JP4312426B2 - Hydraulic friction variable damper - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a hydraulic damper configured such that a shaft member and a cylindrical member, which are slidably fitted in an axial direction, are attenuated and absorbed by a predetermined fluid resistance, and preferably an earthquake or the like. It is applied to a damping damper that quickly attenuates sudden vibrations.
[0002]
[Prior art]
When a sudden vibration such as an earthquake occurs, a vibration damping damper is used to effectively attenuate the vibration of the building structure with respect to the foundation and the bridge with respect to the 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 an orifice communicating between hydraulic chambers on both sides in a cylinder defined by a piston portion constituting a shaft member is formed in the piston portion. The pressure difference generated before and after the piston part when oil flows through the orifice due to the axial movement of the part acts on the piston part as a damping force. Piston / cylinder type hydraulic dampers are efficient in transmitting force and are often used for vehicles.
[0003]
The second conventional example shown in FIG. 4 is composed of a cylinder unit in which hydraulic oil is sealed, a valve unit that generates a damping force, and a ball joint for attachment to a structure. The operating principle is that when vibration is applied to a structure such as a building, relative movement in the axial direction occurs between the piston rod and the cylinder, and hydraulic oil moves between the left and right pressure chambers through a valve unit with an external configuration. . At that time, a damping force is obtained by utilizing 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 building or civil engineering damper.
[0004]
Furthermore, the third conventional example shown in FIG. 5 relates to an improved friction damper, which uses the sliding frictional resistance during relative axial movement between the outer cylinder and the rod 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 to the inner peripheral surface of the outer cylinder is obtained on the slider via the wedge mechanism. Thus, if relative movement in the axial direction occurs due to vibration between the outer cylinder connected to the foundation on the ground side and the rod connected to the foundation on the upper structure side without using a medium such as oil, the axial direction 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 preload, and the vibration is effectively damped. In addition, as the damping damper, there are an elastic-plastic hysteresis energy type such as a steel rod, a speed proportional type using a magnetic viscous material, and the like.
[0005]
[Problems to be solved by the invention]
However, in such a conventional damping damper, in the hydraulic damper having an orifice formed in the piston portion of the first conventional example, the damping force is controlled in flow rate depending on the diameter of the orifice, Although it was 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, the damping force can be adjusted by the pressure regulating valve, and high rigidity, high damping force and high durability can be obtained. However, even when a sudden vibration (displacement, force) due to an earthquake or the like is applied, only the damping control by the predetermined damping force set by the pressure regulating valve is performed, and the effective damping control is sufficiently performed. There wasn't. Further, the improved friction type damper of the third conventional example has a simple configuration without using oil, and the damping force by friction can be adjusted by a function such as preloading. This adjustment was troublesome because it was necessary to disassemble the damper. In addition, the elastic-plastic hysteretic energy type such as the steel rod is disadvantageous in terms of resilience, and the hydraulic damper using a magnetic viscous material is expensive and lacks practical utility.
[0006]
Therefore, the present invention solves the problems in the conventional vibration damping damper as described above, makes it easy to adjust the damping force even after assembly, and automatically adjusts the friction damping force according to the external force. It is an object of the present invention to provide a hydraulic damper that is capable of always performing appropriate damping control.
[0007]
[Means for Solving the Problems]
Thus the present invention provides a configured hydraulic damper as the shaft member and the cylindrical member slidably fitted in the axial direction is impact attenuated absorbed by a given fluid resistance, the In the hydraulic damper configured to receive a supply of pressurized fluid between the shaft member and the tubular member and increase the degree of fastening and fitting of the shaft member to the tubular member, the supply of the pressurized fluid is performed between the shaft member and the tubular member. It is characterized in that it is constructed by introducing a pressure increase caused by a relative axial movement with the cylindrical member . Further, the present invention is characterized in that a limiting member is provided between the shaft member and the tubular member to receive the pressurized fluid and tighten the shaft member. Further, the present invention is characterized in that a plurality of divided members are arranged in the axial direction as the restricting member . Or the invention, so that the supply of pressurized fluid, is made by introducing a relative axial set pressure of a counter balance valve which is opened by the pressure rise caused by the 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 line that communicates between cylinder chambers that are partitioned by a piston portion that constitutes a shaft member and constitutes a cylindrical member. As a means for
[0008]
Embodiment
Embodiments of the hydraulic friction variable damper according to the present invention will be described below 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 friction force variable damper of the present invention. As shown in FIG. 1 (A), the basic configuration of the present invention is that the shaft member 2 and the cylindrical member 3 fitted so as to be slidable in the axial direction are attenuated and absorbed by a predetermined fluid resistance. In the hydraulic damper 1 configured as described above, when the pressurized fluid is supplied between the shaft member 2 and the cylindrical member 3, the shaft member 2 (2C) is fastened to the cylindrical member 3 (3B). It is characterized by being configured to increase the degree.
[0009]
This will be described in detail below. The hydraulic damper 1 is configured by fitting a shaft member 2 and a tubular member 3 that are hinged to a building structure or the like, respectively. The shaft member 2 includes a piston portion 2B having a large diameter portion formed at a substantially central portion in the axial direction, a base portion 2A on both sides thereof, and a tip portion 2C, and the cylindrical portion 3 is a cylinder that accommodates the piston 2B. It is composed of a pressing portion 3B that is a pressing lock portion 4 that applies a limiting force to the portion 3C and the tip portion 2C of the shaft, and a base portion 3A that houses the tip. The portions 3A, 3B and 3C in the cylindrical member 3 may have the same diameter, but in the example shown in the figure, the cylinder portion 3C having the largest diameter, the base portion 3A having a slightly smaller diameter, and the pressure portion 3B having the smallest diameter are configured. Yes.
[0010]
A first opening 9 and a second opening 10 are respectively bored in cylinder chambers 7 and 8 in a cylinder portion 3C that is partitioned by the piston portion 2B and constitutes a cylindrical member. Is connected. A counter balance valve 12 is disposed at a junction through a first check valve 13 and a second check valve 14 that allow only the flow from the openings 9 and 10. A pressurizing path L4 extends from the junction point to the pressurizing lock portion 4 in the cylindrical member 3. The first opening 9 and the second opening 10 are connected via a stop valve 11. An accumulator 17 is disposed downstream of the counter balance valve 12 (above the drawing) via a fifth check valve 18 and a throttle 19, and in the vicinity of the junction of the counter balance valve 12 and the accumulator 17, the first Third and fourth check valves 15 and 16 that allow only flow to the first opening 9 and the second opening 10 are provided.
[0011]
As shown in FIG. 1 (B), the pressurizing lock portion 4 that receives the supply of the pressurized fluid from the pressurizing passage L4 is a pressurizing portion 3B that is a cylindrical member having the smallest diameter constituted by an integral or separate member. It is composed of an inner peripheral pressurizing chamber 5 and a restricting member (lock sleeve) 6 made of steel or the like that is disposed on the inner peripheral side and closely fits to the outer periphery of the tip end portion 2C of the shaft member. Preferably, the lock sleeve 6 is configured by arranging a plurality of divided sleeves in the axial direction.
[0012]
The operation of this embodiment will be described below. When the stop valve 11 is closed, when an external force is applied as indicated by the white arrow in FIG. 1A, the cylinder member 3 moves in the first cylinder chamber 7 by the axial movement of the shaft member 2 to the right in the drawing. Pressure rises, the first check valve 13 is pushed open to pressurize the front surface of the counter balance valve 12, and at the same time, the pressure chamber 5 in the pressurization lock portion 4 is pressurized via the pressurization path L4. A predetermined friction force is obtained by reducing the diameter of a certain lock sleeve 6 and tightening the distal end portion 2 </ b> C 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 set 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 through 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 relative to the shaft member 2.
[0013]
When there is a rapid flow rate change due to an excessive external force, the fluid that has passed through the counter balance valve 12 is absorbed into the accumulator 17 while the impact is absorbed by the throttle 19. As the external force is released, the accumulated fluid returns from the accumulator 17 to the first and second cylinder chambers 7 and 8 via the fifth check valve 18. Further, the accumulator 17 is arranged so 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, it is transmitted to the pressurizing path L4 through the second check valve 14, and an initial lock can be applied. Thus, the damper 1 is appropriately controlled until the set value of the counter balance valve 12 is reached using the cylinder chambers 7 and 8 as the detection unit, and the lock pressure (limit pressure) is controlled almost in proportion to the pressure to attenuate by 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 pressurization lock unit 4 can be changed.
[0014]
When the stop valve 11 is opened, a damper operation with a predetermined attenuation value is performed through the first opening 9 and the second opening 10 below the set value for opening the counter balance valve 12.
<Example>
Set pressure of counter balance valve: 500Kg / 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
When
When the external force 10t is applied, the pressure in the cylinder chamber 7 is P1 = 10 ton / 20 cm ² = 500 Kg / cm ² . Therefore, a holding force of 5 tons is generated in the pressure lock unit 4 by P1 = 500 Kg / cm ² . At the same time, the counter balance valve 12 is opened, pressure oil communicates with the cylinder chambers 7 and 8, and the applied holding force decreases. If the displacement of the external force is 75% of the stroke (15 cm = 20 × 0.75), the energy consumption is 5 ton × 15 cm = 75 ton · cm.
[0015]
FIG. 2 is an overall conceptual view showing a second embodiment of the hydraulic friction variable damper of the present invention. The thing of this Embodiment has installed the throttle valve 20 in the pipe line which connects between the cylinder chambers 7 and 8 in the cylinder part 3C which comprises a cylinder member, It is characterized by the above-mentioned. Therefore, in the present embodiment, by adjusting the opening 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 is opened, and at the same time, a lock limit pressure corresponding to the pressure P1 is generated in the pressurization lock unit 4. Therefore, in the present embodiment, the lock limit pressure can be obtained in association with the counter balance valve 12 in response to the speed of the external force corresponding to the flow rate of the throttle valve 20.
[0016]
The embodiments of the present invention have been described above. However, within the scope of the present invention, the shape and type of the shaft member and the cylindrical member, the fitting form as a hydraulic damper between them, the pressurized fluid The degree of tightening and fitting of the shaft member to the cylindrical member is increased (in addition to the pressurization lock that tightens the shaft member, the shaft member is tightened and the restricting member that can be easily tightened is expanded by supplying pressurized fluid such as spring pressure) The non-pressure lock type that can be axially moved can also be configured to release the non-pressure lock and tighten the shaft member by supplying pressurized fluid generated according to the speed of the external force) , Pressurized fluid supply form (can be configured to pressurize the fluid according to the magnitude or speed of the external force detected by a sensor or the like), the shape of the lock sleeve as the limiting member ( Split steel In addition to the arrangement of a plurality of the above, it may be constituted by one cylindrical wear-resistant resin member or one non-divided cylindrical metal member), the shape of the counter balance valve , Type and setting form of the set pressure, related configuration between the piston part and the cylinder part that constitute the main damping part and divide the cylinder chamber, the shape of the pipe line communicating between the cylinder chambers divided by the piston, The arrangement site (can be installed in the cylinder portion in addition to the external piping), the shape and the form of the stop valve and the throttle valve, etc. can be appropriately employed.
[0017]
【The invention's effect】
As described above in detail, according to the present invention, the shaft member and the cylindrical member that are slidably fitted in the axial direction are configured so that the impact is attenuated and absorbed by a predetermined fluid resistance. and a hydraulic damper, in a hydraulic damper configured to increase the fastening fitting degree of the shaft member relative to the tubular member by being supplied with the pressurized fluid between the shaft member and the tubular member, said pressure Since the pressurized fluid is supplied by introducing a pressure increase caused by the relative axial movement between the shaft member and the tubular member, the damper effect using the hydraulic pressure is exerted while adding pressure. by adjusting the frictional force between the shaft member and the cylindrical member by being supplied with fluid, Ri Do enables the damping force control by the friction, as a detection unit of the cylinder chamber and the like in the cylinder unit, the rate or magnitude of the external force Depending on the length of the shaft member and the cylindrical member To be able to obtain a lock limiting force of frictional, proper damping force control is performed.
[0018]
In addition, when a restricting member that tightens the shaft member by receiving the supply of pressurized fluid between the shaft member and the cylindrical member is disposed, it is a simple method that simply introduces the pressurized fluid and tightens the restricting member. The frictional force can be adjusted.
Furthermore, when the plurality of divided members are arranged in the axial direction as the restricting member, the edge portion of each inner peripheral side end surface of the divided plurality of restricting members is the braking effect of the shaft member by the restricting member. Ru can be further improved.
[0019]
Further, when the pressurized fluid is supplied by introducing a set pressure of a counter balance valve that opens due to a pressure increase caused by a relative axial movement between the shaft member and the cylindrical member. Is properly controlled until the set value of the counter balance valve is reached, and the damping pressure due to friction can be controlled automatically by controlling the lock pressure (limit pressure) in proportion to the pressure. Even after assembly, it is possible to change the set value of the counter balance valve to change the maximum lock limit pressure of the pressurization lock unit.
[0020]
Further, when a stop valve is installed in a pipe line that is defined by the piston portion that constitutes the shaft member and communicates between the cylinder chambers that constitute the cylinder member, the shaft member and the cylinder member are normally separated by opening the stop valve. Damper operation is performed until the counter balance valve set value is reached by closing the stop valve, and the damping pressure due to friction is automatically controlled by controlling the lock pressure (limit pressure) in proportion to the pressure. Can be controlled.
Furthermore, when a throttle valve is installed in a pipe line that is defined by the piston portion constituting the shaft member and communicates between the cylinder chambers constituting the cylindrical member, an external force corresponding to the flow rate of the throttle valve is associated with the counter balance valve. The lock limit pressure can be obtained in response to the speed.
Thus, according to the present invention, the damping force can be easily adjusted even after assembly, and the friction damping force can be automatically adjusted according to the external force, so that appropriate damping control can always be performed. A hydraulic damper is provided.
[Brief description of the drawings]
FIG. 1 is an overall conceptual diagram and an enlarged view of a main part showing a first embodiment of a hydraulic friction variable damper of the present invention.
FIG. 2 is an overall conceptual diagram showing a second embodiment of a hydraulic friction variable damper according to the present invention.
FIG. 3 is a cross-sectional view of a main part of a conventional orifice type hydraulic damper.
FIG. 4 is an overall cross-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 ... Tip 3 ... Cylindrical member 3A ... Base 3B ...・ Pressure part 3C ・ ・ ・ ・ Cylinder part 4 ・ ・ ・ ・ Pressure lock part 5 ・ ・ ・ ・ Pressurization 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 ... Pressure passage

Claims (5)

A hydraulic damper configured to axially slidably fitted a shaft member and the cylindrical member is an impact is attenuated absorbed by a given fluid resistance, and the shaft member and the tubular member In the hydraulic damper configured to increase the degree of fastening and fitting of the shaft member with respect to the cylindrical member by receiving the supply of pressurized fluid during the period, the supply of the pressurized fluid is between the shaft member and the cylindrical member. A hydraulic friction force variable damper configured to introduce a pressure increase caused by relative axial movement .   2. The hydraulic frictional force variable damper according to claim 1, wherein a limiting member that receives supply of pressurized fluid and fastens the shaft member is disposed between the shaft member and the cylindrical member.   The hydraulic frictional force variable damper according to claim 2, wherein a plurality of divided members are arranged in the axial direction as the limiting member. The pressurized fluid is supplied by introducing a set pressure of a counter balance valve that opens due to a pressure increase caused by relative axial movement between the shaft member and the cylindrical member. The hydraulic frictional force variable damper according to any one of claims 1 to 3. The hydraulic pressure according to any one of claims 1 to 4 , wherein a stop valve or a throttle valve is installed in a pipe line defined by a piston portion constituting a shaft member and communicating between cylinder chambers constituting a cylindrical member. Variable friction force damper.

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