JP2016089912A5 - - Google Patents
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- JP2016089912A5 JP2016089912A5 JP2014223389A JP2014223389A JP2016089912A5 JP 2016089912 A5 JP2016089912 A5 JP 2016089912A5 JP 2014223389 A JP2014223389 A JP 2014223389A JP 2014223389 A JP2014223389 A JP 2014223389A JP 2016089912 A5 JP2016089912 A5 JP 2016089912A5
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- 230000036316 preload Effects 0.000 claims description 9
- 239000007789 gas Substances 0.000 claims description 4
- 239000011261 inert gas Substances 0.000 claims description 2
- 230000002093 peripheral Effects 0.000 claims description 2
- 230000001105 regulatory Effects 0.000 claims 4
- 230000037250 Clearance Effects 0.000 description 1
- 230000035512 clearance Effects 0.000 description 1
- 230000000875 corresponding Effects 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- JEIPFZHSYJVQDO-UHFFFAOYSA-N iron(III) oxide Inorganic materials O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 1
- 230000001264 neutralization Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Description
例えば図6を参照して、前記ピストン(10)に、前記2個の油室(27a,27b)を連通するオリフィス(61)を設け、
前記オリフィスは、前記シリンダの内径断面積(A)に対する該オリフィスの流通面積(a)の比である開口面積比率(z)が0.004〜0.040である。また、前記油圧ダンパ(1)は、前記所定値(P)以下の状態で前記移動速度に対する荷重変化が150〜600[kN/(m/sec)]である。
For example, referring to FIG. 6, the piston (10) is provided with an orifice (61) communicating with the two oil chambers (27a, 27b),
The orifice is the ratio opening area ratio of the flow area of the orifice with respect to an inner-diameter cross-sectional area (A) of the cylinder (a) (z) is Ru der 0.004 to 0.040. In the hydraulic damper (1), the load change with respect to the moving speed is 150 to 600 [kN / (m / sec)] in a state equal to or less than the predetermined value (P).
請求項2に係る本発明によると、ピストンに、2個の油室を連通するオリフィスを設け、かつ該オリフィスは、開口面積比率が0.004〜0.040の範囲の極小流通面積からなる。該オリフィスを介してオイルの流れを制限すると、前記油圧ダンパは、前記所定値以下の状態で適正な急勾配からなる減衰力特性を安定して保持して、構造物の地震による被害を低減することができる。
請求項3に係る本発明によると、上記オリフィスを用いて、減衰力特性として最適な、前記所定値以下の状態で150〜600[kN/(m/sec)]の急勾配からなる減衰力特性を安定して保持することができる。600[kN/(m/sec)]以上であると、油室に残圧を発生して振動エネルギを有効に吸収することができない。
According to the present invention according to claim 2, the piston, the orifice communicating two oil chambers provided, and the orifice is that the opening area ratio Do the minimum flow area in the range of 0.004 to 0.040 . When the oil flow is restricted through the orifice, the hydraulic damper stably maintains a damping force characteristic having an appropriate steep slope in a state equal to or less than the predetermined value , thereby reducing damage caused by the earthquake of the structure. be able to.
According to the third aspect of the present invention, a damping force characteristic having a steep slope of 150 to 600 [kN / (m / sec)] in a state equal to or less than the predetermined value, which is the optimum damping force characteristic, using the orifice. Can be held stably. If it is 600 [kN / (m / sec)] or more, residual pressure is generated in the oil chamber and vibration energy cannot be absorbed effectively.
請求項4に係る本発明によると、油圧ダンパは、ピストンロッドが一方の油圧のみに貫通して延びているので、油圧ダンパの構造が簡単となり、信頼性の高い油圧ダンパを用いた構造物の制振装置を提供することができる。また、ピストンロッドが一方の油室のみにあるので、ピストンのストロークにより油圧室の容積が変化するが、該容積変化は、上記予圧室により吸収される。 According to the fourth aspect of the present invention, since the piston rod extends through only one hydraulic pressure, the structure of the hydraulic damper is simplified and the structure using the highly reliable hydraulic damper is used for the hydraulic damper. A vibration damping device can be provided. 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.
請求項5に係る本発明によると、油圧ダンパは、一方の油室にスプリングを配置したので、両油室からピストンに作用するピストンロッドの断面積に基づく圧力差を上記スプリングでバランスすると共に、予圧室からの付勢力と上記スプリングの付勢力がバランスして、油圧室のストローク中心付近に保持される。これにより、油圧ダンパの自然状態における長さが一定となって、油圧ダンパの構造物への取付けが容易となり、かつ構造物の制振装置としての性能が安定し、さらに例え地震等により構造物が塑性領域まで変形したとしても、上記油圧ダンパの中立位置への復元力により構造物を元の状態に戻すことができる。 According to the fifth 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.
請求項6に係る本発明によると、予圧室が不活性ガスを封入したガス室からなるので、油圧室に対向する付勢力を、ガス室のガス圧を調整することにより容易に得ることができる。 According to the sixth 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. .
請求項7に係る本発明によると、油圧ダンパのストローク以上の長さを有する余裕空隙を設けたので、エンド部材に摺接されるピストンロッド部分は、スクレーパで塵埃、錆、水等の付着物が除去された状態になり、油圧ダンパのストロークによりエンド部材のシールが傷付けられたり、油圧室の内部に付着物が浸入することを防止することができる。 According to the seventh aspect of the present invention, since the clearance gap having a length 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. It is possible to prevent the seal of the end member from being damaged by the stroke of the hydraulic damper, and to prevent the deposit from entering the inside of the hydraulic chamber.
請求項8に係る本発明によると、第1及び第2のピストンバルブは、突起、バルブ座板、皿バネ及び油路からなる簡単な構成で足りる。また、周長の長い環状の突起の全周からバルブ座板の外周部が離れることにより、オイルの流路面積を確保して、上記急勾配と緩勾配とに一気に切換えることができ、上記所望の減衰力特性を容易かつ確実に得ることができる。 According to the eighth aspect of the present invention, the first and second piston valves need only have a simple structure 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.
請求項9に係る本発明によると、複数枚からなるバルブ座板に溝を形成することにより、小流通面積からなるオリフィスを高い自由度で容易に形成することができ、上記開口面積比の範囲内において建物の特性に応じたオリフィスを備えた油圧ダンパを容易に提供することができる。 According to the present invention of claim 9 , by forming a groove in a plurality of valve seat plates, an orifice having a small flow area can be easily formed with a high degree of freedom, and the range of the opening area ratio It is possible to easily provide a hydraulic damper having an orifice corresponding to the characteristics of the building.
請求項10に係る本発明によると、バルブ座板に予荷重を作用して、第1及び第2のピストンバルブの減衰力特性の切換えを前記所定値にて適正に行う事ができる。 According to the tenth aspect of the present invention, the preload is applied to the valve seat plate, and the switching of the damping force characteristics of the first and second piston valves can be appropriately performed at the predetermined value.
請求項11に係る本発明によると、間座の枚数又は板厚を調節することにより、上記バルブ座板の予荷重を容易に調整することができ、建物等の構造物の強度、構造、振動特性等に応じて油圧ダンパを適正に調整することができる。 According to the present invention of claim 11 , 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. The hydraulic damper can be adjusted appropriately according to characteristics and the like.
Claims (11)
前記シリンダに少なくとも軸方向に一体のエンド部材と、前記シリンダに軸方向に移動自在なフロート部材との間で前記油圧室を形成し、
前記シリンダの端部の閉塞部と前記フロート部材との間に、前記油圧室から前記フロート部材に作用する油圧に対向する付勢力を有する予圧室を形成し、
前記ピストン部分に、前記2個の油室の一方から他方の油室へのオイルの流れを規制する第1のピストンバルブと、前記他方の油室から一方の油室へのオイルの流れを規制する第2のピストンバルブとを設け、
前記油圧ダンパは、前記第1及び第2のピストンバルブがそれぞれ前記規制される流れと反対方向のオイルの流れに対して、前記シリンダに対する前記ピストンの移動速度が所定値以下の状態では閉じ位置にあって前記オイルの流れを制限し、移動速度に対する荷重変化が150〜800[kN/(m/sec)]の急勾配からなり、前記ピストンの移動速度が前記所定値より速い状態では開かれて前記オイルの流れを許容し、移動速度に対する荷重変化が小さい緩勾配からなる減衰力特性を有する、
ことを特徴とする構造物の制振装置。 The cylinder has a hydraulic chamber filled with oil, the hydraulic chamber is divided into two oil chambers by one piston, and the oil is communicated between the two oil chambers with a predetermined damping force characteristic. In a vibration damping device for a structure comprising a hydraulic damper that is installed on a structural member,
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 hydraulic damper is in a closed position when the moving speed of the piston relative to the cylinder is less than or equal to a predetermined value with respect to an oil flow in a direction opposite to the flow in which the first and second piston valves are respectively regulated. The oil flow is limited, the load change with respect to the moving speed is a steep slope of 150 to 800 [kN / (m / sec)], and the piston is opened when the moving speed of the piston is faster than the predetermined value. The oil flow is allowed and has a damping force characteristic consisting of a gentle gradient with a small load change with respect to the moving speed
A structure damping device characterized by that.
前記シリンダに少なくとも軸方向に一体のエンド部材と、前記シリンダに軸方向に移動自在なフロート部材との間で前記油圧室を形成し、
前記シリンダの端部の閉塞部と前記フロート部材との間に、前記油圧室から前記フロート部材に作用する油圧に対向する付勢力を有する予圧室を形成し、
前記ピストン部分に、前記2個の油室の一方から他方の油室へのオイルの流れを規制する第1のピストンバルブと、前記他方の油室から一方の油室へのオイルの流れを規制する第2のピストンバルブとを設け、
前記ピストンに、前記2個の油室を連通するオリフィスを設け、前記オリフィスは、前記シリンダの内径断面積に対する該オリフィスの流通面積の比である開口面積比率が0.004〜0.040であり、
前記油圧ダンパは、前記第1及び第2のピストンバルブがそれぞれ前記規制される流れと反対方向のオイルの流れに対して、前記シリンダに対する前記ピストンの移動速度が所定値以下の状態では閉じ位置にあって前記オイルの流れを制限し、移動速度に対する荷重変化が前記オリフィスによる急勾配からなり、前記ピストンの移動速度が前記所定値より速い状態では開かれて前記オイルの流れを許容し、移動速度に対する荷重変化が小さい緩勾配からなる減衰力特性を有する、
ことを特徴とする構造物の制振装置。 The cylinder has a hydraulic chamber filled with oil, the hydraulic chamber is divided into two oil chambers by one piston, and the oil is communicated between the two oil chambers with a predetermined damping force characteristic. In a vibration damping device for a structure comprising a hydraulic damper that is installed on a structural member,
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
An orifice that communicates the two oil chambers is provided in the piston, and the orifice has an opening area ratio that is a ratio of a flow area of the orifice to an inner diameter cross-sectional area of the cylinder of 0.004 to 0.040. ,
The hydraulic damper is in a closed position when the moving speed of the piston relative to the cylinder is less than or equal to a predetermined value with respect to an oil flow in a direction opposite to the flow in which the first and second piston valves are respectively regulated. The oil flow is limited, the load change with respect to the moving speed is a steep slope due to the orifice , and the piston is opened when the moving speed of the piston is faster than the predetermined value to allow the oil flow. It has a damping force characteristic consisting of a gentle gradient with a small load change against
A structure damping device characterized by that.
請求項1又は2記載の構造物の制振装置。 Before SL hydraulic damper, the load changes to the moving speed at the predetermined value or less state is 150~600 [kN / (m / sec )],
A vibration damping device for a structure according to claim 1 or 2 .
請求項1ないし3のいずれか1項記載の構造物の制振装置。 In the hydraulic damper, a piston rod connected to the piston extends from the piston through only one of the two oil chambers,
The vibration damping device for a structure according to any one of claims 1 to 3 .
請求項1ないし4のいずれか1項記載の構造物の制振装置。 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.
The structure damping device according to any one of claims 1 to 4 .
請求項1ないし5のいずれか1項記載の構造物の制振装置。 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 5 .
前記キャップ部材と前記エンド部材との間隔を、前記油圧ダンパのストローク以上の長さを有する余裕空隙とした、
請求項1ないし6のいずれか1項記載の構造物の制振装置。 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 6 .
前記ピストンの移動速度が前記所定値以下の場合、前記バルブ座板が前記環状の突起とその全周において実質的に当接し、前記油路のオイルの流れを制限し、
前記ピストンの移動速度が前記所定値を越えると、前記バルブ座板が付勢力に抗して撓んで前記環状の突起からその全周において離れ、前記油路のオイルの流れを一気に許容してなる、
請求項1ないし7のいずれか1項記載の構造物の制振装置。 The first and second piston valves are formed on both side surfaces of the piston, and are attached so that an annular protrusion having a circumference centering on the central axis of the hydraulic damper and an outer peripheral portion in contact with the protrusion. A biased flexible valve seat plate, and oil passages that communicate both side surfaces of the piston on the outer diameter side and the inner diameter side of the protrusion,
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 structure damping device according to any one of claims 1 to 7 .
請求項8記載の構造物の制振装置。 The valve seat plate is composed of a plurality of plates, and at least one groove cut from the outer diameter side is formed in at least one of the valve seat plates of the plurality of plates, and the groove is an inner diameter of the annular protrusion. The orifice is formed by communicating the side and the outer diameter side,
The structure damping device according to claim 8 .
前記両油圧空間に、それぞれ他端が前記突起の外径側に連通する前記油路の一端を連通し、
前記ピストンの両側面における前記突起の突出高さを前記ボス部の突出高さに比して高く構成して、前記バルブ座板が、前記突起に所定予荷重にて当接してなる、
請求項8又は9記載の構造物の制振装置。 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 vibration damping device for a structure according to claim 8 or 9 .
請求項10記載の構造物の制振装置。 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 10 .
Priority Applications (3)
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JP2014223389A JP6567267B2 (en) | 2014-10-31 | 2014-10-31 | Structure damping device |
EP15154991.2A EP2913460B1 (en) | 2014-02-19 | 2015-02-13 | Vibration control device for a building |
US14/626,173 US9540807B2 (en) | 2014-02-19 | 2015-02-19 | Structure vibration control device |
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JP2014223389A JP6567267B2 (en) | 2014-10-31 | 2014-10-31 | Structure damping device |
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JP2016089912A5 true JP2016089912A5 (en) | 2018-08-30 |
JP6567267B2 JP6567267B2 (en) | 2019-08-28 |
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CN109458030B (en) * | 2018-11-22 | 2024-06-25 | 武汉理工大学 | Hydraulic transmission self-resetting supporting device |
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JPS595244Y2 (en) * | 1976-05-20 | 1984-02-16 | 株式会社昭和製作所 | hydraulic shock absorber |
JP3960503B2 (en) * | 1999-03-26 | 2007-08-15 | カヤバ工業株式会社 | Oil damper |
JP3931289B2 (en) * | 1999-08-25 | 2007-06-13 | カヤバ工業株式会社 | Vibration control device |
JP4198296B2 (en) * | 2000-03-28 | 2008-12-17 | カヤバ工業株式会社 | Oil damper |
JP4491818B2 (en) * | 2003-05-30 | 2010-06-30 | 日立オートモティブシステムズ株式会社 | Single cylinder type shock absorber |
JP2005042822A (en) * | 2003-07-22 | 2005-02-17 | Kobe Steel Ltd | Cylindrical liquid damper for base isolator and base isolator using the same |
JP3138457U (en) * | 2007-09-26 | 2008-01-10 | 蘇 人傑 | Seismic reduction device for small buildings |
JP5115814B2 (en) * | 2008-05-30 | 2013-01-09 | 日立オートモティブシステムズ株式会社 | Shock absorber |
JP5785510B2 (en) * | 2012-03-14 | 2015-09-30 | カヤバ工業株式会社 | Buffer valve structure |
JP5941359B2 (en) * | 2012-07-10 | 2016-06-29 | Kyb株式会社 | Buffer valve structure |
JP6122622B2 (en) * | 2012-11-30 | 2017-04-26 | 日立オートモティブシステムズ株式会社 | Cylinder device |
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