JP2012087862A - Hydraulic damper for vibration control - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic damper for vibration control, which enables easy recognition of an amount of hydraulic oil in an oil chamber in a cylinder from the outside, prevents an increase in size, weight or cost of the hydraulic damper for vibration control, and facilitates repairing or exchanging of an oil amount monitoring mechanism.SOLUTION: The hydraulic damper 50 for vibration control includes two oil chambers 18, 20 which are filled with a hydraulic oil and are formed on both sides of a first piston 10 in a cylinder 52, and a pressure type accumulator 51, and also includes an oil amount monitoring mechanism 58 attached to the outer side of the cylinder 52. The oil amount monitoring mechanism 58 includes: casings 60, 62 having a space inside; a second piston 64 stored in the space and segmenting a third oil chamber 72 in the space, which communicates with one of the two oil chambers 18, 20; an elastic member 66 stored in the space so as to energize the second piston 64 toward the third oil chamber 72; and a rod member 68 integrally disposed in the second piston 64 and capable of protruding to the outside of the casings 60, 62.

Description

  The present invention relates to a hydraulic damper for vibration control that is attached to a structure such as a building and is used to absorb a displacement between structures due to an external force such as an earthquake to control the vibration.

  Some conventional damping hydraulic dampers are provided with a pressure regulating valve, an accumulator, and the like outside the cylinder (see Patent Document 1). Conventional hydraulic dampers for vibration control in which such pressure regulating valves, accumulators, and the like are provided outside the cylinder have a complicated appearance due to an increase in the number of parts provided outside the cylinder.

  For this reason, conventional hydraulic dampers for vibration control have been provided with pressure regulating valves, accumulators, etc. inside the cylinder, thereby simplifying the external shape and improving the function of the external appearance. Some have tried to prevent interference between the parts and other members around the hydraulic damper for vibration control (see Patent Documents 2 and 3).

  As shown in FIG. 10, the conventional damping hydraulic damper 2 provided with pressure regulating valves 26, 28, a pressure accumulator 34, etc. in the cylinder includes a cylindrical cover member 6 having an inner peripheral surface 6a, a cover A cylinder 4 constituted by a cover member 8 that closes one end in the axial direction of the member 6 and extends the length in the axial direction of the cover member 6 is provided, and the piston 10 is accommodated in the cylinder 4. It was.

  The piston 10 is formed in a columnar shape. The piston 10 has a round rod-shaped first piston rod portion 14 extending outward in the axial direction from the center of the end surface, and an end surface of the piston 10 opposite to the first piston rod portion 14. The second piston rod portion 16 having a round bar shape extending outward in the axial direction from the center was integrally formed.

  And the piston 10 was provided so that the outer peripheral part could slide to the internal peripheral surface 6a of the cover member 6 of the cylinder 4, and could move to the axial direction (left-right direction in FIG. 10). Further, the cylinder 4 has a first oil chamber 18 and a second oil chamber 20 partitioned by the piston 10 therein. The first oil chamber 18 and the second oil chamber 20 were filled with hydraulic oil.

  As shown in FIG. 10, the first piston rod portion 14 is inserted into the first oil chamber 18 in the fitting hole 6 b formed in the disc portion that closes one end of the cover member 6 of the cylinder 4 from the inside of the first oil chamber 18. The cylinder 4 was fitted so as to be slidable while maintaining the hermetically sealed state, and the tip part protruded outward in the axial direction of the cylinder 4, and the ball joint 42 was attached to the tip.

  The second piston rod portion 16 is slidably fitted from the second oil chamber 20 to the shaft hole 8b of the cover member 8 of the cylinder 4 while maintaining the sealed state in the second oil chamber 20. It was. A ball joint 44 is attached to the tip of the cover member 8 of the cylinder 4 in the axial direction.

  In the solid interior of the piston 10, as shown in FIG. 10, flow paths 22 and 24 communicating the first oil chamber 18 and the second oil chamber 20 are formed along the axial direction thereof. Of these, a relief valve 26 (pressure regulating valve) is arranged in the middle of the flow path 22, and a relief valve 28 (pressure regulating valve) is arranged in the middle of the flow path 24.

  The relief valve 26 closes the flow path 22 so that hydraulic oil does not flow under normal conditions. When the piston 10 moves in the cylinder 4 and the pressure of the hydraulic oil in the first oil chamber 18 exceeds a certain value. The flow path 22 is opened to allow the hydraulic oil to flow from the first oil chamber 18 side to the second oil chamber 20 side.

  The relief valve 28 also closes the flow path 24 so that the hydraulic oil does not flow during normal operation, and the piston 10 moves in the cylinder 4 so that the pressure of the hydraulic oil in the second oil chamber 20 becomes a constant value. If exceeded, the flow path 24 is opened to allow the hydraulic oil to flow from the second oil chamber 20 side to the first oil chamber 18 side.

  Further, in the solid interior of the piston 10, an accumulator oil chamber 32 constituting a pressurizing accumulator 34 provided in the second piston rod portion 16, a first oil chamber 18 and a second oil chamber 20 in the cylinder 4 are provided. The flow path 30 which connects all of these was formed.

  The flow path 30 of the piston 10 includes a not-shown throttle, and the piston 10 moves in the cylinder 4 due to an external force such as an earthquake, so that the hydraulic oil in one of the first oil chamber 18 and the second oil chamber 20 When the pressure rises above a certain value, hydraulic oil flows from one of the oil chambers to the other oil chamber.

  As shown in FIG. 10, the pressurization type accumulator 34 is divided into a space formed inside the second piston rod portion 16 in two and a piston 36 defining the accumulator oil chamber 32 on one side, and a piston 36 is housed in a space opposite to the accumulator oil chamber 32 and urges the piston 36 toward the accumulator oil chamber 32, and is integrally connected to the piston 36 so that the tip is a second piston rod portion. 16 and a rod-like member 40 projecting outside from 16.

  The pressurization type accumulator 34 absorbs the expansion and contraction of the hydraulic oil in the first oil chamber 18 and the second oil chamber 20 in the cylinder 4 and also supplies the hydraulic oil from the accumulator oil chamber 32 to the first and second oil chambers 18 and 2. By supplying the oil chamber 20 to the hydraulic chamber 20, it is possible to prevent the hydraulic oil from being deficient and the first oil chamber 18 and the second oil chamber 20 from becoming negative pressure, thereby stabilizing the performance of the hydraulic damper 2 for vibration control. It was supposed to be possible.

  The pressurization type accumulator 34 also has a function as a reserve tank for hydraulic oil. When the hydraulic oil in the first oil chamber 18 and the second oil chamber 20 becomes insufficient due to oil leakage or the like, the accumulator oil chamber The hydraulic oil can be supplied from 32 to each oil chamber.

  The amount of hydraulic oil in the first oil chamber 18 and the second oil chamber 20 in the cylinder 4 is such that the rod-shaped member 40 is supplied to the second piston rod via the hydraulic oil in the accumulator oil chamber 32 of the pressure accumulator 34. It was possible to monitor by the length dimension protruding from the end face of the part 16 on the ball joint 44 side. A through hole 8 a was formed in the cover member 8 of the cylinder 4 so that the protruding length dimension of the rod-like member 40 can be visually recognized.

  According to such a conventional hydraulic damper for vibration control 2, the rod-shaped member 40 provided integrally with the piston 36 of the pressurization accumulator 34 is exposed to the outside from the end surface on the ball joint 44 side of the second piston rod portion 16. A change in the amount of hydraulic oil in the first oil chamber 18 and the second oil chamber 20 via the hydraulic oil in the accumulator oil chamber 32 of the pressurization type accumulator 34 by visually confirming the protruding length dimension from the outside. Can be recognized from the outside.

Japanese Patent Laid-Open No. 10-274271 Japanese Patent No. 4050103 Japanese Patent No. 4328317

  However, in the above-described conventional damper for damping vibration control 2, as shown in FIG. 10, the rod-shaped member 40 is provided integrally with the piston 36 of the pressure accumulator 34, so that the range in which the rod-shaped member 40 operates is limited. In order to ensure it, it is necessary to make the length dimension of the cover member 8 of the cylinder 4 in the axial direction that much larger, so that the size, weight, and cost of the hydraulic damper 2 for vibration control are increased. was there.

  Further, since the rod-shaped member 40 is provided integrally with the piston 36 of the pressurizing accumulator 34, when a malfunction such as breakage of the rod-shaped member 40 occurs, the damping damper 2 is installed from the building structure. Since it has to be removed and repaired or replaced by dismantling the hydraulic damper 2 for vibration control, there has been a problem that the repair or replacement takes time and effort.

  Therefore, in view of the above problems, the present invention can easily recognize the amount of hydraulic oil in the oil chamber in the cylinder from the outside, and can increase the size, weight, and cost of the hydraulic damper for vibration control. An object of the present invention is to provide a seismic damping hydraulic damper that can prevent incurring and can easily repair or replace an oil amount monitoring mechanism.

In order to solve the above-described problem, a hydraulic damper for vibration control according to the present invention includes:
A hydraulic damper for vibration control having two oil chambers formed on both sides of a first piston in a cylinder and filled with hydraulic oil therein and a pressure-type accumulator,
An oil amount monitoring mechanism attached to the outside of the cylinder;
The oil amount monitoring mechanism is
A housing having a space inside,
A second piston housed in the space and defining a third oil chamber in the space that communicates with one of the two oil chambers;
An elastic member housed in the space so as to urge the second piston toward the third oil chamber;
It has a rod-like member that is provided integrally with the second piston and that can protrude to the outside of the housing.

Moreover, the hydraulic damper for vibration control according to the present invention is
The amount of protrusion of the rod-like member of the oil amount monitoring mechanism to the outside of the housing is reduced in accordance with the amount of oil reduction in the oil chamber in the cylinder. is there.

Moreover, the hydraulic damper for vibration control according to the present invention is
The amount of protrusion of the rod member of the oil amount monitoring mechanism to the outside of the casing increases in accordance with the amount of oil decrease in the oil chamber in the cylinder.

Moreover, the hydraulic damper for vibration control according to the present invention is
The amount of protrusion of the rod-like member of the oil amount monitoring mechanism to the outside of the housing is constant until the oil in the oil chamber in the cylinder decreases by a certain amount or more,
When the oil in the oil chamber is reduced by a certain amount or more, the protruding amount of the rod-shaped member of the oil amount monitoring mechanism to the outside of the housing is reduced.

Moreover, the hydraulic damper for vibration control according to the present invention is
The amount of protrusion of the rod-like member of the oil amount monitoring mechanism to the outside of the housing is constant until the oil in the oil chamber in the cylinder decreases by a certain amount or more,
When the oil in the oil chamber decreases by a certain amount or more, the protruding amount of the rod-shaped member of the oil amount monitoring mechanism to the outside of the housing increases.

Moreover, the hydraulic damper for vibration control according to the present invention is
The third oil chamber is formed on the cylinder side with respect to the second piston.

Moreover, the hydraulic damper for vibration control according to the present invention is
The third oil chamber is formed on the side opposite to the cylinder with respect to the second piston.

Moreover, the hydraulic damper for vibration control according to the present invention is
The oil amount monitoring mechanism has a stopper for limiting the compression amount of the elastic member.

Moreover, the hydraulic damper for vibration control according to the present invention is
The stopper is provided on the rod-shaped member.

Moreover, the hydraulic damper for vibration control according to the present invention is
The stopper is provided on the second piston.

According to such a hydraulic damper for vibration control of the present invention,
A hydraulic damper for vibration control having two oil chambers formed on both sides of a first piston in a cylinder and filled with hydraulic oil therein and a pressure-type accumulator,
An oil amount monitoring mechanism attached to the outside of the cylinder;
The oil amount monitoring mechanism is
A housing having a space inside,
A second piston housed in the space and defining a third oil chamber in the space that communicates with one of the two oil chambers;
An elastic member housed in the space so as to urge the second piston toward the third oil chamber;
By having a rod-shaped member that is provided integrally with the second piston and can protrude to the outside of the housing,
The amount of hydraulic fluid in the oil chamber in the cylinder can be easily recognized from the outside, and it is possible to prevent an increase in the size, weight, and cost of the hydraulic damper for vibration control, and the amount of oil The monitoring mechanism can be easily repaired or replaced.

It is sectional drawing which shows the hydraulic damper 50 for damping | damping based on the 1st Embodiment of this invention. FIG. 2 is an enlarged sectional view showing in detail an oil amount monitoring mechanism 58 shown in FIG. 1. FIG. 3 is a diagram for explaining an operation state of the oil amount monitoring mechanism 58 shown in FIG. 2, and FIG. 3A is a partially enlarged cross-sectional view showing a state when the oil chamber is sufficiently filled with hydraulic oil, FIG. (B) is a partial expanded sectional view which shows a state when the hydraulic fluid of an oil chamber runs short of a fixed amount or more. It is an expanded sectional view which shows the oil quantity monitoring mechanism 82 in the hydraulic damper 80 for vibration control which concerns on the 2nd Embodiment of this invention. FIG. 5 is a diagram for explaining an operation state of the oil amount monitoring mechanism 82 shown in FIG. 4, and FIG. 5A is a partially enlarged cross-sectional view showing a state when the oil chamber is sufficiently filled with hydraulic oil, FIG. (B) is a partial expanded sectional view which shows a state when the hydraulic fluid of an oil chamber runs short of a fixed amount or more. It is an expanded sectional view showing oil quantity monitoring mechanism 92 in damping hydraulic damper 90 concerning a 3rd embodiment of the present invention. FIG. 7 is a diagram for explaining an operation state of the oil amount monitoring mechanism 92 shown in FIG. 6, and FIG. 7A is a partially enlarged cross-sectional view showing a state when the oil chamber is sufficiently filled with hydraulic oil, FIG. (B) is a partial expanded sectional view which shows a state when the hydraulic fluid of an oil chamber runs short of a fixed amount or more. It is an expanded sectional view showing oil quantity monitoring mechanism 122 in hydraulic damper 120 for vibration control concerning a 4th embodiment of the present invention. FIG. 9 is a diagram for explaining an operation state of the oil amount monitoring mechanism 122 shown in FIG. 8, and FIG. 9A is a partially enlarged cross-sectional view showing a state when the oil chamber is sufficiently filled with hydraulic oil, FIG. (B) is a partial expanded sectional view which shows a state when the hydraulic fluid of an oil chamber runs short of a fixed amount or more. It is sectional drawing which shows the conventional hydraulic damper 2 for vibration control.

  EMBODIMENT OF THE INVENTION Hereinafter, the form for implementing the hydraulic damper for damping control which concerns on this invention is demonstrated concretely based on drawing.

  FIG. 1 to FIG. 3 are views that are referred to in order to describe a vibration control hydraulic damper 50 according to the first embodiment of the present invention. In the damping hydraulic damper 50 shown in these drawings, the same parts as those in the conventional damping hydraulic damper 2 are described with the same reference numerals, and a part of the description of the same configuration as in the past is partially described. Shall be omitted except.

  As shown in FIG. 1, the damping hydraulic damper 50 according to the first embodiment of the present invention closes a cylindrical cover member 54 having an inner peripheral surface 54 a and one end of the cover member 54 in the axial direction. At the same time, a cylinder 52 constituted by a cover member 56 extending in the axial direction of the cover member 54 is provided, and the piston 10 (first piston) is accommodated in the cylinder 52.

  The piston 10 is provided such that the outer peripheral portion thereof slides on the inner peripheral surface 54a of the cover member 54 of the cylinder 52 and can move in the axial direction (left and right direction in FIG. 1). The cylinder 52 has a first oil chamber 18 and a second oil chamber 20 that are partitioned by the piston 10, and the first oil chamber 18 and the second oil chamber 20 are filled with hydraulic oil. Has been.

  As shown in FIG. 1, a pressure type accumulator 51 is provided in the second piston rod portion 16. This pressurization type accumulator 51 divides the space formed inside the second piston rod portion 16 into two parts, a piston 36 that defines an accumulator oil chamber 32 on one side, an accumulator oil chamber 32 of the piston 36, A spring 38 is housed in the opposite space and biases the piston 36 toward the accumulator oil chamber 32.

  Similarly to the first oil chamber 18 and the second oil chamber 20 in the cylinder 52, the accumulator oil chamber 32 is filled with hydraulic oil.

  Further, as shown in FIG. 1, an oil amount monitoring mechanism 58 is provided on the outer peripheral portion 54 b of the cover member 54 of the cylinder 52.

  As shown in FIG. 2, the oil amount monitoring mechanism 58 is accommodated in a space provided inside a casing composed of a cylindrical member 60 and a lid member 62, and this space is divided into two. The piston 64 (second piston) that defines and forms the third oil chamber 72 (third oil chamber) in one space and the piston 64 that faces the third oil chamber 72 are accommodated in the other space. An urging spring 66 (elastic member) and a rod-like member 68 that are integrally connected to the axial portion of the piston 64 and whose tip protrudes outward from the lid member 62 and whose protrusion amount can be changed. Yes.

  As shown in FIG. 2, the cylindrical member 60 of the oil amount monitoring mechanism 58 is formed in a cylindrical shape, and a male screw portion 60a is formed at the lower end portion in the axial direction (vertical direction in the drawing). The oil amount monitoring mechanism 58 is integrally fixed to the outside of the cylinder 52 by fastening the male screw portion 60 a of the cylindrical member 60 to a female screw portion 54 c formed on the outer peripheral portion 54 b of the cylinder 52.

  Further, the cylindrical member 60 is formed with a concave portion 60b that forms a space recessed downward from the upper end surface in FIG.

  As shown in FIG. 2, the lid member 62 of the oil amount monitoring mechanism 58 is formed in a disk shape having a step 62 a on the outer peripheral portion, and the diameter of the outer peripheral surface of the lower end portion in the axial direction (vertical direction in the figure). Is formed smaller than the diameter of the outer peripheral surface of the upper end portion in the axial direction.

  The lid member 62 is formed with a through hole 62b penetrating in the axial direction. The diameter of the through hole 62b is formed larger than the diameter of the outer peripheral surface of the upper end portion 68c of the rod-shaped member 68 and smaller than the diameter of the outer peripheral surface of the stopper portion 68b formed at the lower end portion of the rod-shaped member 68. Yes.

  The cylindrical member 60 and the lid member 62 are fixed to each other by screw fastening with the headed bolt 70 in a state where the lower end portion of the lid member 62 is inserted into the concave portion 60b of the cylindrical member 60 and is in contact with each other. It has become. Thereby, a space is formed inside them.

  As shown in FIG. 2, the piston 64 of the oil amount monitoring mechanism 58 is formed in a columnar shape, and the axial direction of the piston 64 in the space formed inside the cylindrical member 60 and the lid member 62 is the cylindrical member 60. Are arranged so as to substantially coincide with the axial direction (vertical direction in the figure).

  The piston 64 comes into contact with the inner peripheral surface of the recess 60b of the cylindrical member 60 in the axial direction (vertical direction in the figure) by winding an O-ring 65 around an endless groove 64a formed on the outer peripheral surface. Thus, it is possible to slide while preventing oil leakage from the third oil chamber 72.

  As shown in FIG. 2, in the space inside the cylindrical member 60 and the lid member 62 of the oil amount monitoring mechanism 58, the space on the cylinder 52 side with respect to the piston 64 is a third oil chamber 72. Is filled with hydraulic oil.

  The third oil chamber 72 is connected to the first oil chamber 72 in the cylinder 52 via a flow path 73 formed in the axial line portion at the lower end of the cylindrical member 60 and a flow path 74 formed in the cover member 54 of the cylinder 52. One oil chamber 18 communicates with the oil chamber 18.

  For this reason, the pressure of the hydraulic oil in the third oil chamber 72 is the pressure of the hydraulic oil in each of the first oil chamber 18, the second oil chamber 20, and the accumulator oil chamber 32 of the pressurization type accumulator 51 in a normal state to be described later. It is the same as the pressure.

  On the other hand, in the space inside the cylindrical member 60 and the lid member 62 on the opposite side of the cylinder 52 from the piston 64, as shown in FIG. 2, the axial direction of the piston 64 (vertical direction in the figure). The elastic spring 66 is disposed in a state where the end portions are in contact with the lid member 62 and the piston 64, respectively. The spring 66 urges the piston 64 pressed by the hydraulic oil in the third oil chamber 72 from the opposite side of the third oil chamber 72.

  Further, as shown in FIG. 3A, the end surface 64c of the piston 64 on the side where the lower end portion of the spring 66 is in contact is below the stopper portion 68b formed at the lower end portion of the rod-shaped member 68 in the drawing. The end surfaces are abutted and integrally connected.

  The rod-shaped member 68 is formed in a round bar shape having a step 68a on the outer peripheral surface thereof, and the diameter of the outer peripheral surface of the stopper portion 68b at the lower end thereof is larger than the diameter of the outer peripheral surface of the upper end portion 68c. ing. The upper end portion 68 c of the rod-shaped member 68 has its tip portion loosely penetrates the through hole 62 b formed in the lid member 62 and protrudes to the outside of the lid member 62.

  FIGS. 3A and 3B are diagrams for explaining the operating state of the oil amount monitoring mechanism 58 of the hydraulic damper for vibration control 50 according to the first embodiment of the present invention.

  First, FIG. 3A shows that the hydraulic oil is sufficiently filled in the accumulator oil chamber 32 and the third oil chamber 72 in the oil amount monitoring mechanism 58 together with the first oil chamber 18 and the second oil chamber 20 in the cylinder 52. FIG. 5 is a view showing an oil amount monitoring mechanism 58 in a state where an external force due to an earthquake or the like is not applied to the piston 10 of the hydraulic damper for vibration control 50 (normal state).

  In this normal state, the hydraulic oil in the accumulator oil chamber 32 of the pressurization type accumulator 51 is urged by a spring 38 that urges the piston 36 toward the accumulator oil chamber 32. Pressure corresponding to the elastic force of 38 is generated. Since the first oil chamber 18 and the second oil chamber 20 in the cylinder 52 and the third oil chamber 72 in the oil amount monitoring mechanism 58 communicate with the accumulator oil chamber 32, these oil chambers 18, 20. , 72 is the same as the pressure of the hydraulic oil in the accumulator oil chamber 32 urged by the spring 38.

  The pressure of the hydraulic oil in the third oil chamber 72 generated by the spring 38 of the pressure accumulator 51 in this way generates a pressing force F that presses the end face 64b of the piston 64 as shown in FIG. Yes. The spring 66 exerts an elastic force S that presses the end face 64 c of the piston 64 against the pressing force F. The length dimension of the spring 66 at this time is a predetermined dimension K0.

  At this time, as shown in FIG. 3A, the step 68a of the rod-shaped member 68 and the lid member 62 are separated from each other in the vertical direction in the figure. Further, the tip of the rod-shaped member 68 protrudes from the upper surface of the lid member 62 by the length of the dimension L0. The rod-like member 68 can move in the vertical direction in the drawing in accordance with the sliding of the piston 64.

  Next, when external force is applied to the surface of the piston 10 of the damping hydraulic damper 50 perpendicular to the axial direction due to an earthquake or the like, and the first oil chamber 18 of the cylinder 52 is compressed and expanded, the first oil The pressure of the hydraulic oil in the chamber 18 and the second oil chamber 20 changes. At this time, since the pressure of the hydraulic oil in the third oil chamber 72 of the oil amount monitoring mechanism 58 also changes, the piston 64 correspondingly moves in the vertical direction in FIG.

  At this time, when the pressing force F pushing the piston 64 by the hydraulic oil in the third oil chamber 72 increases, the length dimension of the spring 66 decreases, but when the pressing force F exceeds a certain level, the lid The step 68 a of the rod-shaped member 68 is in contact with the member 62.

  For this reason, since the compression amount of the spring 66 can be limited so that the length dimension of the spring 66 does not become smaller than a certain dimension, the spring 66 is prevented from receiving a force exceeding the limit and causing damage such as buckling. be able to.

  Next, there is no direct relationship with an operation due to an external force such as an earthquake, and after a long period of time, the first oil chamber 18, the second oil chamber 20, or the accumulator oil chamber 32 in the cylinder 52 of the damping hydraulic damper 50. When the hydraulic oil leaks out and the amount of oil decreases, the amount of oil in the accumulator oil chamber 32 that supplies the hydraulic oil to these oil chambers 18 and 20 decreases. The spring 38 biased toward the accumulator oil chamber 32 extends, and the elastic force of the spring 38 is reduced.

  For this reason, the pressure of the hydraulic oil in the accumulator oil chamber 32 of the pressurization type accumulator 51 is reduced, and the first oil chamber 18, the second oil chamber 20 and the third oil chamber communicating with the accumulator oil chamber 32 together. The pressure applied to the hydraulic oil in 72 is also reduced.

  For this reason, as shown in FIG. 3B, the pressing force F by which the hydraulic oil in the third oil chamber 72 pushes the end face 64 b of the piston 64 becomes small, and the elastic force S by which the spring 66 pushes the end face 64 c of the piston 64. Becomes larger than the pressing force F. For this reason, the length dimension of the spring 66 becomes a dimension K1 larger than the dimension K0 in the normal state. The piston 64 moves toward the third oil chamber 72 (downward in the figure) by the amount by which the length dimension of the spring 66 increases from K0 to K1.

  At this time, since the rod-shaped member 68 integrally connected with the piston 64 is also interlocked, the length of the rod-shaped member 68 protruding from the lid member 62 at the front end is a dimension L1 smaller than the dimension L0 in the normal state. .

  As described above, when the hydraulic oil in the accumulator oil chamber 32 is reduced, the oil amount monitoring mechanism 58 of the damping hydraulic damper 50 has a protrusion amount of the tip of the rod-like member 68 to the outside of the lid member 62. It has come to decrease.

  For this reason, the variation in the amount of hydraulic oil in the first oil chamber 18 and the second oil chamber 20 of the cylinder 52 is determined by visually recognizing the length dimension in which the tip of the rod-shaped member 68 protrudes from the lid member 62 to the outside. Therefore, it is possible to easily determine the amount of hydraulic oil of the damping hydraulic damper 50 from the outside, and whether the damping hydraulic damper 50 has a sufficient amount of oil to perform its original function. Can be recognized from the outside.

  By providing the oil amount monitoring mechanism 58 in the damping hydraulic damper 50 in this way, the pressurizing accumulator 51 of the damping hydraulic damper 50 is like the pressurizing accumulator 34 of the conventional damping hydraulic damper 2. Therefore, the length of the cover member 56 of the cylinder 52 is made shorter than the length of the cover member 8 of the cylinder 4 of the conventional vibration damping hydraulic damper 2. Can do.

  Further, by shortening the length of the cover member 56 of the cylinder 52 of the damping hydraulic damper 50, the weight of the damping hydraulic damper 50 can be reduced.

  Further, the piston 64 of the oil amount monitoring mechanism 58 does not have to have a large pressure receiving area for receiving the pressure of the hydraulic oil as in the pressurization type accumulator 51. Therefore, the structure of the oil amount monitoring mechanism 58 can be reduced, and the weight Can be made lightweight. For this reason, the manufacturing price of the oil amount monitoring mechanism 58 can also be reduced.

  In addition, the conventional oil amount monitoring device using the rod-like member 40 of the damping hydraulic damper 2 has a seismic damping hydraulic damper 2 from the building structure when a malfunction occurs in the device and repair or maintenance work is performed. However, the oil amount monitoring mechanism 58 according to the present embodiment is provided on the outer peripheral portion 54b of the cover member 54 of the cylinder 52. Since it can be easily attached and detached, it can be easily repaired or maintained.

  As described above, according to the damping hydraulic damper 50 according to the first embodiment of the present invention, the amount of hydraulic oil in the oil chambers 18, 20, 32 in the cylinder 52 can be easily increased from the outside. Thus, the seismic hydraulic damper 50 can be prevented from becoming large, heavy, and expensive, and the oil amount monitoring mechanism 58 can be easily repaired and maintained.

  Further, in the hydraulic damper for vibration control 50 according to the first embodiment of the present invention, since the amount of hydraulic oil corresponds to the length dimension protruding to the outside of the rod-shaped member 68, the use of the damper is started. From this, it is possible to estimate the amount of hydraulic oil leakage after a certain period of time, and to predict how long the seismic hydraulic damper 50 can maintain its original function after that time. For this reason, the maintenance frequency of the hydraulic damper 50 for vibration control can be made more appropriate.

  FIG. 4 and FIG. 5 are diagrams which are referred to for explaining a vibration control hydraulic damper 80 according to the second embodiment of the present invention.

  As shown in FIG. 4, the seismic damping hydraulic damper 80 according to the second embodiment is also provided with an oil amount monitoring mechanism 82 on the outer peripheral portion 54 b of the cover member 54 of the cylinder 52.

  As shown in FIG. 4, the oil amount monitoring mechanism 82 in the damping hydraulic damper 80 according to the second embodiment includes a spring 86 (elastic member) that biases the piston 64 toward the third oil chamber 72. However, the spring constant is smaller than that of the spring 66 in the first embodiment, and the step 84a of the rod-shaped member 84 and the lid member 62 are in contact with each other in a normal state. This is different from the oil amount monitoring mechanism 58 according to the first embodiment.

  Further, the rod-shaped member 84 has the same configuration as the rod-shaped member 68 in the first embodiment, but a mark 88 is provided on the peripheral portion of the cross section perpendicular to the axial direction of the upper end portion 84c. Is different from the rod-like member 68 in the first embodiment.

  FIGS. 5A and 5B are diagrams for explaining the operating state of the oil amount monitoring mechanism 82 of the hydraulic damper for vibration control 80 according to the second embodiment of the present invention.

  As shown in FIG. 5A, in the normal state, the oil amount monitoring mechanism 82 is more elastic force S by the spring 86 than the pressing force F pushing the end face 64b of the piston 64 by the hydraulic oil in the third oil chamber 72. Therefore, the step 84 a of the rod-shaped member 84 comes into contact with the lid member 62.

  In this normal state, as shown in FIG. 5 (a), the rod-shaped member 84 has a tip protruding from the upper surface of the lid member 62 by the length of the dimension L0. This state is maintained until the amount of oil in the oil chambers 18 and 20 in the cylinder 52 decreases by a certain amount or more.

  The oil amount monitoring mechanism 82 then leaks the hydraulic oil from the oil chambers 18 and 20 in the cylinder 52 and the oil amount is reduced by a certain amount (critical state), and further the oil is leaked and the oil amount is constant. When the amount decreases, the pressing force F by which the hydraulic oil in the third oil chamber 72 pushes the end face 64b of the piston 64 becomes smaller, and the elastic force S by which the spring 86 pushes the end face 64c of the piston 64 becomes larger. Therefore, as shown in FIG. 5B, the length dimension of the spring 86 becomes a dimension K2 larger than the dimension K0 in the normal state.

  At this time, since the rod-shaped member 84 integrally connected with the piston 64 is also interlocked, as shown in FIG. 5B, the length of the rod-shaped member 84 protruding from the lid member 62 at the front end is normal. The dimension L2 is smaller than the dimension L0 in the state. For this reason, since the mark 88 of the rod-shaped member 84 enters inside from the upper surface of the lid member 62, the mark 88 cannot be visually recognized from the outside.

  As described above, the oil amount monitoring mechanism 82 of the damping hydraulic damper 80 has a rod-shaped member when the amount of hydraulic oil decreases by a certain amount or more after reaching the critical state where the amount of hydraulic oil in the cylinder 52 decreases by a certain amount. The amount of protrusion of the tip end portion 84 to the outside is reduced.

  Also by the damping hydraulic damper 80 according to the second embodiment of the present invention, the oil chambers 18 in the cylinder 52, as in the damping hydraulic damper 50 according to the first embodiment. Since the amount of hydraulic oil in the tanks 20 and 32 can be easily recognized from the outside, an increase in the size, weight, and cost of the hydraulic damper 80 for vibration control can be prevented, and an oil amount monitoring mechanism 82 can be easily repaired and maintained.

  Furthermore, in the damping hydraulic damper 80 according to the second embodiment of the present invention, since the mark 88 is provided on the rod-shaped member 84, the damping hydraulic damper 80 exhibits its original function. It can be easily recognized from the outside whether the oil amount is sufficient.

  In addition, in the hydraulic damper for vibration control 80 according to the second embodiment of the present invention, since the spring 86 having a smaller spring constant than the spring 66 in the first embodiment can be used, the spring 86 is a piston. Since 64 is not pushed down suddenly, it is possible to accurately estimate the future progress of the oil leakage after the critical state.

  FIGS. 6 and 7 are views to be referred to for explaining a vibration damping hydraulic damper 90 according to the third embodiment of the present invention.

  As shown in FIGS. 2 and 4, the oil amount monitoring mechanisms 58 and 82 in the damping hydraulic dampers 50 and 80 according to the first and second embodiments have the third oil chamber 72 with respect to the piston 64. The amount of protrusion of the rod-shaped members 68 and 84 to the outside is reduced due to the decrease in the amount of oil, whereas the vibration damping according to the third embodiment As shown in FIG. 6, the oil amount monitoring mechanism 92 in the hydraulic damper 90 is configured such that the third oil chamber 108 is disposed on the opposite side of the cylinder 52 with respect to the piston 98, and FIG. And as shown to (b), it differs in the point which the protrusion amount to the exterior of the front-end | tip of the rod-shaped member 102 increases by the reduction | decrease of oil amount.

  The damping hydraulic damper 90 according to the third embodiment is also provided with an oil amount monitoring mechanism 92 on the outer peripheral portion 54b of the cover member 54 of the cylinder 52, as shown in FIG.

  As shown in FIG. 6, the oil amount monitoring mechanism 92 divides a space provided in the casing constituted by the cylindrical member 94 and the lid member 96 into two, and a third space is provided in one space. A piston 98 (second piston) that defines an oil chamber 108 (third oil chamber) and a spring 100 (elastic) that is housed in the other space and biases the piston 98 toward the third oil chamber 108. Member) and a rod-like member 102 which is integrally connected to the axial portion of the piston 98 and whose tip protrudes outward from the upper surface of the cylindrical member 94 and the amount of protrusion can be changed, and a lid member 96. It is configured by a possible stopper 104.

  As shown in FIG. 6, the cylindrical member 94 of the oil amount monitoring mechanism 92 is formed in a cylindrical shape having a flange portion 94 a projecting outward at the lower end portion of the outer peripheral portion thereof. A step 94c is formed at the lower end of the recess 94d.

  Further, a through hole 94e penetrating in the axial direction is formed in the upper end portion of the cylindrical member 94, and the rod-like member 102 is loosely inserted into the through hole 94e through a seal member. .

  As shown in FIG. 6, the lid member 96 is formed in a columnar shape, is inserted into the concave portion 94d of the cylindrical member 94, and is fitted and fixed until its upper surface comes into contact with the step 94c. For this reason, a space is formed inside the cylindrical member 94 and the lid member 96.

  Further, in the oil amount monitoring mechanism 92, the end face 94b of the cylindrical member 94 comes into contact with the outer peripheral portion 54b of the cover member 54 of the cylinder 52, and the headed bolt 106 penetrating the through hole of the flange portion 94a is provided with the cover member 54. It is fixed to the cylinder 52 by being screwed into the screw hole.

  The piston 98 of the oil amount monitoring mechanism 92 has a cylindrical member 94 while preventing oil leakage from the third oil chamber 108 by winding an O-ring 99 around an endless groove 98a formed on the outer peripheral surface of the piston 98. It is possible to slide in the axial direction on the inner peripheral surface of the recess 94d.

  As shown in FIG. 6, in the space inside the cylindrical member 94 and the lid member 96 of the oil amount monitoring mechanism 92, the space opposite to the cylinder 52 with respect to the piston 98 is a third oil chamber 108. The inside is filled with hydraulic oil.

  The third oil chamber 108 communicates with the first oil chamber 18 in the cylinder 52 via a flow path 109 formed in the cylindrical member 94 and a flow path 110 formed in the cover member 54 of the cylinder 52. It is supposed to be.

  Therefore, the pressure of the hydraulic oil in the third oil chamber 108 is the pressure of the hydraulic oil in each of the first oil chamber 18, the second oil chamber 20, and the accumulator oil chamber 32 of the pressurization type accumulator 51 in the normal state. It is the same.

  On the other hand, in the space inside the cylindrical member 94 and the lid member 96, the space on the cylinder 52 side with respect to the piston 98 expands and contracts in the axial direction (vertical direction in the figure) of the piston 98 as shown in FIG. The spring 100 is disposed in a state where the end portions are in contact with the lid member 96 and the piston 98, respectively. The spring 100 urges the piston 98 pressed by the hydraulic oil in the third oil chamber 108 from the opposite side of the third oil chamber 108.

  Further, as shown in FIG. 7A, the end surface 98b of the piston 98 opposite to the side on which the spring 100 abuts is abutted with one end surface in the axial direction of the rod-like member 102 and integrally connected thereto. ing. The upper end portion of the rod-like member 102 loosely penetrates the through hole 94e of the tubular member 94 and protrudes outward from the upper surface of the tubular member 94.

  A cylindrical stopper 104 is integrally fixed to an end surface 98c of the piston 98 on the side where the spring 100 abuts.

  FIGS. 7A and 7B are views for explaining the operating state of the oil amount monitoring mechanism 92 of the damping hydraulic damper 90 according to the third embodiment of the present invention.

  First, together with the first oil chamber 18 and the second oil chamber 20 in the cylinder 52, the accumulator oil chamber 32 and the third oil chamber 108 in the oil amount monitoring mechanism 92 are sufficiently filled with hydraulic oil and are used for vibration control. In a state (normal state) where an external force due to an earthquake or the like is not applied to the piston 10 of the hydraulic damper 90, the spring 100 has a predetermined dimension K0 as shown in FIG. The spring 100 exerts an elastic force S that pushes the end face 98c of the piston 98 against the pressing force F that pushes the end face 98b of the piston 98 with the hydraulic oil inside.

  In this normal state, the stopper 104 and the lid member 96 are arranged apart from each other in the vertical direction in the figure, and the rod-like member 102 has its tip protruding from the upper surface of the cylindrical member 94 by a length of the dimension L0. Yes.

  Next, when an external force in the left-right direction in FIG. 1 is applied to the piston 10 of the damping hydraulic damper 90 due to an earthquake or the like, and the first oil chamber 18 of the cylinder 52 is compressed and expanded, the first oil chamber 18 Or the pressure of the hydraulic oil in the second oil chamber 20 changes. At this time, since the pressure of the hydraulic oil in the third oil chamber 108 of the oil amount monitoring mechanism 92 also changes, the piston 98 correspondingly moves in the vertical direction in FIG.

  At this time, when the pressing force F pushing the piston 98 by the hydraulic oil in the third oil chamber 108 increases, the length of the spring 100 decreases, but when the pressing force F exceeds a certain value, the upper surface of the lid member 96 The lower surface of the stopper 104 comes into contact.

  For this reason, since the compression amount of the spring 100 can be limited so that the length dimension of the spring 100 does not become smaller than a certain dimension, the spring 100 is prevented from receiving a force exceeding the limit and causing damage such as buckling. be able to.

  Next, there is no direct relationship with an operation due to an external force such as an earthquake, and after a long period of time, the first oil chamber 18, the second oil chamber 20 or the accumulator oil chamber 32 in the cylinder 52 of the damping hydraulic damper 90. When the hydraulic oil leaks out and the amount of oil decreases, the amount of oil in the accumulator oil chamber 32 that supplies the hydraulic oil to these oil chambers 18 and 20 decreases. The spring 38 biased toward the accumulator oil chamber 32 extends, and the elastic force of the spring 38 is reduced.

  For this reason, the pressure of the working oil in the accumulator oil chamber 32 of the pressurization type accumulator 51 becomes small, and the pressure of the working oil in the first oil chamber 18, the second oil chamber 20, and the third oil chamber 108 also becomes small. .

  Therefore, as shown in FIG. 7B, the pressing force F by which the hydraulic oil in the third oil chamber 108 presses the end surface 98 b of the piston 98 is reduced, and the elastic force S by which the spring 100 presses the end surface 98 c of the piston 98. Therefore, the length dimension of the spring 100 becomes a dimension K3 larger than the dimension K0 in the normal state. The piston 98 moves to the third oil chamber 108 side (upward in the figure) by the amount that the length of the spring 100 is increased from K0 to K3.

  At this time, since the rod-like member 102 integrally connected with the piston 98 is also interlocked, the rod-like member 102 has a length dimension protruding from the upper surface of the cylindrical member 94 at the tip thereof is larger than the dimension L0 in the normal state. L3.

  As described above, the oil amount monitoring mechanism 92 of the damping hydraulic damper 90 is configured such that when the hydraulic oil in the accumulator oil chamber 32 decreases, the protrusion amount of the rod member 102 to the outside increases. ing.

  For this reason, a reduction in the amount of hydraulic oil in the cylinder 52 of the damping hydraulic damper 90 is externally recognized by visually recognizing the length of the tip of the rod-like member 102 protruding from the upper surface of the cylindrical member 94 to the outside. It can be easily found, and it can be recognized from the outside whether the damping hydraulic damper 90 has a sufficient amount of oil to perform its original function.

  Also with the damping hydraulic damper 90 according to the third embodiment of the present invention, the oil chambers 18 in the cylinder 52, as in the damping hydraulic damper 50 according to the first embodiment. Since the oil amount of the hydraulic oil in 20 and 32 can be easily recognized from the outside, an increase in the size, weight, and cost of the hydraulic damper 90 for vibration control can be prevented, and an oil amount monitoring mechanism 92 can be easily repaired and maintained.

  Further, in the hydraulic damper for vibration control 90 according to the third embodiment of the present invention, since the amount of hydraulic oil corresponds to the length dimension protruding to the outside of the rod-like member 102, the use of the damper is started. From this, it is possible to estimate the amount of hydraulic oil leakage after a certain period of time, and to predict how long the seismic hydraulic damper 90 can maintain its original function after that time. For this reason, the frequency of maintenance of the hydraulic damper 90 for vibration control can be made more appropriate.

  FIG. 8 and FIG. 9 are diagrams which are referred to for explaining a vibration control hydraulic damper 120 according to the fourth embodiment of the present invention.

  The damping hydraulic damper 120 according to the fourth embodiment is also provided with an oil amount monitoring mechanism 122 on the outer peripheral portion 54b of the cover member 54 of the cylinder 52, as shown in FIG.

  The oil amount monitoring mechanism 122 in the damping hydraulic damper 120 according to the fourth embodiment includes a spring 126 (elastic member) that biases the piston 98 toward the third oil chamber 108 as shown in FIG. However, the spring constant is smaller than that of the spring 100 in the third embodiment, and the stopper 124 and the lid member 96 are in contact with each other in a normal state. This is different from the oil amount monitoring mechanism 92 according to the embodiment.

  Further, the rod-shaped member 128 has the same configuration as the rod-shaped member 102 in the third embodiment, but the tip thereof is at the same position as the upper surface of the cylindrical member 94 or inside the upper surface (lower side in the figure). ) Is different from the oil amount monitoring mechanism 92 according to the third embodiment.

  FIGS. 9A and 9B are diagrams for explaining the operating state of the oil amount monitoring mechanism 122 of the hydraulic damper for vibration control 120 according to the fourth embodiment of the present invention.

  As shown in FIG. 9A, in the normal state, the oil amount monitoring mechanism 122 is more elastic when the pressing force F pushing the end surface 98b of the piston 98 by the hydraulic oil in the third oil chamber 108 is caused by the spring 126. Since it is larger, the stopper 124 comes into contact with the lid member 96.

  In this normal state, as shown in FIG. 9A, the upper end of the rod-shaped member 128 is located at the same position as the upper surface of the cylindrical member 94 or inside the upper surface. This state is maintained until the amount of oil in the oil chambers 18 and 20 in the cylinder 52 decreases by a certain amount or more.

  The oil amount monitoring mechanism 122 further leaks the hydraulic oil from the oil chambers 18 and 20 inside the cylinder 52 and the oil amount is reduced by a certain amount (critical state), and the oil amount is constant. When the amount decreases, the pressing force F that the hydraulic oil in the third oil chamber 108 presses on the end surface 98b of the piston 98 decreases, and the elastic force S that the spring 126 presses on the end surface 98c of the piston 98 increases. Therefore, the length dimension of the spring 126 becomes a dimension K4 larger than the dimension K0 in the normal state.

  At this time, since the rod-shaped member 128 integrally coupled with the piston 98 is also interlocked, the rod-shaped member 128 has its tip projecting from the upper end surface of the cylindrical member 94, and the projected length dimension is a dimension in a normal state. The dimension L4 is larger than (substantially zero). For this reason, as shown in FIG.9 (b), the front-end | tip part of the rod-shaped member 128 protrudes outside from the upper surface of the cylindrical member 94, and it becomes possible to visually recognize the rod-shaped member 128 from the outside.

  As described above, the oil amount monitoring mechanism 122 of the damping hydraulic damper 120 is in a critical state where the amount of hydraulic oil in the cylinder 52 decreases by a certain amount. The amount of protrusion of the distal end portion of the rod-shaped member 128 to the outside increases after the distal end portion of the 128 protrudes to the outside from the cylindrical member 94 and protrudes to the outside.

  The damping hydraulic damper 120 according to the fourth embodiment of the present invention as described above also includes the inside of the cylinder 52 similarly to the damping hydraulic dampers 80 and 90 according to the second and third embodiments. Since the amount of hydraulic oil in the oil chambers 18, 20, and 32 can be easily recognized from the outside, it is possible to prevent an increase in the size, weight, and cost of the damping damper 120. The oil amount monitoring mechanism 122 can be easily repaired or maintained.

  Furthermore, in the damping hydraulic damper 120 according to the fourth embodiment of the present invention, the tip of the rod-shaped member 128 is located at the same position as the upper surface of the tubular member 94 when the oil amount is sufficient. Alternatively, if the amount of oil decreases more than a certain amount, the tip end of the rod-shaped member 128 comes to be positioned outside the upper surface of the cylindrical member 94. It is possible to more easily recognize from the outside whether the oil amount is sufficient to exhibit the above function.

  In addition, in the hydraulic damper for vibration control 120 according to the fourth embodiment of the present invention, the spring 126 having a smaller spring constant than that of the spring 100 in the third embodiment can be used. Since 98 is not pushed down rapidly, it is possible to accurately estimate the future progress of the oil leakage after the critical state.

  Although the oil amount monitoring mechanism 58 and the like in the first to fourth embodiments are attached to the outer peripheral portion 54b around the axis of the cover member 54 of the cylinder 52, the cover member 54 of the cylinder 52 is provided. It may be attached to an end surface substantially perpendicular to the axis of the cylinder 52, or may be attached to the outer peripheral portion of the cover member 56 of the cylinder 52 or a surface substantially perpendicular to the axis.

  In the oil amount monitoring mechanism 58 in the first embodiment, the third oil chamber 72 is in direct communication with the first oil chamber 18, but the third oil chamber 72 is the first oil chamber. Instead of 18, the second oil chamber 20 may be in direct communication.

  Moreover, in the hydraulic damper for damping vibration 50 according to the first embodiment, the piston 64 and the rod-shaped member 68 are two separate members, and the former is abutted against the former and is integrated. However, the piston 64 and the rod-shaped member 68 may be integrally formed as a single member.

  Further, in the oil amount monitoring mechanism 82 in the second embodiment, a mark 88 is provided on the rod-shaped member 84, but a scale for measuring the length in the axial direction is used instead of the mark 88. It may be provided.

  These marks 88 and scales are provided on rod-like members such as the oil amount monitoring mechanism 58 in the embodiments other than the second embodiment (first, third, and fourth embodiments). May be.

  Further, in the hydraulic damper for vibration control 50 according to the first embodiment, the relief valves 26 and 28, the pressure accumulator 34, etc. are provided inside the cylinder 52 and the cover member 56 of the damper. It does not preclude installation as an external unit outside the cylinder 52 or the cover member 56 of the hydraulic damper 50 for vibration control.

2 Damping hydraulic damper 4 Cylinder 6 Cover member 6a Inner peripheral surface 6b Fitting hole 8 Cover member 8a Through hole 8b Shaft hole 10 Piston 14 First piston rod portion 16 Second piston rod portion 18 First oil chamber 20 Second Oil chamber 22, 24 Flow path 26, 28 Relief valve 30 Flow path 32 Accumulator oil chamber 34 Pressure accumulator 36 Piston 38 Spring 40 Rod member 42, 44 Ball joint 50 Damping hydraulic damper 51 Pressure accumulator 52 Cylinder 54 Cover member 54a inner peripheral surface 54b outer peripheral portion 54c female screw portion 56 cover member 58 oil amount monitoring mechanism 60 cylindrical member 60a male screw portion 60b concave portion 62 lid member 62a stepped portion 62b through hole 64 piston 64a groove portion 64b end surface 64c end surface 65 O-ring 66 spring 68 rod Member 68a Difference 68b Stopper 68c Upper end 70 Head bolt 72 Third oil chamber 73, 74 Flow path 80 Damping hydraulic damper 82 Oil amount monitoring mechanism 84 Rod member 84a Step 84c Upper end 86 Spring 88 Marking 90 Damping hydraulic damper 92 Oil level monitoring mechanism 94 Cylindrical member 94a Flange part 94b End face 94c Step 94d Recess 94e Through hole 96 Lid member 98 Piston 98a Groove part 98b End face 98c End face 99 O-ring 100 Spring 102 Rod-like member 104 Stopper 106 Head bolt 108 Third oil 108 Chamber 109, 110 Flow path 120 Damping hydraulic damper 122 Oil quantity monitoring mechanism 124 Stopper 126 Spring 128 Rod member F Pressing force K, L Length dimension S Elastic force

Claims (10)

A hydraulic damper for vibration control having two oil chambers formed on both sides of a first piston in a cylinder and filled with hydraulic oil therein and a pressure-type accumulator,
An oil amount monitoring mechanism attached to the outside of the cylinder;
The oil amount monitoring mechanism is
A housing having a space inside,
A second piston housed in the space and defining a third oil chamber in the space that communicates with one of the two oil chambers;
An elastic member housed in the space so as to urge the second piston toward the third oil chamber;
A vibration-damping hydraulic damper, comprising: a rod-like member provided integrally with the second piston and capable of projecting to the outside of the housing.   2. The control according to claim 1, wherein the amount of protrusion of the rod member of the oil amount monitoring mechanism to the outside of the housing decreases according to the amount of oil decrease in the oil chamber in the cylinder. Seismic hydraulic damper.   The amount of protrusion of the rod member of the oil amount monitoring mechanism to the outside of the housing increases according to the amount of oil decrease in the oil chamber in the cylinder. Seismic hydraulic damper. The amount of protrusion of the rod-like member of the oil amount monitoring mechanism to the outside of the housing is constant until the oil in the oil chamber in the cylinder decreases by a certain amount or more,
The hydraulic pressure for vibration control according to claim 1, wherein when the oil in the oil chamber decreases by a certain amount or more, a protruding amount of the rod-shaped member of the oil amount monitoring mechanism to the outside of the housing decreases. damper. The amount of protrusion of the rod-like member of the oil amount monitoring mechanism to the outside of the housing is constant until the oil in the oil chamber in the cylinder decreases by a certain amount or more,
The hydraulic pressure for vibration control according to claim 1, wherein when the oil in the oil chamber decreases by a certain amount or more, a protruding amount of the rod-shaped member of the oil amount monitoring mechanism to the outside of the housing increases. damper.   2. The hydraulic damper for vibration control according to claim 1, wherein the third oil chamber is formed on the cylinder side with respect to the second piston.   The seismic damping hydraulic damper according to claim 1, wherein the third oil chamber is formed on the opposite side of the cylinder with respect to the second piston.   The seismic damping hydraulic damper according to any one of claims 1 to 7, wherein the oil amount monitoring mechanism includes a stopper that limits a compression amount of the elastic member.   9. The hydraulic damper for vibration control according to claim 8, wherein the stopper is provided on the rod-shaped member.   9. The hydraulic damper for vibration control according to claim 8, wherein the stopper is provided on the second piston.

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