JP3053156B2 - Fluid pressure damper - Google Patents

Fluid pressure damper

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Publication number
JP3053156B2
JP3053156B2 JP11169694A JP11169694A JP3053156B2 JP 3053156 B2 JP3053156 B2 JP 3053156B2 JP 11169694 A JP11169694 A JP 11169694A JP 11169694 A JP11169694 A JP 11169694A JP 3053156 B2 JP3053156 B2 JP 3053156B2
Authority
JP
Japan
Prior art keywords
fluid
shaft
casing
rotor
damper
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP11169694A
Other languages
Japanese (ja)
Other versions
JPH07301272A (en
Inventor
智 伊藤
Original Assignee
日立粉末冶金株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立粉末冶金株式会社 filed Critical 日立粉末冶金株式会社
Priority to JP11169694A priority Critical patent/JP3053156B2/en
Publication of JPH07301272A publication Critical patent/JPH07301272A/en
Application granted granted Critical
Publication of JP3053156B2 publication Critical patent/JP3053156B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION
【0001】[0001]
【産業上の利用分野】本発明は、回転式流体圧ダンパに
関し、各種装置の蓋や便座等の開閉部に利用されるもの
である。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary type fluid pressure damper, which is used for an opening / closing portion of a lid or a toilet seat of various devices.
【0002】[0002]
【従来の技術】回転式の油圧ダンパは、機械工学便覧に
記載されているように、筒の内壁に隔壁があり、その筒
内にあって翼を備えた軸が回転する構造をなしており、
筒内に油を満たしておいて翼を回転すると、翼と隔壁間
に油圧が生じるとともに、翼と筒の内壁間および隔壁と
軸間の隙間から油漏れが生じることで、回転運動に適宜
な制動、すなわちダンパ作用を得るものである。この構
造では、軸の正逆回転とも同程度のダンパ作用を行な
う。
2. Description of the Related Art As described in the Mechanical Engineering Handbook, a rotary hydraulic damper has a structure in which a partition wall is formed on an inner wall of a cylinder, and a shaft provided with wings is rotated in the cylinder. ,
When the blade is rotated with oil filled in the cylinder, hydraulic pressure is generated between the blade and the partition, and oil leaks from gaps between the blade and the inner wall of the cylinder and between the partition and the shaft. Braking, that is, a damper effect is obtained. In this structure, the same damper action is performed in both forward and reverse rotations of the shaft.
【0003】ところが、蓋の開閉などでは、自重で閉じ
るときにダンパを介して静かに閉じ、開けるときはダン
パ作用を必要としない場合もあり、軸回転方向の一方に
主としてダンパ作用があり、逆回転方向ではダンパ作用
が弱くなるようにした構成もある。その例としては、特
開平4−282036号や特開平3−267027号公
報記載の構造である。
However, when the lid is opened and closed, there is a case where the door is closed gently via a damper when closed by its own weight, and a damper action is not required when the lid is opened. There is a damper action mainly in one direction of the shaft rotation. There is also a configuration in which the damper effect is weakened in the rotation direction. Examples thereof are the structures described in JP-A-4-282036 and JP-A-3-267027.
【0004】前者は、図12(a)に示すような構造で
あり、ケーシング1の内壁に隔壁11があり、ケーシン
グ1内にあって回転翼21付きの軸2が回転するという
基本的な構造は前記したと同様であるが、回転翼21の
長さが短く、その先端面側に切り溝を設けて流体通路2
2とし、回転翼21とケーシング1の内壁との間に配置
された可動弁9Aを備えている。この可動弁9Aは、断
面形状が略コの字をなし、両側突出部の一方は閉鎖壁9
1、他方は流体通路22に対応する切欠部92を有して
おり、閉鎖壁91と切欠部92との間隔は回転翼21の
幅より広く形成されている。同図において、横中心線よ
り上は回転翼21が矢印方向に回転しダンパ作用をして
いる状態である。このときは、回転翼21の流体通路2
2は可動弁9Aの閉鎖壁91で塞がれている。これに対
し、横中心線より下は回転翼21が反対に回転しダンパ
作用をしている状態であり、ケーシング1内に入れられ
た油は流体通路22から可動弁9Aの切欠部92を経由
して漏れが大きくなる。ダンパ作用を高めるためには、
充填される流体の動粘度は10,000cSt(センチ
ストークス)以上の高粘度のものを用いる必要がある。
The former has a structure as shown in FIG. 12 (a), in which a partition 11 is provided on the inner wall of a casing 1, and a basic structure in which a shaft 2 with a rotary wing 21 in the casing 1 rotates. Is the same as that described above, except that the length of the rotary blade 21 is short, and
2 and includes a movable valve 9 </ b> A disposed between the rotor 21 and the inner wall of the casing 1. This movable valve 9A has a substantially U-shaped cross section, and one of the projecting portions on both sides is a closed wall 9A.
1 and the other have a notch 92 corresponding to the fluid passage 22, and the interval between the closing wall 91 and the notch 92 is formed wider than the width of the rotary blade 21. In the figure, above the horizontal center line is a state where the rotor 21 is rotating in the direction of the arrow and acting as a damper. At this time, the fluid passage 2 of the rotor 21
Reference numeral 2 is closed by a closing wall 91 of the movable valve 9A. On the other hand, below the horizontal center line, the rotary wings 21 rotate in the opposite direction to act as a damper, and the oil contained in the casing 1 flows from the fluid passage 22 through the notch 92 of the movable valve 9A. The leakage increases. To increase the damper action,
The dynamic viscosity of the fluid to be filled, it is necessary to use a high viscosity above 10,000 cSt (cm <br/> Stokes).
【0005】後者は、図12(b)に示すような構造で
ある。可動弁9Bは、その一端が軸2に軸支されて軸2
と一体に回転可能であり、また、可動弁9Bの一方の回
転を規制するために軸2から突出するストッパ23を備
えている。同図において、横中心線より上は可動弁9B
が矢印方向に回転しストッパ23に揺動規制された状態
でダンパ作用をしている。これに対し、横中心線より下
は可動弁9Bが反対に回転し、このとき油圧で押されて
ケーシング1内壁との間の隙間が大きくなり、ダンパ作
用が小さくなった状態である。
The latter has a structure as shown in FIG. The movable valve 9B has one end supported by the shaft 2 and
And a stopper 23 protruding from the shaft 2 for restricting one rotation of the movable valve 9B. In the figure, the movable valve 9B is located above the horizontal center line.
Is rotating in the direction of the arrow, and is acting as a damper in a state where the swing is restricted by the stopper 23. On the other hand, below the horizontal center line, the movable valve 9B rotates in the opposite direction. At this time, the gap between the movable valve 9B and the inner wall of the casing 1 is increased by the hydraulic pressure, and the damper action is reduced.
【0006】[0006]
【発明が解決しようとする課題】上述した従来の改良例
は、工夫された可動弁9Aまたは可動弁9Bによって、
ダンパ機能を専ら一方向に得るようにしたものである。
前者においては、可動弁9Aを組み込む際、その向きを
変えるだけでダンパ作用を得る軸回転方向を変更できる
という特長があるが、可動弁9Aの外周および内周面と
もに摺接する構造であり、また、可動弁9Aの閉鎖壁9
1と回転翼21とが接したときの隙間がダンパ性能に直
接影響を与えるので、各部材間の製作寸法誤差や摩耗に
起因してダンパ特性がばらつき易く品質安定性に問題が
ある。また、高粘度の流体を用いるため、環境温度の変
化で粘度の変位量が大きく、ダンパ特性の変化が著しい
という問題がある。同様に、後者のものも、可動弁9B
が回転する構造なので高精度の寸法精度が要求され、ま
た、ダンパ作用方向の変更には別の軸部材を準備しなけ
ればならず、簡単に行なうことができない。 なお、ダ
ンパの性能ないしは制動力を必要に応じて調整したい場
合もあり、これを構造簡易で達成したいという要求もあ
る。
SUMMARY OF THE INVENTION The above-mentioned conventional improvement is achieved by using a devised movable valve 9A or movable valve 9B.
This is to obtain the damper function exclusively in one direction.
The former has a feature that when the movable valve 9A is incorporated, the shaft rotation direction for obtaining the damper function can be changed only by changing its direction. However, the outer and inner peripheral surfaces of the movable valve 9A are in sliding contact with each other. , Closing wall 9 of movable valve 9A
Since the gap at the time of contact between the rotor 1 and the rotor 21 directly affects the damper performance, the damper characteristics tend to vary due to manufacturing dimensional errors and wear between the members, and there is a problem in quality stability. In addition, since a high-viscosity fluid is used, there is a problem that the amount of change in viscosity is large due to a change in environmental temperature, and the change in damper characteristics is remarkable. Similarly, the latter also has a movable valve 9B
Since the structure rotates, high precision dimensional accuracy is required, and another shaft member must be prepared for changing the damper action direction, which cannot be easily performed. In some cases, the performance or damping force of the damper may be adjusted as required, and there is a demand for achieving this with a simple structure.
【0007】本発明の目的は、ダンパ作用を得る軸回転
方向を簡単に変更可能であると共に、摺接箇所が少な
く、構造が簡易な流体圧ダンパを提供することにある。
他の目的は、従来構造では部品の精度、組み付け精度、
部品間の摩耗、温度変化による油の粘性変化等によるダ
ンパの性能ないしは制動力のばらつきや変化についての
配慮がなかったが、その調整手段をできるだけ簡単な構
成で付与し、所望するダンパ性能に調整できるようにす
ることにある。さらに他の目的は、軸の回転を所定の角
度位置に停止させる機構をより少ない部品数で可能にす
ることにある。
SUMMARY OF THE INVENTION An object of the present invention is to provide a fluid pressure damper which can easily change the rotation direction of the shaft for obtaining the damper function, has few sliding contact points, and has a simple structure.
The other purpose is that, with the conventional structure, the accuracy of parts, assembly accuracy,
No consideration was given to variations and changes in damper performance or braking force due to oil viscosity changes due to wear between parts and temperature changes, etc., but adjustment means were provided with the simplest possible configuration to adjust to the desired damper performance. To be able to do it. Still another object is to enable a mechanism for stopping rotation of a shaft at a predetermined angular position with a smaller number of parts.
【0008】[0008]
【課題を解決するための手段】上記目的は、本発明の要
部である、内壁に隔壁11を突設したケーシング1の円
筒室14に、回転翼21を備えた軸2が回転可能に組み
合わされると共に、粘性流体が充填された流体圧ダンパ
において、回転翼21に流体通路22を設ける一方、こ
の回転翼21の先端面を覆うと共にケーシング内壁に接
する摺接部33と、流体通路22の一方側口を覆う弾性
弁部31と、前記流体通路22の他方側に引っ掛けられ
る短片状の係止部32とを一体に形成している断面略7
の字状のシール部材3を有し、シール部材3が係止部3
2を介し引っ掛けた状態で回転翼21に組み付けられて
回転翼21と一体に回転可能であり、かつ、弾性弁部3
1が軸2の一方向の回転でのみ流体通路22の他方側口
を通じて入る粘性流体の流体圧を受けて揺動し流体通路
22の一方側口を解放可能に構成することにより、達成
される。
An object of the present invention is to provide a cylindrical chamber 14 of a casing 1 having a partition wall 11 protruding from an inner wall, which is a main part of the present invention. In the fluid pressure damper filled with the viscous fluid, a fluid passage 22 is provided in the rotating blade 21, and a sliding contact portion 33 that covers a tip end surface of the rotating blade 21 and contacts an inner wall of the casing, and one of the fluid passage 22. An elastic valve portion 31 covering the side opening, and being hooked on the other side of the fluid passage 22;
Section 7 in which the short piece-shaped locking portion 32 is integrally formed.
Has a seal member 3 of the shaped sealing member 3 is the locking portion 3
2 and is rotatable integrally with the rotating blade 21 while being hooked through the elastic blade portion 3.
This is achieved by the configuration in which 1 is rotated only in one direction of the shaft 2 by receiving the fluid pressure of the viscous fluid entering through the other port of the fluid passage 22 and swings to open one port of the fluid passage 22. .
【0009】前記要部構成において、シール部材3が、
回転翼21の先端面を覆うと共にケーシング内壁に接す
る摺接部33と、流体通路22の一方側口を覆う弾性弁
部31と、回転翼21の一側端面を覆う摺接部38とを
一体に有していることが好ましい。また、請求項2の如
回転翼21が流体通路22と共にこの回転翼21の先
端面から軸心方向に向かって流体通路22に通じる縦穴
22aを有する一方、シール部材3が回転翼21の先端
面を覆うと共にケーシング内壁に接する摺接部33と、
縦穴22aに挿入されて縦穴22aの中で流体通路22
を覆う弾性弁部31とを一体に有している断面略Tの字
状に形成されていることが好ましい。この場合、シール
部材3が、回転翼21の一側端面に沿って配置される摺
接片39を有し、この摺接片39により回転翼21の先
端面から突出する方向へ付勢されるようにすることがよ
り好ましい。
[0009] In the above-mentioned main part configuration, the sealing member 3 is
The sliding contact portion 33 that covers the tip end surface of the rotating blade 21 and contacts the inner wall of the casing, the elastic valve portion 31 that covers one side opening of the fluid passage 22, and the sliding contact portion 38 that covers one end surface of the rotating blade 21 are integrally formed. Preferably. Also, as in claim 2
The rotating blade 21 has a vertical hole 22a communicating with the fluid passage 22 from the tip end face of the rotating blade 21 toward the axial direction along with the fluid passage 22, while the sealing member 3 covers the tip end face of the rotating blade 21 and covers the inner wall of the casing. A sliding contact portion 33 that contacts
The fluid passage 22 is inserted into the vertical hole 22a and is inserted into the vertical hole 22a.
It is preferably formed in a substantially T-shaped cross-section integrally having an elastic valve portion 31 covering the same. In this case, the seal member 3 has a sliding contact piece 39 arranged along one end face of the rotary wing 21, and is urged by the sliding contact piece 39 in a direction protruding from the tip end face of the rotary wing 21. It is more preferable to do so.
【0010】前記要部構成において、ケーシング1は略
コップ状をなして、コップ状の開口側にボルト62締め
される閉じ蓋5を有すると共に、コップ状の開口端面と
閉じ蓋5の端面との間に弾性部材81を介在し、ボルト
62の締め付け力に応じて、ケーシング1の円筒室14
に対する軸2および回転翼21の軸方向の位置を変更可
能にした制動力調整機構8を備えていることが好まし
い。前記要部構成において、ケーシング1の内壁に設け
られた係止溝16と、軸2の外周に装着されて前記内壁
と摺接すると共に係止溝16と係脱可能に係合する爪部
72を持つばね部材71とからなる回転止め機構7を備
えていることがより好ましい。
In the above-mentioned main part configuration, the casing 1 has a substantially cup-like shape, has a closing lid 5 to which a bolt 62 is fastened on the opening side of the cup-like shape. An elastic member 81 is interposed between the cylindrical members 14 of the casing 1 according to the tightening force of the bolts 62.
It is preferable to provide a braking force adjusting mechanism 8 that can change the axial position of the shaft 2 and the rotary wing 21 with respect to. In the main part configuration, the locking groove 16 provided on the inner wall of the casing 1 and the claw portion 72 which is mounted on the outer periphery of the shaft 2 and slidably contacts the inner wall and removably engages with the locking groove 16. It is more preferable to provide the rotation stopping mechanism 7 including the spring member 71 that is provided.
【0011】以上の本発明において、粘性流体には各種
粘度の油、水等の液体、空気のような気体も含む。回転
翼に設けられる流体通路は、断面丸形や楕円形、または
図9の(a)と同様に回転翼の外径に通じる切り欠け状
に形成される。この場合、回転翼が樹脂製であるとき金
型構成により成形と同時に形成することも可能である。
前記回転翼の一部を覆うシール部材は、ゴム、金属、
樹脂のような弾性を示す材料を用いて成形したものであ
り、特にニトリルゴムの成形品や銅合金板製が好まし
い。また、前記粘性流体が気体の場合は、シール部材と
内筒壁間の潤滑およびシール性向上のため合成油を塗布
することが好ましい。前記回転止め機構のばね部材は、
樹脂や金属製の円盤の外径から切り溝を設けるとか、孔
明けして薄肉部を形成して、ばね体を形成したものや、
金属線ばねで形成される。なお、ケーシングに回転翼等
を備えた軸等を組み付け、粘性流体を充填する際に注入
したり、余剰流体を排出する出口は、ケーシングの軸心
部や外径部に設けることができ、ボルト等で封印され
る。また、ケーシングの隔壁の数および回転翼の数は、
1個以上あれば機能し、軸の必要回転角度、ダンパの性
能によって決定される。軸回転角度が100度前後の設
定では、通常、隔壁および回転翼が各2個設けられる。
以下、本発明の流体圧ダンパを図に示す実施例により説
明する。
In the present invention, the viscous fluid includes oils of various viscosities, liquids such as water, and gases such as air. The fluid passage provided in the rotor is formed in a round or elliptical cross section, or a cutout communicating with the outer diameter of the rotor as in FIG. 9A. In this case, when the rotor is made of resin, it can be formed simultaneously with molding by a mold configuration.
The seal member covering a part of the rotor is rubber, metal,
It is molded using a material exhibiting elasticity such as resin, and is particularly preferably a molded product of nitrile rubber or a copper alloy plate. When the viscous fluid is a gas, it is preferable to apply a synthetic oil for lubrication between the sealing member and the inner cylinder wall and for improving the sealing property. The spring member of the rotation stopping mechanism,
One that cuts grooves from the outer diameter of a resin or metal disk, or that forms a thin-walled part and forms a spring body,
It is formed of a metal wire spring. In addition, a shaft or the like having a rotor or the like is assembled to the casing, and an outlet for injecting a viscous fluid or discharging an excess fluid can be provided at the shaft center portion or the outer diameter portion of the casing. Sealed. In addition, the number of casing partition walls and the number of rotors
If it is one or more, it functions and is determined by the required rotation angle of the shaft and the performance of the damper. When the shaft rotation angle is about 100 degrees, two partition walls and two rotor blades are usually provided.
Hereinafter, a hydraulic damper of the present invention will be described with reference to an embodiment shown in the drawings.
【0012】[0012]
【実施例】図1(a),(b)は本発明の第1実施例で
ある流体圧ダンパの縦断面図、図2は前記流体圧ダンパ
の横断面図、図3は要部の斜視図、図4(a),
(b),(c)は要部の3例を示す拡大図である。な
お、各図において従来と同一部材ないしは部位には同じ
符号を付している。
1 (a) and 1 (b) are longitudinal sectional views of a hydraulic damper according to a first embodiment of the present invention, FIG. 2 is a transverse sectional view of the hydraulic damper, and FIG. FIG. 4 (a),
(B), (c) is an enlarged view which shows three examples of the principal part. In the drawings, the same members or parts as those in the related art are denoted by the same reference numerals.
【0013】各図に示す流体圧ダンパは、内壁に隔壁1
1を設けたケーシング1と、ケーシング1内に組み込ま
れる回転翼21付きの軸2と、回転翼21の先端面に固
定されたシール部材3と、ケーシング1の開口に対し流
体漏れ防止用のシーリング4と共に取り付けられる閉じ
蓋5とを備えている。
The hydraulic damper shown in each figure has a partition wall 1 on the inner wall.
1, a shaft 2 with a rotary blade 21 incorporated in the casing 1, a seal member 3 fixed to the tip end surface of the rotary blade 21, and a sealing for preventing fluid leakage from the opening of the casing 1 4 and a closing lid 5 attached together.
【0014】ケーシング1は略コップ形状をしている。
底に対応する部分には粘性流体の注入口12が設けられ
ており、内側が軸受部13を兼ね、外側が雌ねじに形成
されて封印用ボルト61が螺着可能な孔に形成されてい
る。ケーシング1の内壁には2個の隔壁11が円筒室1
4に突出している。軸2は、ケーシング1からはみ出す
突出部分側に軸穴24を持ち、ケーシング内壁と摺接し
シーリング4を周回溝内に配置する部分、図3に示した
1対の回転翼21を含む部分、および軸受部13に軸支
される径小軸部25とを一体に有している。なお、軸穴
24にはダンパ作用を必要とする蓋等の軸が嵌合され
る。
The casing 1 has a substantially cup shape.
A viscous fluid injection port 12 is provided at a portion corresponding to the bottom, and the inner side also serves as the bearing section 13, and the outer side is formed in a female screw and formed in a hole into which a sealing bolt 61 can be screwed. On the inner wall of the casing 1, two partition walls 11 are provided.
4 protrudes. The shaft 2 has a shaft hole 24 on a protruding portion side protruding from the casing 1, a portion that slides on the inner wall of the casing and arranges the sealing 4 in the circumferential groove, a portion including the pair of rotor blades 21 illustrated in FIG. 3, and The small diameter shaft part 25 supported by the bearing part 13 is integrally provided. The shaft hole 24 is fitted with a shaft such as a lid that requires a damper action.
【0015】回転翼21には、図3に示す如く断面楕円
ないしは小判状の流体通路22が設けられるとともに、
先端面側に弾性弁部31を持つシール部材3が付設され
ている。このシール部材3は、片側に長片状の弾性弁部
31を持つ断面が略7の字形である。またシール部材3
は、図4(a)のように流体通路22を解放している側
に短片状の係止部32を一体に有し、回転翼21の先端
面側にあって、係止部32を回転翼21の片側上側縁に
引っ掛け、かつその先端面を摺接部33で覆った状態で
装着されており、弾性弁部31が流体通路22の一方側
開口を開閉可能に覆っている。
The rotary wing 21 is provided with a fluid passage 22 having an elliptical cross section or an oval shape as shown in FIG.
A seal member 3 having an elastic valve portion 31 is provided on the distal end surface side. This seal member 3 has a substantially 7-shaped cross section having an elongated elastic valve portion 31 on one side. Sealing member 3
As shown in FIG. 4A, a short piece-shaped locking portion 32 is integrally provided on the side where the fluid passage 22 is opened, and the locking portion 32 is rotated on the tip end surface side of the rotary wing 21. The blade 21 is attached to the upper edge of one side of the blade 21 with its tip end surface covered with a sliding contact portion 33. The elastic valve portion 31 covers one opening of the fluid passage 22 so as to be openable and closable.
【0016】なお、シール部材3の脱落防止対策例とし
ては、係止部32に限られず、図4(b)の如く係止部
32を長く延ばすと共に、その延長部分に流体通路22
を解放する開口部34を形成する方法、同図(b)や
(c)の如く回転翼21の先端面に凹部や凹凸部を設け
ると共に、シール部材3側に対応する凸部35や凹凸部
36を設けて互いに嵌合する方法、同図(c)の如くシ
ール部材3側に係止突起37を設け、流体通路22の孔
縁に引っ掛ける方法が有効であり、これ以外にも適宜に
変更可能である。
The measures for preventing the sealing member 3 from falling off are not limited to the locking portions 32, but the locking portions 32 are extended as shown in FIG.
A method of forming an opening portion 34 for releasing a groove, as shown in FIGS. 13B and 13C, providing a concave portion or an uneven portion on the tip end surface of the rotary blade 21 and a convex portion 35 or an uneven portion corresponding to the seal member 3 side. It is effective to provide an engaging projection 37 on the side of the seal member 3 and hook it on the edge of the hole of the fluid passage 22 as shown in FIG. It is possible.
【0017】上記各部材の組立は、ケーシング1の円筒
室14に対し、回転翼21付きの軸2をシーリング4を
介装した状態で組み入れて、注入口12から粘性流体を
充填した後、軸2を定位置に装着して、閉じ蓋5を当て
がり、複数本のボルト62を用いてケーシング1の開口
フランジ端面に設けられたねじ孔15に締め付けると共
に、注入口12がボルト61で塞がれることにより完成
される。
The above-mentioned components are assembled by inserting the shaft 2 with the rotary wings 21 into the cylindrical chamber 14 of the casing 1 with the sealing 4 interposed therebetween, filling the injection port 12 with a viscous fluid, and then filling the shaft. 2 is fixed to a fixed position, the closing lid 5 is put on, and the bolts 61 are used to tighten the screw holes 15 provided on the end face of the opening flange of the casing 1 using a plurality of bolts 62. It is completed by being done.
【0018】[0018]
【第1実施例の作用】以上の流体圧ダンパは、ダンパ作
用時を示す図1(a)の如く、軸2が矢印方向に回転さ
れる過程において、流体通路22がシール部材3の弾性
弁部31により常に閉じられる。この結果、粘性流体は
隔壁11と軸2との間のはめ合隙間16を通じて専ら移
動し、それに比例した強さの制動力で作動する。また、
同図(b)は軸2を逆転したときの状態を示している。
この逆回転される過程においては、粘性流体は流体通路
22内に入り込んで弾性弁部31を開方向へ押圧して、
流体通路22を解放する。この結果、粘性流体は隔壁1
1と軸2との間のはめ合隙間16に加えて、流体通路2
2を通じて移動可能となり、それに比例した弱い制動力
で作動する。
In the above-described fluid pressure damper, as shown in FIG. 1 (a) showing the operation of the damper, when the shaft 2 is rotated in the direction of the arrow, the fluid passage 22 is connected to the elastic valve of the seal member 3. It is always closed by the part 31. As a result, the viscous fluid moves exclusively through the fitting gap 16 between the partition 11 and the shaft 2, and operates with a braking force having a strength proportional thereto. Also,
FIG. 2B shows a state when the shaft 2 is reversed.
In the process of the reverse rotation, the viscous fluid enters the fluid passage 22 and presses the elastic valve portion 31 in the opening direction.
The fluid passage 22 is released. As a result, the viscous fluid passes through the partition 1
In addition to the fitting gap 16 between the shaft 1 and the shaft 2, the fluid passage 2
2 and can be operated with a weak braking force proportional thereto.
【0019】そして、前記流体圧ダンパの構成におい
て、シール部材3は、回転翼21の先端面部に固定され
ているので、ケーシング1の内壁に対しシール部材3の
当接する摺接部33外面のみが摩耗するだけである。し
たがって、品質管理としては摺接部33の厚さ管理およ
びその外面の摩耗を考慮するだけでよく、従来のように
シール部材3と回転翼21との当接部のはめ合寸法精度
や摩耗について考慮する必要がなくなり、精度的に大き
く緩和される。ここで、シール部材3は、ゴム質材料に
し、回転翼21とケーシング1の内壁との隙間よりも厚
く形成すると、その内壁に密着するようになり、粘性流
体のシール性が向上する。流体通路22を覆う弾性弁部
31は、流体通路22からの流体圧が加わったときだけ
揺動変形し、流体通路22を解放する一方向弁の作用を
する。また、シール部材3の形状は、断面が略7の字で
あることから、回転翼21に対する装着の向きを変えれ
ば制動力を得る回転方向を変更することができる。
In the structure of the fluid pressure damper, since the seal member 3 is fixed to the tip end portion of the rotary blade 21, only the outer surface of the sliding contact portion 33 where the seal member 3 contacts the inner wall of the casing 1. It just wears. Therefore, it is only necessary to consider the thickness control of the sliding contact portion 33 and the wear of the outer surface thereof as quality control, and it is necessary to consider the fitting dimensional accuracy and wear of the contact portion between the seal member 3 and the rotary blade 21 as in the related art. There is no need to consider it, and accuracy is greatly reduced. Here, if the seal member 3 is made of a rubber material and is formed to be thicker than the gap between the rotary blade 21 and the inner wall of the casing 1, the seal member 3 comes into close contact with the inner wall, and the sealing property of the viscous fluid is improved. The elastic valve portion 31 covering the fluid passage 22 swings and deforms only when the fluid pressure from the fluid passage 22 is applied, and acts as a one-way valve that releases the fluid passage 22. Further, since the shape of the seal member 3 has a substantially 7-shaped cross section, the rotation direction in which the braking force is obtained can be changed by changing the mounting direction with respect to the rotary wing 21.
【0020】また、図5から図7はシール部材3の構成
に機能を付加した3例を示している。図5(a),
(b)はシール部材3の第2実施例を示し、前記摺接部
33とは別にケーシング1におけるコップ形状の底に対
応する側に摺接部38を設けた例である。つまり、第2
実施例のシール部材3は、回転翼21の先端面を覆うと
共にケーシング内壁に接する摺接部33と、流体通路2
2の一方側口を覆う弾性弁部31と、回転翼21の一側
端面を覆う摺接部38とを一体に有している樹脂成形体
からなっている。この構成では、前記作用に加えて、摺
接部38がコップ形状の底面に対しても弾性的に接し、
その部分のシール性が確実に得られる。
FIGS. 5 to 7 show three examples in which functions are added to the structure of the seal member 3. FIG. FIG. 5 (a),
(B) shows a second embodiment of the seal member 3, in which a sliding contact portion 38 is provided on the side of the casing 1 corresponding to the bottom of the cup shape separately from the sliding contact portion 33. That is, the second
The seal member 3 according to the embodiment includes a sliding contact portion 33 that covers the tip end surface of the rotary wing 21 and is in contact with the inner wall of the casing.
2 is a resin molded body integrally having an elastic valve portion 31 covering one side opening and a sliding contact portion 38 covering one end surface of the rotary blade 21. In this configuration, in addition to the above operation, the sliding contact portion 38 elastically contacts the bottom surface of the cup shape,
The sealing property of that portion is reliably obtained.
【0021】図6(a),(b)はシール部材3の第3
実施例を示している。第3実施例のシール部材3は回転
翼21の先端面を覆うと共にケーシング内壁に接する摺
接部33と、弾性弁部31aとを一体に有している断面
略Tの字状に形成さている。そして、回転翼21は流体
通路22と共にこの回転翼21の先端面から軸心方向に
向かって流体通路22に通じる縦穴22aを有してお
り、シール部材3の弾性弁部31aを縦穴22aに挿入
して縦穴22aの中で流体通路22を覆うようにした構
成例である。この場合、弾性弁部31aの基部31bが
縦穴22aに対して圧入されるよう厚く形成されてお
り、シール部材3は同図(b)の如く流体通路22の上
側部位において圧入された状態で係止されている。
FIGS. 6A and 6B show a third example of the seal member 3.
An example is shown. The seal member 3 of the third embodiment is formed in a substantially T-shaped cross-section that integrally includes a sliding contact portion 33 that covers the tip end surface of the rotor blade 21 and contacts the inner wall of the casing and an elastic valve portion 31a. . The rotating blade 21 has a vertical hole 22a communicating with the fluid passage 22 from the tip end face of the rotating blade 21 toward the axial direction together with the fluid passage 22. The elastic valve portion 31a of the seal member 3 is inserted into the vertical hole 22a. This is a configuration example in which the fluid passage 22 is covered in the vertical hole 22a. In this case, the base portion 31b of the elastic valve portion 31a is formed thick so as to be press-fitted into the vertical hole 22a, and the seal member 3 is engaged in a state where it is press-fitted in the upper portion of the fluid passage 22 as shown in FIG. Has been stopped.
【0022】図7(a),(b)はシール部材3の第4
実施例を示している。第4実施例は、第3実施例に対し
摺接片39を一体に形成した例である。つまり、シール
部材3は、摺接部33と、弾性弁部31aと、回転翼2
1の一側端面に沿って配置される摺接片39とを有して
いる。そして、回転翼21の一側端面に形成した長溝2
9に対し、摺接片39を配置した構成である。この場
合、長溝29は摺接片39よりもその長さが多少小さく
設定されている。したがって、摺接片39は第2実施例
の摺接部38と同様な作用、つまりがコップ形状の底面
に対しても弾性的に接し、その部分のシール性が確実に
得られることに加え、シール部材3を回転翼21の先端
面から突出する方向へ付勢する。この付勢力によって摺
接部33のシール性も確実に得られることとなる。
FIGS. 7A and 7B show a fourth example of the seal member 3.
An example is shown. The fourth embodiment is an example in which the sliding contact piece 39 is formed integrally with the third embodiment. That is, the seal member 3 includes the sliding contact portion 33, the elastic valve portion 31a, and the rotary blade 2
1 and a sliding contact piece 39 arranged along one end face of the first side. A long groove 2 formed on one end face of the rotating blade 21
9 is a configuration in which a sliding contact piece 39 is arranged. In this case, the length of the long groove 29 is set slightly smaller than the length of the sliding contact piece 39. Therefore, the sliding contact piece 39 has the same function as the sliding contact portion 38 of the second embodiment, that is, the sliding contact piece 39 also elastically contacts the bottom surface of the cup shape, and in addition to the sealing property of the portion being reliably obtained, The seal member 3 is urged in a direction protruding from the tip end surface of the rotary wing 21. With this biasing force, the sealing property of the sliding contact portion 33 can be reliably obtained.
【0023】図8は本発明の第5実施例である流体圧ダ
ンパの横断面図、図9は要部の縦断面図である。なお、
第5実施例は前記流体圧ダンパに回転止め機構を付設し
た例であり、第1実施例と同一部材ないしは部位に同じ
符号を付し、要部のみを説明する。また、図1,図3,
図4およびその説明は第5実施例の流体圧ダンパでも共
通である。前記回転止め機構7は、閉じ蓋5の内端面に
接する軸2の周囲部に組み付けられており、軸2周りに
装着されるばね部材71と、ばね部材71の一部に設け
られて先端に爪部72を持つ係止用のばね片部73と、
ケーシング1の内壁に設けられた係止溝17とからな
る。また、ばね部材71は、内径に設けられた溝74を
有し、この溝74が軸2の径大端面寄りの外周部分に突
設されたキー部26に係合して回り止めされる。
FIG. 8 is a transverse sectional view of a fluid pressure damper according to a fifth embodiment of the present invention, and FIG. 9 is a longitudinal sectional view of a main part. In addition,
The fifth embodiment is an example in which the fluid pressure damper is provided with a rotation stopping mechanism, and the same members or parts as those in the first embodiment are denoted by the same reference numerals, and only the main part will be described. Also, FIG. 1, FIG. 3,
FIG. 4 and its description are common to the fluid pressure damper of the fifth embodiment. The rotation stopping mechanism 7 is assembled around the shaft 2 in contact with the inner end surface of the closing lid 5. A spring member 71 mounted around the shaft 2, and a spring member 71 provided on a part of the spring member 71 and provided at a tip thereof A spring piece 73 for locking having a claw 72;
A locking groove 17 provided on the inner wall of the casing 1. The spring member 71 has a groove 74 provided on the inner diameter, and the groove 74 is engaged with the key portion 26 protruding from the outer peripheral portion of the shaft 2 near the large-diameter end surface to prevent rotation.
【0024】[0024]
【第5実施例の作用】以上の回転止め機構7は、軸2が
回転することにより、ばね片部73の爪部72が係止溝
17に入り込んで係脱可能に係合したとき、そのばね片
部73のばね力および爪部72と係止溝17との係合力
が軸2に加わる回転モーメントの抵抗として作用し、軸
2の回り止めとなる。つまり、この回転止め機構7は、
軸2と一体に回転するばね部材71の爪部72をケーシ
ング1側の係止溝17に係合させて回り止めをし、前記
ばね力および係合力に抗して軸2を回転してばね部材7
1の爪部72と係止溝17との係止を解くことで回転止
めが解除される。このような軸2の回転止め機構7は、
例えば、軸穴24に軸を介して連結される蓋等が開状態
にあり、この開状態から不用意に倒れて閉じないように
したいとき等に用いられる。
The function of the fifth embodiment is such that when the shaft 2 rotates, the claw 72 of the spring piece 73 enters the locking groove 17 and engages removably. The spring force of the spring piece portion 73 and the engaging force between the claw portion 72 and the locking groove 17 act as a resistance to the rotational moment applied to the shaft 2, thereby preventing the shaft 2 from rotating. That is, the rotation stopping mechanism 7
The claw 72 of the spring member 71 that rotates integrally with the shaft 2 is engaged with the locking groove 17 on the casing 1 to prevent rotation, and the shaft 2 is rotated against the spring force and the engaging force to rotate the spring. Member 7
The rotation stop is released by releasing the lock between the first claw portion 72 and the locking groove 17. Such a rotation stopping mechanism 7 for the shaft 2
For example, this is used when a lid or the like connected to the shaft hole 24 via a shaft is in an open state, and it is desired to prevent the cover from inadvertently falling down from this open state and not closing.
【0025】この構成においては、ケーシング1の内壁
の延長部で閉じ蓋5寄りに係止溝17を設け、また、前
記内壁と軸2との間にあって係止溝17と係合可能な爪
部72を備えたばね部材71を軸2に固設して一体に回
転するように構成しているので、コイルばねで付勢する
ボールを凹部に係合するような従来の回転止め機構に対
して、コイルばねを収納する孔等を形成する必要がな
く、ボールに相当する爪部72をばね部材71と一体に
成形して部品点数を少なくでき、しかも薄肉に形成でき
ることからスペース的にも小さくコンパクト化に優れて
いる。
In this configuration, a locking groove 17 is provided on the extension of the inner wall of the casing 1 near the closing lid 5, and a claw portion between the inner wall and the shaft 2 and engageable with the locking groove 17. Since the spring member 71 provided with the shaft 72 is fixed to the shaft 2 so as to rotate integrally therewith, a conventional rotation stopping mechanism in which a ball biased by a coil spring is engaged with a concave portion is provided. There is no need to form a hole or the like for accommodating a coil spring, and the claw portion 72 corresponding to a ball is formed integrally with the spring member 71, so that the number of parts can be reduced. Is excellent.
【0026】図10および図11は本発明の第6実施例
である流体圧ダンパを示し、図10は回転翼21の断面
を含む方向の横断面図、図11は隔壁11の断面を含む
方向の横断面図である。なお、第6実施例は前記流体圧
ダンパに制動力調整機構を付設した例であり、第1,5
実施例と同一部材ないしは部位に同じ符号を付し、要部
のみを説明する。また、図1,図3,図4,図9および
その説明は第6実施例の流体圧ダンパでも共通である。
前記制動力調整機構8は、ダンパの制動力を可変するた
めに、ケーシング1の底面側に対する軸2の隙間27a
および隔壁11に対する軸2の隙間27bを調整可能に
したものであり、ケーシング1の開口側端面と閉じ蓋5
との間に介装された弾性部材81を有している。この弾
性部材81は、合成ゴム製であり、所定厚の円盤状をな
し、閉じ蓋5の内側フランジに対応する貫通孔およびボ
トル62に対応する貫通孔が形成されている。
FIGS. 10 and 11 show a fluid pressure damper according to a sixth embodiment of the present invention. FIG. 10 is a cross-sectional view of a section including a section of a rotary wing 21, and FIG. FIG. The sixth embodiment is an example in which a braking force adjusting mechanism is added to the fluid pressure damper.
The same members or parts as in the embodiment are denoted by the same reference numerals, and only the main part will be described. Also, FIGS. 1, 3, 4, 9 and the description thereof are common to the fluid pressure damper of the sixth embodiment.
The braking force adjusting mechanism 8 includes a gap 27a between the shaft 2 and the bottom surface of the casing 1 for varying the braking force of the damper.
And the gap 27b of the shaft 2 with respect to the partition 11 can be adjusted.
And an elastic member 81 interposed therebetween. The elastic member 81 is made of synthetic rubber, has a disk shape having a predetermined thickness, and has a through hole corresponding to the inner flange of the closing lid 5 and a through hole corresponding to the bottle 62.
【0027】[0027]
【第6実施例の作用】以上の制動力調整機構8は、弾性
部材81をケーシング1の開口側端面と閉じ蓋5との間
に介在して、ケーシング1のねじ孔15にボルト62を
締め付けことにより、閉じ蓋5の押圧力で軸2が一体的
に円筒室14内に押し込まれる。すると、図10および
図11に示される隙間27aおよび隙間27bが減少し
て、そこから粘性流体の漏れないしは移動が少なくな
り、ダンパの制動力が強くなる。逆に、各ボルト62を
緩めると、弾性部材81の復帰力で閉じ蓋5が軸方向に
後退し、再び隙間27a,27bを図10および図11
の如く形成して、そこから粘性流体の漏れないしは移動
が多くなり、ダンパの制動力が低下する。この隙間27
a,27bはボルト62の締め付け力に反比例し、また
その移動が僅かでも制動力調整に有効である。
In the braking force adjusting mechanism 8 described above, the elastic member 81 is interposed between the opening end face of the casing 1 and the closing lid 5 and the bolt 62 is tightened in the screw hole 15 of the casing 1. Thus, the shaft 2 is integrally pushed into the cylindrical chamber 14 by the pressing force of the closing lid 5. Then, the gaps 27a and 27b shown in FIGS. 10 and 11 are reduced, and the leakage or movement of the viscous fluid is reduced therefrom, and the damping force of the damper is increased. Conversely, when the bolts 62 are loosened, the closing lid 5 retreats in the axial direction due to the return force of the elastic member 81, and the gaps 27a and 27b are formed again in FIGS.
And the leakage or movement of the viscous fluid therefrom increases, and the damping force of the damper decreases. This gap 27
a and 27b are inversely proportional to the tightening force of the bolt 62, and even if the movement is slight, it is effective for adjusting the braking force.
【0028】この構成においては、ケーシング1の開口
側端面と閉じ蓋5との間に介在される弾性部材81は、
隙間27a,27bの大きさをボルト62の締め付け力
に応じて可変する役割をなす。回転翼21と隔壁11と
の幅寸法を一致させておき、回転翼21の端面はケーシ
ング1の底側端面ないしは円筒室17の端面に当接する
ように閉じ蓋5の内側端面で押し付け、ケーシング1と
閉じ蓋5とをボルト締めすれば、回転翼21と相手部材
との隙間が狭くなり、回転翼21が回転したときにその
隙間27a,27bから漏れる流体は僅かとなる。した
がって、このような調整例としては、ケーシング1の内
壁に対しシール部材3の当接する摺接部33が摩耗した
り、流体粘度が下がってダンパ作用が低下した場合など
である。また、故意または部材の摩耗等により回転翼2
1と相手部材との隙間27a,27bが大きい場合は、
その隙間27a,27bからの流体漏れは大きくなる。
このような場合にも容易に補正することができる。
In this configuration, the elastic member 81 interposed between the opening-side end face of the casing 1 and the closing lid 5 is
The size of the gaps 27 a and 27 b is changed according to the tightening force of the bolt 62. The width of the rotor 21 and the width of the partition 11 are matched, and the end face of the rotor 21 is pressed against the bottom end face of the casing 1 or the inner end face of the closing lid 5 so as to contact the end face of the cylindrical chamber 17. If the rotating blade 21 and the counterpart member are tightened with bolts, the fluid leaking from the clearances 27a and 27b when the rotating blade 21 rotates becomes small. Therefore, examples of such adjustment include a case where the sliding portion 33 of the seal member 3 that abuts against the inner wall of the casing 1 is worn, and a case where the damper action is reduced due to a decrease in fluid viscosity. In addition, the rotating blades 2 are intentionally or worn due to wear of the members.
When the gaps 27a and 27b between the first member and the mating member are large,
Fluid leakage from the gaps 27a and 27b increases.
Even in such a case, correction can be easily made.
【0029】[0029]
【発明の効果】以上説明したように、本発明に係る流体
圧ダンパは、構造が簡単な一方向弁を回転翼に付設した
ものであるから、性能に優れたダンパを安価に提供でき
る。ダンパの制動力調整機能を付与したものは、温度変
化や摩耗によるダンパ性能の変化を補正できるので、常
に最適なダンパ性能を持って、寿命をより長くでき、こ
れにより用途的な拡大も期待できる。また、軸回転止め
機能は部品数を最小限とし、設置スペースを薄くできる
ので、コンパクトで組み立て性が良好となる等の効果が
ある。
As described above, the fluid pressure damper according to the present invention has a simple structure with a one-way valve attached to the rotor, so that a damper with excellent performance can be provided at low cost. The one with the damper braking force adjustment function can compensate for changes in damper performance due to temperature changes and wear, so that it always has optimal damper performance and can have a longer life, which can be expected to expand applications. . In addition, since the shaft rotation stopping function minimizes the number of parts and can reduce the installation space, there is an effect that compactness and good assemblability are improved.
【図面の簡単な説明】[Brief description of the drawings]
【図1】本発明の第1実施例に係る流体圧ダンパをその
作用と共に示す縦断面図である。
FIG. 1 is a longitudinal sectional view showing a hydraulic damper according to a first embodiment of the present invention together with its operation.
【図2】前記流体圧ダンパの横断面図である。FIG. 2 is a cross-sectional view of the hydraulic damper.
【図3】前記流体圧ダンパの回転翼部を示す斜視図であ
る。
FIG. 3 is a perspective view showing a rotating blade portion of the fluid pressure damper.
【図4】前記流体圧ダンパのシール部材およびその変形
例を示す断面図である。
FIG. 4 is a sectional view showing a seal member of the fluid pressure damper and a modified example thereof.
【図5】前記シール部材に付加機能を持たせた第2実施
例を示す要部図である。
FIG. 5 is a main part view showing a second embodiment in which the seal member has an additional function.
【図6】前記シール部材に付加機能を持たせた第3実施
例を示す要部図である。
FIG. 6 is a main part view showing a third embodiment in which the seal member has an additional function.
【図7】前記シール部材に付加機能を持たせた第4実施
例を示す要部図である。
FIG. 7 is a main part view showing a fourth embodiment in which the seal member has an additional function.
【図8】前記流体圧ダンパに回転止め機構を付設した第
5実施例を示す断面図である。
FIG. 8 is a sectional view showing a fifth embodiment in which a rotation stopping mechanism is added to the fluid pressure damper.
【図9】前記回転止め機構の構造を示す断面図である。FIG. 9 is a sectional view showing a structure of the rotation stopping mechanism.
【図10】前記流体圧ダンパに制動力調整機構を付設し
た第6実施例を示す断面図である。
FIG. 10 is a sectional view showing a sixth embodiment in which a braking force adjusting mechanism is added to the fluid pressure damper.
【図11】前記制動力調整機構の構造を示す断面図であ
る。
FIG. 11 is a sectional view showing a structure of the braking force adjusting mechanism.
【図12】従来の流体圧ダンパについて2例を示す要部
断面図である。
FIG. 12 is a sectional view of a main part showing two examples of a conventional fluid pressure damper.
【符号の説明】[Explanation of symbols]
1はケーシング、11は隔壁、17は係止溝 2は軸、21は回転翼、22は流体通路、22aは縦穴 3はシール部材、31及び31aは弾性弁部、33及び
38は摺接部、39は摺接片 5は閉じ蓋 62はボルト 7は回転止め機構、71はばね部材、72は爪部 8は制動力調整機構、81は弾性部材
1 is a casing, 11 is a partition, 17 is a locking groove, 2 is a shaft, 21 is a rotor, 22 is a fluid passage, 22a is a vertical hole, 3 is a sealing member, 31 and 31a are elastic valve parts, and 33 and 38 are sliding contact parts. , 39 are sliding contact pieces 5 are closed lids 62 are bolts 7 are rotation preventing mechanisms, 71 is a spring member, 72 is a claw portion 8 is a braking force adjusting mechanism, and 81 is an elastic member.
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7,DB名) F16F 9/14 F16F 9/56 A47K 13/12 E05F 3/14 ──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. 7 , DB name) F16F 9/14 F16F 9/56 A47K 13/12 E05F 3/14

Claims (4)

    (57)【特許請求の範囲】(57) [Claims]
  1. 【請求項1】 内壁に隔壁を突設したケーシングの円筒
    室に、回転翼を備えた軸が回転可能に組み合わされると
    共に、粘性流体が充填された流体圧ダンパにおいて、 前記回転翼に流体通路を設ける一方、前記 回転翼の先端面を覆うと共にケーシング内壁に接す
    る摺接部と、前記流体通路の一方側口を覆う長片状の
    性弁部と、前記流体通路の他方側に引っ掛けられる短片
    状の係止部とを一体に形成している断面略7の字状の
    ール部材を有し、 前記シール部材が係止部を回転翼の他方側に引っ掛けた
    状態で回転翼に組み付けられて回転翼と一体に回転可能
    であり、かつ、前記弾性弁部が前記軸の一方向の回転で
    のみ流体通路の他方側口を通じて入る粘性流体の流体圧
    を受けて揺動し流体通路の一方側口を解放可能にするこ
    とを特徴とする流体圧ダンパ。
    1. A fluid pressure damper in which a shaft provided with a rotating blade is rotatably combined with a cylindrical chamber of a casing having a partition wall protruding from an inner wall, and a viscous fluid is filled therein. providing one, the sliding contact portion in contact with the inner wall of the casing covers the front end face of the rotor blades, and one covering the side opening length schistose bullet <br/> of valve portion of the fluid passage, the other side of said fluid passage Short piece hooked on
    A seal member having a substantially U- shaped cross-section integrally formed with a lock member having a shape like a cross section , wherein the seal member hooks the lock member on the other side of the rotor blade.
    The elastic valve portion is attached to the rotor in this state and is rotatable integrally with the rotor, and receives the fluid pressure of the viscous fluid entering through the other port of the fluid passage only in one rotation of the shaft. A fluid pressure damper, which oscillates to open one side opening of a fluid passage.
  2. 【請求項2】 内壁に隔壁を突設したケーシングの円筒
    室に、回転翼を備えた軸が回転可能に組み合わされると
    共に、粘性流体が充填された流体圧ダンパにおいて、 前記 回転翼に対し流体通路と共に、この回転翼の先端面
    から軸心方向に向かって流体通路に通じる縦穴を設け
    一方、前記 回転翼の先端面を覆うと共にケーシング内壁に接す
    る摺接部と、前記縦穴に挿入されて縦穴の中で前記流体
    通路を覆う弾性弁部とを一体に形成している断面略Tの
    字状のシール部材を有し、 前記シール部材が前記縦穴に弾性弁部を挿入した状態で
    回転翼に組み付けられて回転翼と一体に回転可能であ
    り、かつ、前記弾性弁部が前記軸の一方向の回転でのみ
    流体通路の他方側口を通じて入る粘性流体の流体圧を受
    けて揺動し流体通路の一方側口を解放可能にすることを
    特徴とする 流体圧ダンパ。
    2. A casing cylinder having a partition wall protruding from an inner wall.
    When a shaft with rotating blades is rotatably combined with the chamber
    Both the hydraulic damper viscous fluid-filled, with the flow fluid path to the rotor blade, while the Ru provided vertical holes leading to the fluid passage toward the distal end surface of the rotor blades in the axial direction, of the rotor blade A sealing member having a substantially T-shaped cross section, which integrally forms a sliding contact portion that covers the front end surface and contacts the inner wall of the casing and an elastic valve portion that is inserted into the vertical hole and covers the fluid passage in the vertical hole. has, in a state where the sealing member is inserted an elastic valve portion to the vertical hole
    It is assembled with the rotor and can rotate integrally with the rotor.
    And the elastic valve section is rotated only in one direction of the shaft.
    Receives the fluid pressure of viscous fluid entering through the other port of the fluid passage.
    To open one side of the fluid passage.
    Features a hydraulic damper.
  3. 【請求項3】 前記シール部材が、前記回転翼の一側端
    面に沿って配置される摺接片を有し、この摺接片により
    回転翼の先端面から突出する方向へ付勢されている請求
    に記載の流体圧ダンパ。
    3. The seal member has a sliding contact piece disposed along one end face of the rotating blade, and is urged by the sliding contact piece in a direction protruding from a tip end surface of the rotating blade. The fluid pressure damper according to claim 2 .
  4. 【請求項4】 前記ケーシングは略コップ状をなして、
    コップ状の開口側にボルト締めされる閉じ蓋を有すると
    共に、前記コップ状の開口端面と閉じ蓋の端面との間に
    弾性部材を介在し、前記ボルトの締め付け力に応じて、
    ケーシングの円筒室に対する軸および回転翼の軸方向の
    位置を変更可能にした制動力調整機構を備えている請求
    項1からの何れかに記載の流体圧ダンパ。
    4. The casing has a substantially cup shape,
    With a closing lid bolted to the cup-shaped opening side, an elastic member is interposed between the cup-shaped opening end face and the end face of the closing lid, and according to the tightening force of the bolt,
    The fluid pressure damper according to any one of claims 1 to 3 , further comprising a braking force adjusting mechanism capable of changing an axial position of the shaft and the rotor with respect to the cylindrical chamber of the casing.
JP11169694A 1994-04-28 1994-04-28 Fluid pressure damper Expired - Fee Related JP3053156B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP11169694A JP3053156B2 (en) 1994-04-28 1994-04-28 Fluid pressure damper

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP11169694A JP3053156B2 (en) 1994-04-28 1994-04-28 Fluid pressure damper

Publications (2)

Publication Number Publication Date
JPH07301272A JPH07301272A (en) 1995-11-14
JP3053156B2 true JP3053156B2 (en) 2000-06-19

Family

ID=14567851

Family Applications (1)

Application Number Title Priority Date Filing Date
JP11169694A Expired - Fee Related JP3053156B2 (en) 1994-04-28 1994-04-28 Fluid pressure damper

Country Status (1)

Country Link
JP (1) JP3053156B2 (en)

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