the synchronized Filtered-X LMS algorithm, each filter coefficient W _i of the adaptive digital filter W is changed after a certain period of time. After the convergence to the optimum value, the drive signal y is supplied to the engine mount 20A so that idle vibration and muffled sound vibration transmitted from the engine 22 to the vehicle body member 28 via the engine mount 20A are reduced. become. The engine mount 20B also shows the same behavior.

Incidentally, the engine mounts 20A, 20A
B is disposed at a position distant from the roll inertia main shaft (the roll shaft of the power unit) in the longitudinal direction of the vehicle body of the engine 22 mounted horizontally, but the torque fluctuation of the engine 22 at the time of low engine rotation such as idling. When a power unit generates a roll vibration about the roll inertia main axis in the power unit, the roll rotational force increases the mount shaft P _1.
In the engine 22 mounted in the width direction of the power unit that does not coincide with the vehicle unit, that is, in the horizontally mounted engine 22, the engine mount 20A is used as an oblique exciting force (hereinafter, referred to as an oblique exciting force) inclined in the front-rear direction of the vehicle body. 20B.

When the oblique excitation force is input to the load sensor 54, a residual vibration signal having a value larger than the actually generated residual vibration of the vehicle body member 28 may be output. However, in the present embodiment, the thickness of the front-rear side portion 59b of the large-diameter tube portion 59 of the cover member 57 that faces the front-rear direction of the vehicle body is formed thick, and the rigidity of the large-diameter tube portion 59 in the front-rear direction of the vehicle body is increased. Since the large-diameter cylinder portion 59 is unlikely to be elastically deformed in the front-rear direction of the vehicle body even if the above-described oblique excitation force is input, the sensitivity of the load sensor 57 to the oblique excitation force can be reduced. .

Further, the thickness of the left and right side portions 59a of the lid member 57 facing the left and right direction of the vehicle body is formed thin, and
9 is set small vertical stiffness, exciting force along the mounting shaft P ₁ (hereinafter, referred to as the axial direction exciting force.)
Is input, the enlarged diameter cylindrical portion 59 is elastically deformed in the direction of the mount axis P ₁ , and the axial excitation force can be reliably transmitted to the load sensor 54.

[0054] The present embodiments are, therefore, increase the stiffness against vibration force to enter the flare tube portion 59 of the lid member 57 in the longitudinal direction of the vehicle body, and the pressurized inputs along the mounting shaft P ₁ vibration Due to the structure with low rigidity against force, even if an oblique excitation force is input due to roll vibration generated by the power unit, etc., the sensitivity of the load sensor to the oblique excitation force is degraded, and high-precision vibration control Can be provided.

Further, in this embodiment, the thickness of the right and left side portions 59a of the enlarged diameter cylindrical portion 59 which faces the left and right direction of the vehicle body is formed thin, and the thickness of the front and rear side portions 59b which face the front and rear direction of the vehicle body. The simple structure of thickening makes the load sensor 54 less sensitive to oblique excitation force and easily achieves the object of improving the sensitivity of the load sensor 54 to axial excitation force. be able to.

Next, a second embodiment of the lid member will be described with reference to FIGS. FIG. 5 shows the appearance of the lid member 80 of the present embodiment from the lateral side of the vehicle body, and FIG. 6 shows a part of a cross section of the lid member 80 along the front-rear direction of the vehicle body. It is.

The cover member 80 includes a large-diameter tube portion 84 that rises from the outer peripheral edge of the bottom cover 82 abutting on the load sensor 54 toward the yoke 52a and a large-diameter tube portion 84.
And an outer peripheral locking portion 86 extending annularly outward in the radial direction from the peripheral edge of the upper end of the outer peripheral portion 4. A plurality of press-in holes 88 are formed on the outer peripheral side of the bottom cover.
The vehicle body side connection bolt 56 is press-fitted therein.

In addition to the lid member 80, the thickness of the enlarged-diameter cylindrical portion 84 is formed to be thick over the entire circumference.
As shown in FIG. 5, a long hole 90 extending in the front-rear direction of the vehicle body is formed in a left-right side portion 84a of the large-diameter tube portion 84 facing the left-right direction of the vehicle body.

The lid member 8 is provided below the load sensor 54.
The bottom cover 82 presses the load sensor 54 toward the yoke 52a to apply a predetermined preload when the outer peripheral locking portion 86 is fixed by caulking by forming the lower caulking portion 43c of the device case 43. While the lid member 80 is in the device case 4
3 are integrated.

According to the engine mounts 20B and 20A using the cover member 80 having the above-described structure, even if the power unit generates a roll vibration and the oblique excitation force is input during low engine rotation such as idling, the cover member 80 Diameter expansion tube part 84
The front and rear side portions 84b facing the front and rear direction of the vehicle body are formed to have a large thickness, and the rigidity of the enlarged diameter cylindrical portion 84 in the front and rear direction of the vehicle body is set to be large. Since the cylindrical portion 84 is not easily elastically deformed in the front-rear direction of the vehicle body, the sensitivity of the load sensor 57 to the oblique excitation force can be reduced.

Further, a long hole 90 is formed in a left and right side portion 84a of the lid member 84 which faces the left and right direction of the vehicle body so that the diameter-enlarging cylindrical portion 8 is formed.
Since the vertical stiffness of 4 is set to be small, when an axial excitation force is input along the mount axis P ₁ , the enlarged-diameter cylindrical portion 84 is elastically deformed in the direction of the mount axis P _{1 to} cause the axial excitation. The force can be reliably transmitted to the load sensor 54.

Therefore, the lid member 80 of this embodiment is also
Increasing the stiffness against vibration force to be input in the longitudinal direction of the vehicle body, and, since the small structure rigidity against vibration force to be input along the mounting shaft P _1, such as by roll vibration generated by the power unit Even if an oblique excitation force is input, the sensitivity of the load sensor to the oblique excitation force is reduced, and an anti-vibration support device capable of performing anti-vibration control with high accuracy can be provided.

Further, in the present embodiment, the thickness of the entire circumference of the enlarged diameter cylindrical portion 84 is increased, and a long hole 90 is formed in the left and right side portion 84a of the enlarged diameter cylindrical portion 84 facing the left and right direction of the vehicle body. With this simple structure, it is possible to easily achieve the object of reducing the sensitivity of the load sensor 54 to the oblique excitation force and improving the sensitivity of the load sensor 54 to the axial excitation force.

Next, a third embodiment of the lid member will be described with reference to FIGS. FIG. 7 shows the lid member 92 of the present embodiment in a plan view, and FIG. 6 shows the lid member 92 from the lateral side of the vehicle body.

The cover member 92 includes a large-diameter tube portion 96 that rises from the outer peripheral edge of the bottom cover 94 in contact with the load sensor 54 toward the yoke 52a side, and a large-diameter tube portion 9 that rises.
6 is provided with an outer peripheral locking portion 98 extending annularly outward from the upper peripheral edge in the radial direction. A plurality of press-fit holes 100 are formed on the outer peripheral side of the bottom cover.
The vehicle body side connection bolt 56 is press-fitted in the inside of the cylinder 00.

The lid member 92 is formed by cutting out the position of the outer peripheral locking portion 98 in the left-right direction of the vehicle body, while the thickness of the enlarged-diameter cylindrical portion 96 is formed to be large over the entire circumference. A notch 98a is formed.

The lid member 9 is provided below the load sensor 54.
When the outer peripheral locking portion 98 is caulked and fixed by forming the lower caulking portion 43c of the device case 43, the bottom lid 82 presses the load sensor 54 toward the yoke 52a to apply a predetermined preload. While the lid member 80 is in the device case 4
3 are integrated.

According to the engine mounts 20B and 20A using the cover member 92 having the above-described structure, even if the power unit generates a roll vibration and the oblique excitation force is input at the time of low engine rotation such as idling, the diameter expansion cylinder The thickness of the front-rear side portion 96b of the portion 96 that faces the front-rear direction of the vehicle body is formed thick, and the rigidity of the large-diameter cylindrical portion 96 in the front-rear direction of the vehicle body is set to be large. Also, since the enlarged-diameter tube portion 96 is not easily elastically deformed in the front-rear direction of the vehicle body, the sensitivity of the load sensor 57 to the oblique excitation force can be reduced.

A notch 98a is formed at a position of the outer peripheral locking portion 98 facing the left and right direction of the vehicle body, and a portion which is not fixed by caulking at the lower caulking portion 43c of the device case 43 is provided. vertical stiffness of the section 96 is reduced, the axial excitation force is inputted along the mounting shaft P _1, the load in the axial direction exciting force flare tube portion 96 is elastically deformed to mount axis P ₁ direction The signal can be reliably transmitted to the sensor 54.

Therefore, the lid member 92 of this embodiment is also
Increasing the stiffness against vibration force to be input in the longitudinal direction of the vehicle body, and, since the small structure rigidity against vibration force to be input along the mounting shaft P _1, such as by roll vibration generated by the power unit Even if an oblique excitation force is input, the sensitivity of the load sensor to the oblique excitation force is reduced, and an anti-vibration support device capable of performing anti-vibration control with high accuracy can be provided.

Further, in this embodiment, a simple structure in which the wall thickness of the outer peripheral locking portion 98 is cut off in the left-right direction of the vehicle body by increasing the thickness of the entire circumference of the enlarged-diameter cylindrical portion 96 is obtained. The purpose of making the load sensor 54 less sensitive to the exciting force and improving the sensitivity of the load sensor 54 to the axial exciting force can be easily achieved.

Next, a fourth embodiment of the lid member will be described with reference to FIGS. FIG. 9 shows the lid member 102 of the present embodiment in a plan view, and FIG.
FIG. 10 is a view taken along line XX of FIG. 9.

The lid member 102 rises while increasing its diameter from the outer peripheral edge of the bottom lid 104 in contact with the load sensor 54 toward the yoke 52a, and has a thickened cylindrical portion 1 having a large thickness.
06, and an outer peripheral locking portion 108 extending annularly outward from the upper peripheral edge of the enlarged diameter cylindrical portion 106 in the radial direction. ,
It is formed only at the position facing the front-back direction of the vehicle body, and there is no member rising from the bottom lid 104 at the position facing the left-right direction of the vehicle body. In addition, a plurality of press-fit holes 110 are formed on the outer peripheral side of the bottom cover 104, and these press-fit holes 110
The vehicle body side connection bolt 56 is press-fitted therein.

According to the engine mounts 20B and 20A using the lid member 102 having the above-described structure, even if the power unit generates a roll vibration and the oblique excitation force is input when the engine is running at a low speed such as idling, the front and rear of the vehicle body can be prevented. The thickness of the enlarged diameter cylindrical portion 106 facing in the direction is formed thick so that the rigidity of the vehicle body in the front-rear direction is set to be large. Since it is difficult to deform elastically, the sensitivity of the load sensor 57 to the oblique excitation force can be reduced.

[0075] Further, since the enlarged diameter cylindrical portion 106 and the outer locking portion 108 at a position facing the lateral direction of the vehicle body is not present becomes small vertical rigidity, axially along the mounting shaft P ₁ When the excitation force is input, the mounting axis P ₁
By elastically deforming in the direction, the axial excitation force can be reliably transmitted to the load sensor 54.

Therefore, the lid member 102 of the present embodiment is
In addition, even if an oblique excitation force is input due to roll vibration or the like generated by the power unit, the sensitivity of the load sensor to the oblique excitation force is reduced, and the anti-vibration support device that can perform the anti-vibration control with high accuracy Can be provided.

Further, in the present embodiment, the enlarged diameter cylindrical portion 106 having a large thickness, and the outer peripheral locking portion 108 extending annularly outward in the radial direction from the upper peripheral edge of the enlarged diameter cylindrical portion 106 are provided. Is formed only at a position facing the front-rear direction of the vehicle body, so that the sensitivity of the load sensor 54 is degraded with respect to the oblique excitation force, and the sensitivity of the load sensor 54 with respect to the axial excitation force is improved. The purpose can be easily achieved.

In each of the above-described embodiments, the engine 2 having the anti-vibration support device according to the present invention mounted horizontally is described.
2 has been described, but it goes without saying that the present invention can be applied to an engine mounted vertically. In this case, since the roll inertia main shaft is in the front-rear direction of the vehicle body, the anti-vibration support devices are disposed on the left and right sides of the vehicle body of the engine, and the enlarged diameter cylinder portions 59, 84, 96, and 106 of each embodiment have rigidity in the vehicle left-right direction. It is formed so as to have high rigidity in the vehicle longitudinal direction.

[Brief description of the drawings]

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

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

FIG. 3 is a plan view showing a lid member according to the first embodiment of the present invention.

FIG. 4 is a view taken along the line IV-IV in FIG. 3;

FIG. 5 is a view showing a lid member according to a second embodiment of the present invention as viewed from a lateral side in a vehicle body left-right direction.

FIG. 6 is a diagram illustrating a cross section of a lid member according to a fourth embodiment in a vehicle longitudinal direction.

FIG. 7 is a plan view showing a lid member according to a third embodiment of the present invention.

FIG. 8 is a diagram illustrating a lid member according to a third embodiment as viewed from a side surface in a lateral direction of a vehicle body.

FIG. 9 is a plan view showing a lid member according to a fourth embodiment of the present invention.

FIG. 10 is a view taken along line XX of FIG. 9;

FIG. 11 is a view showing the structure of a conventional vibration-proof support device.

[Explanation of symbols]

 20A, 20B Anti-vibration support device 22 Engine 28 Body member 32 Support elastic body 43 Device case 43c Lower end caulking portion 46 Magnetic path member (movable member) 48 Leaf spring (movable member) 52 Electromagnetic actuator 52a Yoke 54 Load sensor 57, 80, 92, 102 Lid member 59, 84, 96, 106 Large-diameter cylindrical part 60, 86, 98, 108 Outer periphery locking part 90 Slot 98a Notch

Claims (5)

[Claims] 1. A cylindrical device case arranged so as to support vibrations of a power unit in the vertical and roll directions and supporting the power unit on a vehicle body member in a vibration-proof manner, wherein an axis of the power unit is oriented in a supporting direction of the power unit. Within
A supporting elastic body, a movable member that forms a part of a partition of the fluid chamber and is displaceable in a direction that changes the volume of the fluid chamber;
An electromagnetic actuator capable of generating a displacement force for displacing the movable member in the support direction is coaxially arranged, and a load sensor is coaxially arranged adjacent to a yoke of the electromagnetic actuator which is located closest to the vehicle body member. An anti-vibration device which is arranged and closed by an opening of the device case, which is opened from the load sensor to the vehicle body member, with a lid member, and an outer peripheral portion of the lid member is caulked and fixed to an opening end of the device case. In the supporting device, the outer peripheral portion of the lid member has a structure in which rigidity is large with respect to a vibration force input in a width direction of the power unit and small in rigidity with respect to a vibration force input along the axial direction. An anti-vibration support device, characterized in that: 2. An enlarged-diameter tube portion which rises while increasing an outer peripheral portion of the lid member from an outer periphery of a sensor fixing portion with which the load sensor contacts, toward the yoke side, and an upper peripheral edge of the enlarged-diameter tube portion. And an outer peripheral locking portion fixed to the opening end of the device case by caulking and extending outward in the radial direction, and a portion of the enlarged diameter cylindrical portion facing the width direction of the power unit. 2. The vibration isolating support device according to claim 1, wherein the thickness of the portion of the power unit of the enlarged diameter cylindrical portion facing the roll axis direction is reduced. 3. An enlarged-diameter cylindrical portion which rises while increasing the outer peripheral portion of the lid member from the outer periphery of the sensor fixing portion with which the load sensor contacts, toward the yoke side, and an upper peripheral edge of the enlarged-diameter cylindrical portion. And an outer peripheral locking portion that extends radially outward from the outer case and is caulked and fixed to the opening end of the device case, and increases the thickness of the entire circumference of the enlarged diameter cylindrical portion. 2. The anti-vibration support device according to claim 1, wherein an elongated hole extending in a width direction of the power unit is formed at a portion of the enlarged diameter cylindrical portion facing the roll axis direction of the power unit. 4. An enlarged-diameter cylindrical portion which rises while increasing the outer peripheral portion of the lid member from the outer periphery of the sensor fixing portion with which the load sensor contacts to the yoke side, and an upper peripheral edge of the enlarged-diameter cylindrical portion. And an outer peripheral locking portion that extends radially outward from the outer case and is caulked and fixed to the opening end of the device case, and increases the thickness of the entire circumference of the enlarged diameter cylindrical portion. 2. A power supply unit according to claim 1, wherein a portion of the outer peripheral locking portion facing the roll axis direction of the power unit is cut out.
The anti-vibration support device according to the above. 5. An enlarged-diameter cylindrical portion which rises while increasing the outer peripheral portion of the lid member from the outer periphery of the sensor fixing portion with which the load sensor contacts to the yoke side, and an upper peripheral edge of the enlarged-diameter cylindrical portion. And an outer peripheral locking portion that extends radially outward from the outer case and is caulked and fixed to the opening end of the device case, and increases the thickness of the entire circumference of the enlarged diameter cylindrical portion. 2. An anti-vibration support device according to claim 1, wherein a portion of the power-supply unit of the large-diameter tube portion and the outer peripheral locking portion that faces the roll axis direction is cut out.