JP5620596B1 - Structure damping device - Google Patents

Abstract

A damping force characteristic of a hydraulic damper is changed according to the strength of an earthquake, and the characteristic is maintained for a long time regardless of a change in environmental temperature. A hydraulic damper includes a preload chamber in which high pressure gas is sealed in series with a hydraulic chamber. The preload chamber 29 absorbs the volume change of the hydraulic chamber 27 due to the temperature change of the oil and the volume change of the hydraulic chamber by the piston rod 6, and balances the urging force of the spring 40 in the oil chamber 27a and the preload chamber 29. The piston valves 371 and 372 have a large damping force characteristic for a weak earthquake and a low damping force characteristic for a strong earthquake. [Selection] Figure 3

Description

  The present invention relates to a vibration damping device that is attached obliquely between two structural members such as a column and a beam to suppress the shaking of the structure in the event of an earthquake.

  Conventionally, there is a structure using a hydraulic damper as a structure damping device (see Patent Documents 1, 2, and 3). In the hydraulic damper, a hydraulic chamber formed in a cylinder is partitioned by a piston, and piston rods are inserted through wall surfaces provided at both ends of the hydraulic chamber. In the hydraulic damper, the piston rod side is connected to one structural member and the cylinder side is diagonally connected to the other structural member to form a brace damper, and the vibration of the structure due to an earthquake is caused by the two oil chambers partitioned by the piston. The viscous fluid (oil) is attenuated by flowing through the throttle oil passage.

  Since the piston rod penetrates the hydraulic chamber, the volume of the hydraulic chamber does not change due to the movement of the piston rod.

JP-A-6-346625 JP 10-227145 A JP 2000-54677 A

  The hydraulic dampers installed in the walls and attics of buildings are affected by the temperature and solar radiation, and the ambient temperature exceeds 50 ° C from below freezing. Exposed to diurnal changes. The ambient temperature change affects oil (viscous fluid) filled in the hydraulic chamber of the hydraulic damper, and the oil repeatedly expands and contracts.

  The hydraulic damper is configured such that the movement of the piston rod does not cause a change in the volume of the hydraulic chamber, and the volume of the hydraulic chamber formed by the cylinder and both end wall surfaces is constant. Therefore, when the oil expands and contracts due to the above temperature change, the oil pressure in the hydraulic chamber changes greatly, and a large oil pressure change acts on the seal attached to the wall surface on which the piston rod is slidably inserted. If the oil leaks to the outside of the hydraulic chamber or the outside air enters the hydraulic chamber, the function of the hydraulic damper may be deteriorated at an early stage.

  Therefore, the present invention has a structure in which the volume of the hydraulic chamber of the hydraulic damper can be changed, and the damping force characteristic can be changed corresponding to the strength of the earthquake, so that the function can be maintained over a long period of time. An object of the present invention is to provide a vibration damping device for an object.

The present invention has a cylinder (5) hydraulic chamber filled with oil in the (27), and divided into two oil chambers (27a) (27b) by said hydraulic chamber one piston (10) the includes a hydraulic dampers (1) communicating with oil between the two oil chambers by a predetermined attenuation characteristic, one of the structural members of the end of the piston rod (6) connecting to the piston (10) ( 2), the end (9) of the cylinder is connected to the other structural member (3), and the hydraulic damper (1) is installed obliquely between the one and the other structural members. In the structure damping device (A)
The hydraulic chamber (27) is formed between an end member (19) integrated at least in the axial direction with the cylinder (5) and a float member (23) movable in the axial direction with respect to the cylinder,
A preload chamber having a biasing force that opposes the hydraulic pressure acting on the float member (23) from the hydraulic chamber (27) between the closed portion (9) at the end of the cylinder and the float member (23). 29)
The piston (10) includes a first piston valve (37 ₁ ) for restricting the flow of oil from one of the two oil chambers (27a) to the other oil chamber (27b), and the other oil A second piston valve (37 ₂ ) for restricting the flow of oil from the chamber (27b) to the one oil chamber (27a);
Each of the first and second piston valves (37 ₁ , 37 ₂ ) has a moving speed of the piston (10) relative to the cylinder (5) with respect to an oil flow in a direction opposite to the regulated flow. In a low state, the resistance force against the oil flow is large, and in a state where the moving speed of the piston (10) is fast, the resistance force against the oil flow is small.
It is in the structure damping device characterized by the above.

For example, referring to FIG. 5, the first and second piston valves (37 ₁ , 37 ₂ ) are respectively connected to the cylinder (5) with respect to the oil flow in the direction opposite to the restricted flow. When the moving speed (V) of the piston (10) is less than or equal to a predetermined value (P), it is in the closed position and restricts the flow of oil, and the hydraulic damper (1) has a steep slope with a large load change with respect to the moving speed. It becomes a state (S) close to a rigid body having a large damping characteristic that rises at a position where the piston is opened when the moving speed (V) of the piston is faster than the predetermined value (P) to allow the oil flow, and the hydraulic damper (1) is a damping state (T) with a small damping characteristic consisting of a gentle gradient with a small load change with respect to the moving speed .

  For example, referring to FIG. 3, in the hydraulic damper (1), the piston rod (6) penetrates only one oil chamber (27a) of the two oil chambers from the piston (10). It extends.

  The hydraulic damper (1) is contracted between the end member (19) and the piston (10), and a spring (40) is disposed in the one oil chamber (27a).

  The preload chamber comprises a gas chamber (29) in which an inert gas having a predetermined pressure is sealed.

One end of the cylinder (5) is closed with a cap member (7), and a scraper (30) for scraping off the adhering matter of the piston rod (6) is provided on the cap member,
The space between the cap member (7) and the end member (19) was a marginal gap (31) having a length equal to or longer than the stroke of the hydraulic damper (1).

For example, referring to FIG. 4, the first and second piston valves (37 ₁ , 37 ₂ ) are formed on both side surfaces (10a, 10b) of the piston (10), and the hydraulic damper (1) annular projection consisting of circumference around the central axis (45), projecting outer peripheral portion raised is urged to abut the flexible valve seat plate (50), before Symbol piston (10 ) And oil passages (47) (49) respectively communicating with the outer diameter side and the inner diameter side of the protrusion ,
When the moving speed of the piston (10) is equal to or less than the predetermined value (P), the valve seat plate (50) substantially contacts the annular protrusion on the entire circumference thereof, and the oil flow in the oil passage is reduced. Limit
When the moving speed of the piston exceeds the predetermined value (P), the valve seat plate (50) bends against the urging force and moves away from the annular protrusion (45) in its entire circumference, and the oil passage The oil flow is allowed at once.

For example, referring to FIG. 7, both sides of the piston (10 ′) between the annular protrusion (45) and a boss part (44) for inserting the piston rod (6a) of the piston (10 ′). Each of the surfaces (10′a, 10′b) has hydraulic spaces (46, 46),
One end of each of the oil passages (47) and (49) communicating with the both hydraulic spaces, the other end communicating with the outer diameter side of the protrusion (45),
The protrusion height (H) of the protrusion (45) on both side surfaces (10′a, 10′b) of the piston is configured to be higher than the protrusion height (h) of the boss portion (44) ( H> h), the valve seat plate (50) comes into contact with the protrusion (45) with a predetermined preload.

  A predetermined number of spacers (55) are interposed between the boss portion (44) and the valve seat plate (50) so that the valve seat plate (50) is disposed on both side surfaces (10′a, 10) of the piston. It is attached to 'b).

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, it does not have any influence on the structure as described in a claim by this.

  According to the first aspect of the present invention, the hydraulic damper includes the preload chamber in series with the hydraulic chamber, and the float member resists the biasing force of the preload chamber even if the oil in the hydraulic chamber expands or contracts due to a temperature change. Therefore, the volume of the hydraulic chamber is changed according to the expansion or contraction of the oil to prevent leakage of the oil from the hydraulic chamber or the intake of air into the hydraulic chamber. Can be maintained over a long period of time.

  Also, when the piston part is provided with the first and second piston valves, the earthquake is weak and the moving speed of the piston is low, the hydraulic damper is in a state close to a rigid body having a large resistance force against the oil flow and a large damping force characteristic. The hydraulic damper mounted diagonally between the structural members can effectively suppress the shaking of the structure, and when the earthquake is strong and the moving speed of the piston is high, the hydraulic damper is between the oil chambers. It is a vibration damping state with low resistance to oil flow and low damping force characteristics, which suppresses vibrations of the structure, prevents damage to the mounting part of the hydraulic damper, and effectively absorbs vibrations of the structure. it can.

  Together, these vibration damping devices that use hydraulic dampers suppress or dampen the structure according to the magnitude of the earthquake, and the hydraulic dampers perform their performance regardless of environmental temperature changes. It is possible to maintain and reduce the damage caused by the earthquake of the structure over a long period of time.

Damping force characteristic of hydraulic damper, when the moving speed of the piston is less than the predetermined value, becomes greater steepness of the resistance load change relative moving speed, the moving speed is equal to or larger than the predetermined value, smaller resistance load change with respect to the moving speed Because it has a gentle slope, it suppresses the shaking of the structure against small energy from weak earthquakes, roads, etc., and maintains the quality of the structure such as the habitability of buildings, and also against large energy from strong earthquakes, etc. The energy can be absorbed to effectively prevent the destruction of structures such as buildings and improve the earthquake resistance.

According to the second aspect of the present invention, since the piston rod extends through only one hydraulic pressure, the hydraulic damper has a simplified structure of the hydraulic damper and the basic structure of the hydraulic damper established for automobiles. Therefore, it is possible to provide a structure damping device using a highly reliable hydraulic damper. Further, since the piston rod is only in one oil chamber, the volume of the hydraulic chamber changes depending on the stroke of the piston, but the volume change is absorbed by the preload chamber.

According to the third aspect of the present invention, since the hydraulic damper has a spring disposed in one oil chamber, the pressure difference based on the cross-sectional area of the piston rod acting on the piston from both oil chambers is balanced by the spring, The urging force from the preload chamber and the urging force of the spring are balanced and held near the stroke center of the hydraulic chamber. As a result, the length of the hydraulic damper in the natural state becomes constant, the mounting of the hydraulic damper to the structure becomes easy, and the performance of the structure as a vibration damping device is stabilized. Even if it is deformed to the plastic region, the structure can be returned to the original state by the restoring force to the neutral position of the hydraulic damper.

According to the fourth aspect of the present invention, since the preload chamber is composed of a gas chamber filled with an inert gas, the urging force facing the hydraulic chamber can be easily obtained by adjusting the gas pressure in the gas chamber. .

According to the fifth aspect of the present invention, since the clearance gap having a length equal to or longer than the stroke of the hydraulic damper is provided, the piston rod portion slidably contacted with the end member is attached with dust, rust, water, etc. by the scraper. There ready for being removed, can be or damaged seal end member by be sampled stroke of the hydraulic damper, it deposits on the inside of the hydraulic chamber to prevent intrusion.

According to the sixth aspect of the present invention, the first and second piston valves need only have a simple configuration including a protrusion, a valve seat plate, a disc spring, and an oil passage. Further, the outer peripheral portion of the valve seat plate is separated from the entire circumference of the annular protrusion having a long circumference, so that the oil passage area can be ensured and can be switched between the steep slope and the gentle slope at once. The damping force characteristic can be obtained easily and reliably.

According to the seventh aspect of the present invention, it is possible to appropriately switch the damping force characteristics of the first and second piston valves at the predetermined value by applying a preload to the valve seat plate.

According to the eighth aspect of the present invention, the preload of the valve seat plate can be easily adjusted by adjusting the number of spacers or the plate thickness, and the strength, structure, vibration of the structure such as a building can be adjusted. The hydraulic damper can be adjusted appropriately according to characteristics and the like.

The front view which shows embodiment which applied the damping device which concerns on this invention to the building. The front view which shows the hydraulic damper. FIG. It is an enlarged view of the piston part which shows a piston valve, (a) is aa sectional drawing of (b), (b) is a side view. The figure which shows the damping-force characteristic of a hydraulic damper. Sectional drawing which shows the state which the valve seat plate of the piston valve bent. Sectional drawing which shows the piston valve which changed partially.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, the vibration damping device A having the hydraulic damper 1 is installed obliquely between a pillar 2 and a beam 3 of a building. This vibration damping device A is suitable for use in wooden houses such as the frame construction method, 2 × 4 construction method, etc., but is not limited to this, such as lightweight steel structures, heavy steel structures, and other towers, bridges, etc. It can be applied to any structure, and can be applied not only to new construction but also to seismic reinforcement of existing structures. Further, the vibration damping device A is not limited to one in which the hydraulic damper 1 is directly connected between the structural members, and the hydraulic damper may be interposed in a part of the brace structure.

  The hydraulic damper 1 has a cylinder 5 and a piston rod 6 as shown in FIGS. One end of the cylinder 5 is closed by a cap member 7, and the other end is closed by a connecting member 9. One end of the piston rod 6 is a small-diameter portion 6a, and the piston 10 is fitted to the small-diameter portion 6a. A boss portion 11 is integrally fixed to the other end of the piston rod 6. A mounting bracket 13 is rotatably connected to the boss portion 11 via a bolt 12. A boss 15 is integrally fixed to the other end connecting member 9 of the cylinder 5, and the other mounting bracket 17 is rotatably connected to the boss 15 via a bolt 16.

  An annular end member 19 is fitted on one side of the cylinder 5, and the end member 19 is defined by the snap ring 20 so that its axial position is integrated with the cylinder 5. An O-ring 21 is attached to the outer peripheral surface of the end member 19, and an O-ring 22 is also attached to the inner peripheral surface through which the piston rod 6 penetrates. The space is oil-tight. A float member 23 is fitted to the other side of the cylinder 5 so as to be movable in the axial direction. A slide ring 25 and a seal ring 26 are mounted on the outer peripheral surface of the float member 23 side by side in the axial direction. Yes. The float member 23 partitions the space before and after the axial direction in an oil-tight and air-tight manner.

  A space between the end member 19 and the float member 23 in the cylinder 5 is filled with oil having a predetermined viscosity to form a hydraulic chamber 27. The oil means a liquid having a predetermined viscosity and is generally oil, but is not limited to oil in a narrow sense. An inert gas such as nitrogen gas having a predetermined pressure is sealed in a space between the float member 23 and the connecting member 9 in the cylinder 5 to constitute a gas chamber (preload chamber) 29. The cap member 7 at one end of the cylinder has a guide hole 7a that slidably passes through the piston rod 6 and supports the piston rod. The piston rod 6 is slidably contacted with the piston rod 6 in the guide hole 7a. A scraper 30 for scraping off dust adhering to the surface is mounted. A space between the end member 19 and the cap member 7 in the cylinder 5 is an air chamber (extra gap) 31 through which air can freely enter and exit. The interval between the air chambers 31 in the axial direction is longer than the stroke of the hydraulic damper 1.

A spring bracket 32 is disposed adjacent to the hydraulic chamber 27 side of the end member 19, and a spring bearing ring member 33 is disposed so as to be fitted to the small diameter portion 6 a of the piston rod 6. A nut 36 is screwed onto the tip of the small-diameter portion 6a of the piston rod 6 via a washer 35, the spring receiving ring member 33 is in contact with the small-diameter portion step portion 6b, and the first and the first on both sides of the piston 10. 2 piston valves ₃₇ 1, 37 ₂ as interposed by sandwiching the piston 10 positioned by the nut 36, the spring receiving ring member 33, the piston 10 and both the piston valve ₃₇ 1, 37 ₂ with respect to the piston rod 6 Has been. The piston 10 divides the hydraulic chamber 27 into a rod side oil chamber 27a and a non-rod side oil chamber 27b. In the rod side oil chamber 27a, a coil spring 40 is contracted between the spring receiving metal fitting 32 and the spring receiving ring member 33.

  As shown in detail in FIG. 4, the piston 10 has annular and convex projections 45, 45 centered on the piston rod 6 on both side surfaces 10 a, 10 b, and the projection 45 and the piston rod small diameter are formed. Between the boss portion 44 into which the portion 6a is inserted, annular hydraulic spaces 46, 46 are formed. The protrusion 45 and the boss portion 44 have the same protruding height, that is, flush with the piston side surfaces 10a and 10b. The piston 10 has a plurality of (three) push-side oil passages 47 communicating with the hydraulic space 46 on one side surface 10a and the outer diameter side of the projection 45 on the other side surface 10b, and the hydraulic pressure on the other side surface 10b. A plurality of (three) pull-side oil passages 49 are formed to communicate the space 46 with the outer diameter side of the projection 45 on one side surface 10a. These oil passages 47, 49 have the same shape and the same number. It consists of a rectangular section that is long in the circumferential direction.

Said first and second piston valves 37 _1, 37 ₂ is made of an annular leaf spring, the outer peripheral portion thereof with the valve seat plate 50 abuts on the annular projection 45, the valve seat plate 50 of the annular And a disc spring 51 that presses against the protrusion 45 with a predetermined biasing force. First and second piston valves ₃₇ 1, 37 ₂ of the left and right of the piston 10, for each one of the movement of the piston 10, Ryoaburashitsu 27a, the movement of the oil through the oil passage 47 or 49 of 27b It functions as a check valve for regulating, and controls the flow of oil through the oil passage 47 or 49 of both oil chambers 27a and 27b to a predetermined characteristic with respect to the other movement of the piston. That is, the first and second piston valves 37 _1, 37 _2, as shown in FIG. 5, with respect to the flow of each of the regulated the flows in the opposite direction oil, the piston 10 below the predetermined value P When the moving speed V of the piston 10 is larger than the predetermined value P, the change in the load F that moves the piston is large with respect to the moving speed change (S portion). On the other hand, it has a damping force characteristic in which a change in the load F that moves the piston is small (T portion). The predetermined value P is substantially displayed as a point in FIG. 5, but is switched between the steep slope (S portion) and the gentle slope (T portion) in a narrow region like the point. However, as shown by a chain line in FIG. 5, it may be a smooth switching within a certain range, and the predetermined value is a concept including this. In the present embodiment, the first and second piston valves 37 _1, 37 ₂ of each valve seat plate 50 is 2 plate, but the disc spring 51 is made of three, which, depending on the characteristics The number, the radial dimension, and the plate thickness are appropriately set. Further, a pressure ring 53 having a predetermined oil-tight property and slidingly contacting the inner peripheral surface of the cylinder 5 is mounted on the outer peripheral surface of the piston 10.

  Since the present embodiment is configured as described above, the hydraulic damper 1 is provided between the column 2 and the beam 3 by attaching the mounting brackets 13 and 17 to the column 2 and the beam 3 of the house with screws or the like. Installed diagonally. A change in the ambient temperature affects the temperature of the oil in the hydraulic chamber 27 and the oil expands or contracts. Then, the float member 23 that is slidably supported by the cylinder 5 and constitutes a free piston responds to the urging force of the high-pressure gas in the gas chamber 29 according to the volume change of the hydraulic chamber 27 due to the expansion or contraction of the oil. Move against or in sequence. As a result, even when the volume of the oil in the hydraulic chamber changes due to the ambient temperature, the float member 23 moves and is absorbed by the elastic compression of the high pressure gas, and the O-rings 21 and 22 of the end member 19 and the slide ring of the float member 23 are absorbed. It is possible to prevent oil leakage and suction of air or the like from each of the rings without applying excessive pressure to the 25 and the seal ring 26.

  The piston rod 6 extends to the rod side oil chamber 27a of the hydraulic chamber 27 so as to protrude outside the cylinder 5, and the piston rod 6 does not extend to the non-rod side oil chamber 27b. A hydraulic pressure difference in cross-sectional integral of the piston rod 6 is generated. Accordingly, the piston 10 exerts a biasing force in the direction of movement toward the piston rod 6 due to the area difference between the oil chambers 27a and 27b with respect to the piston 10, but in the present embodiment, the rod-side oil chamber 27a. The urging force of the spring 40 disposed on the piston 10 acts on the piston 10, and the piston 10 is located between the total compression position of the spring 40, which is a position where the spring urging force and the biasing force due to the area difference are balanced, Held in an intermediate position.

  The hydraulic pressure in the hydraulic chamber 27 based on the urging force of the spring 40 acts on the float member 23, but high-pressure gas is sealed in the gas chamber 29, and the float member 23 has a hydraulic pressure on the hydraulic chamber 27 side. The gas pressure on the gas chamber 29 side is balanced and held at a predetermined position.

  Thus, the hydraulic damper 1 is in a predetermined length in a natural state where no external force is applied, and the hydraulic damper 1 having the predetermined length is connected to the column 2 and the beam 3 as described above. Installed between. In this state, the piston 10 is positioned approximately at the center of the possible stroke range of the hydraulic chamber 27.

When a building shakes due to an earthquake, the hydraulic damper 1 is expanded and contracted, and receives a force by which the piston 10 located substantially in the center of the stroke range moves in the left-right direction in FIG. When the piston 10 tries to move the hydraulic chamber 27 in the right direction (pushing direction), the oil in the non-rod side oil chamber 27b flows into the left hydraulic space 46 through the push side oil passage 47, and the first piston valve. 37 by bending the _first valve seat plate 50 acts force flowing into the rod side oil chamber 27a, on the contrary, when the piston 10 tries to move the oil pressure chamber 27 in the left direction (pulling direction), the rod-side oil flows to the right hydraulic space 46 through the oil pulling side oil passage 49 of the chamber 27a, the direction of force flowing deflect the second piston valve 37 _{and second} valve seat plate 50 in a non-rod side oil chamber 27b acts . At this time, in the push-side movement of the piston 10, the valve seat plate 50 of the _second piston valve 372 comes into contact with the annular protrusion 45, and the right hydraulic space 46 and the pulling-side oil passage 49 from the non-rod side oil chamber 27 _b. The flow of oil flowing through the rod-side oil chamber 27a through the rod-side oil chamber 27a is blocked, and when the piston 10 is pulled, the valve seat plate 50 of the _first piston valve 371 comes into contact with the annular protrusion 45 and the rod-side oil 45 The flow of oil from the chamber 27a through the left hydraulic space 46 and the push side oil passage 47 to the non-rod side oil chamber 27a is blocked.

When the earthquake is weak and the building shake is small, the force in the telescopic direction acting on the hydraulic damper 1 is also small and weak. In this case, the force that the piston 10 tries to move in the hydraulic chamber 27 is weak and its speed is low. When the hydraulic damper 1 contracts, that is, when the piston 10 moves toward the non-rod side oil chamber 27b, the oil in the non-rod side oil chamber 27b will flow to the left hydraulic space 46 through the push side oil passage 47. However, since the force for moving the piston 10 is weak and slow, the increase in hydraulic pressure acting on the left hydraulic space 46 is small. Accordingly, the first piston valve 37 _1, the valve seat plate 50 by the biasing force of the disc spring 51 is held substantially in contact with the closed position the annular projection 45. Similarly, when the hydraulic damper 1 extends, that is, when the piston 10 moves toward the rod-side oil chamber 27a, the oil in the rod-side oil chamber 27a will flow to the right hydraulic space 46 through the pull-side oil passage 49. Although a smaller hydraulic pressure of said right hydraulic space 46, the second piston valve 37 _2, the valve seat plate 50 is held substantially in contact with the closed position the annular projection 45.

  Therefore, when the magnitude of the earthquake is relatively small and the energy acting on the building is small, the hydraulic damper 1 causes the oil to flow to the non-rod side oil chamber 27b and the rod side oil chamber 27a in both the contraction and extension directions. The flow is limited and the damping force characteristic is large, and the expansion / contraction movement of the hydraulic damper 1 receives a large resistance force. That is, when the moving speed of the piston 10 is slow, the flow rate of the oil in the oil chambers 27a and 27b is a slight amount due to the gap between the valve seat plate 50 and the annular protrusion 45, as shown in S part of FIG. A large load (resistance force) acts, and the hydraulic damper 1 is in a state close to a rigid body in which the gradient of the load F with respect to the piston speed V is large. As a result, when the magnitude of the earthquake is small or the vibration of the vehicle passing through the road is small and the vibration energy is small and the vibration of the building is relatively small, the vibration damping device A including the hydraulic damper 1 is rigid with respect to the building. It functions as a cheek cane and brace close to, which suppresses shaking of the building and improves the strength of the building. At this time, even if concentrated loads are applied to the mounting portions 13 and 17 of the pillar 2 and the beam 3 of the hydraulic damper 1, the vibration energy is relatively small, so that the mounting portions are not damaged. The oil flowing between the oil chambers 27a and 27b flows through a narrow passage such as a gap between the valve seat plate 50 and the annular protrusion 45 while receiving a large resistance, so that it is converted into heat and becomes hysteresis. It effectively absorbs the shaking energy. In this way, for small vibration energy that occurs at a relatively high frequency, the building is suppressed from shaking by the hydraulic damper with the above-mentioned high damping force characteristics, and the quality of the structure such as the habitability of the building is improved. can do.

When the magnitude of the earthquake is large and the shaking of the building is large, the force in the expansion / contraction direction acting on the hydraulic damper 1 increases, the stroke increases, and the speed increases. In this state, the piston 10 moves quickly with a large stroke, and when the piston 10 moves to the right, the oil pressure flowing from the non-rod side oil chamber 27b through the push side oil passage 47 into the left hydraulic space 46 is increased. higher becomes the first piston valve 37 ₁ in the valve seat plate 50, as shown in FIG. 6, its peripheral portion against the biasing force of the disc spring 51 as a spring force and backup the seat plate itself cyclic It bends in the direction away from the projection 45. Similarly, when the piston 10 is moved to the left, from the rod-side oil chamber 27a, the hydraulic pressure of the oil is increased to flow into the right hydraulic space 46 through the pulling side oil passage 49, the second piston valve 37 _second valve The seat plate 50 bends in a direction away from the annular protrusion 45.

As a result, the first and second piston valves 37 ₁ and 37 ₂ have flow paths C and D formed between the valve seat plate 50 and the annular protrusion 45, as shown in FIG. As the oil flows through the oil chambers 27a and 27b through C and D, the gradient of the load F with respect to the speed V becomes low and the damping force characteristic is low as shown in a T portion of FIG. It expands and contracts with low resistance. Therefore, in the event of a large earthquake, the hydraulic damper 1 controls the shaking of the building with a relatively low damping force characteristic and absorbs the earthquake energy. At this time, as shown in FIG. 6, the outer diameter portion of the valve seat plate 50 is separated from the annular protrusion 45 and the entire circumference thereof, and has a relatively large area between the annular protrusion 45 having a long circumferential length. The flow paths C and D are formed at a stretch. Thereby, as shown in FIG. 5, the damping force characteristic of the hydraulic damper is instantaneously switched from a steep slope (S) to a gentle slope (T) at a predetermined value P.

  In this state, since the hydraulic damper 1 dampens while expanding and contracting, an excessively large concentrated load does not act in the vicinity of the mounting brackets 13 and 17, and the mounting portion or the column 2 and the beam 3 of the mounting portion are not moved. Reduces being destroyed. Further, the seismic energy is converted into heat and absorbed by a relatively large amount of oil flowing while being squeezed through the upper flow paths C and D. Further, even if the building is deformed to the plastic deformation region due to the earthquake, the hydraulic damper 1 balances the gas pressures of the spring 40 and the gas chamber 29 and the two oils due to the area difference of the piston rod 6 after the earthquake is over. The building 27a, 27b is urged to return to the initial position, and the building deformed until the plastic deformation is also returned to its original state (initial posture) by urging the hydraulic damper 1 to the stroke center position. Thereby, although the frequency is low, when a large earthquake occurs, the building is effectively damped by the vibration damping device A, and the building can be prevented from being destroyed and the earthquake resistance can be improved.

The hydraulic damper 1 is provided with an air chamber (extra gap) 31 on the side from which the piston rod 6 projects from the cylinder 5, and the piston rod 6 in the air chamber 31 portion is dusted by the scraper 30 of the cap member 7. It is in a clean state with rust and water removed. Therefore, even if the hydraulic damper 1 expands and contracts due to the earthquake and the piston rod 6 slidably contacts the through hole of the end member 19, the slidable contact portion is a portion in the clean state. It is possible to prevent dust and the like adhering to the rod from damaging the seal 22 of the end member 19 and intruding the dust and water into the hydraulic chamber 27.

An embodiment in which the piston valves 37 ′ ₁ and 37 ′ ₂ are partially changed will be described with reference to FIG. Note that parts similar to those of the previous embodiment are denoted by the same reference numerals and description thereof is omitted. Piston 10 'has the boss | hub part 44 and the cyclic | annular protrusion 45 which insert the piston rod small diameter part 6a. The protrusion height H of the protrusion 45 on both side surfaces 10 ′ a and 10 ′ b of the piston is configured to be higher than the protrusion height h of the boss portion 44. The first and second piston valves 37 ′ ₁ and 37 ′ ₂ are provided with nuts 36 between the piston rod stepped portions 6b on both side surfaces of the piston 10 ′ via washers 35, spring receiving ring members 33 and the like. Installed by tightening.

  By tightening the nut 36, the valve seat plate 50 and the disc spring 51 are pressed so that the central portion thereof is in contact with the boss portion 44 and the outer peripheral portion of the valve seat plate 50 is in contact with the protrusion 45. Due to the difference in protrusion height (H> h) between the protrusion 45 and the boss portion 44, the valve seat plate 50 made of a leaf spring is bent and given a predetermined preload in a direction in which the outer peripheral portion contacts the protrusion 45.

  Accordingly, when the moving speed of the piston 10 ′ is equal to or lower than a predetermined value and the predetermined hydraulic pressure does not act on the hydraulic space 46, the valve seat plate 50 is held at the closed position by the predetermined preload. Accordingly, the damping force characteristic of the hydraulic damper 1 has a steep slope (S) in FIG. As a result, the hydraulic damper 1 is close to a rigid body for weak earthquakes and the like, can suppress the shaking of the building, and against strong earthquakes of a predetermined magnitude or more in which the piston moving speed V is a predetermined value P or more. Can be switched to a gentle gradient T at once, and the building can be damped to suppress its destruction.

As shown in FIG. 7, a first and second piston valves 37 ′ are interposed between a boss portion 44 and a valve seat plate 50 with a predetermined number (one in this embodiment) of spacers 55 interposed therebetween. _1, 37 _'2 is mounted. By adjusting the number or thickness of the spacers 55, the predetermined preload acting on the valve seat plate 50 can be adjusted. As a result, the preload is adjusted in accordance with the material of the structural member (whether wooden or lightweight steel), the strength, scale, vibration characteristics, etc. of the building. It is possible to apply a corresponding hydraulic damper.

The structure of the piston valve 37 _1, 37 ₂ is not limited to an annular protrusion 45 and the valve seat plate 50, such as those made of biased valve structure includes a damping force characteristic shown in FIG. 5 Other structures may be used as long as they are good . Also, the gas chamber (preload chamber) 29 is not limited to the encapsulating nitrogen gas or the like, may be obtained by accommodating the high spring constant spring, the movement of the float member 23 to face the hydraulic pressure in the hydraulic pressure chamber 27 The piston rod 6 penetrates only the rod side oil chamber 27a, but penetrates the non-rod side oil chamber 27b as long as it has an urging force that can be absorbed. It may be supported by the float member 23. In this case, the spring 40 is not necessarily required.

1 Hydraulic damper 2 Structural member (pillar)
3 Structural members (beams)
5 Cylinder 6 Piston rod 7 Cap member 9 End of cylinder (connecting member)
10, 10 'Piston 19 End member 23 Float member 27 Hydraulic chamber 27a One oil chamber (rod side oil chamber)
27b The other oil chamber (non-rod side oil chamber)
29 Preload chamber (gas chamber)
30 Scraper 31 Clearance (air chamber)
37 ₁ , 37 ′ ₁ First piston valve 37 ₂ , 37 ′ ₂ Second piston valve 40 Spring 45 Protrusion 46 Hydraulic space 47, 49 (push side) oil passage, (pull side) oil passage 50 Valve seat plate 51 Disc spring

Claims (8)

Has a hydraulic chamber filled with oil in the cylinder, the hydraulic chamber is divided into two oil chambers by a single piston, for communicating the oil at a predetermined attenuation characteristic between the two oil chambers An end of a piston rod connected to the piston is connected to one structural member, and the end of the cylinder is connected to the other structural member, and the hydraulic damper is connected to the one and the other structure. In the vibration damping device of the structure that is installed diagonally between the members,
Forming the hydraulic chamber between an end member integral with the cylinder at least in the axial direction and a float member movable in the axial direction on the cylinder;
A preload chamber having an urging force that opposes the hydraulic pressure acting on the float member from the hydraulic chamber is formed between the closed portion at the end of the cylinder and the float member,
A first piston valve that restricts the flow of oil from one of the two oil chambers to the other oil chamber, and a flow of oil from the other oil chamber to the one oil chamber are regulated in the piston portion. And a second piston valve that
The first and second piston valves are in a closed position when the moving speed of the piston relative to the cylinder is equal to or less than a predetermined value with respect to the oil flow in a direction opposite to the regulated flow, The hydraulic damper is in a state close to a rigid body having a large damping characteristic that rises with a steep slope with a large load change with respect to the moving speed, and is opened when the moving speed of the piston is faster than the predetermined value. The oil flow is allowed, and the hydraulic damper is in a damping state with a small damping characteristic composed of a gentle gradient with a small load change with respect to the moving speed .
A structure damping device characterized by that. In the hydraulic damper, the piston rod extends from the piston through only one of the two oil chambers,
A structure damping device according to claim 1. The hydraulic damper is configured to be contracted between the end member and the piston, and a spring is disposed in the one oil chamber.
A structure damping device according to claim 2 . The preload chamber is composed of a gas chamber in which an inert gas having a predetermined pressure is sealed.
The vibration damping device for a structure according to any one of claims 1 to 3 . One end of the cylinder is closed with a cap member, and a scraper is provided on the cap member to scrape off deposits on the piston rod.
The space between the cap member and the end member is a margin gap having a length equal to or longer than the stroke of the hydraulic damper.
The structure damping device according to any one of claims 1 to 4 . The first and second piston valves are formed on both side surfaces of the piston, and an annular protrusion having a circumference centering on a central axis of the hydraulic damper, and an outer peripheral portion abutting on the protrusion. has a flexible valve seat plate biased and, an oil passage communicating respectively with both sides of the front Symbol piston outer diameter and the inner diameter side of the projection,
When the moving speed of the piston is equal to or less than the predetermined value, the valve seat plate substantially contacts the annular protrusion and the entire circumference thereof, and restricts the flow of oil in the oil passage,
When the moving speed of the piston exceeds the predetermined value, the valve seat plate bends against the urging force and separates from the annular protrusion at the entire circumference, allowing the oil flow in the oil passage at a stretch. ,
The vibration damping device for a structure according to any one of claims 1 to 5 . Each having a hydraulic space on each side surface of the piston between the annular projection and a boss portion into which the piston rod of the piston is fitted;
The both hydraulic spaces communicate with one end of the oil passage whose other end communicates with the outer diameter side of the protrusion,
The protrusion height of the protrusion on both side surfaces of the piston is configured to be higher than the protrusion height of the boss portion, and the valve seat plate is in contact with the protrusion with a predetermined preload.
A structure damping device according to claim 6 . The valve seat plate is attached to both side surfaces of the piston with a predetermined number of spacers between the boss portion and the valve seat plate.
The structure damping device according to claim 7 .

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