JP2001001764A - Active vibration isolating support system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent tilting of an armature caused by unbalanced load applied by a movable member of an active vibration isolating support system without employing a bearing. SOLUTION: An active vibration control support system M to prevent transmission of vibration from an engine E to a body frame F has an electromagnetic actuator 29 to change capacity of a liquid chamber 24 by reciprocating a movable member 20. A shaft 381 of an armature 38 actuated by a coil 34 can move freely along an axis L, and is supported by a pair of upper and lower elastic bodies 44, 47 composed of disk-like carrier plates 51, 52 to suppress vibration in the direction perpendicular to the axis L. Since the elastic bodies 44, 47 are disposed far apart from each other in the axis L direction, a tilt of the shaft 381 of the armature 38 can be minimized even if each of the elastic bodies is displaced to some extent in the directions perpendicular to the axis L.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an elastic body receiving a load of a vibrating body, a liquid chamber in which the elastic body forms at least a part of a wall, a movable member for changing the volume of the liquid chamber, and a movable member. The present invention relates to an active vibration isolating support device including an actuator for driving a connected armature by an electromagnetic force generated by a coil.

[0002]

2. Description of the Related Art Such an active vibration isolating support device is disclosed in
It is known from JP-A-1101071.

In this active vibration isolating support device, a movable member for changing the volume of the liquid chamber is constituted by a disc-shaped leaf spring having an outer peripheral portion fixed to a case, and is driven by a coil of an actuator. The armature has no special bearing and is directly fixed and supported on the lower surface of the central part of the movable member. Then, the armature is attracted by the excitation of the coil, and the movable member integrated with the armature is reciprocated in the direction along the axis.

[0004]

In the above-mentioned conventional active vibration damping support device, when the movable member for changing the volume of the liquid chamber is deviated from the axis by an uneven load received from the liquid in the liquid chamber, the armature is supported by the bearing. , The armature integral with the movable member also tilts with respect to the axis. Therefore, it is necessary to set a large air gap so as not to contact the yoke even when the armature is tilted, and as a result, the characteristics of the magnetic circuit deteriorate. To solve this problem, the size of the coil may be increased to increase the magnetic force that can be generated, but this will increase the power consumption of the coil.

Therefore, it is conceivable to slidably support the armature with a bearing so that the armature does not incline. However, in this case, the bearing is twisted due to an unbalanced load transmitted from the movable member to the armature. There is a problem that the life is shortened.

The present invention has been made in view of the above circumstances, and has as its object to prevent the inclination of an armature due to an eccentric load input from a movable member without using a bearing in an active vibration isolator. .

[0007]

According to the first aspect of the present invention, there is provided an elastic body receiving a load of a vibrating body, and the elastic body forms at least a part of a wall surface. A liquid chamber, a movable member that changes the volume of the liquid chamber, and an active vibration isolation support device including an actuator that drives an armature connected to the movable member along an axis with an electromagnetic force generated by a coil. There is proposed an active vibration damping support device characterized in that the armature is supported by a first elastic support member and a second elastic support member which are arranged apart from each other in the axial direction.

According to the above construction, since the armature is supported by the first elastic support member and the second elastic support member, the armature can be moved in the axial direction by the deformation of the two elastic support members without using a weak bearing against twisting. It can be tolerated, and since the two elastic support members are spaced apart in the axial direction, the inclination of the armature can be minimized. Further, it is possible to apply a set load in the axial direction to the armature using the first elastic support member and the second elastic support member.

According to the invention described in claim 2,
In addition to the configuration of claim 1, the first elastic support member and the second elastic support member
An active vibration-damping support device, wherein the elastic support member is constituted by a plate-like member extending in a direction substantially perpendicular to the axis, and allows movement of the armature in the axis direction and restricts movement in the direction perpendicular to the axis. Is proposed.

According to the above construction, since the first elastic support member and the second elastic support member are formed of the plate-like members extending in a direction substantially perpendicular to the axis, the two elastic support members can be easily deformed in the axial direction. As a result, the armature can be freely moved in the axial direction, and it is difficult for the two elastic support members to deform in the direction orthogonal to the axis, so that the inclination of the armature can be suppressed more effectively.

According to the third aspect of the present invention,
In addition to the configuration of claim 2, the first elastic support member and the second elastic support member
Each of the elastic support members is composed of a pair of disc-shaped leaf springs whose center part is fixed to the armature at a different position and whose outer peripheral part is fixed to the support part at the same position, and the armature is driven in one direction. Wherein one of the leaf springs is deformed into a posture orthogonal to the axis when the armature is driven, and the other leaf spring is deformed into a posture perpendicular to the axis when the armature is driven in the other direction. A support device is proposed.

According to the above construction, each elastic support member is constituted by a pair of disc-shaped leaf springs whose center is fixed to the armature at different positions and whose outer periphery is fixed to the support at the same position. Even if the armature is driven in any direction along the axis, one of the leaf springs is deformed to a posture orthogonal to the axis, and the rigidity against the inclination of the armature can be increased.

The engine E of the embodiment corresponds to the vibrating body of the present invention, the first elastic body 14 of the embodiment corresponds to the elastic body of the present invention, and the first liquid chamber 24 of the embodiment corresponds to the vibrating body of the present invention. The yoke 32 and the bottom plate 35 of the embodiment correspond to the liquid chamber, the upper elastic body 44 of the embodiment corresponds to the first elastic support member of the invention, and the lower elastic body of the embodiment. 47 corresponds to the second elastic support member of the present invention, and the first and second leaf springs 51 and 52 of the embodiment correspond to the leaf spring of the present invention.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

FIGS. 1 to 5 show a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view of an active vibration isolating support device, FIG. 2 is a sectional view taken along line 2-2 of FIG. FIG. 4 is a sectional view taken along line 3-3 of FIG. 1, FIG. 4 is a sectional view taken along line 4-4 of FIG. 1, and FIG.

Active anti-vibration support device M shown in FIGS. 1 to 5
Is for elastically supporting the engine E of the automobile on the body frame F, and detects an engine speed sensor S ₁ for detecting the engine speed and a load inputted to the active vibration isolator M. a load sensor S ₂ for an acceleration sensor S ₃ for detecting the acceleration acting on the engine E is controlled by the connected electronic control unit U.

The active vibration isolator M has a structure substantially symmetrical with respect to the axis L. The inner cylinder 12 is welded to a plate-like mounting bracket 11 connected to the engine E.
And an outer cylinder 13 coaxially arranged on the outer periphery of the inner cylinder 12. The upper and lower ends of a first elastic body 14 formed of thick rubber are provided on the inner cylinder 12 and the outer cylinder 13, respectively. Are bonded by vulcanization adhesion. A first orifice forming member 15 disc-shaped having an opening 15 ₂ in the center, a second orifice-forming member 16 which is formed in an annular shape having a top surface and a gutter-shaped cross section opening, also has an upper surface opened gutter A third orifice forming member 17 having an annular cross section and formed in an annular shape is integrated by welding, and the outer peripheral portions of the first orifice forming member 15 and the second orifice forming member 16 are overlapped with each other to form the outer portion. It is fixed to the caulking portion 13 ₁ which is provided in the lower portion of the tube 13.

The outer periphery of a second elastic body 18 formed of a film-like rubber is fixed to the inner periphery of the third orifice forming member 17 by vulcanization bonding. It is fixed by vulcanization bonding to a movable member 20 which is disposed so as to be able to move up and down. The outer periphery of the outer tube 13 of the caulking portion 13 diaphragm 22 to the ring member 21 fixed to ₁ is fixed by vulcanization adhesion, the inner periphery of the diaphragm 22 is fixed by vulcanization adhesion to the movable member 20 .

Thus, a first liquid chamber 24 filled with liquid is defined between the first elastic body 14 and the second elastic body 18, and a first liquid chamber 24 filled with liquid between the second elastic body 18 and the diaphragm 22 is formed. A two-liquid chamber 25 is defined. The first liquid chamber 24 and the second liquid chamber 25 are provided with the first to third orifice forming members 1.
The upper orifice 26 and the lower orifice 27 formed by 5, 16, 17 communicate with each other.

The upper orifice 26 forms a first orifice.
Formed between the member 15 and the second orifice forming member 16
Is a ring-shaped passage which is provided in a part thereof.
6₁On one side communicates with the first orifice forming member 15
Hole 15₁Is formed, and the partition 26 is formed.₁On the other side of
2 orifice forming member 16 with communication hole 16₁Is formed
You. Therefore, the upper orifice 26 has the first orifice shape.
Communication hole 15 of component member 15 ₁To the second orifice forming member
16 communication holes 16₁Formed over a range of approximately one round up to
(See FIG. 2).

The lower orifice 27 is an annular passage formed between the second orifice forming member 16 and the third orifice forming member 17, and a partition wall 2 provided in a part thereof is provided.
In one side of ₇₁ the communication hole 16 ₁ in the second orifice-forming member 16 is formed, the communication hole 17 ₁ is formed in the third orifice-forming member 17 at the other side of the partition wall 27 _1. Accordingly, the lower orifice 27 is formed over substantially one round in the range of the communication hole 16 ₁ of the second orifice-forming member 16 to the communicating hole 17 ₁ of the third orifice-forming member 17 (see FIG. 3).

From the above, the first liquid chamber 24 and the second liquid chamber 24
The liquid chamber 25 communicates with each other by an upper orifice 26 and a lower orifice 27 connected in series.

[0023] caulked portion 13 ₁ of the outer cylinder 13, an annular mounting bracket 28 for fixing the active vibration isolation support system M to the vehicle body frame F is fixed, the a lower surface of the mounting bracket 28 An actuator support member 30 for supporting an actuator 29 for driving the movable member 20 is welded. A yoke 32 is fixed to the actuator support member 30, and a coil 34 wound around a bobbin 33 is housed in a space formed inside the yoke 32. A columnar shaft 3 extending upward from the center of a disk-shaped armature 38 facing the lower surface of the coil 34
8 ₁ loosely fits into the through hole 32 ₁ passing through the center of the yoke 32.

The shaft portion 38 projecting upward from the through hole 32 ₁
The vicinity of the upper end of ₁ and a bracket 43 fixed to the upper surface of the yoke 32 are connected by a disk-shaped upper elastic body 44. Also the vicinity of the lower end of the shaft portion 38 _1, a bracket 46 fixed to the bottom plate 35 which closes the lower surface of the yoke 32 are connected by a disc-shaped lower elastic member 47. Therefore, armature 38
Shaft portion 38 ₁ of the floating support by the upper elastic member 44 and the lower elastic member 47.

The upper elastic body 44 has a disc-shaped first leaf spring 51.
The first and second leaf springs 52 are provided to reduce the spring constant in the direction of the axis L.
Eight lightenings 51 ₁ arranged in the circumferential direction are provided in 1, 52
, 52 ₁ ... are formed. First leaf spring 51 and second leaf spring 51
With the center of the leaf spring 52 is fixed at a distance from each other in the shaft portion 38 ₁ of the armature 38 in the axis L direction by a distance d,
The outer periphery of the bracket 43 is
With this, it is fixed to the upper surface of the yoke 32. As shown in FIG. 5B, when the armature 38 is in the neutral position, the upper first leaf spring 51 is inclined downward in the radially outward direction,
The lower second leaf spring 52 has a radially outer side inclined upward.

[0026] While the lower elastic member 47 are substantially the same structure as the upper elastic member 44 is disposed upside down, the center shaft portion 38 ₁ of the armature 38 in the axis L direction distance d The outer peripheral portions are fixed to the upper surface of the bottom plate 35 by the bracket 46 in a state where the outer peripheral portions are overlapped with each other.

The armature 38 is urged upward by a coil spring 41 disposed between the armature 38 and the bottom plate 35 so that the shaft 38
Spherical portion 38 ₂ formed on the upper end of the ₁ abuts to resiliently on the lower surface of the movable member 20. That is, the shaft 3 of the armature 38
8 ₁ and the movable member 20 are in point contact with each other at the contact portion P, and the swing and sliding of the movable member 20 with respect to the armature 38 are allowed. Coil 34 of actuator 29
Shaft part 38 ₁ of armature 38 when is in a demagnetized state
The elastic force of the coil spring 41 acts upward, the pressure of the liquid and the elastic force of the second elastic body 18 act downward, and the upper elastic body 44 and the lower elastic body 47
Are acting in the vertical direction, and stop at a neutral position where those loads are balanced.

A conical stopper is provided at the bottom opening of the yoke 32.
Face 32_TwoAre formed, and the arc is
A conical stopper surface 38 on the outer periphery of the mature 38_ThreeFormed
Is done. And the stopper surface 32 of the yoke 32_TwoAnd armor
Stopper surface 38 of the tuner 38 _ThreeAir gap β between
Is formed.

When low-frequency engine shake vibration occurs while the automobile is running, the load input from the engine E deforms the first elastic body 14 and changes the volume of the first liquid chamber 24. , A first liquid chamber 24 and a second liquid chamber 24 connected via an upper orifice 26 and a lower orifice 27.
Liquid flows between the liquid chambers 25. As the volume of the first liquid chamber 24 increases or decreases, the volume of the second liquid chamber 25 decreases or expands accordingly. However, the change in the volume of the second liquid chamber 25 is absorbed by the elastic deformation of the diaphragm 22. At this time,
The shapes and dimensions of the upper orifice 26 and the lower orifice 27 and the spring constant of the first elastic body 14 are set so as to exhibit a high spring constant and a high damping force in the frequency range of the engine shake vibration. Vibration transmitted to the body frame F can be effectively reduced.

In the frequency range of the engine shake vibration, the actuator 29 is kept in a non-operating state.

When vibration having a frequency higher than that of the engine shake vibration, that is, idle vibration or muffled vibration caused by rotation of the crankshaft of the engine E occurs,
Since the liquid in the upper orifice 26 and the lower orifice 27 connecting the first liquid chamber 24 and the second liquid chamber 25 becomes a stick state and cannot exhibit the vibration-proof function, the actuator 29 is driven to exhibit the vibration-proof function. Let it.

The electronic control unit U controls energization of the coil 34 of the actuator 29 based on signals from the engine speed sensor S ₁ , load sensor S ₂ and acceleration sensor S ₃ . Specifically, when the engine E is deflected upward due to vibration and the volume of the first liquid chamber 24 increases and the hydraulic pressure decreases, the coil 34 is excited to attract the armature 38. As a result, the armature 38 presses the movable member 20 in the axial portion 38 ₁ of the upper end of the spherical portion 38 ₂ moves upward, to deform the second elastic body 18 connected to the inner periphery to the movable member 20 upward . Thereby, the first liquid chamber 2
In order to suppress a decrease in the fluid pressure due to a decrease in the volume of 4, the active vibration isolation support device M generates an active support force for preventing an upward load transmission from the engine E to the vehicle body frame F.

Conversely, when the engine E is deviated downward due to vibration and the volume of the first liquid chamber 24 decreases and the hydraulic pressure increases, the coil 34 is demagnetized and the suction of the armature 38 is released. As a result, the movable member 2 that moves downward by hydraulic pressure
The armature 38 pressed to 0 moves downward against the resilience of the coil spring 41, and the second elastic body 18 having an inner periphery connected to the movable member 20 deforms downward. This allows
Since the volume of the first liquid chamber 24 increases to suppress the increase in the hydraulic pressure, the active vibration isolation support device M generates an active supporting force for preventing downward load transmission from the engine E to the body frame F. I do.

The armature 38, which reciprocates up and down during the operation of the actuator 29, has a shaft 38
The upper and lower ends of ₁ are supported by an upper elastic body 44 and a lower elastic body 47, respectively. Further, the two elastic bodies 44 and 47, which are disc-shaped, can be easily deformed in the direction of the axis L while being deformed in the radial direction. since it is difficult to, the shaft portion 38 ₁ of the armature 38 can be easily moved up and down is held in the correct position along the axis L. When the movable member 20 reciprocates vertically, the second elastic body 18 and the diaphragm 22
1 is tilted in the direction of the arrow in FIG. 1 under a lateral bias load from the liquid, the movable member 20 and the shaft 38 _{1 of the} armature 38
Are in point contact with each other at the contact portion P so as to be relatively displaceable, the movable member 20 can freely swing without affecting the armature 38, and the bias transmitted from the movable member 20 to the armature 38 can be adjusted. Load can be minimized.

In particular, the upper elastic body 44 that supports the vicinity of the upper end of the armature 38 and the lower elastic body 47 that supports the vicinity of the lower end of the armature 38 are disposed far apart in the direction of the axis L. , 47 also displaced slightly in a direction perpendicular to the axis L, whereby the inclination of the shaft portion 38 ₁ of the armature 38 generated is minimized. Thereby, the air gap β between the yoke 32 and the armature 38 can be reduced, and the size of the coil 34 can be reduced to reduce power consumption.
Thus, it is possible to drive the armature 38 in a correct posture along the axis L without using a bearing whose durability is likely to be reduced by an eccentric load input from the movable member 20.

The upper elastic body 44 and the lower elastic body 47 are
Although the structure is originally hardly deformed by a load in the direction perpendicular to the axis L, the features of the present embodiment are further enhanced.
Hereinafter, this will be described using the upper elastic body 44 as an example.

[0037] Figure 5 upper elastic member 44 by a shaft portion 38 ₁ of the upward movement of the armature 38 from the neutral state of FIG. 5 (b)
When deformed to the state shown in FIG.
The leaf spring 52 assumes a posture perpendicular to the axis L, and the rigidity against a load in a direction perpendicular to the axis L increases. Upper elastic member 44 in the reverse by the shaft portion 38 ₁ of the downward movement of the armature 38
5B is deformed from the neutral state of FIG. 5B to the state of FIG. 5C, the first leaf spring 51 which has been inclined up to that point becomes a posture orthogonal to the axis L, and the load in the direction orthogonal to the axis L is changed. The rigidity with respect to increases. Thereby, the actuator 29
Of the armature 38 throughout the entire range of operation of the armature 38 ₁
Can be correctly held on the axis L.

The upper elastic body 44 and the lower elastic body 4
7 it is possible to provide a set load of the axis L direction to the shaft portion 38 ₁ of the armature 38 by, abolished the coil spring 41, it is also possible to cover the feature in the upper elastic member 44 and the lower elastic member 47 .

Next, a second embodiment of the present invention will be described with reference to FIGS. The second embodiment is different from the first embodiment in the structure of the upper elastic body 44 and the lower elastic body 47, and the other structures are the same as the first embodiment.

[0040] is composed of a both disk-shaped rubber upper elastic member 44 and the lower elastic member 47 of the second embodiment, a bracket fixed from the through hole 32 ₁ of the yoke 32 to the shaft portion 38 ₁ projecting upward 42, a bracket 43 fixed to the upper surface of the yoke 32 are connected by upper elastic member 44 and the shaft portion 38 fixed the bracket 45 to the _first lower end, a bracket 4 fixed to the bottom plate 35 which closes the lower surface of the yoke 32
6 are connected by a lower elastic body 47. Thus, the shaft portion 38 ₁ of the armature 38 is floatingly supported by the upper elastic member 44 and the lower elastic member 47.

The upper elastic body 44 and the lower elastic body 47 made of the disc-shaped rubber of the second embodiment are easily deformable in the direction of the axis L and difficult to deform in the radial direction. It is possible to obtain the same operation and effect as those of the first embodiment.

Although the embodiments of the present invention have been described in detail, various design changes can be made in the present invention without departing from the gist thereof.

For example, in the embodiment, the active vibration damping support device M for supporting the engine E of the automobile has been exemplified. However, the active vibration damping support device of the present invention is applied to support other vibrators such as machine tools. be able to. If it is not necessary to reduce the vibration in the engine shake area by the active vibration isolator M, the second liquid chamber 25, the upper orifice 26, the lower orifice 27, and the diaphragm 22 can be omitted.

[0044]

As described above, according to the first aspect of the present invention, since the armature is supported by the first elastic support member and the second elastic support member, the two elastic members can be used without using a bearing which is weak against twisting. The movement of the armature in the axial direction can be allowed by the deformation of the support member, and furthermore, by arranging the two elastic support members apart from each other in the axial direction, the inclination of the armature can be minimized. Further, it is possible to apply a set load in the axial direction to the armature using the first elastic support member and the second elastic support member.

According to the second aspect of the present invention,
Since the first elastic support member and the second elastic support member are constituted by plate-like members extending in a direction substantially perpendicular to the axis, the two elastic support members are easily deformed in the axial direction, and the armature can freely move in the axial direction. In addition, both elastic support members are difficult to deform in the direction perpendicular to the axis, and the inclination of the armature can be more effectively suppressed.

According to the third aspect of the present invention,
Since each elastic support member is constituted by a pair of disc-shaped leaf springs whose center part is fixed to the armature at a different position and whose outer peripheral part is fixed to the support part at the same position, the armature moves in any direction along the axis. Even when driven, one of the leaf springs is deformed to a posture orthogonal to the axis, and the rigidity against the inclination of the armature can be increased.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of an active vibration isolation support device.

FIG. 2 is a sectional view taken along line 2-2 of FIG.

FIG. 3 is a sectional view taken along line 3-3 in FIG. 1;

FIG. 4 is a sectional view taken along line 4-4 of FIG. 1;

FIG. 5 is an explanatory view of an operation.

FIG. 6 is a longitudinal sectional view of a main part of an active vibration isolation support device according to a second embodiment of the present invention.

FIG. 7 is a sectional view taken along line 7-7 of FIG. 6;

[Explanation of symbols]

 E engine (vibrating body) L axis 14 first elastic body (elastic body) 20 movable member 24 first liquid chamber (liquid chamber) 29 actuator 32 yoke (supporting part) 34 coil 35 bottom plate (supporting part) 38 armature 44 upper elasticity Body (first elastic support member) 47 Lower elastic body (second elastic support member) 51 First leaf spring (leaf spring) 52 Second leaf spring (leaf spring)

Continued on the front page (72) Inventor Ken Iinuma 1-4-1 Chuo, Wako-shi, Saitama Pref. Inside of Honda R & D Co., Ltd. (72) Inventor Ken Watanabe 1-4-1 Chuo, Wako-shi, Saitama Co., Ltd. F-term in Honda R & D Co., Ltd. (reference) 3D035 CA01 CA05 CA32 3J047 AA03 CA02 CB10 CD20 FA02

Claims (3)

[Claims] An elastic body (1) receiving a load of a vibrating body (E)
4), a liquid chamber (24) in which the elastic body (14) forms at least a part of a wall surface, a movable member (20) for changing the volume of the liquid chamber (24), and a movable member (20). An actuator (29) for driving the armature (38) along the axis (L) by an electromagnetic force generated by the coil (34), wherein the armature (38) is separated in the direction of the axis (L). An active vibration isolator and support device, wherein the armature (38) is supported by the first elastic support member (44) and the second elastic support member (47) arranged as follows. 2. The first elastic support member (44) and the second elastic support member (47) are composed of plate-like members extending in a direction substantially perpendicular to the axis (L), and the axis (L) of the armature (38). 2. A movement in a direction perpendicular to the axis (L) and a movement in a direction perpendicular to the axis (L) are restricted.
4. The active vibration isolation support device according to claim 1. 3. The first elastic support member (44) and the second elastic support member (47) are fixed to the armature (38) at different central portions, and have the outer peripheral portion at the same position. , 35) and a pair of disc-shaped leaf springs (51, 52) fixed to the armature (3, 35).
8) When one of the leaf springs (51) is driven in one direction,
Is deformed to a posture orthogonal to the axis (L), and when the armature (38) is driven in the other direction, the other leaf spring (5)
3. The active vibration isolator according to claim 2, wherein 2) is deformed to a posture orthogonal to the axis L. 4.