JPH03223537A - Damping force regulator - Google Patents

Abstract

PURPOSE:To facilitate an assembling operation by providing an extending side relief valve of an extending side damping valve, a force doubling piston for altering an flexing amount of the peripheral edge of the valve and a sub-valve for supplying oil pressure in a connecting member on the front end of a piston rod. CONSTITUTION:When a piston section 3 slides in a cylinder 1 and working oil in a rod side oil chamber A flows to an oil chamber B through a damping force generating section 5 in a connecting member 20 connected to a piston rod 2, the peripheral end of an extending side relief valve 50 is flexed to generate an extending side damping force. When predetermined voltage is then applied to a piezo-electric element 4, a deflection amount of the peripheral end of a subvalve 60 in a back pressure regulating section 5 is restrained small and oil pressure generated and raised acts on a force doubling piston 53 so that a deflection amount of the peripheral end of the extending side relief valve 50 is altered to regulate the extending side damping force. Since a damping force regulator is disposed in a connecting member screwed in the front end of the piston rod in this way the regulator can be assembled with its easy assembling operation.

Description

Detailed Description of the Invention (Industrial Application Field) This invention uses a piezoelectric element as an electrostrictive member to change the deflection of the peripheral end of a rebound leaf valve as a rebound damping valve, thereby increasing the rebound damping force. The present invention relates to an improvement of a damping force adjustment device that can adjust the damping force.

(Prior art and its problems) A damping force adjustment device for a hydraulic shock absorber, which expands the piezoelectric element by applying a voltage to a piezoelectric element, which is an electrostrictive member, to create a flexible seam at the peripheral end of a leaf valve, which is a decay valve. "C" is formed so that the damping force generated by the leaf valve can be adjusted by changing the leaf valve. The proposed method has the disadvantage that the adjustment of the damping force cannot be made as large as when the piezoelectric element is deformed.

That is, this N conventional proposal directly changes the bending stitch at the peripheral end of the leaf valve, which is a damping force valve, by the expansion force generated in the piezoelectric element F when a voltage is applied to the piezoelectric element F, which is an electrostrictive member. Accordingly, the damping force generated by the leaf valve is adjusted in height.

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

It is not possible to change the deflection noise at the circumferential end of the leaf valve by more than the expansion amount of the element, and therefore, when a large deflection noise is required at the circumferential end of the leaf valve, the pressure "e" element is connected in series. Therefore, there is a risk that the axial length of the entire damping force adjustment device will be increased.

Therefore, the present application is directed to adjusting the generated damping force by first increasing the deflection of the peripheral end of the leaf valve, which is the damping valve, compared to the expansion of the piezoelectric element, which is the electrostrictive member.
We have proposed a damping force adjustment device that increases the It is not formed so that only the side damping force can be adjusted.

Also, according to the proposal mentioned above, only the damping force adjustment on the rebound side was adjusted to 1liT.
In order to make this possible, it is undesirable to simply disable the part that adjusts the damping force on the compression side, as this will result in dead stock of fll material. Therefore, a separate proposal for a damping force adjustment device on the rebound side is requested. will be done.

This invention was devised in view of the circumstances mentioned in Section 1, and its purpose is to expand the piezoelectric element f-, which is an electronic component, and to reduce the expansion-side eclipse of the expansion-side leaf. It is possible to increase the deflection of the peripheral end of the valve, and
It is an object of the present invention to provide a damping force adjusting device that has a structure with r* width and can increase the J1 width of the rebound damping force.

[Means to solve the problem]

1-In order to solve the above-mentioned [1], the configuration of the present invention is modified such that when a voltage is applied to a piezoelectric element, which is an electrostrictive member disposed in a piston rod inserted into a cylinder, the voltage generated in the piezoelectric element is In a damping force adjusting device formed to be able to adjust the damping force generated by the leaf valve by changing the stack of the circumferential end of the leaf valve, which is a damping valve, by the expansion force of the expansion side damping valve, A leaf hartz, a booster piston that changes the circumferential deflection amount of the extension side leaf valve, and a sub-valve that supplies increased hydraulic pressure to the booster piston are arranged in a connecting member connected to the tip of the piston rod. It is characterized by:

The expansion side leaf hart which is the expansion side damping hartz is composed of an annular leaf valve, and generates a predetermined expansion side damping force when the inner peripheral end of the expansion side leaf valve is deflected, and the inner peripheral end of the expansion side leaf valve Suppose that the damping force generated is adjusted to a higher tendency when the deflection of the damper is changed.

In addition, the sub-valve consists of an annular leaf valve, and
It is assumed that when a predetermined voltage is applied to the piezoelectric element, which is an electrostrictive member, the amount of deflection of the inner peripheral end of the piezoelectric element is suppressed to supply increased hydraulic pressure to the upstream side of the sub-valve, that is, to the back side of the 1x capiston.

Furthermore, it is assumed that the 1x capiston moves forward when high hydraulic pressure is supplied to its back surface to change the amount of deflection of the inner circumferential end of the expansion side leaf valve.

(Function) Therefore, when the piston part slides within the cylinder, the hydraulic oil from the rod-side oil chamber flows into the piston-side oil chamber via the damping force generating part in the connecting member connected to the piston rod. When flowing out, the hydraulic oil causes the circumferential edge of the growth-side leaf heart to flex, and at that time, a predetermined rebound-side damping force is generated.

When a predetermined voltage is applied to the piezoelectric element, which is an electronic component, at the time of 1-, the amount of deflection of the circumferential end of the sub-valve in the back pressure adjustment section is suppressed to a small level, thereby increasing the hydraulic pressure. This causes the booster piston to slide and change the amount of deflection of the peripheral end of the rebound leaf valve, which is the rebound damping valve. The expansion damping force generated by the leaf valve is adjusted by +tj of the expansion tool E of the piezoelectric element.

Moreover, when the application of a predetermined voltage to the piezoelectric sf is released,
The deflection of the peripheral end of the sub-valve is eliminated, and the high hydraulic pressure acting on the back of the 1x capiston is also eliminated, so the force exerted by the 1x capiston is released and the expansion side leaf valve, which had been changed until then, is The deflection of the inner circumferential end is restored to its old state, and the damping force generated by the expansion side leaf harness is returned to the initially set magnitude.

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

As shown in the drawings, a hydraulic shock absorber according to an embodiment of the present invention has a piston rod 2 inserted into a cylinder l so as to be freely retractable and protrusive. 1- The cylinder 1 is divided into a rod-side oil chamber A and a piston-side oil chamber B, and has a piston portion 3 that slides within the cylinder 1.

The hydraulic shock absorber includes a piezoelectric element 4, which is an electrostrictive member, in a through hole 2a formed in the axial center of the piston rod 2.

The piezoelectric J-f 4, which is the electrostrictive member, may include
The Riet wires are connected to each other, and the ends of the Riet wires protrude to the outside from the projecting end of the piston rod 2, which is the upper end in the drawing.

The piezoelectric element 4, which is the electrostrictive member, expands when a predetermined voltage is applied thereto, and as described later, the expansion-side damping force is adjusted by the expansion force.

In the illustrated example, the tension 1 & 1 described in 1 is developed in such a way that the tip of the piezoelectric element 4, which is the end in the figure, moves downward in the figure.

On the other hand, in the hydraulic shock absorber 1-, a connecting member 20 is connected to the tip of the piston rod 2, and the piston main body 30 of the piston portion 3 is screwed onto the outer periphery of the connecting member 20. A rebound damping force generating section 5 and a back pressure adjustment PJ 6 are arranged inside the pump 20.

That is, in the embodiment shown in FIG. 1, the connecting member 20 has a partition wall 20a on the inner periphery of the intermediate portion thereof, and has a distal end portion 21 which is on the ΦF end side in the figure and a base end portion 22 which is on the upper end side in the figure. It is formed in such a way that it is divided into

The expansion side damping force generating section 5 is disposed inside the distal end section 21, while the back pressure adjusting section 6 is disposed inside the proximal end section 22.

In this embodiment, the piston main body 30 is formed by a boat 30a 41 and has a thief valve 30b in the boat 303, or the thief valve 5f] Ob
, the hydraulic oil is allowed to flow from the piston side oil chamber B to the port/seat side oil chamber A via the boat Oa, or the opposite flow is prevented, and the boat 30a is the pressure side boat. It is set as follows.

That is, in this embodiment, the piston portion 3 is connected to the cylinder l.
When the hydraulic shock absorber is operated on the extension side, the hydraulic shock absorber moves upward by L, the hydraulic oil from the rod side oil chamber A flows into the piston side oil chamber B via the back pressure adjustment section 6 and the extension side reduction force generation section 5, which will be described later. It is shaped like this.

By the way, in this embodiment, the growth-side damping force generating section 5 includes a growth-side leaf valve 50 which is a growth-side damping valve made of an annular leaf valve. l- Annular seat 8851 a of the annular valve seat 51 screwed onto the tip 11 of the light distribution end 21
It comes into contact with the

In addition, the annular seat 151a is placed close to the outer peripheral end of the expansion side leaf valve 511 so that the annular seat 151a is in contact with the back surface of the expansion side leaf valve 50.
It is formed protrudingly on the L-flow side of 1.

On the other hand, the expansion side leaf hull 50 (1) has an inner circumferential annular seat m 52 a protrudingly formed on the downstream side of the valve disk 52 and an outer circumferential annular fixing portion 52 b that are brought into contact with each other on its pressure receiving surface.

Incidentally, the F valve disk 52 is disposed within the distal end portion 2I so as to be slidable in the axial direction of the distal end portion 21.

The E-marked valve disk 52 has an annular groove 52c between the -h-oriented circumferential annular seat portion 52a and the outer circumferential annular fixing portion S2b, and the annular groove 52c has a wall thickness of the valve disk 52. A boat 52d passing through the section is opened.

Therefore, the expansion side leaf valve 50 in this embodiment is
Its outer peripheral end side is held between the outer peripheral side annular fixing portion 52b of the valve disc 52 and the annular seat 151a of the valve seat 51, and its inner peripheral end is fixed in a flexible manner. When hydraulic pressure acts on the inner circumferential end of the expansion side leaf valve 50, this bends downward in the figure, and at that time, it is possible to generate a predetermined expansion side reducing a force.

However, since the outer peripheral end side of the expansion side leaf heart 50 is held between the outermost outer peripheral side annular fixing part 52b and the annular seat part 51a slightly closer to the inner periphery, the expansion side leaf heart 50 is pressed by the outer circumferential side annular fixing part S2b using the annular seat part 51a as a fulcrum, the inner circumferential edge of the expansion side leaf heartz 50 or the so-called ram M
The leaf valve 50 moves and is pressed against the inner circumferential annular seat portion 52a of the valve disc 52, thereby changing its bending radius, and therefore, the damping force generated by the expansion leaf valve 50 is changed to a higher tendency. Become.

By the way, a booster piston 53 is adjacent to the -L flow side end surface of the Hartz disk 52 via a steel ball S as an alignment structure, and the booster piston 53 acts in a downward direction in the figure. The acting force of the Harz disk 5
2, it is configured to act on the inner circumferential end of the expansion side leaf heartz 50.

That is, the booster piston 53 passes through the center of the partition wall 20a from the tip that is the upper end of the shaft portion 53a in the figure ΦF to the tip portion 2.
1, the outer periphery of the collar portion 53b is in sliding contact with the inner periphery of the proximal end portion 22, and the shaft portion 53a is disposed within the proximal end or the distal end 1811zt, which is the upper end side in the figure. 11 are inserted through the center of the bottom of the housing 54, which has a rounded bottom and houses a back pressure adjustment 79B6, which will be described later.

On the other hand, the L2 double capiston 53 has a transparent
The lower end of the 1M through hole 53C communicates with the inside of the tip portion 21, that is, the upstream side of the valve disc 52, via the horizontal hole 53d, and the upper end of the through hole 5]c communicates with the housing 54. If it communicates with the inside, there is "C".

In addition, the 1-doubling capiston 53 has a pressure chamber R adjacent to the back pressure surface, which is one end surface 1 in the figure, of the collar portion 53b, and the pressure chamber R is located inside the cylinder 1, which is an upstream oil chamber. It communicates with the lot side oil chamber A, and also communicates with the back pressure adjustment part 6 in the L housing 54.

That is, the connecting member 20 has a communication hole 22a in the base end 22.
The cylinder l is opened through the communication hole 22a.
The inner rod side oil chamber A and the inner side of the base end portion 22, that is, the pressure chamber R indicated by L, can communicate with each other, and the housing 54 is also provided with a communication hole 54a. Communication between the inside of the housing 54 and the pressure chamber R is possible through the communication hole 54a.

By the way, 1v housed in the housing 54
The pressure adjustment section 6 is formed so as to be able to supply high oil pressure to the pressure chamber R.

That is, in this invention, the back pressure adjustment section 6 is as follows.

This sub-valve 60 has an annular valve seat 61 similar to the expansion-side leaf valve 50 which is the expansion-side damping valve described above.
With the intervention of the valve disc 62, the bending edge of the inner peripheral end is changed.

By suppressing the amount of deflection of the inner peripheral end of the sub-valve 60, a high hydraulic pressure is supplied to the upstream side thereof, that is, the pressure chamber R.

That is, the sub-valve 60 has the annular seat part 61a of the annular valve seat 61 in contact with the back surface near the outer peripheral end, and the inner annular seat part 62a of the valve disc 62 and the outer annular fixed part on the pressure receiving surface. The inner circumferential end is fixed in a free form via the outer circumferential end n, and the inner circumferential end is pressed against the valve disc 6 by making contact with the valve disc 62b.
It is pressed against the inner peripheral side annular sheet 162a of No. 2 to change its deflection scale.

The valve disc 62 is disposed within the housing 54 so as to be able to slide in the axial direction of the housing 54, that is, in the vertical direction in the figure, while the valve disc 62 is arranged so as to be slidable in the axial direction of the housing 54, that is, in the vertical direction in the figure. A boat 62d has an annular groove 62c between it and the side annular fixing part 62b, and penetrates the flesh H of the valve disk 62 into the annular groove 62c.
It is said that it will be opened.

Incidentally, the F valve disk 62 is set to move downward in the figure by the expansion force generated from the piezoelectric element 4 when a predetermined voltage is applied to the piezoelectric element 4, which is the electric φ member. J-, Pressure distribution "The expansion force from the R element 4 acts on the L flow side end of the valve disc 62 via the bushing rod 40 and the steel ball S located between the valve discs 62. It is said that

Further, the force generated from the pressure R f4 is propagated to the bushing rod 40 via the bushing flock 41 and the steel ball S.

Incidentally, the four-shaped Harz sheet 61 is secured to the bottom of the housing 54 at its downstream end.

Therefore, in the hydraulic slack #i'IA according to this embodiment formed as shown in E, the back pressure can be adjusted! ! 6, a booster piston 53 connected thereto, and a rebound damping force generating section 5 that adjusts the rebound damping force generated by the booster piston 53, forming the damping force adjustment device of the present invention. At the same time, the damping force 31gM device is housed in a connecting member 2o screwed onto the tip of the piston port 2, and the damping force adjusting device is assembled into a so-called assembly. Become Ofo.

The expansion side leaf valve 50 is a side damping valve that generates a predetermined expansion side damping force during the expansion and contraction operation of the hydraulic shock absorber.
When a voltage is applied to the piezoelectric element 41\, 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 tend to be high.

In that case, when voltage is applied to the piezoelectric element 4, the piezoelectric element 4
The expansion force generated from -1 changes the amount of deflection of the inner peripheral end of the sub-valve 60 and increases the amount of hydraulic fluid tNkk? that passes through the inner peripheral end of the sub-valve 60. 'tA limit, and the high hydraulic pressure generated by this acts on the boost piston 53, whereby the boost piston 5 moves forward and the amount of deflection of the inner circumferential end of the expansion side Leaf Harz 50, which is the expansion side damping valve, is reduced. Therefore, the amount of deflection of the inner circumferential end of the expansion side leaf hartz 50 is extremely large compared to the expansion force of the L piezoelectric element 4, and therefore, the expansion side capital reduction generated in the expansion side leaf hartz 50 is This means that the force can be adjusted over a wider range than the *grit of the piezoelectric element 4, which is an electrostrictive member.

The hydraulic oil that has passed through the inner circumferential end of the sub-valve 60 flows out through the through hole 53c of the booster piston 53 and the horizontal hole 51d to the side of the valve disc 52 adjacent to the expansion side leaf valve 50. .

(Effects of the Invention) As described above, according to the present invention, when a voltage is applied to the piezoelectric element, which is an electrostrictive member, the pressure i! It is possible to make the deflection force at the peripheral end of the rebound leaf valve extremely large compared to the expansion force generated by the element, and therefore the rebound damping force generated by the rebound leaf valve can be controlled over a wide range. Of course, it is possible to adjust J1 by adjusting the back pressure m rod part, the booster piston, and the rebound damping force generating part that constitute the damping force adjustment device, or in the connecting member screwed to the tip of the piston rod. Assuming that the damping force adjustment device is installed in a become, etc.
It has many effects.

[Brief explanation of drawings]

The drawing is a partial longitudinal sectional view showing a hydraulic Ith device according to an embodiment of the present invention. (Explanation of symbols) l...Cylinder 2...Piston loft 4...Piezoelectric element 20, which is an electrostrictive member...Connection member 50...Rebound side leaf valve 53, which is an expansion side damping valve.
...Boosting piston 60...Sub valve agent Izumi Amano 2.
1 - T - Continued 7 City 1 - "Book (Method) + 1 Table 2 Year 5 No. 19 Day 1.1 Display of Shiji 1? 2000 Patent Application No. 16757 2, Name of Invention M Means Adjustment Device 3 , Supplement 11-Relationship with Matter 1G Patent Applicant Address Name (092) Kaya Hachiryo Co., Ltd., 11th Director Address Kyobashi 2-chome, Chuo-ku, Tokyo [15-2 Corner - Building f]
F, L (561) 5124~5 names (67 6)
Patent Attorney Izumi Amano 5, Supplement 11-Instruction with +1 +i-I&, April 2, 2411 (Dispatch I) 6, Supplement + Subject Attachment (1) Specifications page 1, line 17, ``30 inventions'' ``Name of the invention'' is corrected to ``3. Detailed description of the invention''.

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 changes the amount of deflection of the peripheral end of a leaf valve, which is a damping force valve. In a damping force adjustment device formed to be able to adjust the damping force generated by the leaf valve, the expansion side leaf valve is an expansion side damping valve, and the expansion side leaf valve is configured to change the peripheral end deflection amount of the expansion side leaf valve. A damping force adjusting device characterized in that a power piston and a sub-valve for supplying increased hydraulic pressure to the booster piston are arranged in a connecting member connected to the tip of a piston rod.