JP2001041278A - Active type vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently increase a control force to eliminate vibration transmitted to a vibration receiving part and to suppress the manufacturing cost of a device. SOLUTION: In an active damper 10 fixed at a vehicle body 12, when the internal part of a gas-sealed chamber 52 is converted from an atmospheric pressure to a negative pressure, a drive partition wall 44 is displaced downward and a liquid pressure in a pressure receiving liquid chamber 48 is decreased. This constitution bends downward an elastic body 28 for deformation and a mass body 38 coupled to the elastic body 28 is displaced downward. When the internal part of the gas-sealed chamber 52 is brought into an atmospheric pressure, the drive partition wall 44 is displaced upward through the restoration force of an elastic ring 46 and a liquid pressure in the pressure receiving liquid chamber 48 is increased. This constitution bends upward the elastic body 28 for deformation and displaces upward the mass body 38 securely fixed at the elastic body 28.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to, for example, automobiles,
The present invention relates to an active vibration absorber applied to general industrial machines and the like, which actively cancels vibration transmitted from a vibration generator such as an engine to a vibration receiver such as a frame.

[0002]

2. Description of the Related Art In a motor vehicle, an anti-vibration device is arranged between an engine and a vehicle body as an engine mount. Such an anti-vibration device has a structure in which a pressure-receiving liquid chamber that expands and contracts due to the internal resistance of the rubber-like elastic body and the deformation of the rubber-like elastic body and a sub-liquid chamber that is connected to the pressure-receiving liquid chamber through a restriction passage (orifice). Vibration energy is absorbed by the liquid column resonance generated between them, and the vibration from the engine is attenuated to suppress the vibration transmitted to the vehicle body. However, in such a vibration isolator, although the vibration from the engine can be attenuated at a constant damping rate, theoretically, the vibration transmitted from the engine to the vehicle body cannot be completely eliminated.

Therefore, application of an active damper, which is an active vibration absorber capable of completely canceling the vibration transmitted from the vibration generator to the vibration receiver in theory, to an automobile has been studied. As an active damper, for example, there is a type in which a mass body (mass) having a mass corresponding to the vibrating body is elastically supported by a coil spring or the like, and the mass body is vibrated by an electromagnetic actuator using an electromagnet.
The active damper is fixed to the vibration receiving portion, and the actuator is driven in accordance with the frequency of vibration transmitted to the vibration receiving portion, and the mass is vibrated by the actuator, so that the reaction force (control force) ) Can actively cancel the vibration transmitted to the vibration receiving portion.

[0004]

However, in the above-described active damper, an expensive electromagnetic actuator is used to vibrate the mass body.
At the time of assembly, it is necessary to assemble the mover and electromagnet made of a ferromagnetic material that compose the electromagnetic actuator. As a result, the manufacturing cost of the active damper increases, and it can be applied to automobiles that require low cost. Had become difficult.

In an active damper using an electromagnetic actuator, in order to increase the control force for canceling the vibration transmitted to the vibration receiving portion, the driving force generated by the electromagnetic actuator must be increased. The current consumed by the actuator increases. Therefore, when an active damper using an electromagnetic actuator is applied to a car, the control capacity of the active damper cannot be sufficiently increased because the battery capacity of the car is limited, and the vibration transmitted to the vehicle body is effectively reduced. There is a possibility that it cannot be canceled.

An object of the present invention is to provide a low-cost active vibration absorber capable of sufficiently increasing a control force for canceling vibration transmitted to a vibration receiving portion in consideration of the above fact.

[0007]

According to a first aspect of the present invention, there is provided an active vibration absorbing device, comprising: a mounting member connected to a vibration receiving portion; a mass having a mass corresponding to a vibration absorbing region in the vibration receiving portion; A pressure-receiving liquid chamber provided between the mounting member and the support member, the liquid being sealed therein, and the pressure-receiving liquid chamber connected to the mounting member and the support member, respectively. An elastic body that constitutes a part of the partition wall and has a pressure receiving displacement portion that is displaced along the amplitude direction of the vibration of the vibration receiving portion with a change in the liquid pressure in the pressure receiving liquid chamber, and is adjacent to the pressure receiving liquid chamber; And the pressure-receiving area of the pressure-receiving liquid chamber is made larger than the pressure-receiving area of the pressure-receiving displacement section, and the gas-filling is performed. The pressure receiving liquid A drive partition wall displaced in the direction of volume expansion and contraction, and pressure supply means for alternately communicating the gas-filled chamber with either a negative or positive pressure supply source or an external space with respect to the external space. Things.

According to the active vibration absorber of the above construction, the pressure supply means alternately connects the gas-filled chamber to either the external space or the pressure supply source which is set to the negative or positive pressure with respect to the external space. Thereby, when the gas filling chamber is communicated with the pressure supply source, the pressure in the gas filling chamber becomes a positive pressure or a negative pressure with respect to the pressure in the external space (external pressure), and the gas filling chamber is connected to the external space. At times, the pressure in the gas chamber becomes equal to the external pressure. At this time, when the gas filled chamber becomes negative pressure, the drive partition wall is displaced in the direction of volume expansion of the pressure receiving liquid chamber,
When the pressure of the gas filling chamber becomes positive, the driving partition wall is displaced in the direction of reducing the volume. Thereafter, when the pressure of the gas filling chamber becomes equal to the external pressure, the driving partition wall is displaced in a direction opposite to that at the time of negative pressure or positive pressure due to its elastic restoring force.

Therefore, if the communication destination of the gas filling chamber is alternately switched between the pressure supply source and the external space at a cycle corresponding to the vibration transmitted to the vibration receiving portion, the liquid filled in the pressure receiving liquid chamber will not be cycled. Hydraulic pressure change occurs. Due to the periodic liquid pressure change, the pressure receiving displacement portion of the elastic body is displaced along the vibration amplitude direction, and vibrates the mass body at a cycle corresponding to the cycle of the liquid pressure change. As a result, a control force that cancels the vibration of the vibration receiving unit can be generated by the vibration of the mass body, so that the vibration transmitted to the vibration absorbing region of the vibration receiving unit can be attenuated.

[0010] Further, since the area for pressurizing the liquid in the pressure receiving liquid chamber of the driving partition is wider than the pressure receiving area of the pressure receiving displacement portion, the displacement of the driving partition is expanded to the pressure receiving displacement portion of the elastic body via the liquid. Therefore, the amplitude of the pressure receiving displacement portion with respect to the amplitude of the driving partition can be increased. Therefore, without increasing the negative or positive pressure in the pressure supply,
Since the control force for canceling the vibration can be increased, the vibration transmitted to the vibration absorbing region of the vibration receiving portion can be effectively attenuated.

Here, the vibration absorbing region in the vibration receiving portion is
This is the area where the vibration is canceled by the control force generated by vibrating the mass body. When the vibration receiving section is a completely rigid body, the entire vibration receiving section becomes the vibration absorbing area. In the case where such a non-rigid body is the vibration receiving portion, the vicinity of the connection portion of the vibration receiving portion with the mounting member is the vibration absorbing region.

According to a second aspect of the present invention, in the active vibration absorber of the first aspect, the pressure supply means communicates with the gas filled chamber at a period corresponding to the vibration transmitted to the vibration receiving portion. The tip is alternately switched between a pressure supply source and an external space.

According to the active vibration absorbing device having the above structure, the pressure supply means alternately switches the communication destination of the gas filling chamber between the pressure supply source and the external space at a cycle corresponding to the vibration transmitted to the vibration receiving portion. This makes it possible to vibrate the mass body at a cycle corresponding to the vibration transmitted to the vibration receiving unit.For example, while vibrating the mass body at a cycle equal to the vibration cycle transmitted to the vibration receiving unit, By vibrating the mass body with a phase inverted from the phase of the transmitted vibration, the vibration transmitted to the vibration receiving unit due to the inertial force of the mass body can be effectively attenuated.

According to a third aspect of the present invention, in the active vibration absorber of the first or second aspect, the pressure supply means is connected to an intake manifold of the engine using the gas filled chamber as a pressure supply source. A supply path, a pressure release path connecting the gas filled chamber to an external space, and an on-off valve for opening and closing the pressure supply path and the pressure release path, respectively.
It has.

According to the active vibration absorber of the above construction, the pressure supply path connects the gas filling chamber to the intake manifold of the engine as a pressure supply source, so that the pressure in the intake manifold is higher than the external pressure when the engine is operating. Since the pressure is negative, when the pressure supply path is opened by the on-off valve and the pressure release path is closed, the pressure in the gas filled chamber can be reduced to a negative pressure, and the pressure supply path is closed by the on-off valve, When the pressure release passage is open, the inside of the gas filled chamber can be made equal to the outside air pressure. As a result, when the apparatus is applied to an automobile or the like, it is not necessary to provide a special pressure supply source for supplying a negative pressure or a positive pressure.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an active vibration damping device according to an embodiment of the present invention will be described with reference to the drawings.

(First Embodiment) FIGS. 1 and 2 show an active damper 1 according to a first embodiment of the present invention.
0 is shown. In the drawings, reference symbol S indicates an axis which is a center line of the apparatus, and the following description will be made with a direction along the axis S as an axial direction.

The active damper 10 is fastened and fixed to a vehicle body 12 of an automobile as shown in FIG. Also body 1
An engine 14 serving as a vibration generating unit is mounted on the vehicle 2 via a plurality of vibration isolating devices 16, and a plurality of active dampers 10 are arranged around an engine mounting portion of the vehicle body 12. Here, as the vibration isolator 16, for example, a liquid sealing type having a rubber-like elastic body serving as a vibration absorbing main body and a plurality of liquid chambers connected to each other by a restriction passage is used.

As shown in FIG. 1, the active damper 10 has a bottomed cylindrical mounting bracket 18 whose lower end is closed as an outer shell. At the upper end of the mounting bracket 18,
A flange portion 19 that extends in the radial direction and has an outer peripheral end bent upward is provided. A bolt 20 penetrates from the inside to the bottom plate portion of the mounting bracket 18 and is fixed by welding or the like, and a shaft portion of the bolt 20 projects downward along the axis S. The bolt 20 penetrates the vehicle body 12, and a nut 21 is screwed into a tip portion thereof. Thereby, the mounting bracket 18 is connected and fixed to the vehicle body 12.

As shown in FIG. 1, a substantially cylindrical outer cylinder fitting 22 is disposed on the mounting fitting 18. A thin disk-shaped flange portion 23 extending in the radial direction is formed at a lower end portion of the outer tube fitting 22, and the outer diameter of the flange portion 23 is slightly larger than the outer diameter of the flange portion 19 of the mounting bracket 18. A cylindrical caulking portion 24 is formed at the extension end portion so as to protrude downward as shown by a two-dot chain line in FIG.

The flange portion 23 of the outer tube fitting 22 is placed on the flange portion 19 of the mounting member 18, and the caulking portion 24 is caulked inward as shown by the solid line in FIG. You.

On the upper side of the outer tube fitting 22, there is formed a tapered fixed support portion 26 having a diameter increasing upward. A substantially columnar elastic body 28 is fixed to the inner peripheral side of the fixed support portion 26. The lower side of the elastic body 28 is formed in a V-shape that opens downward, and a tapered surface 29 corresponding to the fixed support portion 26 of the outer cylinder fitting 22 is formed on the outer periphery of the lower end of the elastic body 28. . The elastic body 28 has its tapered surface 29 vulcanized and adhered to the fixed support portion 26, and
2 are connected. On the lower surface of the elastic body 28, a substantially truncated conical recess 30 is formed on the inner peripheral side of the tapered surface 29.

At the inner peripheral end of the tapered surface 29 of the elastic body 28, a cylindrical elastic film 32 is integrally provided so as to extend downward. A portion near the lower end formed in a flange shape extending in the radial direction while covering the inner peripheral surface is clamped and fixed by the flange portion 19 of the mounting bracket 18 and the flange portion 23 of the outer cylinder bracket 22.

A metal top plate fitting 34 is vulcanized and bonded to the top surface of the elastic body 28. A bolt shaft 36 is fixed to the upper surface of the top plate fitting 34 by welding or the like so as to protrude upward along the axis S. A mass body 38 formed by processing a metal material into a thick disk is placed on the top plate fitting 34, and the bolt shaft 36 penetrates the center of the mass body 38, and a nut 40 is screwed into a tip end thereof. Have been. This allows
The mass body 38 is fastened and fixed on the top plate fitting 34.

A substantially cylindrical support member 4 is provided in the outer tube member 22.
2 has been inserted. The support fitting 42 is disposed on the lower side in the outer cylinder fitting 22, and a disc-shaped flange 43 extending in the radial direction is formed at the lower end thereof. The outer peripheral surface of the support fitting 42 is in pressure contact with the inner peripheral surface of the outer tubular fitting 22 via the elastic film 32. At this time, the elastic film 32 is
2 and the support fitting 42 are sealed so as to be in a liquid-tight state.

The flange 43 of the support fitting 42 is inserted between the flange 19 of the mounting fitting 18 and the flange 23 of the outer tubular fitting 22, and the flanges 19, 23 together with the lower end of the elastic film 32. It is clamped and fixed.

On the inner peripheral side of the support fitting 42, a support fitting 42
A disk-shaped drive partition 44 is disposed so as to close the inner peripheral side of the drive partition. The drive partition wall 44 includes a metal disk 45 disposed on the inner peripheral side and a rubber elastic ring 46 disposed on the outer peripheral side of the metal disk 45.

At the outer peripheral end of the metal disk 45, a cylindrical fixing portion 47 projecting upward is bent and formed. The inner peripheral surface of the elastic ring 46 is vulcanized and bonded to the outer peripheral surface of the fixing portion 47, and the outer peripheral surface is vulcanized and bonded to the upper end of the inner peripheral surface of the support fitting 42. Thus, the inner peripheral side of the support fitting 42 is closed by the driving partition 44.

Here, the space closed by the concave portion 30 of the elastic body 28 and the driving partition 44 constitutes a pressure receiving liquid chamber 48, and a liquid such as water, oil, ethylene glycol or the like is filled in the pressure receiving liquid chamber 48. It is enclosed. In the active damper 10, the elastic body 2 is changed according to a change in the liquid pressure in the pressure receiving liquid chamber 48.
8 is elastically deformed along the axial direction. In addition, the drive partition wall 44 can be displaced along an axial direction which is a direction in which the volume of the pressure receiving liquid chamber 48 is expanded or contracted by the elastic deformation of the elastic ring 46.

As shown in FIG. 1, a block member 50 formed in a cylindrical shape is inserted into the mounting bracket 18. Thereby, the lower surface side of the support fitting 42 is closed by the block member 50. The inner peripheral space of the support fitting 42 whose lower surface is closed by the block member 50 and whose upper surface is closed by the drive partition wall 44 is filled with the gas filled chamber 5.
It is 2.

The block member 50 has a pipe-shaped communication passage 51 penetrating the block member 50 along the axial direction. Further, a through hole 54 connected to the communication passage 51 of the block member 50 is formed in the bottom plate portion of the mounting bracket 18.

One end of a pressure pipe 56 is connected to the through hole 54 of the mounting bracket 18 through a nipple (not shown), and the other end of the pressure pipe 56 is connected to a three-port two-position switching valve (hereinafter, switching valve). (Referred to as a valve) 58.

The switching valve 58 is connected to a pressure supply pipe 62 communicating with the intake manifold 60 of the engine and a pressure release pipe 64 communicating with the external space. The switching valve 58 is an electromagnetic opening / closing valve having a built-in electromagnetic solenoid. In an excited state in which a driving voltage (for example, DC 12 V) is applied, the switching valve 58 connects the pressure supply pipe 62 with the pressure pipe 56 and receives a driving voltage. In a non-excited state, the pressure release pipe 64 communicates with the pressure pipe 56.

The inside of the intake manifold 60 is always maintained at a negative pressure with respect to the atmospheric pressure when the engine is operating. Therefore, when the drive voltage is applied to the switching valve 58, the gas filling chamber 52 communicates with the intake manifold 60, and the internal pressure of the gas filling chamber 52 becomes negative, and when the driving voltage is not applied to the switching valve 58, The gas filling chamber 52 communicates with the external space to form the gas filling chamber 5.
2 becomes equal to the atmospheric pressure.

In the active damper 10, the gas filling chamber 5
When the internal pressure of the second pressure chamber 2 is changed from the atmospheric pressure to a negative pressure, the metal disk 45 of the driving partition 44 is displaced downward along the axial direction as shown by the solid line in FIG. descend. As a result, the elastic body 28 is bent and deformed downward in the axial direction with the outer peripheral portion as a fulcrum, and the mass body 38 connected and fixed to the top of the elastic body 28 via the top plate fitting 34 is displaced downward. .

When the internal pressure of the gas filling chamber 52 changes from negative pressure to atmospheric pressure, the metal disk 45 of the drive partition 44 is moved by the elastic restoring force of the elastic ring 46 as shown by a two-dot chain line in FIG. The pressure receiving liquid chamber 48 is displaced upward along the axial direction.
The hydraulic pressure inside increases. As a result, the elastic body 28 is bent and deformed upward along the axial direction with the outer peripheral portion as a fulcrum, and the mass body 38 connected and fixed to the top of the elastic body 28 via the top plate fitting 34 is displaced upward. . At this time, the mass body 38 is moved by the restoring force and the inertia force of the elastic ring 46 as shown in FIG.
Move to above the initial position shown in.

[0037] Here, when the gas charging chamber 52 becomes a negative pressure from the atmospheric pressure, essentially by downward displacement of the metal disk 45 having an outer diameter which is the R ₁ as shown in FIG. 2 When the pressure in the pressure receiving liquid chamber 48 is reduced, and the pressure of the gas filled chamber 52 is changed from negative pressure to atmospheric pressure, the metal disk 45 is displaced upward to substantially reduce the pressure in the pressure receiving liquid chamber 48. Increase hydraulic pressure.

On the other hand, the elastic body 28 has a tapered surface 29 on the outer peripheral side.
Are fixed to the fixing support portion 26 of the outer tube fitting 22. From this, it can be approximately considered that the outer peripheral portion of the elastic body 28 is a rigid body that does not elastically deform even when subjected to the liquid pressure in the pressure receiving liquid chamber 48. Therefore, the elastic body 28 is
When the metal disk 45 is displaced and the liquid pressure in the pressure receiving liquid chamber 48 changes, only the pressure receiving displacement portion 31 which is a part on the inner peripheral side is substantially axially moved as shown in FIG. Displace along the direction. In the present embodiment, the shape, rigidity, and the like of the elastic body 28 are designed such that the diameter R ₂ of the pressure receiving displacement portion 31 about the axis S is smaller than the outer diameter R ₁ of the metal disk 45.

The active damper 10 is provided with a controller 66 for controlling the switching valve 58. The controller 66 is connected to a vibration sensor 68 installed on the vehicle body 12. The vibration sensor 68 is installed at an intermediate portion between the engine 14 and the active damper 10 on the vehicle body 12, detects vibration of the vehicle body 12, and generates an electric signal having a waveform (for example, a sine waveform) corresponding to the vibration. It outputs to the controller 66 as a detection signal.

The controller 66 receives the signal from the vibration sensor 68 and determines the frequency and phase of the vibration in the vehicle body 12. The controller 66 determines the ratio between the on-time for turning on the drive voltage to the switching valve 58 and the off-time for turning off the drive voltage so that the mass vibrates at the same frequency as the frequency of vibration of the vehicle body 12, that is, the duty of the drive voltage. Set the ratio. Further, the controller 66 includes the mass 3
The drive voltage output timing is adjusted so that 8 vibrates in a phase having a certain time lag from the vibration phase in the vehicle body 12 or in a phase opposite to the vibration phase in the vehicle body 12.

Next, the operation of the active damper 10 according to the embodiment of the present invention will be described.

When the engine 14 mounted on the vehicle body 12 operates, the vibration of the engine 14 is transmitted to the vehicle body 12 via the vibration isolator 16. The vibration from the engine 14 is
The vehicle body 12 is attenuated at a constant attenuation rate by the vibration isolator 16.
However, the vibration transmitted to the vehicle body 12 cannot be completely eliminated, and the vehicle body 12 vibrates due to the vibration from the engine 14.

When the vehicle body 12 vibrates, the vibration sensor 68
The controller 66 detects the vibration of the vehicle body 12 and outputs a detection signal.
Output to Upon receiving the detection signal from the vibration sensor 68, the controller 66 operates the switching valve 58 so that the mass body 38 vibrates at a frequency equal to the frequency of vibration in the vehicle body 12.
And the output timing of the drive voltage is adjusted so that the mass body 38 oscillates in a phase having a predetermined time lag from the phase of the vibration in the vehicle body 12 or in an opposite phase.

The active damper 10 applies a control force equal to the product of the mass of the mass body 38 and the acceleration to the vehicle body 12 when the mass body 38 vibrates. At this time, the vibration frequency of the mass body 38 is made equal to the vibration frequency of the vehicle body 12, and the mass body 38 is vibrated at a phase (including an opposite phase) having a certain time lag from the vibration phase of the vehicle body, so that the active body is activated. The control force of the damper 10 cancels the vibration of the vehicle body 12,
Or act to weaken. Therefore, by vibrating the mass body 38 in response to the vibration in the vehicle body 12,
The vibration level of the vehicle body 12 during the operation of the engine 14 can be greatly reduced.

Here, since the vehicle body 12 is not a completely rigid body, the vibration transmitted from the engine 14 to the vehicle body 12 propagates from the mounting portion of the engine 14 on the vehicle body 12 to the periphery. Therefore, even when the active damper 10 is operated, the vibration does not disappear near the mounting portion of the engine 14 on the vehicle body 12, and the vibration sensor 68 detects the vibration near the mounting portion of the engine 14 on the vehicle body 12.

Since the plurality of active dampers 10 are arranged so as to surround the mounting portion of the engine 14 on the vehicle body 12, it is possible to effectively transmit the vibration from the vicinity of the mounting portion of the active damper 10 to the outside of the vehicle body 12. (Vibration cutoff). As a result, the vibration level transmitted to the inside of the vehicle can be significantly reduced.

Further, in the active damper 10, the outer diameter R ₁ of the metal disk 45, which substantially changes the pressure in the pressure receiving liquid chamber 48, substantially changes in the axial direction by receiving the liquid pressure in the pressure receiving liquid chamber 48. Since the diameter of the displaced pressure receiving displacement portion 31 is made larger than the diameter R _2, the displacement of the driving partition 44 is expanded and transmitted to the pressure receiving displacement portion 31 of the elastic body 28 via the liquid. , The amplitude of the elastic body 30 can be increased.

As a result, even if the negative pressure in the intake manifold 60 is not large, the vibration stroke of the mass body 38 can be increased, and the control force acting from the active damper 10 to the vicinity of the mounting portion of the active damper 10 in the vehicle body 12 increases. The active damper 1 in the vehicle body 12
Vibration transmitted to the vicinity of the zero attachment portion can be effectively attenuated.

The type of vibration from the engine 14 includes, for example, shake vibration (less than 15 Hz) generated when the vehicle runs at 70 to 80 km / h, idling operation and low-speed operation with a vehicle speed of 5 km / h or less. There are idle vibrations (20 to 30 Hz) and the like generated by the controller 61. The type of these vibrations is determined by the controller 61, and only when specific vibrations, for example, shake vibrations are transmitted to the vehicle body 12, the active damper 10 is turned off. You may make it operate.

In this embodiment, only the case where the active damper 10 is arranged on the vehicle body 12 has been described. However, the active damper 10 is arranged on the engine May be suppressed.

Further, in the active damper 10, the intake manifold 60 is used as a pressure supply source to the gas filling chamber 52, and the negative pressure and the atmospheric pressure are alternately supplied to the gas filling chamber 52. Even if the chamber 52 is connected to an exhaust manifold and the positive pressure and the atmospheric pressure are alternately supplied to the gas filling chamber 52, the mass body 38 can be vibrated.

In the active damper 10 described above,
Since the electromagnetic actuator is not used to vibrate the mass body 38, the mass body 38 can be vibrated simply by switching the communication destination of the gas filled chamber 52 to either the intake manifold 60 or the external space by the switching valve 58. Compared with the case where an electromagnetic actuator is used, the apparatus cost can be reduced and the assembling work of the apparatus can be simplified.

(Second Embodiment) FIG. 4 shows an active damper 110 according to a second embodiment of the present invention. In FIG. 4, members having the same configuration and operation as those of the first embodiment described above with reference to FIGS. 1 to 3 are denoted by the same reference numerals, and description thereof is omitted. Similarly to the active damper 10, a plurality of active dampers 110 of the present embodiment are arranged so as to surround the engine mounting portion of the vehicle body 12 (see FIG. 3).

As shown in FIG. 4, the active damper 110 has, as an outer shell, a bottomed cylindrical outer tube fitting 118 whose lower end is closed. The outer cylindrical member 118 includes an upper cylindrical portion 120 and a lower cylindrical portion 122 having different diameters.
Is provided, and a stepped flange portion 124 is provided at an intermediate portion between the large-diameter upper cylindrical portion 120 and the small-diameter lower cylindrical portion 122.
Are formed.

A bolt 126 is provided on the bottom plate of the outer cylinder fitting 118.
Are fixed by welding or the like, and the shaft of the bolt 126 projects downward along the axis S. This bolt 1
Reference numeral 26 penetrates the vehicle body 12, and a nut 128 is screwed into a tip end thereof. Thereby, the outer cylinder fitting 118 is attached to the vehicle body 12.
Is fixed.

In the upper cylindrical portion 120, thin supporting cylinders 130 whose axial ends are larger than the inner diameter of the lower cylindrical portion 122 are inserted. This support cylinder 1
A reduced diameter portion 131 having a smaller diameter than both ends is provided at an intermediate portion in the axial direction of 30. As shown in FIG. 5, the reduced diameter portion 131 has a groove 133 having a rectangular cross section formed on the outer peripheral surface of the support cylinder 130 along the circumferential direction over the entire circumference.

As shown in FIG. 4, an elastic body 135 made of rubber is bonded to the inner peripheral surface of the support cylinder 130 by vulcanization. The elastic body 135 is formed in a substantially truncated conical shape whose cross section is reduced upward, and the vicinity of the outer periphery at the lower end is vulcanized and bonded to the upper end of the inner peripheral surface of the support cylinder 130, and the upper end is supported by the support cylinder 130. Projecting upward from Elastic body 1
In the center of the bottom surface of 35, a circular concave portion 137 concaved upward is formed.

A metal top plate 139 is vulcanized and bonded to the top surface of the elastic body 135. A bolt shaft 141 is fixed to the upper surface of the top plate fitting 139 by welding or the like so as to protrude upward along the axis S. A mass body 38 formed by processing a metal material into a thick disk is placed on the top plate fitting 139, and the bolt shaft 141 passes through the center of the mass body 38, and a nut 145 is screwed into a tip end thereof. Have been.
Thus, the mass body 38 is fastened and fixed on the top plate fitting 139.

A substantially cylindrical partition member 147 is inserted into the support cylinder 130. A cylindrical hollow portion 149 penetrating in the axial direction is formed on the inner peripheral side of the partition member 34, and a partition housing portion 151 having an inner diameter that is larger than the upper side is formed at the lower end of the hollow portion 149. Is formed. Here, the partition member 147 is arranged such that the outer peripheral portion of the upper surface is in close contact with the outer peripheral portion of the lower surface of the elastic body 135. The inner diameter of the hollow portion 149 is equal to the inner diameter of the concave portion 137 of the elastic body 135.

A disk-shaped drive partition 153 is disposed in the partition storage portion 151 of the partition member 147. Driving partition 1
Reference numeral 53 denotes a resin disk 154 disposed on the inner peripheral side and a rubber elastic ring 155 disposed on the outer peripheral side of the resin disk 154.

The inner peripheral surface of the elastic ring 155 is
In addition to being fixed to the outer peripheral surface of the partition wall 54, the outer peripheral surface is fixed to the lower end of the inner peripheral surface of the partition wall housing portion 151. This allows
The lower surface of the hollow portion 149 of the partition member 147 is
3 closed. Here, the concave portion 1 of the elastic body 135
37 and a hollow portion 149 closed by the drive partition 153
Constitutes a pressure receiving liquid chamber 157, and the pressure receiving liquid chamber 157
The elastic body 135 is elastically deformed along the axial direction in accordance with a change in the internal liquid pressure. The driving partition 153 is
When the elastic ring 155 is elastically deformed,
57 can be displaced along an axial direction which is a direction for expanding and contracting the volume.

As shown in FIG. 5, a groove 148 is formed on the outer peripheral surface of the partition member 147 along the circumferential direction, and one end of the groove 148 is formed from the inner wall of the groove 40 to the hollow 14.
A communication passage 159 is formed to penetrate to the inner peripheral surface of the nozzle 9.

As shown in FIG. 4, the support cylinder 130 has the inner peripheral surface of the reduced diameter portion 131 in close contact with the outer peripheral surface of the partition member 147. Thereby, the groove 133 of the partition member 147 is formed.
Is closed by a reduced diameter portion 131. As shown in FIG. 2, a through hole 161 is formed in the reduced diameter portion 131 of the support cylinder 130 at a position corresponding to the other end of the groove 40, and the through hole 161 is formed in the groove 133 of the support cylinder 130. And the groove 148 of the partition member 147 communicate with each other.

A disk-shaped flange portion 163 extending radially is formed at the lower end portion of the outer peripheral surface of the partition member 147, and the upper surface side of the flange portion 163 is the lower surface of the reduced diameter portion 131 of the support cylinder 130. Is in contact with The flange 16
A ring-shaped spacer 165 is inserted between the lower surface of the third member 3 and the upper surface of the flange portion 163 of the outer tube fitting 118, whereby the support cylinder 130 and the partition member 147 are positioned in the axial direction. A cylindrical hollow portion 167 having an inner diameter equal to the inner diameter of the partition wall housing portion 151 is formed on the inner peripheral side of the spacer 165.

In the upper cylindrical part 120 of the outer cylinder fitting 118, a thin intermediate cylinder 169 is provided between the outer cylinder fitting 118 and the outer peripheral surface of the support cylinder 130.
Is arranged. The length of the intermediate cylinder 169 in the axial direction is equal to that of the support cylinder 130, and the inner peripheral surface covers the outer peripheral surface of the support cylinder 130. Support cylinder 1
30 and the lower end of the intermediate cylinder 169
8 is in contact with the upper surface of the flange portion 124, and in this state, the support cylinder 130 and the intermediate cylinder 169 are fixed in the outer cylinder fitting 118 by caulking the upper end of the outer cylinder fitting 118 to the inner peripheral side. ing.

On the inner peripheral surface of the intermediate cylinder 169, both ends in the axial direction of a substantially cylindrical rubber diaphragm 171 are respectively vulcanized and bonded over the entire circumference. The diaphragm 171 closes the outer peripheral side of the groove 133 of the support cylinder 130, and is curved in an arch shape so that the axial middle portion protrudes into the groove 24. Here, the diaphragm 17
An annular space formed in the groove 133 whose outer peripheral side is closed by 1 is a sub liquid chamber 173. An air chamber 175 is provided between the outer peripheral surface of the diaphragm 171 and the inner peripheral surface of the intermediate cylinder 169 so that the diaphragm 171 can be elastically deformed in the radial direction. The air chamber 175 is communicated with the outside of the apparatus as needed.

The sub liquid chamber 173 and the pressure receiving liquid chamber 157 communicate with each other through a through hole 161 of the support cylinder 130, a groove 133 and a communication passage 159 in the support cylinder 130, and these through holes 161, the groove 133, and the Passage 15
Reference numeral 9 denotes a restriction passage 177 as an orifice. Here, liquids such as water, oil, and ethylene glycol are filled and sealed in the pressure receiving liquid chamber 157, the auxiliary liquid chamber 173, and the restriction passage 177.

In the active damper 110 of the present embodiment, the rigidity of the diaphragm 171 constituting a part of the partition wall of the sub liquid chamber 173 has a magnitude corresponding to the frequency of the shake vibration in the automobile, and the liquid in the restriction passage 177 has The flow resistance is also set to a magnitude corresponding to the frequency of the shake vibration.

A cylindrical block member 179 is inserted into the lower cylindrical portion 122 of the outer cylinder fitting 118. The block member 179 has an upper surface outer peripheral portion brought into close contact with a lower surface inner peripheral portion of the spacer 165. Thus, the lower surface side of the hollow portion 167 of the spacer 165 is closed by the block member 179. This block member 17
9, the upper surface side is closed, and the driving partition 153 is closed on the upper surface side of the hollow portion 149 of the spacer 165.
Is a gas filled chamber 181.

The block member 179 has a pipe-shaped communication passage 183 penetrating the block member 179 along the axial direction.
Are formed. A through hole 161 connected to the communication path 159 is formed in the bottom plate of the outer cylinder fitting 118.

One end of a pressure pipe 56 is connected to a through hole 161 of the outer cylinder fitting 118 via a nipple (not shown) or the like, and the other end of the pressure pipe 56 is connected to a three-port two-position switching valve (hereinafter, referred to as a three-port valve). (Referred to as a switching valve) 58.

A pressure supply pipe 62 communicating with the intake manifold 60 of the engine and a pressure release pipe 64 communicating with the external space are connected to the switching valve 58, respectively. The switching valve 58 is an electromagnetic opening / closing valve having a built-in electromagnetic solenoid. In an excited state in which a driving voltage (for example, DC 12 V) is applied, the switching valve 58 connects the pressure supply pipe 62 with the pressure pipe 56 and receives a driving voltage. In a non-excited state, the pressure release pipe 64 communicates with the pressure pipe 56.

Here, the intake manifold 60 is always maintained at a negative pressure with respect to the atmospheric pressure when the engine is operating. Therefore, when a drive voltage is applied to the switching valve 58, the gas filling chamber 181 communicates with the intake manifold 60, and the internal pressure of the gas filling chamber 181 becomes negative, and when no driving voltage is applied to the switching valve 58, The gas filling chamber 181 communicates with the external space, and the internal pressure of the gas filling chamber 181 becomes equal to the atmospheric pressure.

In the active damper 110, when the internal pressure of the gas filling chamber 181 changes from atmospheric pressure to negative pressure, the driving partition 153 is displaced downward along the axial direction, and the pressure receiving liquid chamber 157 is displaced downward.
The hydraulic pressure inside decreases. As a result, the elastic body 135 is bent and deformed downward in the axial direction with the outer peripheral portion as a fulcrum, and the mass body 38 connected and fixed to the top of the elastic body 135 is displaced downward.

When the internal pressure of the gas filling chamber 181 changes from negative pressure to atmospheric pressure, the driving partition 153 is displaced upward along the axial direction by the elastic restoring force of the elastic ring 155, and the pressure in the pressure receiving liquid chamber 157 is reduced. Hydraulic pressure rises. As a result, the elastic body 135 is bent and deformed upward in the axial direction with the outer peripheral portion as a fulcrum, and the mass body 38 connected and fixed to the top of the elastic body 135 is displaced upward. At this time, the mass body 38
Moves above the initial position shown in FIG. 4 due to the restoring force and inertia force of the elastic ring 155.

Here, when the pressure of the gas filling chamber 181 is changed from the atmospheric pressure to the negative pressure, the resin disk 15 having an outer diameter of R ₃ is used.
4 lowers the liquid pressure in the pressure receiving liquid chamber 157 substantially, and when the pressure of the gas filling chamber 181 changes from negative pressure to atmospheric pressure, the resin disk 154 moves upward. The hydraulic pressure in the pressure receiving liquid chamber 157 is substantially increased.

On the other hand, in the elastic body 135, the periphery of the concave portion 137 is fixed to the upper surface of the partition member 147. For this reason, the outer peripheral portion of the concave portion 137 of the elastic body 135 is
It can be considered approximately a rigid body that does not elastically deform even when subjected to the liquid pressure in 57. Therefore, the elastic body 135 is
When the resin disk 154 of the driving partition 153 is displaced, the pressure receiving liquid chamber 1 is displaced.
When the hydraulic pressure in 57 changes, only the pressure receiving displacement portion 136, which is a part on the inner peripheral side, is displaced along the axial direction substantially, as shown in FIG. In the present embodiment, the diameter R ₄ of the pressure receiving displacement portion 136 about the axis S is the resin disc 15.
The shape of the elastic body 135 to be smaller than the outside diameter R ₃ of 4, rigidity is designed.

The active damper 110 has a controller 66 for controlling the switching valve 58. The controller 66 is connected to a vibration sensor 68 installed on the vehicle body 12. The vibration sensor 68 is provided at an intermediate portion between the engine 14 and the active damper 110 on the vehicle body 12, detects vibration of the vehicle body 12, and generates an electric signal having a waveform (for example, a sine waveform) corresponding to the vibration. It outputs to the controller 66 as a detection signal.

The controller 66 receives the signal from the vibration sensor 68 and determines the frequency and phase of the vibration in the vehicle body 12. The controller 66 determines the ratio between the on-time for turning on the drive voltage to the switching valve 58 and the off-time for turning off the drive voltage so that the mass vibrates at the same frequency as the frequency of vibration of the vehicle body 12, that is, the duty of the drive voltage. Set the ratio. Further, the controller 66 includes the mass 3
The drive voltage output timing is adjusted so that 8 vibrates in a phase having a certain time lag from the vibration phase in the vehicle body 12 or in a phase opposite to the vibration phase in the vehicle body 12.

Next, the operation of the active damper 110 according to the embodiment of the present invention will be described.

The active damper 110 of the present embodiment also allows the controller 66 to control the switching valve 68 in the same manner as in the case of the active damper 10 so that the vehicle body 1
2, the transmission of vibration from the vicinity of the mounting portion of the active damper 110 to the outer region can be effectively prevented (vibration blocking), so that the vibration level transmitted to the inside of the vehicle can be significantly reduced.

The active damper 1 according to the present embodiment
10 also shows the active damper 1 according to the first embodiment.
As in the case of 0, the outer diameter R ₃ of the resin disk 154 that substantially changes the liquid pressure in the pressure receiving liquid chamber 157 receives the liquid pressure in the pressure receiving liquid chamber 157 and is substantially displaced in the axial direction. Part 136
Is larger than the diameter R _{4 of} the driving partition wall 1.
The displacement of the pressure receiving portion 1 of the elastic body 135 is caused by the displacement of
36, the amplitude of the elastic body 135 with respect to the amplitude of the driving partition 153 can be increased.

Further, the active damper 11 of the present embodiment
In the case of 0, the rigidity of the diaphragm 171 constituting a part of the partition wall of the sub liquid chamber 173 is set to a magnitude corresponding to the frequency of the shake vibration in the automobile, and the flow resistance of the liquid in the restriction passage 177 also corresponds to the frequency of the shake vibration. Due to the size, when the liquid in the pressure receiving liquid chamber 157 changes at a cycle in which the liquid pressure in the sub liquid chamber 173 is substantially equal to the shake vibration (less than 15 Hz), that is, the driving partition 153 is substantially equal to the shake vibration. When vibrating at the frequency, a resonance phenomenon (liquid column resonance) occurs in the liquid flowing between the pressure receiving liquid chamber 157 and the sub liquid chamber 173 through the restriction passage 177, and the liquid column resonance causes the liquid inside the pressure receiving liquid chamber 157. Therefore, the displacement of the elastic body 135 along the axial direction caused by the change in the hydraulic pressure can be increased, and the amplitude of the mass body 135 can be increased.

Therefore, when the vibration transmitted from the engine 14 to the vehicle body 12 is a shake vibration, the vehicle body 1 can be driven without increasing the negative pressure in the intake manifold 91.
Since the control force for canceling the second vibration can be increased, the shake vibration transmitted to the vehicle body 12 can be particularly effectively attenuated. The type of vibration from the engine 14 may be other than the above-described shake vibration. There are idle vibration (20 to 30 Hz) and the like that occur in the case of idling operation and low-speed operation with a vehicle speed of 5 km / h or less, but the rigidity of the diaphragm 171 and the flow resistance of the restriction passage 177 are reduced by vibrations other than shake vibration such as idle vibration. May be set (tuned) so as to increase the amplitude of the mass body 135 by the liquid column resonance action at the time of transmitting vibration other than the shake vibration.

[0085]

As described above, according to the active vibration absorbing device of the present invention, the control force for canceling the vibration transmitted to the vibration receiving portion can be sufficiently increased, and the manufacturing cost of the device can be greatly reduced. it can.

[Brief description of the drawings]

FIG. 1 is a side sectional view of an active damper according to a first embodiment of the present invention.

FIG. 2 is a side sectional view showing an operation state of the active damper according to the first embodiment of the present invention.

FIG. 3 is a schematic diagram showing a state in which an active damper and an engine according to the embodiment of the present invention are mounted on a vehicle body.

FIG. 4 is a side sectional view of an active damper according to a second embodiment of the present invention.

FIG. 5 is a perspective view showing a support cylinder and a partition member in an active damper according to a second embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Active damper (active vibration absorption device) 12 Body (vibration receiving part) 28 Elastic body 31 Pressure receiving displacement part 38 Mass body 34 Top plate metal fitting (support member) 44 Drive partition wall 48 Pressure receiving liquid chamber 52 Gas sealing chamber 57 Pressure supply pipe (pressure) Supply path) 58 Switching valve (pressure supply means) 60 Intake manifold (pressure supply source) 64 Pressure release pipe (pressure release path) 66 Controller (pressure supply means) 110 Active damper (active vibration absorber) 135 Elastic body 136 Pressure receiving displacement Part 139 Top plate bracket (support member) 153 Driving partition 157 Pressure receiving liquid chamber 181 Gas filling chamber

Claims (3)

[Claims] 1. A mounting member connected to a vibration receiving unit, a mass body having a mass corresponding to a vibration absorbing area in the vibration receiving unit, a supporting member to which the mass body is fixed, the mounting member and the supporting member And a pressure receiving liquid chamber in which a liquid is sealed, and a part of a partition of the pressure receiving liquid chamber which is connected to the mounting member and the support member, respectively, and a liquid pressure in the pressure receiving liquid chamber. An elastic body provided with a pressure receiving displacement portion that is displaced along the amplitude direction of the vibration of the vibration receiving portion with the change, a gas sealing chamber provided so as to be adjacent to the pressure receiving liquid chamber, and the pressure receiving liquid chamber; A space between the pressure receiving liquid chamber and the pressurized liquid chamber in the pressure receiving liquid chamber is wider than a pressure receiving area of the pressure receiving displacement section, and a volume expansion / contraction direction of the pressure receiving liquid chamber is changed according to a change in air pressure in the gas sealing chamber. A drive partition wall displaced to Active vibration absorber negative pressure or a body filled chamber to the external space, characterized in that it comprises a pressure supply means for communicating alternately to one of a positive pressure and pressure source and the external space. 2. The pressure supply means alternately switches the communication destination of the gas filling chamber between a pressure supply source and an external space at a period corresponding to the vibration transmitted to the vibration receiving portion. 2. The active vibration absorber according to claim 1. 3. The pressure supply means includes: a pressure supply path connected to an intake manifold of an engine using the gas-filled chamber as a pressure supply source; a pressure release path connected to the gas-filled chamber to an external space; The active vibration damping device according to claim 1 or 2, further comprising an on-off valve that opens and closes the passage and the pressure release passage, respectively.