Fluid Control Valve

Abstract

To provide a fluid control valve with a simple mechanical structure capable of appropriately controlling circulation of fluid by smooth circulation of fluid in one direction, circulation of fluid with throttling in an opposite direction as a return to the one direction, and smooth circulation by release of the throttling later.SOLUTION: A fluid control valve includes: a spool 103 that can slide between a first port 107 and a second port 108; a coil spring 104 that elastically energizes the spool to a first port side; a communication passage 105f that is communicated with a circulation passage 103f communicated with the first port; and a movable passage 103d that is provided in the spool and whose communication range with the communication passage is changed by the sliding movement of the spool. The communication range of the movable passage with the communication passage increases when the spool is slidably moved to the first port side by the coil spring, and the communication range with the communication passage is narrowed so as to throttle the circulation of the fluid when the spool is slidably moved to a second port side by the hydrostatic pressure of the fluid that acts from the first port side.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a fluid control valve with a simple mechanical structure that can appropriately control the flow of fluid by smooth flow of fluid in one direction, and by throttling the fluid in the opposite direction that returns the fluid to the one direction, and then releasing the throttling to allow smooth flow. [Background technology]

[0002] 2. Description of the Related Art Known examples of mechanical elements operated by fluid control include oil dampers that absorb earthquake energy.

[0003] An example of this type of oil damper is known from Patent Document 1. The "oil damper for a seismic isolation device" in Patent Document 1 is an oil damper for a seismic isolation device that, when used in combination with a seismic isolation bearing, constitutes a seismic isolation device and absorbs and attenuates the energy of earthquake shaking in order to suppress relative displacement between the foundation and the upper building during an earthquake, and includes a first cylinder connected to one of the foundation and the upper building, a first piston slidably provided within the first cylinder and dividing the first cylinder into two oil chambers, left and right, a first hydraulic cylinder having a piston rod with a pressing portion that is provided integrally with the first piston and connected to the other of the foundation and the upper building, a communication passage that connects the two oil chambers to each other outside the first hydraulic cylinder, a valve body provided midway in the communication passage and that opens and closes the communication passage, a movable spring seat, and a spring that is provided between the valve body and the spring seat and biases the valve body toward the closing side. a damping valve that generates a damping force by opening the valve body with hydraulic pressure supplied from the oil chamber of the first cylinder as the first piston of the first hydraulic cylinder is displaced; a second cylinder that communicates with the back side of the spring seat of the damping valve; a second piston that is slidably provided within the second cylinder; and a second piston rod that has an engaging portion and is integral with the second piston, the second hydraulic cylinder being actuated when the engaging portion is pressed by the pressing portion of the first piston rod when the displacement of the first piston reaches a predetermined value, and introducing hydraulic pressure from within the second cylinder to the back side of the spring seat to compress the spring via the spring seat and increase the spring force of the spring, thereby strengthening the damping force. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 4442770 Summary of the Invention [Problem to be solved by the invention]

[0005] The oil damper disclosed in the background art is an excellent device that, when the displacement of the first piston reaches a predetermined value, introduces hydraulic pressure from within the second cylinder of the second hydraulic cylinder to the back side of the spring seat of the damping valve, increasing the spring force of the spring that biases the valve body to open and close the communication passage that communicates with the first hydraulic cylinder, thereby strengthening the damping force, and can change the damping performance in accordance with the stroke of the first piston rod caused by seismic motion.

[0006] In this oil damper, the oil introduced to the back side of the spring seat is prevented from returning to the second cylinder by a check valve, but is allowed to do so by a minute passage with a needle valve installed in parallel with the check valve. Specifically, the oil on the back side passes through the minute passage and returns to the relay valve assembly via piping, and then passes through the throttle passage in the relay valve assembly and returns to the second cylinder via piping (see paragraph

[0040] of the above-mentioned Patent Document 1). This allows the damping valve to gradually return to its normal characteristics after the earthquake has subsided.

[0007] However, in the background art, it is difficult to adjust the device to return the oil slowly over a long period of time (about 4 to 5 minutes), and there is also the problem that the oil does not return completely to the second cylinder.

[0008] Furthermore, while it may be possible to use a solenoid valve for simplification, there is a problem in that it becomes unusable in the event of a power outage.

[0009] The present invention has been devised in view of the above-mentioned conventional problems, and aims to provide a fluid control valve with a simple mechanical structure that is capable of appropriately controlling the flow of fluid by smooth flow in one direction, and by throttling the fluid in the opposite direction, which is the return direction to the one direction, and then releasing the throttling to allow smooth flow. [Means for solving the problem]

[0010] A fluid control valve according to the present invention is a fluid control valve that is provided in a flow path, for allowing a fluid to flow in one direction and throttling the flow of the fluid in the opposite direction, and includes a flow path member having a first port and a second port at both ends connected to the flow path and provided with a passage portion through which the fluid flows, a spool having a flow path that is connected to the first port and through which the fluid flows, and provided in the passage portion so as to be slidable in a reciprocating direction between the first port and the second port, a spring that is provided in the passage portion and elastically biases the spool from the second port side toward the first port side, and a spring that is provided in the flow path member. the movable passage is characterized in that it comprises a communication passage for communicating the passage portion with the flow passage, and a movable passage provided in the spool so as to communicate with the communication passage, the communication range with the communication passage being changed by the sliding movement of the spool in the reciprocating direction, the communication range with the communication passage being expanded when the spool is slidably moved toward the first port by the elastic bias of the spring, and the communication range with the communication passage being narrowed so as to restrict the flow of fluid when the spool is slidably moved toward the second port against the elastic bias of the spring by the fluid pressure of the fluid acting on the spool from the first port side.

[0011] The first port is characterized in that a spring force adjusting means is provided for adjusting the spring force of the spring by changing the position of the spool that is elastically biased by the spring.

[0012] The flow passage of the spool is characterized in that a pressure receiving portion on which the fluid pressure of the fluid acts is formed. [Effects of the Invention]

[0013] The fluid control valve of the present invention has a simple mechanical structure and can appropriately control the flow of fluid by smooth flow in one direction, and by flowing the fluid in the opposite direction, which is the return direction to the one direction, by throttling the fluid and then releasing the throttling to allow smooth flow. [Brief explanation of the drawings]

[0014] [Figure 1]1 is an explanatory diagram illustrating a preferred embodiment of a fluid control valve according to the present invention, illustrating a state in which a fluid flows in one direction. FIG. [Figure 2] 2 is an explanatory diagram illustrating a state in which a fluid flows in the opposite direction through the fluid control valve shown in FIG. 1. FIG. [Figure 3] 2 is a perspective view showing an example of a spool provided in the fluid control valve shown in FIG. 1. FIG. [Figure 4] 2 is a perspective view showing an example of a screw member provided in the fluid control valve shown in FIG. 1. FIG. [Figure 5] 1 is an explanatory diagram illustrating a hydraulic circuit of an oil damper system that is an application example of a fluid control valve according to the present invention. FIG. [Figure 6] FIG. 6 is a cross-sectional view illustrating a damping valve unit of the oil damper system of FIG. 5. [Figure 7] FIG. 6 is a cross-sectional view illustrating a control cylinder unit of the oil damper system of FIG. 5. [Figure 8] FIG. 6 is an explanatory diagram illustrating a control valve unit of the oil damper system of FIG. 5, which is provided with a fluid control valve according to the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0015] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A preferred embodiment of a fluid control valve according to the present invention will be described in detail below with reference to the accompanying drawings.

[0016] As shown in FIGS. 1 and 2, a fluid control valve 100 according to this embodiment is provided midway along a flow path 101 made up of pipes, tubes, and the like.

[0017] A fluid flows through the flow channel 101. The fluid may be a liquid or a gas.

[0018] The fluid flows alternately back and forth within the flow channel 101, first in one direction (indicated by arrow a in the figure) and then in the opposite direction (indicated by arrow b in the figure).

[0019] FIG. 1(A) is a side cross-sectional view illustrating the state of the fluid control valve 100 when a fluid flows in one direction a, and FIG. 1(B) is a circuit diagram at that time. FIG. 2(A) is a side cross-sectional view illustrating the state of the fluid control valve 100 when a fluid flows in the opposite direction b, and FIG. 2(B) is a circuit diagram at that time.

[0020] The fluid control valve 100 according to this embodiment is mainly composed of a flow path member 102 interposed in a flow path 101, and a spool 103 and a coil spring 104 built into the flow path member 102.

[0021] The flow path member 102 is configured by connecting a first flow path body 105 and a second flow path body 106 in series in the direction of fluid flow.

[0022] The first flow path body 105 is formed as a large-diameter hollow cylinder having an open end in the longitudinal direction and a first end wall 105a at the other end in the longitudinal direction, and inside the first flow path body 105, a first passage portion 105c is defined and formed inside the inner peripheral wall 105b.

[0023] A first port 107 connected to the flow path 101 is formed by an opening at one end of the first flow path body 105 in the longitudinal direction.

[0024] The first flow path body 105 is formed with a female screw portion 105d extending from the first port 107 toward the inside of the first passage portion 105c.

[0025] A through hole 105e for connecting the second flow path body 106 is formed in the first end wall 105a.

[0026] The second flow path body 106 is formed as a hollow cylindrical body having a smaller diameter than the first flow path body 105, with one longitudinal end open and a second end wall 106a at the other longitudinal end, and a second flow path portion 106b having a smaller diameter than the first flow path portion 105c is defined inside the second flow path body 106.

[0027] A through-hole that constitutes a second port 108 connected to the flow channel 101 is formed in the second end wall 106a.

[0028] The opened end of the second flow path body 106 in the length direction is inserted into the through-hole 105 e of the first flow path body 105 and joined thereto, whereby the second flow path body 106 is connected to the first flow path body 105 .

[0029] By connecting the first flow path body 105 and the second flow path body 106 to the flow path member 102, a first port 107 and a second port 108 connected to the flow path 101 are provided at both ends in the longitudinal direction, and the communication between the first passage portion 105c and the second passage portion 106b forms a passage portion that allows fluid to circulate between the first port 107 and the second port 108.

[0030] In the illustration, the flow path member 102 is shown with the second flow path body 106 provided above the first flow path body 105, with the first port 107 at the bottom and the second port 108 at the top, and the passage section oriented vertically; however, the flow path member 102 may be used in any orientation, such as with the second flow path body 106 provided below the first flow path body 105, with the first port 107 at the top and the second port 108 at the bottom, or with the passage sections (first and second flow path sections 105c, 106b) oriented horizontally or diagonally instead of vertically.

[0031] In the flow path member 102, an annular screw member 109 having an external thread 109a formed on its outer periphery is provided as a spring force adjusting means, which will be described later, by threading it into the internal thread 105d on the first port 107 side.

[0032] A spool 103 is provided inside the first flow path body 105. The spool 103 is formed in the shape of a solid cylinder that is in sliding contact with the inner peripheral wall 105b of the first flow path body 105, and is provided in a first passage portion 105c that constitutes a passage portion so as to be slidable back and forth between the first port 107 and the second port 108, specifically between the first port 107 and the first end wall 105a of the first flow path body 105.

[0033] The spool 103 is blocked by the first end wall 105a and cannot move to the second passage portion 106b of the second passage body 106, and can only move within the first passage portion 105c of the first passage body 105.

[0034] As shown in detail in FIG. 3, one longitudinal end of the spool 103 on the first port 107 side of the flow path member 102 is formed with a flat surface 103a so as to be able to abut against the screw member 109, and the other longitudinal end on the second port 108 side is formed with a recess 103c surrounded by an annular protrusion 103b.

[0035] The inner diameter of the recess 103c is formed to be approximately the same as the inner diameter of the second passage portion 106b of the second flow path body 106.

[0036] When the spool 103 is slid toward the first end wall 105a, the annular convex portion 103b surrounding the recess 103c has its tip approaching and abutting the end wall 105a, and when the spool 103 is slid toward the first port 107, its tip moves away from the first end wall 105a.

[0037] The annular projection 103b is cut out at an appropriate location in the circumferential direction by a predetermined length in the depth direction of the recess 103c, and at least one movable passage 103d that connects the recess 103c to the outside of the spool 103 is formed.

[0038] In the illustrated example, two movable passages 103d are formed in the diameter direction of the annular convex portion 103b. The movable passages 103d may be elongated holes formed with a predetermined length in the depth direction of the recess 103c without being cut out.

[0039] A reduced diameter portion 103e is formed in the spool 103 at an intermediate portion between one longitudinal end and the other longitudinal end. A flow passage 103f, through which fluid flows in from a first port 107, is formed in the spool 103 between the reduced diameter portion 103e and a flat surface 103a that forms one end of the spool 103.

[0040] In this embodiment, the flow passage 103f is formed in a T-shape by a horizontal passage 103g that crosses the spool 103 in the diameter direction of the first passage portion 105c and a vertical passage 103h that faces the first port 107 from the horizontal passage 103g, and a pressure-receiving portion that receives fluid pressure is formed by the horizontal passage 103g.

[0041] The flow passage 103f only needs to be able to apply the fluid pressure of the fluid flowing in from the first port 107 to the spool 103 to slide the spool 103, and its shape is not limited to a T-shape and may be any shape.

[0042] A coil spring 104 is provided in the second passage portion 106b of the second flow path body 106 that constitutes the passage portion.

[0043] The coil spring 104 has one longitudinal end supported by the second end wall 106a of the second flow path body 106 and the other longitudinal end supported by the recess 103c of the spool 103, with the recess 103c and the second end wall 106a serving as spring seats.

[0044] The coil spring 104 elastically biases the spool 103 from the second port 108 side toward the first port 107 side.

[0045] The spool 103, which is elastically biased by the coil spring 104, is supported within the first passage portion 105c so as not to be removed from the first flow path body 105, as the flat surface 103a at one end thereof abuts against a screw member 109 which is threaded into the female screw portion 105d on the first port 107 side.

[0046] As shown in FIG. 4, the screw member 109 is formed in an annular shape, thereby ensuring the flow of fluid through the first port 107.

[0047] By screwing the male thread portion 109a on the outer surface of the screw member 109 into the female thread portion 105d of the first flow path body 105, the screw member 109 can be attached and detached to the flow path member 102. By screwing the screw member 109 shallowly into the first passage portion 105c, the reciprocating sliding range of the spool 103 is widened, and on the other hand, by screwing it deeply into the inner depths of the first passage portion 105c, the reciprocating sliding range of the spool 103 is narrowed.

[0048] In the drawing, the screw member 109 has a groove 109b formed in the diameter direction, into which a tool such as a screwdriver for adjusting the amount of screwing is engaged.

[0049] To explain the assembly method, the coil spring 104 is attached to the second passage portion 106b of the second flow path body 106, and then the spool 103 is inserted into the first passage portion 105c of the first flow path body 105. After that, the screw member 109 is screwed into the female thread portion 105d of the first flow path body 105, and the spool 103 supported by the screw member 109 is elastically biased by the coil spring 104.

[0050] By changing the position of the spool 103 by increasing or decreasing the amount of screwing of the screw member 109 attached closer to the first port 107 than the spool 103, the spring force of the coil spring 104 can be increased or decreased.

[0051] The first flow path body 105 has a communicating passage 105f that is always connected to the flow path 103f, which is formed by recessing the first passage portion 105c into a groove or recess of a predetermined width over an appropriate length along the reciprocating sliding direction of the spool 103 from a position that is a distance (see dimension x in the figure) shorter than the movable passage 103d formed in the spool 103 from the first end wall 105a of the first flow path body 105 in the length direction (depth direction of the recess 103c) of the movable passage 103d toward the first port 107.

[0052] The predetermined width is preferably equal to or greater than the width of the movable passage 103d in order to ensure communication with the movable passage 103d.

[0053] Instead of forming the communication passage 105f by recessing it, it may be formed by expanding the inner diameter of the first passage portion 105c over the entire inner circumferential surface thereof.

[0054] The closer the spool 103 is to the first end wall 105a, the narrower the fluid flow path becomes.

[0055] The dimension x may be longer than the movable passage 103d, in which case the flow passage 103f and the communication passage 105f are connected by an extremely narrow gap between the inner circumference of the first flow passage body 105 and the outer circumference of the annular convex portion 103b of the spool 103.

[0056] The movable passage 103d is always in communication with the communication passage 105f, whereby the first passage portion 105c and the second passage portion 106b are always in communication with each other.

[0057] The communication passage 105f and the movable passage 103d of the spool 103 are such that when the tip of the annular convex portion 103b abuts against the first end wall 105a due to the reciprocating sliding movement of the spool 103, they are narrowed and in communication with each other at the narrowest, and when the tip of the annular convex portion 103b moves away from the first end wall 105a, the communication range between the two is increased or decreased so as to be widely in communication.

[0058] When the spool 103 moves to the first port 107 side and the annular convex portion 103b moves to the position of the communication passage 105f, the communication passage 105f of the first flow path body 105 is directly in communication with the second passage portion 106b.

[0059] The movable passage 103d is such that when the spool 103 is elastically biased by the coil spring 104 and slides and moves to the first port 107 side, and when the spool 103 abuts against the screw member 109, the communication range with the communication passage 105f widens, and when the spool 103 slides and moves to the second port 108 side against the elastic bias of the coil spring 104 by the fluid pressure of the fluid flowing from the first port 107 side and acting on the spool 103 through the flow passage 103f, the communication range with the communication passage 105f narrows so as to restrict the flow of the fluid.

[0060] "Restricting the flow of the fluid" means applying a brake to the flow of the fluid. Specifically, it means reducing the flow rate Qa per unit time when the fluid flows in the opposite direction with respect to the flow rate Q per unit time when the fluid flows in one direction (Qa < Q).

[0061] Next, the operation of the fluid control valve 100 according to the present embodiment will be described. When there is no fluid flow, as shown in FIG. 1, the spool 103 is moved to the first port 107 side by the elastic bias of the coil spring 104, and the spool 103 is positioned with its flat surface 103a abutting against the screw member 109.

[0062] At this time, the communication range between the movable passage 103d and the communication passage 105f is widest, and the second port 108 is connected to the first port 107 via the second passage portion 106b, the communication passage 105f, and the flow passage 103f in the first passage portion 105c.

[0063] When fluid flows in one direction from second port 108 to first port 107, the state is as shown in FIG. 1, in which spool 103 is elastically biased toward first port 107 by coil spring 104, the communication range between movable passage 103d and communication passage 105f is expanded, and second passage portion 106b and first passage portion 105c are directly connected, allowing fluid to flow smoothly in one direction as shown by arrow a in the figure.

[0064] On the other hand, when the fluid flows in the opposite direction, from the first port 107 to the second port 108, the fluid pressure of the fluid flowing from the first port 107 into the first passage portion 105c acts on the spool 103 via the T-shaped flow passage 103f.

[0065] 2, the fluid pressure compresses the coil spring 104, causing the spool 103 to slide toward the second port 108. At this time, the flat surface 103a of the spool 103 also becomes a pressure-receiving portion.

[0066] The communication range between the movable passage 103d and the communication passage 105f is narrowed by the sliding movement of the spool 103. As a result, the fluid that has flowed in from the first port 107 is subjected to a throttling action when it flows from the communication passage 105f through the movable passage 103d into the second passage portion 106b, as shown by arrow b in the figure, and is circulated to the second port 108.

[0067] Thereafter, when the fluid pressure of the fluid flowing in the opposite direction decreases and the elastic force of the coil spring 104 becomes dominant, the spool 103 slides toward the first port 107, expanding the communication range between the movable passage 103d and the communication passage 105f, and the second passage portion 106b and the first passage portion 105c are directly connected again, i.e., the state returns to that shown in FIG. 1, and the fluid flows smoothly in the opposite direction as indicated by the arrow c in the figure.

[0068] In the fluid control valve 100 according to this embodiment, when the spool 103 is slidably moved toward the first port 107 by the elastic bias of the coil spring 104, the communication range between the movable passage 103d and the communication passage 105f expands, allowing the fluid to flow in one direction, from the second port 108 to the first port 107. On the other hand, when the spool 103 is slidably moved toward the second port 108 against the elastic bias of the coil spring 104 by the fluid pressure of the fluid flowing from the first port 107 into the first passage portion 105c and acting on the spool 103, the communication range between the movable passage 103d and the communication passage 105f narrows, allowing the fluid to flow in the opposite direction, from the first port 107 to the second port 108, while throttling the flow of the fluid. Therefore, it is possible to appropriately control the smooth flow of the fluid in one direction and the throttling of the fluid in the opposite direction, which is the return direction to the one direction.

[0069] Then, in the return flow in the opposite direction, as the fluid pressure drops, the spool 103 is again slid toward the first port 107 due to the elastic force of the coil spring 104, thereby expanding the communication range between the movable passage 103d and the communication passage 105f, thereby ensuring the return of the fluid that has been released from the restriction, and making it possible to appropriately control smooth flow without any residual fluid remaining.

[0070] The fluid control valve 100 according to this embodiment includes first and second flow path bodies 105, 106, each having a first port 107 and a second port 108 connected to a flow path 101 at both ends, and each having first and second passage portions 105c, 106b through which a fluid flows, and a flow path 103f, which is connected to the first port 107 and through which a fluid flows, and a spool 103 provided in the first passage portion 105c so as to be slidable in a reciprocating direction between the first port 107 and the second port 108, and a coil spring 104 provided in the second passage portion 106b, which elastically biases the spool 103 from the second port 108 side toward the first port 107 side. 4, a communicating passage 105f provided in the first flow path body 105 for connecting the first passage portion 105c and the flow path 103f, and a movable passage 103d provided in the spool 103 so as to communicate with the communicating passage 105f, the range of communication with the communicating passage 105f being changed by the sliding movement of the spool 103 in the reciprocating direction. The mechanical elements are the hollow cylindrical flow path member 102, the solid cylindrical spool 103, and the coil spring 104, and although the mechanical structure is simple, requiring only machining of the flow path 103f, the communicating passage 105f, and the movable passage 103d, it is possible to achieve the excellent fluid control as described above.

[0071] Furthermore, because it is mechanical, it is not affected by power outages or other factors and can constantly and accurately control fluid.

[0072] A screw member 109 is provided on the first port 107 side of the spool 103 as a spring force adjustment means for adjusting the spring force of the coil spring 104 by changing the position of the spool 103 that is elastically biased by the coil spring 104, so that the communication range between the movable passage 103d and the communication passage 105f can be adjusted freely and preferably.

[0073] A pressure-receiving section (side passage 103g) on ​​which the fluid pressure of the fluid acts is formed in the flow passage 103f of the spool 103, and by utilizing the path through which the fluid flows, the fluid pressure can be appropriately applied to the spool 103 with a compact configuration.

[0074] Next, application examples of the fluid control valve 100 according to this embodiment will be described with reference to FIGS.

[0075] FIG. 5 is an explanatory diagram illustrating the hydraulic circuit of an oil damper system, which is an application example; FIG. 6 is a cross-sectional view illustrating a damping valve unit of the oil damper system; FIG. 7 is a cross-sectional view illustrating a control cylinder unit of the oil damper system; and FIG. 8 is an explanatory diagram illustrating a control valve unit of the oil damper system equipped with a fluid control valve according to this embodiment.

[0076] The oil damper system 1 is installed between the vibration input side and the vibration damping target side, for example, between the ground 2 or the foundation of a building 3 that moves integrally with the ground 2 to absorb earthquake energy, and the building 3 supported on the foundation by seismic isolation bearings.

[0077] The oil damper system 1 is mainly composed of a uniflow type cylinder unit 4.

[0078] The uniflow type cylinder unit 4 itself is known and is configured to include an outer cylinder 5, a hydraulic oil reservoir 6 provided inside the outer cylinder 5 and storing hydraulic oil F while maintaining a free surface, an inner cylinder 7 provided inside the outer cylinder 5, a piston 8 provided inside the inner cylinder 7 so as to slide freely in a liquid-tight manner and to divide the interior of the inner cylinder 7 into two hydraulic oil outlet chambers R1 and R2, a piston rod 9 connected integrally to the piston 8, which penetrates the inner cylinder 7 and protrudes liquid-tightly outward from the outer cylinder 5 and is slidable, a first damper check valve 11 provided between the hydraulic oil reservoir 6 and the hydraulic oil inlet chamber R2 and which allows hydraulic oil F to flow only from the hydraulic oil reservoir chamber 6 to the hydraulic oil inlet chamber R2 and blocks backflow, and a second damper check valve 12 provided on the piston 8 and which allows hydraulic oil F to flow only from the hydraulic oil inlet chamber R2 to the hydraulic oil outlet chamber R1 and blocks backflow.

[0079] In the uniflow type cylinder unit 4, when the piston 8 moves back and forth, the hydraulic oil in the hydraulic oil outflow chamber R1 flows out to the outer cylinder 5, and at the same time, the hydraulic oil flows from the outer cylinder 5 into the hydraulic oil inflow chamber R2, so that the hydraulic oil flows in one direction.

[0080] The pressure-receiving area of ​​the piston 8 on the hydraulic oil outflow chamber R1 side to which the piston rod 9 is connected is a value obtained by subtracting the cross-sectional area of ​​the piston rod 9, and is set to half of that on the hydraulic oil inflow chamber R2 side.

[0081] The oil damper system 1 is basically configured by providing a damping valve unit 10 that generates an energy absorption effect between the hydraulic oil outflow chamber R1 of the cylinder unit 4 and the hydraulic oil reservoir chamber 6 in the outer cylinder 5.

[0082] As shown in Figure 6, the damping valve unit 10 is composed of a valve body 13 having a hydraulic oil inlet port P1 connected to the hydraulic oil outflow chamber R1 of the inner cylinder 7 and a hydraulic oil outflow port P2 connected to the hydraulic oil storage chamber 6, a valve element 14 that is movably provided within the valve body 13 and moves to open and close the hydraulic oil inlet port P1, a spring seat 15 that is arranged within the valve body 13 on the opposite side to the valve element 14 and is movably provided in a liquid-tight state relative to the valve body 13, and a pressure-regulating spring 16 as a spring member that is provided within the valve body 13 between the spring seat 15 and the valve element 14 and is supported by the spring seat 15 to bias the valve element 14.

[0083] That is, the valve body 14 is disposed at one end of the pressure adjustment spring 16, and the spring seat 15 is disposed at the other end of the pressure adjustment spring 16.

[0084] In the damping valve unit 10, the pressure regulating spring 16 biases the valve body 14 toward the hydraulic oil inlet port P1, and the biasing force of the pressure regulating spring 16 causes the valve body 14 to close the hydraulic oil inlet port P1, thereby isolating the hydraulic oil outlet chamber R1 from the hydraulic oil reservoir 6. On the other hand, the valve body 14 opens the hydraulic oil inlet port P1 against the biasing force of the pressure regulating spring 16, thereby connecting the hydraulic oil inlet port P1 to the hydraulic oil outlet port P2, and thereby connecting the hydraulic oil outlet chamber R1 to the hydraulic oil reservoir 6.

[0085] In the damping valve unit 10, when the hydraulic oil is pushed by the piston 8 and flows from the hydraulic oil outflow chamber R1 toward the outer cylinder 5, the hydraulic oil inflow port P1 is opened by the action of moving the valve body 14 against the spring force of the pressure regulating spring 16, causing a pressure loss in the hydraulic oil and absorbing energy.

[0086] The valve body 13 of the damping valve unit 10 is further provided with an introduction port P3, which will be described later, facing the rear surface of the spring seat 15 (the side opposite to the side where the pressure adjustment spring 16 is installed).

[0087] The operation of the uniflow type cylinder unit 4 is such that when the piston rod 9 is pulled out from the outer cylinder 5 in the protruding direction and the piston 8 moves to narrow the hydraulic oil outflow chamber R1 of the inner cylinder 7, hydraulic oil F flows out from the hydraulic oil outflow chamber R1 toward the damping valve unit 10.

[0088] The outflow pressure of the hydraulic oil F flowing out from the hydraulic oil outflow chamber R1 acts on the hydraulic oil inlet port P1, moving the valve body 14, which is biased by the pressure regulating spring 16, against the spring force of the pressure regulating spring 16, thereby opening the hydraulic oil inlet port P1.

[0089] When the hydraulic oil inlet port P1 is opened, the hydraulic oil F flows through the valve body 13 of the damping valve unit 10, through the gap between the inner surface of the valve body 13 and the valve element 14, toward the hydraulic oil outlet port P2, and then flows from the hydraulic oil outlet port P2 toward the hydraulic oil reservoir 6.

[0090] Furthermore, the hydraulic oil F passes through the first damper check valve 11 and flows into the hydraulic oil inlet chamber R2.

[0091] In the damping valve unit 10, the opening operation of the valve body 14 due to the outflow pressure of the hydraulic oil F from the hydraulic oil outflow chamber R1 is restricted by the pressure regulating spring 16, that is, by continuing to circulate the hydraulic oil F while maintaining the compressed state of the pressure regulating spring 16, the energy absorption function of the oil damper system 1 is exerted.

[0092] When the hydraulic oil outflow chamber R1 is narrowed and hydraulic oil F flows out of the hydraulic oil outflow chamber R1, the hydraulic oil F flows into the hydraulic oil inflow chamber R2, which is widened, from the hydraulic oil reservoir 6 through the first damper check valve 11.

[0093] On the other hand, when the piston rod 9 is pushed in the retracting direction toward the outer cylinder 5 and the piston 8 moves to expand the hydraulic oil outflow chamber R1 of the inner cylinder 7, thereby narrowing the hydraulic oil inflow chamber R2, because the first damper check valve 11 is closed and, as mentioned above, the pressure-receiving area on the hydraulic oil inflow chamber R2 side of the piston 8 is twice the pressure-receiving area on the hydraulic oil outflow chamber R1 side, the hydraulic oil F in the pressurized hydraulic oil inflow chamber R2 is sent into the hydraulic oil outflow chamber R1 through the second damper check valve 12 of the piston 8 in an amount twice that when the piston rod 9 is extended, and half of that amount of hydraulic oil F is further pushed out of the hydraulic oil outflow chamber R1 and flows out toward the damping valve unit 10.

[0094] In the hydraulic oil outflow chamber R1, the hydraulic oil F flows in at twice the amount from the hydraulic oil inflow chamber R2, and half of that amount is replenished and the hydraulic oil F is always filled.

[0095] During the retraction of the piston rod 9, as during the extension, the outflow pressure of the hydraulic oil F flowing out of the hydraulic oil outflow chamber R1 acts on the hydraulic oil inlet port P1, moving the valve body 14, which is biased by the pressure regulating spring 16, against the spring force of the pressure regulating spring 16, thereby opening the hydraulic oil inlet port P1.

[0096] When the hydraulic oil inlet port P1 is opened, the hydraulic oil F flows through the valve body 13 of the damping valve unit 10 toward the hydraulic oil outlet port P2, and further flows from the hydraulic oil outlet port P2 toward the hydraulic oil reservoir 6.

[0097] In the damping valve unit 10, even when the piston rod 9 is retracted, the opening operation of the valve body 14 due to the outflow pressure of the hydraulic oil F from the hydraulic oil outflow chamber R1 is restricted by the pressure regulating spring 16, that is, the hydraulic oil F continues to circulate while maintaining the compressed state of the pressure regulating spring 16, thereby achieving the energy absorption function of the oil damper system 1.

[0098] Whether the piston rod 9 is protruding or retracting, if the sliding amount of the piston 8 is the same, the amount of hydraulic oil F flowing into the damping valve unit 10 is the same, and therefore the amount of energy absorption is the same.

[0099] In the uniflow type cylinder unit 4 that constitutes the oil damper system 1, as described above, the hydraulic oil F flows in one direction, flowing out only from the hydraulic oil outflow chamber R1 toward the hydraulic oil storage chamber 6 and flowing in only from the hydraulic oil storage chamber 6 to the hydraulic oil inflow chamber R2.

[0100] Between the hydraulic oil outflow chamber R1 and the hydraulic oil reservoir 6, a relief valve 17 is provided to release and control the hydraulic pressure of the hydraulic oil F in the hydraulic oil outflow chamber R1 when the piston rod 9 operates at high speed.

[0101] The cylinder unit 4 has an outer cylinder 5 connected to one of the vibration input side and the vibration attenuation target side, for example, the ground 2.

[0102] The cylinder unit 4 also has a piston rod 9 connected to the other of the vibration input side and the vibration attenuation target side, for example, a building 3 .

[0103] The cylinder unit 4 is provided so as to be connected to, for example, the ground 2 and the building 3, and the piston rod 9 and the outer cylinder 5 of the cylinder unit 4 are provided with attachment portions 37 for attachment to these objects.

[0104] When an earthquake causes a relative displacement between the ground 2 and the building 3, the piston rod 9 of the cylinder unit 4 itself moves forward and backward by a stroke amount corresponding to the amount of the relative displacement.

[0105] In this specification, the "extension and retraction stroke of the piston rod 9" refers to the change in length of the cylinder unit 4, which occurs when the piston rod 9 is pulled out in a direction protruding outward from the outer cylinder 5 and the inner cylinder 7, or pushed in a direction retracting inward, accompanying the reciprocating movement of the piston 8, causing the length dimension of the cylinder unit 4 to become longer or shorter in the length direction of the piston rod 9.

[0106] Similarly, the "extending stroke of the piston rod 9" refers to the change in the length of the cylinder unit 4 as it lengthens in the longitudinal direction of the piston rod 9, and the "retracting stroke of the piston rod 9" refers to the change in the length of the cylinder unit 4 as it shortens in the longitudinal direction of the piston rod 9.

[0107] These strokes refer to the displacement of the piston rod 9 from the inoperative state of the cylinder unit 4 in which the piston rod 9 is stopped at the initial position.

[0108] Furthermore, the "protrusion" of the piston rod 9 means that, as the piston 8 reciprocates, the piston rod 9 is pulled out in a direction that protrudes outward from the outer cylinder 5 and the inner cylinder 7, and the length dimension of the cylinder unit 4 becomes longer in the length direction of the piston rod 9. The "recession" of the piston rod 9 means that the piston rod 9 is pushed in a direction that retracts into the outer cylinder 5 and the inner cylinder 7, and the length dimension of the cylinder unit 4 becomes shorter in the length direction of the piston rod 9.

[0109] As shown in FIG. 5, the cylinder unit 4 is provided with a transmission member 18 that transmits the amount of extension and retraction stroke of the piston rod 9 that moves the piston 8.

[0110] The transmission member 18 is formed of a shaft that is long in the extension / retraction stroke direction of the piston rod 9. The transmission member 18 has a base end 18a, which is one end in the length direction, attached to the piston rod 9, and a tip end 18b, which is the other end in the length direction, supported outside the outer cylinder 5 so as to be freely movable.

[0111] The transmission member 18, whose base end 18a is attached to the piston rod 9, slides outside the cylinder unit 4 in accordance with the extension and retraction movement of the piston rod 9, and when the piston rod 9 performs an extension stroke, the tip 18b moves in the direction of the extension stroke by the same amount, and when the piston rod 9 performs a retraction stroke, the tip 18b moves in the direction of the retraction stroke by the same amount.

[0112] A pair of control cylinder units 19, 19 are provided outside the outer cylinder 5 of the cylinder unit 4, on either side of the transmission member 18, along the extending / retracting stroke direction of the piston rod 9.

[0113] One control cylinder unit 19 is provided to act on the extension stroke of the piston rod 9 and the other control cylinder unit 19 is provided to act on the retraction stroke.

[0114] As shown in FIG. 7, each of these control cylinder units 19, 19 comprises a cylinder case 20, a control piston 21 that is slidably provided in the cylinder case 20 in an airtight state and divides the interior of the cylinder case 20 into an oil chamber 20a filled with control oil f and an air chamber 20c that is maintained at atmospheric pressure through an air hole 20b provided in the cylinder case 20, and a control piston rod that is slidably movable in and out of the cylinder case 20, with one end connected to the control piston 21 from the oil chamber 20a side and the other end protruding fluid-tightly outside the cylinder case 20. 22, and a control oil inlet / outlet port P4 which is provided in the cylinder case 20 and discharges control oil f from an oil chamber 20a narrowed by a control piston 21 which is slid by the protruding operation of the control piston rod 22 toward the damping valve unit 10, and which, as will be described later, allows control oil f returned from the damping valve unit 10 to flow into the oil chamber 20a when the cylinder unit 4 has finished operating and is in a non-operating state, thereby narrowing the air chamber 20c and pushing back the control piston 21 together with the control piston rod 22.

[0115] In this specification, "the control piston rod 22 protrudes or retracts" refers to a change in length in which the control piston rod 22 is pulled out in a direction protruding outward from the cylinder case 20 or pushed in a direction retracting inward, accompanied by the reciprocating movement of the control piston 21, causing the length dimension of the control cylinder unit 19 to become longer or shorter in the length direction of the control piston rod 22.

[0116] An operating part 24 is provided at the tip 18b of the transmission member 18, and a passive part 25 with which the operating part 24 can be freely engaged and disengaged is provided at the protruding tip of the other end of the control piston rod 22 of the pair of control cylinder units 19 on both sides of the transmission member 18.

[0117] As shown in Figure 5, the pair of control cylinder units 19, 19 are installed so that the protruding directions of their control piston rods 22, 22 are opposite to each other, and so that the operating part 24 of the transmission member 18 is located between their passive parts 25, 25 in the direction of the extending and retracting stroke of the piston rod 9.

[0118] Furthermore, when the piston rod 9 of the cylinder unit 4 is in a neutral position in the direction of the protruding and retracting stroke (in other words, when the cylinder unit 4 is in its initial non-operating state) and the air chamber 20c is narrowed and the protruding stroke amount of the control piston rods 22 and 22 is positioned at its initial position of "0", the passive parts 25 and 25 of these control cylinder units 19 and 19 are spaced apart from the operating part 24 by a distance equal to the predetermined protruding and retracting stroke amount set for the piston rod 9.

[0119] The predetermined extension / retraction stroke amount refers to a protrusion stroke amount S and a retraction stroke amount S that are set equal in the protrusion stroke direction and the retraction stroke direction, respectively, with the neutral position N of the piston rod 9 as a reference, as shown in FIG.

[0120] That is, the operating portion 24 and each of the passive portions 25, 25 are equally spaced apart by a distance corresponding to the predetermined stroke amount S of the piston rod 9.

[0121] When the piston rod 9 is extended or retracted within a predetermined stroke amount S, the operating part 24 of the transmission member 18 moves accordingly, but the operating part 24 does not engage with the passive part 25 of any of the control cylinder units 19, and the control cylinder units 19 are not operated.

[0122] When the piston rod 9 experiences an excessive protruding stroke exceeding the predetermined retraction stroke amount S, for example, an excessive protruding stroke, the operating portion 24 engages with the passive portion 25 of the control piston rod 22 of one of the control cylinder units 19 .

[0123] The passive portion 25 then causes the control piston rod 22 to protrude by an excess protruding stroke amount that exceeds the predetermined protruding / retracting stroke amount S.

[0124] The control piston 21 is slid by the control piston rod 22 that is actuated to protrude, and control oil f is discharged from the inlet / outlet port P4 of the cylinder case 20 in an amount corresponding to the excess protruding stroke.

[0125] When the piston rod 9 repeating the extending and retracting strokes moves to the retracting stroke, the operating portion 24 of the transmission member 18 disengages from the passive portion 25 that has engaged to operate the control piston rod 22 to extend.

[0126] If the excess protrusion stroke amount during the next protrusion stroke does not exceed the previous excess protrusion stroke amount, the control piston rod 22 that had been protruding during that time will remain in the same position and no control oil f will be discharged.On the other hand, if the excess protrusion stroke amount increases beyond the previous excess protrusion stroke, the operating part 24 will again engage with the passive part 25, causing the control piston rod 22 to protrude again by the newly increased excess protrusion stroke amount, and as a result, control oil f will be discharged from the control cylinder unit 19 in an amount corresponding to the increased excess protrusion stroke.

[0127] When an excessive plunger stroke that exceeds the predetermined plunger stroke amount S occurs in the piston rod 9, the operating part 24 of the transmission member 18 causes the control piston rod 22 of the other control cylinder unit 19 to protrude in the same manner as the control piston rod 22 of the one control cylinder unit 19 described above, and control oil f for the excess plunger stroke and the increased excess plunger stroke is discharged from the inlet / outlet port P4 of the cylinder case 20.

[0128] In this way, when the extension / retraction stroke amount of the piston rod 9 of the cylinder unit 4 exceeds the predetermined extension / retraction stroke amount S, the control cylinder unit 19 first discharges control oil f in an amount corresponding to the excess extension / retraction stroke amount when it exceeds the predetermined extension / retraction stroke amount S, and then repeats this process of discharging control oil f in an amount corresponding to the excess extension / retraction stroke amount that exceeds the previous excess extension / retraction stroke amount.

[0129] That is, when the predetermined extension / retraction stroke amount S is exceeded, and thereafter, each time the excess extension / retraction stroke amount increases, both of the pair of control cylinder units 19, 19 discharge an increased amount of control oil f.

[0130] As shown in FIG. 5, a control oil supply system 26 is provided between the pair of control cylinder units 19, 19 and the damping valve unit 10.

[0131] The control oil supply system 26 is composed of a piping system and has a communication section 27 that connects the inlet / outlet ports P4, P4 of a pair of control cylinder units 19, 19, and also connects the communication section 27 to the inlet port P3 of the damping valve unit 10.

[0132] The control oil supply system 26 is provided with a control valve unit 30 (see FIG. 8) that is disposed between the communication part 27 and the inlet port P3 of the damping valve unit 10 and that includes a check valve 28 and a fluid control valve 100.

[0133] The check valve 28 allows the control oil f to flow from the communication portion 27 toward the introduction port P3, and prevents backflow (see arrow p in FIG. 8).

[0134] Then, hydraulic pressure is generated at the back surface of the spring seat 15 by the control oil f flowing into the valve body 13 from the inlet port P3, and this hydraulic pressure acts on the check valve 28 as back pressure.

[0135] Unlike the valve element 14, the spring seat 15 is provided in the valve body 13 so as to be movable in a liquid-tight manner.

[0136] Therefore, the control oil f flowing in from the inlet port P3 remains inside the valve body 13, pressing and displacing the spring seat 15, and therefore the control oil f does not mix with the hydraulic oil F and flow into the hydraulic oil reservoir 6 from the hydraulic oil outlet port P2.

[0137] That is, in the control oil supply system 26 equipped with the check valve 28, the control oil f discharged from each of the inlet / outlet ports P4, P4 flows back and forth between these pairs of inlet / outlet ports P4, P4, or passes through the check valve 28 and the inlet port P3 and flows onto the back surface of the spring seat 15 in the damping valve unit 10, generating oil pressure on the back surface of the spring seat 15 that changes the spring force of the pressure regulating spring 16.

[0138] The piston rod 9 of the cylinder unit 4 alternately protrudes and retracts, and as a result, when the control piston rods 22, 22 of a pair of control cylinder units 19, 19 are alternately protruded, control oil f is alternately and intermittently discharged from each inlet / outlet port P4, P4.

[0139] The check valve 28 introduces the control oil f into the inlet / outlet port P3 when the oil pressure of the control oil f discharged from the inlet / outlet port P4 of either of the control cylinder units 19 during the protruding operation and acting through the communicating part 27 exceeds its valve opening pressure, and on the other hand, when the oil pressure of the control oil f is below its valve opening pressure, the check valve 28 prevents the control oil f from flowing into the inlet port P3.

[0140] The control oil f, whose flow is blocked by the check valve 28, flows through the communicating section 27 into the inflow / outflow port P4 of the other control cylinder unit 19 (in a state where no oil pressure is generated in the oil chamber 20a and the control piston rod 22 can move toward the air chamber 20c).

[0141] This communication section 27 functions as a relief circuit when the control oil f cannot pass through the check valve 28, such as when the oil pressure generated at the back of the spring seat 15 (back pressure of the check valve 28) reaches the set upper limit value.

[0142] An excess protruding stroke amount and an excess retracting stroke amount occur, and then as these stroke amounts increase sequentially, the hydraulic pressure of the control oil f generated by a pair of control cylinder units 19, 19 which are alternately operated to protrude repeatedly acts on the check valve 28, and the check valve 28 causes the control oil f to flow into the inlet port P3 of the damping valve unit 10 each time the pressure exceeds the valve opening pressure.

[0143] As a result, within the valve body 13 of the damping valve unit 10, the control oil f is introduced from the inlet port P3 to the back surface of the spring seat 15, and the amount of control oil f gradually increases, causing the pressure regulating spring 16 to gradually contract between itself and the valve body 14, and this contraction causes the spring force of the pressure regulating spring 16 that biases the valve body 14 to change so that it becomes larger.

[0144] That is, the spring seat 15 is moved so as to compress the pressure regulating spring 16 by the hydraulic pressure of the control oil f introduced from the inlet port P3, thereby causing a change in the spring force of the pressure regulating spring 16 according to the amount of excess protruding stroke or excess retracting stroke.

[0145] As shown in FIG. 8, the control oil supply system 26 is provided with a bypass path 29 that bypasses the check valve 28 in order to return the control oil f to the pair of control cylinder units 19, 19, and the above-mentioned fluid control valve 100 is provided in parallel with the check valve 28 in this bypass path 29.

[0146] This fluid control valve 100, for example, when an earthquake subsides and the cylinder unit 4 finishes operating and becomes inactive (the piston rod 9 returns to the neutral position N in the extending / retracting stroke direction), uses the fluid pressure flowing in from the first port as described above to sequentially return the control oil f sent to the damping valve unit 10 from the inlet port P3 through the communicating portion 27 to the inlet / outlet ports P4, P4 of the pair of control cylinder units 19, 19 (see arrow q in Figure 8).

[0147] During operation of the cylinder unit 4, the fluid control valve 100 allows the control oil f blocked by the check valve 28 to bypass (see arrow r in FIG. 8).

[0148] In this oil damper system 1, for example, as described above, when an earthquake has subsided and the cylinder unit 4 has ceased operation and is in an inoperative state, the flow of hydraulic oil F that moves the valve body 14 ceases. In order to return each control piston rod 22, 22 to its initial position with a protruding stroke amount of "0", the damping valve unit 10 is provided with a return means for returning the control oil f from the damping valve unit 10 to the inlet / outlet ports P4, P4 of each control cylinder unit 19, 19.

[0149] In the example of the damping valve unit 10 shown in Figure 6, the return means is configured so that the pressure adjustment spring 16 is set to have a spring force that presses the spring seat 15 so that the control oil f flows out to the control oil supply system 26.

[0150] In other words, when the cylinder unit 4 transitions from an operating state to a non-operating state, only a slight hydraulic pressure acts on the valve body 14 of the damping valve unit 10 at the hydraulic oil inlet port P1, which is connected to the hydraulic oil outflow chamber R1, and the operating part 24 does not engage with the passive part 25 to cause the control piston rod 22 to protrude.

[0151] At this time, as the pressure regulating spring 16 expands and restores from a state in which it has been compressed by the control oil f via the spring seat 15, it presses the spring seat 15 to block the inlet port P3, and pushes almost all of the control oil f back from the valve body 13 through the fluid control valve 100 (arrow q) to the control oil supply system 26 and, ultimately, to the inlet / outlet port P4 of each control cylinder unit 19, 19.

[0152] When the hydraulic oil F is flowing, the pressure adjustment spring 16 is compressed by the valve body 14, and the reaction force acting on the spring seat 15 increases accordingly, and a strong force is applied to push back the control oil f.

[0153] However, the pressure receiving portion 103g of the spool 103 is strongly pressed and reaches the first end wall 105a side, and the movable passage 103d is at its narrowest.

[0154] For this reason, the amount of control oil f that returns to the second flow path body 106 until the earthquake subsides (1 to 2 minutes) is extremely small.

[0155] It is desirable that the spring force of the pressure regulating spring 16 is such that even when the cylinder unit 4 is in an inoperative state where the flow of hydraulic oil F has ceased, the control oil f gradually flows out and is returned to the control oil supply system 26 via the fluid control valve 100.

[0156] At this time, in the fluid control valve 100, the movable passage 103d is slightly wider than when the hydraulic oil F is flowing.

[0157] The pressure adjustment spring 16 is preferably installed in such a way that no or only a small deformation load is applied to the pressure adjustment spring 16, while the valve body 14 can close the hydraulic oil inlet port P1 and the spring seat 15 can close the introduction port P3.

[0158] In FIG. 5, reference numeral 31 denotes a hydraulic pressure gauge that displays the hydraulic pressure in the control oil supply system 26, and reference numeral 32 denotes an on-off valve for draining the control oil f provided in the control valve unit 30.

[0159] To explain the operation of the oil damper system 1, the cylinder unit 4 is set between the ground 2 and the building 3 so that the piston rod 9 is in the neutral position N in the direction of the extending and retracting stroke.

[0160] For example, when an earthquake occurs and the cylinder unit 4 begins to operate, if the piston rod 9 does not have an excessive protruding stroke or excessive retracting stroke, the pair of control cylinder units 19, 19 will not be operated, and the cylinder unit 4 will absorb the earthquake energy by having the valve body 14 of the damping valve unit 10 open and close in response to the outflow pressure of the hydraulic oil F with the initial spring characteristics set in the pressure regulating spring 16.

[0161] When an excess extension / retraction stroke amount exceeding the predetermined extension / retraction stroke amount S occurs in the piston rod 9, the operating portion 24 of the transmission member 18 operates the control cylinder units 19, 19.

[0162] When the control piston rod 22 of one of the control cylinder units 19 is extended by either the initial excessive protruding stroke or excessive retracting stroke and the control oil f is introduced from the inlet / outlet port P4 through the check valve 28 to the back of the spring seat 15 of the damping valve unit 10, the pressure regulating spring 16 is compressed, and as a result, the damping valve unit 10 opens and closes the valve body 14 against the outflow pressure of the working oil F due to the spring characteristics of the pressure regulating spring 16, which have been changed to a spring force greater than the initial spring characteristics, thereby increasing the absorption of earthquake energy.

[0163] When the excess extension / retraction stroke is within the initial excess extension / retraction stroke amount and does not exceed this amount, the pair of control piston rods 19, 19 are not operated to extend further by the transmission member 18.

[0164] On the other hand, whenever an excess protruding stroke or excess retracting stroke occurs that exceeds the previous excess protruding stroke, the check valve 28 is opened by the oil pressure of the control oil f discharged from each of the pair of control cylinder units 19, 19, and each time this occurs, the control oil f is introduced into the damping valve unit 10, causing the spring force of the pressure regulating spring 16 to change increasingly significantly.

[0165] Therefore, the larger the extension / retraction stroke of the piston rod 9 caused by an earthquake, the greater the spring force of the pressure adjustment spring 16 of the damping valve unit 10 can be made to change the energy absorption performance to a greater extent.

[0166] Thereafter, for example, when the earthquake subsides and the cylinder unit 4 finishes operating and becomes inoperative (the piston rod 9 returns to the neutral position N in the extending / retracting stroke direction), the movable passage 103d widens slightly, and in the damping valve unit 10, the pressure regulating spring 16, which had been in a contracted state until then, expands with the valve body 14 side as the base point, making it slightly easier for it to elastically restore, thereby pressing the spring seat 15 toward the inlet port P3, and the control oil f introduced into the valve body 13 can be gradually returned to the control oil supply system 26.

[0167] In the control oil supply system 26, the control oil f flows from the bypass passage 29 through the fluid control valve 100 in the direction of the arrow q.

[0168] In the fluid control valve 100, while the fluid pressure of the control oil f flowing out from the inlet port P3 is high, this fluid pressure moves the spool 103 toward the second port 108, compressing the coil spring 104 and narrowing the movable passage 103d, thereby restricting the flow of the control oil f flowing through this narrowed movable passage 103d.

[0169] Thereafter, as the fluid pressure decreases, the spool 103 is pushed back by the elastic force of the coil spring 104, widening the movable passage 103d, and almost the entire amount of control oil f flows smoothly from the inlet port P3 side through this widened movable passage 103d and flows out from the second port 108.

[0170] The control oil f flowing out of the fluid control valve 100 flows into the communicating portion 27 and is then returned to the oil chambers 20a, 20a through the inlet / outlet ports P4, P4 of each control cylinder unit 19, 19, causing the control pistons 21, 21 to slide to narrow the air chambers 20c, 20c, and the control cylinder rods 22, 22 are retracted into the cylinder cases 20, 20, and the control cylinder units 19, 19 are returned to their initial state.

[0171] In this oil damper system 1, when the flow of hydraulic oil F that moves the valve body 14 ceases, in order to return each of the control piston rods 22, 22 to their initial positions, a return means that returns the control oil f to each of the control cylinder units 19, 19 is configured as a pressure regulating spring 16 and is provided in the damping valve unit 10.Therefore, between the control cylinder unit 19 where the control oil f circulates and the control oil supply system 26, there are no points where foreign matter such as dirt can get mixed into the control oil f, and early deterioration of the control oil f can be prevented.

[0172] When the spring force of the pressure regulating spring 16 is large, the movable passage 103d is narrowed, so the control oil f slowly returns to the control cylinder units 19, 19 over time (high damping performance is maintained at least until the earthquake subsides), and as the spring force of the pressure regulating spring 16 decreases, the movable passage 103d becomes larger, so all of the control oil f can be returned to the control cylinder units 19, 19.

[0173] In addition, by increasing or decreasing the amount of screwing of the screw member 109 and changing the position of the spool 103, the spring force of the coil spring 104 can be increased or decreased, so by adjusting the relationship between the spring force of the pressure adjustment spring 16 and the degree of opening of the movable passage 103d, the time it takes for the control oil f to return to the control cylinder units 19, 19 can be adjusted.

[0174] Furthermore, by providing the damping valve unit 10 with the pressure adjusting spring 16 as the return means, maintenance work relating to the spring characteristics for adjusting performance can be performed on the damping valve unit 10 alone.

[0175] As a result, the maintainability of the oil damper system 1 can be improved.

[0176] A bypass path 29 that bypasses the check valve 28 is provided in the control oil supply system 26, and a fluid control valve 100 is provided in the bypass path 29 in parallel with the check valve 28 to sequentially return the control oil f from the inlet port P3 of the damping valve unit 10 to the inlet / outlet ports P4, P4 of the pair of control cylinder units 19, 19 via the communicating part 27.Therefore, after the end of an earthquake, the cylinder unit 4 and the pair of control cylinder units 19, 19 can be smoothly returned to the neutral state they were in before operation. [Explanation of symbols]

[0177] 100 Fluid control valve 101 Flow path 102 Flow path member 103 spool 103d Movable passage 103f Distribution path 103g Yokoji 104 Coil spring 105 First flow path body 105c 1st passage section 105f communication path 106 Second flow path body 106b 2nd passage section 107 Port 1 108 Second Port 109 Screw parts

Claims

1. A fluid control valve that is provided in a flow path and allows a fluid to flow in one direction and restricts the flow of a fluid in the opposite direction, a flow path member having a first port and a second port connected to the flow path at both ends and provided with a passage portion through which a fluid flows; a spool having a flow passage communicating with the first port through which a fluid flows, the spool being provided in the passage portion so as to be slidable back and forth between the first port and the second port; a spring provided in the passage portion and elastically biasing the spool from the second port side toward the first port side; a communication passage provided in the flow path member for communicating the passage portion with the flow path; a movable passage provided on the spool so as to communicate with the communication passage, the range of communication with the communication passage being changed by sliding movement of the spool in a reciprocating direction; a fluid control valve characterized in that the range of communication between the movable passage and the communication passage widens when the spool is slidably moved toward the first port by the elastic bias of the spring, and the range of communication between the movable passage and the communication passage narrows so as to restrict the flow of fluid when the spool is slidably moved toward the second port against the elastic bias of the spring by fluid pressure of fluid acting on the spool from the first port side.

2. 2. The fluid control valve according to claim 1, wherein the first port is provided with a spring force adjusting means for adjusting the spring force of the spring by changing the position of the spool elastically biased by the spring.

3. 3. The fluid control valve according to claim 1, wherein a pressure receiving portion on which fluid pressure of the fluid acts is formed in the flow passage of the spool.

Images