JPH0241384Y2 - - Google Patents
Info
- Publication number
- JPH0241384Y2 JPH0241384Y2 JP4750185U JP4750185U JPH0241384Y2 JP H0241384 Y2 JPH0241384 Y2 JP H0241384Y2 JP 4750185 U JP4750185 U JP 4750185U JP 4750185 U JP4750185 U JP 4750185U JP H0241384 Y2 JPH0241384 Y2 JP H0241384Y2
- Authority
- JP
- Japan
- Prior art keywords
- weight
- cylinder chamber
- flow rate
- pipe
- oil
- 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
Links
Landscapes
- Vibration Prevention Devices (AREA)
- Fluid-Damping Devices (AREA)
Description
【考案の詳細な説明】
産業上の利用分野
本考案は例えば大型デイーゼル機関用振動減衰
器に関する。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a vibration damper for, for example, large diesel engines.
従来の技術
現在、大型デイーゼル機関においては、その機
関架構の振動を減少させるために、固有振動を起
こす共振回転数を機関の使用回転数外に追い上げ
る方法が取られている。その方法の１つとして、
機関にブレーシングを取付けて機関架構の固有振
動数を上昇させる方法がよく用いられている。BACKGROUND OF THE INVENTION Currently, in large diesel engines, in order to reduce the vibration of the engine frame, a method is used to raise the resonant rotational speed at which natural vibration occurs to a speed other than the engine's operating speed. One of the methods is
A commonly used method is to attach bracing to the engine to increase the natural frequency of the engine frame.
考案が解決しようとする問題点
上記従来の構成によると、ブレーシングの剛性
を十分に取る必要があるため、舶用機関の場合、
ブレーシングを取付ける船体のデツキの剛性を十
分に大きくする必要があり、また陸用機関の場
合、ブレーシングを取付ける相手側の構造物がな
い等の問題があつた。Problems to be solved by the invention According to the above conventional configuration, it is necessary to ensure sufficient rigidity of bracing, so in the case of marine engines,
It is necessary to increase the rigidity of the hull deck to which the bracing is attached, and in the case of land-based engines, there are problems such as there being no structure to attach the bracing to.
そこで、本考案は上記問題を解消し得る振動減
衰器を提供することを目的とする。 Therefore, an object of the present invention is to provide a vibration damper that can solve the above problems.
問題を解決するための手段
上記問題を解決するため、本考案の振動減衰器
は、振動物体に取付けられる支持本体に、重錘を
所定方向で移動自在に設け、上記支持本体の重錘
移動方向における一端側にシリンダ室を形成する
と共に、重錘の一端部に上記シリンダ室内を摺動
自在なピストンを設け、上記重錘の他端側に、重
錘を一端側に付勢するばね体を設け、上記シリン
ダ室の先端部にフレキシブル管の一端部を第１流
量調整弁を介して接続すると共に、該フレキシブ
ル管の他端部と液体タンクとを、第２流量調整弁
を有する第１配管を介して接続し、且つ上記シリ
ンダ室先端側と液体タンクとを、逆止弁を有する
第２配管を介して接続したものである。Means for Solving the Problem In order to solve the above problem, the vibration damper of the present invention is provided with a weight movable in a predetermined direction on a support body attached to a vibrating object, and a weight is movable in a predetermined direction. A cylinder chamber is formed at one end of the weight, a piston that is slidable within the cylinder chamber is provided at one end of the weight, and a spring body is provided at the other end of the weight for biasing the weight toward the one end. a first pipe having a second flow rate regulating valve, connecting one end of the flexible pipe to the distal end of the cylinder chamber via a first flow rate regulating valve, and connecting the other end of the flexible pipe to the liquid tank; The front end side of the cylinder chamber and the liquid tank are connected via a second pipe having a check valve.
作 用
上記構成において、支持本体を振動物体に取付
けると共重錘はその振動により所定方向で往復移
動する。上記重錘が例えばばね体側に移動する
時、液体タンクの液体が第１及び第２配管を介し
てシリンダ室内に吸込まれ、その後重錘がシリン
ダ室側に移動してピストンによりシリンダ室内の
油がフレキシブル管内に押し出されると、第１流
量調整弁の部分で油量が絞られて減衰が成され
る。Operation In the above configuration, when the support body is attached to a vibrating object, the co-weight is reciprocated in a predetermined direction due to the vibration. When the weight moves toward the spring body, for example, the liquid in the liquid tank is sucked into the cylinder chamber through the first and second piping, and then the weight moves toward the cylinder chamber and the piston causes the oil in the cylinder chamber to be sucked into the cylinder chamber. When the oil is pushed out into the flexible pipe, the amount of oil is throttled at the first flow rate regulating valve to achieve damping.
実施例
以下、本考案の一実施例を図面に基づき説明す
る。第１図及び第２図はおいて、１は振動物体に
着脱自在にされた水平円筒状の支持本体で、その
内部には円柱状の重錘２が前後一対の軸受３を介
して円筒状軸心方向で移動自在に支持されてい
る。上記支持本体１の重錘２移動方向の一端側に
は小径部１ａが突設されてシリンダ室４が形成さ
れ、また支持本体１の他端側には小径筒５が取付
けられると共に、この小径筒５内には重錘２を一
端側に付勢する圧縮ばね（ばね体）６が装着され
ている。更に、上記重錘２の一端部には、シリン
ダ室４内を摺動自在にされたピストン７が設けら
れている。８は一端部が上記支持本体１の小径部
１ａ先端に、第１流量調整弁９を有する連通管１
０を介して、連通されたフレキシブル管で、また
その他端部は第２流量調整弁１１を有する第１配
管１２を介して油タンク（液体タンク）１３に接
続されている。１４は上記支持本体１のシリンダ
室４と油タンク１３とを接続する第２配管で、途
中には油タンク１３内の油をシリンダ室４側にの
み流す逆止弁１５とリリーフ弁１６とが設けられ
ている。Embodiment Hereinafter, an embodiment of the present invention will be described based on the drawings. In Figs. 1 and 2, reference numeral 1 denotes a horizontal cylindrical support body that is detachably attached to a vibrating object. It is supported so that it can move freely in the direction of the heart. A small diameter portion 1a is protruded from one end of the supporting body 1 in the direction of movement of the weight 2 to form a cylinder chamber 4, and a small diameter cylinder 5 is attached to the other end of the supporting body 1. A compression spring (spring body) 6 is installed inside the cylinder 5 to bias the weight 2 toward one end. Furthermore, a piston 7 that is slidable within the cylinder chamber 4 is provided at one end of the weight 2 . Reference numeral 8 denotes a communication pipe 1 having a first flow rate regulating valve 9 at one end thereof at the tip of the small diameter portion 1a of the support body 1.
The other end is connected to an oil tank (liquid tank) 13 via a first pipe 12 having a second flow rate regulating valve 11. Reference numeral 14 denotes a second pipe connecting the cylinder chamber 4 of the support body 1 and the oil tank 13, and a check valve 15 and a relief valve 16 for allowing the oil in the oil tank 13 to flow only to the cylinder chamber 4 side are provided in the middle. It is provided.
次に作用について説明する。 Next, the effect will be explained.
第３図に示すように、上記振動減衰器を例えば
振動しているデイーゼル機関１７に取付けると、
重錘２はデイーゼル機関１７の振動により矢印
Ａ，Ｂで示すように所定方向で往復移動する。上
記重錘２が図面上右側（矢印Ａにて示す）に移動
する時に、第１及び第２配管１２，１４を介して
油タンク１３より油がシリンダ室４内に吸込ま
れ、そしてその後重錘２が図面上左側（矢印Ｂに
て示す）に移動した時に、シリンダ室４内の油は
ピストン７により連通管１０を介してフレキシブ
ル管８内に押し出されるが、連通管１０に設けら
れた第１流量調整弁９の部分で油量が絞られて減
衰が成される。なお、フレキシブル管８内に押し
出された油は第１配管１２を介して油タンク１３
に戻る。そして、重錘２が再び右側に移動した時
に、油タンク１３から油がシリンダ室４内に流入
し、続いて重錘２が左側に移動した時に上記と同
様の減衰機能が生じる。このようにして、重錘２
が往復移動するごとに減衰作用が生じ、デイーゼ
ル機関の振動が減衰される。なお、第１流量調整
弁９はシリンダ室４とフレキシブル管８との間の
油量を調整するものであり、重錘２と圧縮ばね６
から成る振動系に対して減衰効果を有している。
また、第２流量調整弁１１はフレキシブル管８か
らの油の流出量及び油の流入量を調整するもので
あり、フレキシブル管８の振動系に対するばね効
果を調整することができる。上記第２流量調整弁
１１により油量を絞れば、フレキシブル管８のば
ね効果は大きくなり、重錘２と圧縮ばね６とから
成る振動系の固有振動数を大きくすることができ
る。例えば、ばね定数は第２流量調整弁１１を閉
じた時が最大となり、その時のばね定数はフレキ
シブル管８本体のばね定数と圧縮ばね６との和に
なる。また、第２流量調整弁１１を全開にした時
が最小となり、ほぼ圧縮ばね６のばね定数とな
る。更に、上記リリーフ弁１６は油の圧力が上昇
し過ぎた時に油を系外に逃がして圧力を下げるた
めのものである。 As shown in FIG. 3, when the vibration damper is attached to a vibrating diesel engine 17, for example,
The weight 2 reciprocates in a predetermined direction as shown by arrows A and B due to the vibrations of the diesel engine 17. When the weight 2 moves to the right in the drawing (indicated by arrow A), oil is sucked into the cylinder chamber 4 from the oil tank 13 via the first and second pipes 12 and 14, and then the weight 2 moves to the left in the drawing (indicated by arrow B), the oil in the cylinder chamber 4 is pushed out by the piston 7 into the flexible tube 8 through the communication tube 10. 1. The oil amount is throttled at the flow rate adjustment valve 9 to achieve damping. Note that the oil pushed into the flexible pipe 8 is transferred to the oil tank 13 via the first pipe 12.
Return to Then, when the weight 2 moves to the right again, oil flows into the cylinder chamber 4 from the oil tank 13, and when the weight 2 subsequently moves to the left, a damping function similar to that described above occurs. In this way, the weight 2
A damping effect occurs each time the motor reciprocates, damping the vibrations of the diesel engine. The first flow rate regulating valve 9 is for adjusting the amount of oil between the cylinder chamber 4 and the flexible pipe 8, and the first flow rate regulating valve 9 is for adjusting the amount of oil between the cylinder chamber 4 and the flexible pipe 8.
It has a damping effect on the vibration system consisting of.
Further, the second flow rate regulating valve 11 is for adjusting the amount of oil flowing out and the amount of oil flowing in from the flexible pipe 8, and can adjust the spring effect on the vibration system of the flexible pipe 8. If the amount of oil is throttled by the second flow rate regulating valve 11, the spring effect of the flexible tube 8 will be increased, and the natural frequency of the vibration system consisting of the weight 2 and the compression spring 6 can be increased. For example, the spring constant is maximum when the second flow rate regulating valve 11 is closed, and the spring constant at that time is the sum of the spring constant of the flexible tube 8 body and the compression spring 6. Further, when the second flow rate regulating valve 11 is fully opened, the spring constant becomes the minimum and becomes approximately the spring constant of the compression spring 6. Further, the relief valve 16 is used to release oil to the outside of the system and lower the pressure when the oil pressure rises too much.
考案の効果
上記本考案の構成によると、振動減衰器そのも
のを振動物体に取付けるだけでよく、例えば従来
のようにブレーシングを設けた場合に生じる相手
部材の強度向上を必要としないと共に、相手部材
が無い場合にも用いることができる。また、フレ
キシブル管と液体タンクとを接続する第１配管途
中に第２流量調整弁を設けたので、重錘に作用す
るばね体のばね定数を、弁の開閉だけで調整で
き、従つて重錘とばね体とから成る固有振動数を
振動物体の振動数に容易に一致させることができ
る。このように、減衰器の振動数を振動物体の振
動数に近づけると、はじき合いの現象が現われ、
振動物体の振動数を変化させることができ、両者
を一致させればはじき合い量が最も大きくなる。
更に、シリンダ室とフレキシブル管との間に第１
流量調整弁を設けたので、これにより最適の減衰
値を得ることができ、従つて吸振効果を大きくす
ることができる。Effects of the invention According to the above-mentioned configuration of the present invention, it is sufficient to simply attach the vibration damper itself to the vibrating object, and there is no need to improve the strength of the mating member, which occurs when bracing is provided, for example, as in the past. It can also be used when there is no In addition, since a second flow rate adjustment valve is provided in the middle of the first pipe that connects the flexible pipe and the liquid tank, the spring constant of the spring body that acts on the weight can be adjusted simply by opening and closing the valve. The natural frequency of the spring body and the spring body can be easily matched to the frequency of the vibrating object. In this way, when the frequency of the damper approaches the frequency of the vibrating object, a phenomenon of repulsion appears,
The frequency of the vibrating object can be changed, and if they match, the amount of repulsion will be the largest.
Furthermore, a first tube is provided between the cylinder chamber and the flexible pipe.
Since the flow rate regulating valve is provided, it is possible to obtain an optimum damping value, thereby increasing the vibration absorption effect.
図面は本考案の一実施例を示すもので、第１図
は全体断面図、第２図は第１図の−矢視図、
第３図は使用例を示す概略側面図である。
１……支持本体、２……重錘、４……シリンダ
室、６……圧縮ばね（ばね体）、７……ピストン、
８……フレキシブル管、９……第１流量調整弁、
１１……第２流量調整弁、１２……第１配管、１
３……油タンク（液体タンク）、１４……第２配
管、１５……逆止弁。
The drawings show one embodiment of the present invention; FIG. 1 is an overall sectional view, FIG. 2 is a view taken along the - arrow in FIG. 1, and FIG.
FIG. 3 is a schematic side view showing an example of use. 1... Support body, 2... Weight, 4... Cylinder chamber, 6... Compression spring (spring body), 7... Piston,
8... Flexible pipe, 9... First flow rate adjustment valve,
11...Second flow rate regulating valve, 12...First piping, 1
3...Oil tank (liquid tank), 14...Second piping, 15...Check valve.
Claims (1)
定方向で移動自在に設け、上記支持本体の重錘移
動方向における一端側にシリンダ室を形成すると
共に、重錘の一端部に上記シリンダ室内を摺動自
在なピストンを設け、上記重錘の他端側に、重錘
を一端側に付勢するばね体を設け、上記シリンダ
室の先端部にフレキシブル管の一端部を第１流量
調整弁を介して接続すると共に、該フレキシブル
管の他端部と液体タンクとを、第２流量調整弁を
有する第１配管を介して接続し、且つ上記シリン
ダ室先端側と液体タンクとを、逆止弁を有する第
２配管を介して接続したことを特徴とする振動減
衰器。 A weight is provided on a support body attached to a vibrating object so as to be movable in a predetermined direction, a cylinder chamber is formed at one end of the support body in the movement direction of the weight, and a cylinder chamber is provided at one end of the weight to slide inside the cylinder chamber. A movable piston is provided, a spring body is provided at the other end of the weight for biasing the weight toward one end, and one end of the flexible tube is connected to the tip of the cylinder chamber through a first flow rate regulating valve. At the same time, the other end of the flexible pipe and the liquid tank are connected via a first pipe having a second flow rate regulating valve, and the front end side of the cylinder chamber and the liquid tank are connected via a check valve. A vibration damper, characterized in that the vibration damper is connected via a second pipe having a second pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4750185U JPH0241384Y2 (en) | 1985-03-29 | 1985-03-29 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4750185U JPH0241384Y2 (en) | 1985-03-29 | 1985-03-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61162632U JPS61162632U (en) | 1986-10-08 |
| JPH0241384Y2 true JPH0241384Y2 (en) | 1990-11-05 |
Family
ID=30562889
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4750185U Expired JPH0241384Y2 (en) | 1985-03-29 | 1985-03-29 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0241384Y2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0731003Y2 (en) * | 1988-04-05 | 1995-07-19 | 三菱重工業株式会社 | Engine anti-vibration device |
| JPH075309Y2 (en) * | 1988-05-28 | 1995-02-08 | 三菱重工業株式会社 | Anti-vibration device for marine equipment |
| JPH0732994Y2 (en) * | 1989-05-22 | 1995-07-31 | 三菱重工業株式会社 | Vibration system vibration device |
| DE102011080318A1 (en) * | 2011-08-03 | 2013-02-07 | Carl Zeiss Smt Gmbh | Damping arrangement for the dissipation of vibration energy of an element in a system, in particular in a microlithographic projection exposure apparatus |
-
1985
- 1985-03-29 JP JP4750185U patent/JPH0241384Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61162632U (en) | 1986-10-08 |
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