JP2004036753A - Hydraulic frictional force variable damper - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic frictional force variable damper which facilitates adjustment of damping force even after assembly, and enables automatic adjustment of frictional damping force corresponding to external forces and continuous appropriate damping control. <P>SOLUTION: In a hydraulic damper 1, a shaft member 2 and a cylindrical member 3 freely slidably fitted in the axial direction are configured to damp to adsorb an impact by a prescribed fluid resistance (a stop valve 11, or the like). Pressurized fluid is supplied between the shaft member 2 and the cylindrical member 3 through a pressure path L4. A limit member 6 such as a lock sleeve is tightened to increase fastening and fitting degree of the shaft member 2C to the cylindrical member 3B. The frictional force between the shaft member and the cylindrical member is adjusted by supply of prescribed fluid while developing the damper effect using hydraulic pressure. By so doing, the damping control by friction can be materialized. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a hydraulic damper in which a shaft member and a cylindrical member fitted slidably in the axial direction are configured so that shock is attenuated and absorbed by a predetermined fluid resistance, and is preferably an earthquake damper or the like. Applied to a vibration damper that quickly attenuates sudden vibrations.
[0002]
[Prior art]
BACKGROUND ART When a sudden vibration such as an earthquake occurs, a vibration damper is used to effectively attenuate a vibration of a building structure with respect to a foundation or a bridge with respect to a pier. Various types of vibration dampers have been proposed and used. The first conventional example shown in FIG. 3 is a hydraulic damper in which orifices are provided in the piston section between the hydraulic chambers on both sides of a cylinder defined by a piston section forming a shaft member. The pressure difference generated before and after the piston portion when oil flows through the orifice due to axial movement of the portion acts on the piston portion as a damping force. The piston-cylinder type hydraulic damper is effective in transmitting force and is frequently used for vehicles.
[0003]
The second prior art shown in FIG. 4 is composed of a cylinder unit in which hydraulic oil is sealed, a valve unit for generating a damping force, and a ball joint for attachment to a structure. The principle of operation is that when vibration is applied to a structure such as a building, the piston rod and the cylinder move relative to each other in the axial direction, and the hydraulic oil moves between the left and right pressure chambers through the externally configured valve unit. . At this time, damping force is obtained by using a fluid resistance that pushes out a pressure regulating valve installed in the valve unit, and high rigidity, high damping force and high durability can be obtained as a damper for buildings and civil engineering.
[0004]
Further, the third conventional example shown in FIG. 5 relates to an improved friction type damper, in which a sliding friction resistance at the time of relative axial movement between an outer cylinder and a rod is used as a damping force. is there. A disc spring and a wedge mechanism are employed for adjusting the frictional force. A preload in the thrust direction is applied by the disc spring, and a predetermined frictional force is obtained on the inner peripheral surface of the outer cylinder by the slider via the wedge mechanism. Thus, without using a medium such as oil, if the axial relative movement due to vibration occurs between the outer cylinder connected to the ground foundation and the rod connected to the upper structure side foundation, the axial The force is converted in the radial direction via the wedge mechanism, and a frictional force is applied between the inner peripheral surface of the outer cylinder and the slider in addition to the force caused by the preload, so that the vibration is effectively damped. Other examples of the vibration damper include an elastic-plastic hysteretic energy type such as a steel rod and a velocity proportional type using a magnetic viscous body.
[0005]
[Problems to be solved by the invention]
However, in such a conventional vibration damper, in the hydraulic damper in which the orifice is formed in the piston portion of the first conventional example, the damping force is flow-controlled depending on the diameter of the orifice. Although cheap, the performance was fixed. Further, in the hydraulic damper having the external valve unit using the pressure regulating valve of the second conventional example, it is possible to adjust the damping force by the pressure regulating valve to obtain high rigidity, high damping force and high durability. However, even when sudden vibration (displacement, force) due to an earthquake or the like is applied, effective damping control is sufficiently performed only by performing damping control with a predetermined damping force set by the pressure regulating valve. Did not. Further, in the improved friction type damper of the third conventional example, although the damping force can be adjusted by friction with a simple structure without using oil and by a function such as preloading, the damping force after assembly is obtained. Adjustment was troublesome because it was necessary to disassemble the damper. In addition, the elasto-plastic hysteretic energy type such as the steel rod is disadvantageous in restoring property, and the hydraulic damper using the magnetic viscous material is expensive and has poor practicality.
[0006]
Therefore, the present invention solves the above-mentioned problems in the conventional vibration damper, and makes it easy to adjust the damping force even after assembling, and to automatically adjust the friction damping force according to the external force. It is an object of the present invention to provide a hydraulic damper capable of always performing appropriate damping control.
[0007]
[Means for Solving the Problems]
For this reason, the present invention provides a hydraulic damper in which a shaft member and a cylindrical member fitted slidably in the axial direction are configured so that shock is attenuated and absorbed by a predetermined fluid resistance. The pressurized fluid is supplied between the cylinder member and the cylindrical member to increase the degree of engagement of the shaft member with the cylindrical member. Further, the present invention is characterized in that a limiting member for receiving a supply of pressurized fluid and fastening the shaft member is provided between the shaft member and the cylindrical member. Further, the invention is characterized in that the limiting member is constituted by arranging a plurality of divided members in the axial direction. Further, the present invention is characterized in that the supply of the pressurized fluid is performed by introducing a pressure increase caused by a relative axial movement between the shaft member and the cylindrical member. Further, in the present invention, the supply of the pressurized fluid is performed by introducing a set pressure of a counterbalance valve that opens by a pressure increase caused by a relative axial movement between the shaft member and the cylindrical member. It is characterized by comprising. Further, the present invention is characterized in that a stop valve or a throttle valve is installed in a pipe which is partitioned by a piston portion forming a shaft member and communicates between cylinder chambers forming a cylindrical member, and solving these problems. Means.
[0008]
Embodiment
Hereinafter, an embodiment of a hydraulic variable frictional damper of the present invention will be described in detail with reference to the drawings. FIG. 1 is an overall conceptual diagram and an enlarged view of a main part showing a first embodiment of a hydraulic frictional force variable damper of the present invention. As shown in FIG. 1 (A), the basic configuration of the present invention is such that the shaft member 2 and the cylindrical member 3 fitted slidably in the axial direction absorb shock by attenuated due to predetermined fluid resistance. In the hydraulic damper 1 configured as described above, the pressurized fluid is supplied between the shaft member 2 and the cylindrical member 3 to fasten the shaft member 2 (2C) to the cylindrical member 3 (3B). It is characterized in that the degree is increased.
[0009]
Details will be described below. The hydraulic damper 1 is configured by fitting a shaft member 2 and a cylindrical member 3 that are each hinged to a building structure or the like to each other. The shaft member 2 is composed of a piston portion 2B formed at a substantially central portion in the axial direction and having a large diameter, base portions 2A and tip portions 2C on both sides thereof, and a cylinder portion 3 is a cylinder that accommodates the piston 2B. It comprises a pressing portion 3B, which is a pressing lock portion 4 for applying a limiting force to the portion 3C and the distal end portion 2C of the shaft, and a base portion 3A for accommodating the distal end. Each portion 3A, 3B and 3C of the cylindrical member 3 may have the same diameter, but in the example shown in the figure, it is composed of a cylinder portion 3C having the largest diameter, a base portion 3A having a slightly smaller diameter, and a pressing portion 3B having a smallest diameter. I have.
[0010]
A first opening 9 and a second opening 10 are respectively formed in cylinder chambers 7 and 8 in a cylinder part 3C which is partitioned by the piston part 2B and constitutes a cylindrical member. Is connected. A counterbalance valve 12 is disposed at the junction via a first check valve 13 and a second check valve 14 that allow only the flow from these openings 9, 10. A pressure path L4 extends from the junction to the pressure lock portion 4 of the tubular member 3. The first opening 9 and the second opening 10 are connected via a stop valve 11. An accumulator 17 is disposed downstream (above the drawing) of the counterbalance valve 12 via a fifth check valve 18 and a throttle 19. The accumulator 17 is located near the junction of the counterbalance valve 12 and the accumulator 17. Third and fourth check valves 15 and 16 are provided which allow only the flow to the first opening 9 and the second opening 10.
[0011]
As shown in FIG. 1 (B), the pressurizing lock unit 4 receiving the supply of the pressurized fluid from the pressurizing path L4 is a pressurizing unit 3B which is a cylindrical member having the smallest diameter and formed integrally or as a separate member. It is composed of a pressurizing chamber 5 on the inner periphery, and a restricting member (lock sleeve) 6 made of steel or the like, which is further disposed on the inner peripheral side and closely fits on the outer periphery of the tip 2C of the shaft member. Preferably, the lock sleeve 6 is configured by arranging a plurality of divided pieces in the axial direction.
[0012]
The operation of the embodiment will be described below. When the stop valve 11 is closed and an external force is applied as shown by a white arrow in FIG. 1A, the cylindrical member 3 moves in the first cylinder chamber 7 by the axial movement of the shaft member 2 to the right in the drawing. , The first check valve 13 is pushed open to pressurize the front surface of the counterbalance valve 12 and at the same time pressurize the pressure chamber 5 in the pressurizing lock section 4 via the pressurizing path L4 to restrict the pressure. A certain frictional force is obtained by reducing the diameter of a certain lock sleeve 6 and tightening the tip 2C of the shaft member 2. At this time, the second check valve 14 is closed. When the external force exceeds a predetermined value, the pressure in the first cylinder chamber 7 reaches the predetermined value and the counter balance valve 12 is opened. Then, the first cylinder chamber 7 and the second cylinder chamber 8 communicate with each other via the third and fourth check valves 15 and 16 to circulate the pressure oil. Thereby, the frictional force obtained by pressurizing the pressure chamber 5 decreases, and the cylindrical member 3 moves with respect to the shaft member 2.
[0013]
If there is a sudden change in the flow rate due to an excessive external force, the fluid that has passed through the counterbalance valve 12 is absorbed into the accumulator 17 while absorbing the impact by the throttle 19. With the release of the external force, the accumulated fluid returns from the accumulator 17 to the first and second cylinder chambers 7 and 8 via the fifth check valve 18. The accumulator 17 is arranged such that a predetermined initial pressure is applied from the accumulator 17 to the fifth check valve 18, the third check valve 15, the first check valve 13, and the fourth check valve. 16, transmitted to the pressurizing path L4 via the second check valve 14, and can be provided with an initial lock. Thus, the damper 1 is properly controlled until the set value of the counter balance valve 12 is reached by using the cylinder chambers 7 and 8 as the detection unit, and controls the lock pressure (limit pressure) almost in proportion to the pressure to attenuate due to friction. The power can be controlled automatically. If the set value of the counter balance valve 12 is changed, the maximum lock limit pressure of the pressure lock unit 4 can be changed.
[0014]
When the stop valve 11 is opened, a damping operation of a predetermined damping value is performed through the first opening 9 and the second opening 10 below the set value of the opening of the counterbalance valve 12.
<Example>
Set pressure of counter balance valve: 500 kg / cm ²
Pressure receiving area of cylinder chambers 7 and 8: 20 cm ² each
Pressure lock mechanism: 5-ton holding force generation stroke at a pressure of 500 kg / cm ² : ± 20 cm
And when
When an external force of 10 t is applied, the pressure in the cylinder chamber 7 becomes P1 = 10 ton / 20 cm ² = 500 kg / cm ² . Therefore, a holding force of 5 ton is generated in the pressure lock unit 4 by P1 = 500 kg / cm ² . At the same time, the counterbalance valve 12 is opened, the pressure oil communicates with the cylinder chambers 7 and 8, and the applied holding force decreases. Assuming that the displacement of the external force is 75% of the stroke (15 cm = 20 × 0.75), the consumed energy is 5 ton × 15 cm = 75 ton · cm.
[0015]
FIG. 2 is an overall conceptual diagram showing a second embodiment of the hydraulic variable friction force damper of the present invention. The present embodiment is characterized in that a throttle valve 20 is installed in a conduit communicating between cylinder chambers 7 and 8 in a cylinder portion 3C constituting a cylindrical member. Therefore, in the present embodiment, by adjusting the opening degree of the throttle valve 20, the fluid between the cylinder chambers 7 and 8 is attenuated by the throttle valve 20 while the speed of the external force is within the set flow rate of the throttle valve 20. Flows, and the shaft member 2 and the cylindrical member 3 move relative to each other. When the speed of the external force exceeds the set flow rate of the throttle valve 20, a pressure difference of P1> P2 occurs on both sides of the throttle valve 20. When the set pressure of the counter balance valve 12 is P1, the counter balance valve 12 opens, and at the same time, a lock limiting pressure corresponding to the pressure P1 is generated in the pressurizing lock unit 4. Therefore, according to the present embodiment, the lock limit pressure can be obtained in response to the speed of the external force corresponding to the flow rate of the throttle valve 20 in association with the counterbalance valve 12.
[0016]
The embodiments of the present invention have been described above. However, within the scope of the present invention, the shapes and types of the shaft member and the cylindrical member, the fitting form as a hydraulic damper between them, the pressurized fluid Of the degree of engagement of the shaft member with the cylindrical member in response to the supply of the pressure member (in addition to the pressure lock for tightening the shaft member, the restricting member that can easily tighten the shaft member is expanded by the supply of pressurized fluid by spring pressure or the like) The pressureless lock type, which is configured to be axially movable, can be configured to release the pressureless lock by supplying a pressurized fluid generated according to the speed of the external force and tighten the shaft member.) Supply form of the pressurized fluid (the magnitude or speed of the external force may be detected by a sensor or the like, and the fluid may be pressurized according to the magnitude), and the shape of the lock sleeve as the restricting member ( Split steel May be constituted by one cylindrical wear-resistant resin member or one cylindrical metal member that is not divided, etc.), and the shape of the counterbalance valve. , The type and setting form of the set pressure, the related configuration between the piston portion and the cylinder portion that constitute the main damping section and divide the cylinder chamber, the shape of the conduit communicating between the cylinder chambers partitioned by the piston, The arrangement portion (which can be installed in the cylinder portion in addition to the external piping), and the shapes and types of the stop valve and the throttle valve can be appropriately adopted.
[0017]
【The invention's effect】
As described above in detail, according to the present invention, the shaft member and the cylindrical member slidably fitted in the axial direction are configured such that the shock is attenuated and absorbed by a predetermined fluid resistance. In the hydraulic damper described above, by supplying a pressurized fluid between the shaft member and the cylindrical member to increase the degree of engagement of the shaft member with the cylindrical member, a damper effect using hydraulic pressure is provided. While exerting the above, the frictional force between the shaft member and the cylindrical member is adjusted by receiving the supply of the pressurized fluid, so that the damping force can be controlled by the friction.
[0018]
Further, when a restricting member for receiving the supply of pressurized fluid and tightening the shaft member is provided between the shaft member and the cylindrical member, a simple method of introducing the pressurized fluid and tightening the restricting member is used. The friction force can be adjusted.
Further, when the limiting member is formed by arranging a plurality of divided limiting members in the axial direction, the edge of each inner peripheral end surface of the plurality of divided limiting members has a braking effect on the shaft member by the limiting member. Can be further enhanced.
Furthermore, in the case where the supply of the pressurized fluid is performed by introducing a pressure increase caused by a relative axial movement between the shaft member and the cylindrical member, a cylinder chamber or the like in the cylinder portion is provided. As the detection unit, a lock limiting force due to friction between the shaft member and the cylindrical member can be obtained according to the speed or magnitude of the external force, and appropriate damping force control is performed.
[0019]
Further, in the case where the supply of the pressurized fluid is performed by introducing a set pressure of a counterbalance valve that opens by a pressure increase caused by a relative axial movement between the shaft member and the cylindrical member. Is controlled appropriately until the set value of the counter balance valve is reached, and the damping force due to friction can be automatically controlled by controlling the lock pressure (limit pressure) almost in proportion to the pressure. Even after assembling, it is possible to change the set value of the counter balance valve to change the maximum lock limit pressure of the pressure lock unit.
[0020]
Further, when a stop valve is installed in a pipe defined by a piston portion constituting a shaft member and communicating between cylinder chambers constituting a cylinder member, the shaft member and the cylinder member are normally moved by opening the stop valve. The damper operates, and the stop valve is closed. The counter valve is properly controlled until it reaches the set value. The lock pressure (limit pressure) is controlled in proportion to the pressure to automatically reduce the damping force due to friction. Can be controlled.
Furthermore, when a throttle valve is installed in a pipe defined by a piston part forming a shaft member and communicating between cylinder chambers forming a cylindrical member, an external force corresponding to a flow rate of the throttle valve is associated with a counterbalance valve. The lock limit pressure can be obtained in response to the speed of the lock.
Thus, according to the present invention, it is possible to easily adjust the damping force even after assembling, and furthermore, it is possible to automatically adjust the friction damping force according to the external force, and to always perform appropriate damping control. A hydraulic damper is provided.
[Brief description of the drawings]
FIG. 1 is an overall conceptual diagram and a main part enlarged view showing a first embodiment of a hydraulic variable friction force damper of the present invention.
FIG. 2 is an overall conceptual diagram showing a second embodiment of the hydraulic variable friction force damper of the present invention.
FIG. 3 is a sectional view of a main part of a conventional orifice type hydraulic damper.
FIG. 4 is an overall sectional view of a conventional improved hydraulic damper.
FIG. 5 is an overall sectional view of a conventional friction damper.
[Explanation of symbols]
1, damper 2, shaft member 2A, base 2B, piston 2C, distal end 3, tubular member 3A, base 3B・ Pressure section 3C ・ ・ ・ ・ ・ ・ Cylinder section 4 ・ ・ ・ ・ ・ ・ Pressure lock section 5 ・ ・ ・ ・ ・ ・ Pressure chamber 6 ・ ・ ・ ・ ・ ・ Restriction member (lock sleeve)
7 First cylinder chamber 8 Second cylinder chamber 9 First opening 10 Second opening 11 Stop valve 12 Counter balance Valve 13 First check valve 14 Second check valve 15 Third check valve 16 Fourth check valve 17 Accumulator 18 ... Fifth check valve 19... Throttle 20... Throttle valve L4.

Claims (6)

In a hydraulic damper configured so that a shaft member and a cylindrical member slidably fitted in the axial direction are attenuated and absorbed by a predetermined fluid resistance, between the shaft member and the cylindrical member And a supply of pressurized fluid to increase the degree of engagement of the shaft member with the cylindrical member. The hydraulic friction variable damper according to claim 1, wherein a limiting member that receives a supply of pressurized fluid and tightens the shaft member is disposed between the shaft member and the cylindrical member. The hydraulic friction variable damper according to claim 2, wherein a plurality of divided members are arranged in the axial direction as the limiting member. 4. The pressure fluid supply system according to claim 1, wherein the supply of the pressurized fluid is performed by introducing a pressure increase caused by a relative axial movement between the shaft member and the cylindrical member. 2. The hydraulic friction variable damper according to 1. The pressurized fluid is supplied by introducing a set pressure of a counterbalance valve that opens due to a pressure increase caused by a relative axial movement between the shaft member and the cylindrical member. The hydraulic variable friction force damper according to any one of claims 1 to 3, wherein The hydraulic pressure according to any one of claims 1 to 5, wherein a stop valve or a throttle valve is installed in a pipe which is defined by a piston portion forming a shaft member and communicates between cylinder chambers forming a cylinder member. Variable friction force damper.

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