JPH03260429A - Damping force adjuster - Google Patents

Abstract

PURPOSE:To extremely enlarge the quantity of the flexure on the peripheral end of a leaf valve on each side in comparison with the quantity of expansion of a piezoelectric element by providing such constituting that the quantity of the flexure on the peripheral end of each side leaf valve is changed due to change in the hydraulic pressure supplied to the rear of each side leaf valve. CONSTITUTION:When a piston body 30 slides inside a cylinder 1, the working fluid from the oil chamber on the so-called upper stream side reaches, on one side, the rear sides of the leaf valve 5 and 6 on respective sides generating main damping force through sub valves 7 and 8 on respective sides, and reaches the pressure receiving face sides of the leaf valves 5 and 6 on respective sides, and the working fluid passes flexing the peripheral end of the leaf valve on each side, thereby the specified damping force on each side comes to be generated respectively. At that time, when the specified voltage is applied to the piezoelectric element 4 being an electrostrictive member, the respective quantities of flexure on the peripheral ends of sub-valves 7, 8 on respective sides in the leaf valves 5 and 6 on respective sides are changed respectively accompanying this, and the quantities of the flexure on the peripheral ends of respective valves are changed.

Description

Detailed Description of the Invention (Field of Industrial Application) This invention uses a piezoelectric element as an electrostrictive member to change the circumferential deflection of a leaf valve as a damping valve, thereby reducing the T generated by the leaf valve. The present invention relates to an improvement in a damping force adjustment device formed to be able to adjust a damping force.

[Conventional technology and its issues]

The damping force adjustment device of the hydraulic pressure regulator applies a voltage to a piezoelectric element, which is a strain member, and expands the piezoelectric element to change the amount of peripheral deflection of a leaf valve, which is a damping valve. For example, one that is formed so that the main damping force can be changed is
Various proposals have been made, such as the proposal related to No. 9645, but in conventional proposals of this type, there is a disadvantage that the damping force adjustment device cannot be made large compared to the amount of deformation of the piezoelectric element.

That is, in this type of conventional proposal, when a voltage is applied to a piezoelectric element, which is an electrostrictive member, and the piezoelectric element expands, the expansion force directly changes the peripheral end deflection grade of a leaf valve, which is a damping force valve for generating damping force. In particular, this is said to adjust the damping force generated by the leaf valve.

Therefore, in the case of the above-mentioned conventional proposal.

It is not possible to change the amount of deflection at the circumferential edge of the leaf valve beyond the expansion amount of the piezoelectric element, and therefore, if a large amount of deflection is required at the circumferential edge of the leaf valve, the amount of piezoelectric elements connected in series must be significantly increased. If the number of piezoelectric elements connected in series is significantly increased, the length of the entire damping force adjusting device in the axial direction is disadvantageously increased.

This invention was created in view of the above-mentioned circumstances,
The purpose of this is to increase the amount of peripheral bending of the leaf valve, which is a damping valve, compared to the expansion amount of the piezoelectric element, which is an electrostrictive member, and to increase the amount of adjustment of the generated damping force. It is an object of the present invention to provide a damping force adjustment device that is optimal for use in.

[Means to solve the problem]

In order to solve the above-mentioned object, the structure of the present invention is adapted to attenuate the expansion force generated in the piezoelectric element when voltage is applied to the piezoelectric element, which is an electrostrictive member disposed in the piston rod inserted into the cylinder. In a damping force adjustment device formed to be able to adjust the main damping force generated by the leaf valve by changing the amount of deflection of the circumferential end of a leaf valve, which is a valve, the expansion side leaf valve is an expansion side damping valve; The pressure-side leaf valves, which are compression-side damping valves, are arranged on the end faces of the piston body that slides within the cylinder, and are formed so that back pressure acts on the back surface of each side through the sub-valves on each side. , the sub-valve on each side is located at the tip of the piston rod, respectively. The electrostrictive member C is disposed within the inlet member at the tip end of the structure, and supplies hydraulic pressure to the back surface of the leaf valve on each side, and changes the amount of deflection of each circumferential end using the expansion force generated by the electrostrictive member C. It is characterized by being formed so that the hydraulic pressure supplied to the rear surface can be changed.

[For production]

Therefore, when the piston body (piston part) slides in the cylinder, the hydraulic oil is supplied from the oil chamber on the so-called H flow side, and on the other hand, the hydraulic oil is supplied from each side that generates the main damping force via each sub-valve. It extends to the back side of the leaf valve and also to the pressure receiving surface side of the leaf valve on each side, and by bending the circumferential edge of each gap and valve and allowing the hydraulic oil to pass through, a predetermined attenuation is achieved. Each force will be generated.

At that time, when a predetermined voltage is applied to the piezoelectric element, which is an electrostrictive member, the amount of deflection of each peripheral end of the sub-valve on each side is changed, and along with this, the back pressure in the leaf valve on each side is changed. The amount of deflection of the peripheral end of the leaf valve on each side is changed, and the damping force on each side generated by the leaf valve on each side is changed.

As a result, the damping force on each side generated by each of the above leaf valves is equal to pressure! Each change is made to a width greater than the amount of expansion of the element.

Moreover, when the application of a predetermined voltage to the piezoelectric element is released,
The circumferential deflection amount of each sub-valve on each side is restored to the old state, and as a result, the hydraulic pressure acting on the back surface of each leaf valve on each side is also returned to the old state, and the leaf valves on each side are The generated damping force is returned to its original setting.

(Example) Hereinafter, the present invention will be described in detail based on the illustrated example.

As shown in the drawings, hydraulic pressure Ia according to an embodiment of the present invention
The impactor is made up of a piston rod 2 that is inserted into the cylinder 1 so as to be freely protrusive and retractable. It has a piston part 3 that partitions an oil chamber A and a piston-side oil chamber B.

The E-distribution pressure #shock device is configured such that a piezoelectric element 4, which is an electrostrictive member, is disposed within a through hole 2a formed in the axial center of the piston rod 2.

1. The piezoelectric element 4, which is the electrostrictive member, is connected to a Riet wire (not shown), and the end of the sort wire or the rear end of the piston rod 2, which is the upper end in the figure, protrudes outward. There is.

The piezoelectric element 4 expands when a predetermined voltage is applied thereto, and the expansion force can be used to change and adjust the main damping forces on the expansion side and compression side, respectively, as described later.

In the illustrated example, the expansion force described above is exerted so that only the tip of the piezoelectric element 4, which is the lower end in the figure, moves downward in the figure.

The piston rod 2 has a tip spigot member 20 connected to its tip 2b, and the tip spigot member 20.
The piston portion 3 is interposed on the outer periphery of the piston.

The piston part 3 has a piston main body 30 that slides within the cylinder 1, and also has an expansion side leaf valve 5 and a compression side leaf valve 5 arranged to sandwich the piston main body 30.

The expansion side leaf valve 5 is connected to the piston main body 30.
The compression side leaf half flow is arranged to close the lower end opening of the compression side boat 30b drilled in the piston body 30. It becomes.

The leaf valves 5 and 6 on each side are each formed of an annular leaf valve, and are fixed in such a manner that the inner peripheral end is fixed and the outer peripheral end is free, and when each outer peripheral end is bent, the main expansion side and It is said that each damping force on the compression side is generated.

That is, each of the side leaf valves 5 and 6 is sandwiched between its inner circumferential end or the inner circumferential upper and lower end surfaces of the piston body 30 and spacers 50 and 60 disposed to face the upper and lower end surfaces. At the same time, the outer peripheral end thereof is adjacent to the upper and lower end surfaces of the outer peripheral side of the piston body 30 and valve stoppers 51 and 61 disposed so as to face the upper and lower end surfaces.

The valve stoppers 51.61 are then actuated by the urging force from the urging springs 52.62, respectively, on each side of the leaf valve 5.
The energizing spring 52.62 is adapted to press the outer peripheral end of 6 against the upper and lower end surfaces of the outer peripheral side of the piston body O.
The magnitude of the damping force generated by the leaf valves 5, 6 on each side is determined by selecting the biasing force and the bending rigidity of each of the leaf valves 5, 6.

Furthermore, in this embodiment, hydraulic chambers 53.63 are formed on the back side of each side leaf valve 5, 6, respectively.
is the spacer 50.60 and the valve stopper 51.
．． 61 and the valve stopper 51. It is assumed that housings 54 and 64 are formed to accommodate the fil.

The hydraulic chambers 53, 53 communicate with the inside of the tip pilot member 20 through communication holes 50a, 60a formed in the spacer 50, 60.

The tip inlet member 2a has a rear surface of each of the leaf pulps 5.6, ie, each hydraulic chamber 53.6, inside thereof.
It has an expansion side sub-valve 7 and a compression side suffal valve 8 for supplying hydraulic pressure to.

That is, the tip pilot member 20 is composed of a rod portion 21 which is on the lower end side of the IA, and a connecting portion 22 which is connected to the rod portion 21 and is on the upper end side in the figure. A cylindrical inner cavity 21a formed inside the
The above-mentioned sub valves 7.8 are housed on each side.

Each side sub-valve 7.8 is formed so that the amount of deflection of each peripheral end can be changed by the expansion force generated in the electrostrictive member 4, and in this embodiment,
Each of the sub-valves 7.8 is an annular leaf valve, and is configured to allow the flow of hydraulic oil through the sub-valves 7.8 on each side when the outer peripheral end thereof is deflected.

To explain briefly, the extension side suffix 7 is formed by bringing the annular seat portion 71a of the valve seat 71 into contact with its back surface, which is the lower surface in the figure.

The valve seat 71 is fitted into the inner cavity 21a with a seal 71b interposed therebetween, and is supported from below by a perforated plug 23 screwed onto the open end, which is the lower end in the figure. .

The valve seat 71 has an orifice 71c that communicates the expansion side leaf valve 5 side and the perforated plug 23 side, or the orifice 7c is arranged so that the expansion side leaf valve 5 side and the perforated plug 23 side are connected to each other. This makes it possible to install hydraulic pressure on the back side of 5.

It should be noted that the annular seat portion 71a is placed close to the inner circumferential end of the expansion side sub-valve 7, as it comes into contact with the back surface of the expansion side sub-valve 7.

Further, it is assumed that the expansion side sub-valve 7 has an inner circumferential fixing portion 72a and an outer circumferential side seat portion 72b of the valve disc 72 in contact with the pressure receiving surface which is the upper surface in FIG.

The valve disc 72 is fitted into the inner cavity 21a so as to be slidable in the vertical direction.

The valve disc 72 has an annular groove 72c between the inner peripheral side fixing part 72a and the outer peripheral side seat part 72b, and the thick part of the valve disc 72 is passed through the annular groove 72c. The boat 72d is opened.

Therefore, the extension side salvage valve 7 in this embodiment is sandwiched between the inner circumferential end side of the inner circumferential side fixing part 72a of the valve disk 72 and the annular seat part 71a of the half sea door 1, and the outer circumference thereof The end is fixed so that it can be bent, and therefore, when hydraulic pressure is applied to the outer M end of the expansion side sub-valve 7, this will bend downward in the figure.

At this time, a predetermined flow rate of hydraulic oil is ensured.

However, on the inner peripheral end side of the expansion side sub-valve 7, there is an innermost inner peripheral fixing part 72a and an annular seat part 7 slightly closer to the outer peripheral side.
1a, so when the inner peripheral end of the expansion side sub-valve 7 is pressed against the inner peripheral fixing part 72a using the annular seat part 71a as a fulcrum, the expansion side The outer peripheral end of the expansion side sub-valve 7 undergoes so-called lateral movement and is pressed against the outer peripheral seat portion 72b of the valve disk 72, and the amount of deflection of the outer peripheral end of the expansion side sub-valve 7 is changed. The flow rate of the hydraulic oil through the outer peripheral end is changed to a decreasing tendency.

On the other hand, the pressure-side flat valve 8 has an annular seat portion 81a of a valve seat 81 in contact with its back surface, which is the upper surface in the figure.

The valve seat 81 is vertically movable, that is, accommodated in the axial direction C of the rod portion 21 in the inner cavity 21a.

The valve seat 81 has a notch 81b formed with a thick wall C, and allows communication between the pressure side leaf hull pro side and the rear side of the valve seat 8I. (are doing.

It should be noted that the annular seat portion 81a is positioned closer to the inner circumferential end of the pressure side sub-valve 8, as it comes into contact with the back surface of the pressure side sub-valve 8.

Further, the pressure-side flat valve 8 also has a 3# half disk 82, in which the inner circumferential side fixed portion 82a and the outer circumferential side seat portion 82b of the valve disk 82 are brought into contact with the pressure receiving surface, which is the lower side in FIG. Similar to the above valve seat 81,
It is assumed that it is fitted into the inner cavity 21a so as to be able to move upwardly, that is, to be slidable in the axial direction of the opening/end portion 2I.

The valve disc 82 has an annular groove 82c between the inner fixing part 82a and the outer seat part 82b, and the thick part of the valve disc 82 is passed through the annular groove 82c. The boat FI2d is opened.

Therefore, the pressure-side flat valve 8 in this embodiment has its inner peripheral end sandwiched between the inner peripheral fixed part 82a of the valve disk 82 and the annular seat part 81a of the valve seat 81, and its outer peripheral end is bent. Therefore, the outer circumferential end of the pressure side sub-valve 8 (when hydraulic pressure is applied, this will bend toward the side in the figure).
At this time, a predetermined flow rate of hydraulic oil is ensured.

The inner peripheral end side of the pressure side sub-valve 8 is sandwiched between the innermost inner peripheral side fixed part 82a and the annular seat part 8La slightly closer to the outer peripheral side, so that the IE side When the inner peripheral end of the sub-valve 8 is actively pressed against the inner peripheral fixing part 82a using the annular seat part 81a as a fulcrum, the outer peripheral end of the pressure-side sub-valve 8 makes a so-called ramming movement and pushes against the outer peripheral seat part of the valve disc 82. 82b, and the outside F of the pressure side Satsuharub 8
The amount of deflection of the L end is changed, and therefore the pressure side sub-valve 8
The flow rate of hydraulic fluid through the outer peripheral end of the valve will be changed to a decreasing tendency.

By the way, the hydraulic oil flowing out to the downstream side through the sub-valves 7 and 8 on each side flows through the communication holes 21b and 21c opened in the rod portion 21 and the spacer 50, 60, respectively. Perforated communication holes 50a, 6
The hydraulic pressure is assumed to flow into the hydraulic chamber 53, 63 through Oa.

Furthermore, hydraulic oil is allowed to flow into the piston main body 30 via the expansion side boat 30a and the compression side boat 30b, which are open to the piston body 30, respectively, to the upstream side of each side sub-valve 7.8.

That is, the second piston main body 44.30 has an extension side sub-boat 30c bored from the inner peripheral surface near the lower end of the piston main body 30 to the lower end surface of the piston main body 30, and also has A pressure side sub-boat 39d extends from the inner peripheral surface near the upper end to the L end surface of the piston body 30.
It is said that the hole may have been opened.

The sub-boats 3 (lc, 39d) on each side are as follows:
The inner peripheral surface of the piston body 30 or the adjacent rod portion 2
It communicates with communication holes 21d and 21e drilled in the slot 21, and also communicates with the inner space 21a of the rod portion 21 via the communication holes 21d and 21e.

Further, each side sub-boat 30c, 30d has an annular @3 formed on the upper and lower end surfaces of the piston main body 30, respectively.
0e, 30f and each side boat 30a, 30b
are connected to each other.

Furthermore, the space behind the valve seat 81 is communicated with the check valve 9 through an orifice 21f opened in the loft 21.

By the way, in this embodiment, the check valve 9 is provided continuously on the outer periphery of the tip pilot member 20 so as to cover the boundary between the rod portion 21 and the connecting portion 22 of the tip pilot member 20. The piston part 3 is disposed inside the casing 9°, and the hydraulic pressure from the lot side oil chamber A flows into the space behind the valve seat 81 during the extension stroke of the piston part 3 or cylinder l. It says it will prevent it from spreading.

That is, when the oil pressure in the lot side oil chamber A reaches the space behind the valve seat 81 during the extension stroke of the oil pressure Is# device, the check valve 9 shown in i- indicates that the valve seat 81 is This is provided in order to eliminate the problem that the expansion force from the piezoelectric element 4, which acts to lower the valve seat 81, does not work properly and the valve seat 81 does not perform a predetermined lowering operation.

It goes without saying that the specific structure of the check valve 9 is not limited to the so-called non-return valve type having a non-return blink as shown in the first embodiment.

In addition, the casing 90 housing the check valve 9 is provided with an oil chamber A on the mouth and bottom sides of the cylinder l, which is the inside and outside of the casing 90.
A boat 90a is opened to allow communication with the port.

Next, in this embodiment, there is a space 21a between the valve disc 72 and the valve disc 82.
A bushing block 40, which is slidably disposed within, is disposed.

Further, behind the valve seat 81, a bushing block 41 is slidably disposed within the space 21a.
or distributed.

A flock 42 is arranged between the bush block 41 and the piezoelectric element 4, which is the electrostrictive member.

Furthermore, steel balls 43 are disposed between the bushing block 40 and the valve disks 72, 82, and between the bushing block 41 and the valve seat 81 and block 42, respectively. 43, the expansion force generated from the piezoelectric element 4 is applied to each member when a predetermined voltage is applied to the piezoelectric element 4.

Therefore, in the hydraulic shock absorber according to this embodiment formed as described above, when the hydraulic oil passes through the boats on each side of the piston body 30: lOa, 30b, the respective hydraulic oil While flowing into the pressure receiving surface side of the side leaf valve 5.6, each sub-bow) -30c, 30d
to the pressure receiving surface side of each side sub-valve 7.8, and the hydraulic oil is formed on the back side of each side leaf valve 5, 6 through the side sub-valve 7.8. Therefore, the amount of deflection of the outer peripheral ends of the leaf valves 5.6 on each side is suppressed.

The amount of deflection of the outer peripheral end of each sub-valve 7.8 is controlled by applying a predetermined voltage to the piezoelectric element 4. In particular, in this embodiment, when the voltage applied to the piezoelectric element 4 is When the amount of deflection of the outer peripheral end of each side sub-valve 7, 8 is changed by application operation, the amount of oil supplied to the back of each side leaf valve 5.6, that is, the oil pressure, must be decreased. Therefore, the amount of deflection of the outer peripheral end of each side leaf valve 5, 6 is increased, and the damping force generated by each side leaf valve 5.6 is adjusted to decrease. It becomes C.

Each side leaf valve 5 is a damping valve on each side that generates a predetermined damping force on each side when the hydraulic shock absorber expands and contracts.
, 6, when a voltage is applied to the piezoelectric element 4, which is an electrostrictive member, the amount of deflection of the inner peripheral end thereof is changed, and the generated damping force is adjusted to be higher.

In that case, when voltage is applied to the piezoelectric element 4, the piezoelectric element 4
The expansion force generated from -1, each side sub-valve 7.8
The amount of deflection of the outer circumferential end of the sub-valve 7.8 is changed to limit the flow rate of hydraulic oil passing through the outer circumferential edge of each side sub-valve 7.8. Since the flow rate is changed and the main damping force on each side generated by the leaf valves 5 and 6 on each side is changed, the weight of the leaf valves 5 and 6 on each side is changed compared to the *weight of the piezoelectric element 4. It is possible to make the amount of deflection of the outer circumferential end extremely large, and therefore, the individual damping forces generated by each side leaf valve 5.6 can be adjusted over a wide range compared to the expansion edge of the piezoelectric element 4.
You will get it.

(Effect of the invention, L!L) According to the present invention, the expansion force generated from the piezoelectric element when voltage is applied to the piezoelectric element is
It acts to change the amount of circumferential deflection of each side sub-valve to control the flow rate of hydraulic oil passing through each side sub-valve, thereby changing the hydraulic pressure supplied to the back of each side leaf valve. Since the amount of deflection #a of the peripheral end of the side leaf valve is changed, it is possible to make the amount of peripheral end deflection of each side leaf valve extremely large compared to the expansion amount of the piezoelectric element, and therefore, This has the advantage that the damping force on each side generated by each side leaf valve can be adjusted over a wide range compared to the amount of expansion of the piezoelectric element.

[Brief explanation of drawings]

The drawing is a partial vertical sectional view showing a hydraulic #l# device according to an embodiment of the present invention. (Explanation of symbols) Engineering...Cylinder 2...Piston rod 4--Piezoelectric element 5, which is an electrostrictive member...Rebound side leaf hull pro, which is an expansion side damping valve...
・Compression side leaf valve 7, which is a damping valve on the compression side... Sub-valve 8 on the expansion side... Sub-valve 30 on the compression side... Piston body agent Patent attorney Izumi Amano

Claims (1)

[Claims] When a voltage is applied to a piezoelectric element, which is an electrostrictive member disposed in a piston rod inserted into a cylinder, the expansion force generated in the piezoelectric element is used to change the amount of deflection of the peripheral end of a leaf valve, which is a damping valve. In a damping force adjustment device formed to be able to adjust the main damping force generated by the valve, a rebound leaf valve, which is a damping valve on the rebound side, and a compression leaf valve, which is a compression damping valve, slide within the cylinder. They are arranged on the end face of the piston body, and are formed so that back pressure acts on the back surface of each side through the sub-valves on each side, and the sub-valves on each side are connected to the end of the piston rod. While being disposed within the tip spigot member, it supplies hydraulic pressure to the back surface of the leaf valves on each side, and changes the amount of deflection of each circumferential end using the expansion force generated in the electrostrictive member. a damping force adjusting device, characterized in that it is formed to be able to change the hydraulic pressure supplied to the damping force.