JPS61100632A - Vibration tester - Google Patents
Vibration testerInfo
- Publication number
- JPS61100632A JPS61100632A JP59222035A JP22203584A JPS61100632A JP S61100632 A JPS61100632 A JP S61100632A JP 59222035 A JP59222035 A JP 59222035A JP 22203584 A JP22203584 A JP 22203584A JP S61100632 A JPS61100632 A JP S61100632A
- Authority
- JP
- Japan
- Prior art keywords
- zero point
- vibration
- vibrator
- drift
- vibrators
- 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.)
- Pending
Links
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
- G01M7/02—Vibration-testing by means of a shake table
- G01M7/06—Multidirectional test stands
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Safety Devices In Control Systems (AREA)
Abstract
Description
【発明の詳細な説明】 〔発明の利用分野〕 本発明は、複数の油圧加振機を備え一軸、二軸。[Detailed description of the invention] [Field of application of the invention] The present invention includes a plurality of hydraulic vibration exciters, one axle and two axes.
三軸方向に振動を与えることができる振動試験機に関す
る。This invention relates to a vibration testing machine that can apply vibration in three axial directions.
従来のこの種の振動試験機には、零点のドリフトの検出
装置及びその自動調整装置は付加されていなかった。（
例えば特開昭５４−１０８６５６号公報）そのため、加
振機の零点がドリフトした場合、他の加振機或いはガイ
ド装置によって振動台の位置が拘束されていることによ
り、加振機の変位が拘束され各加振機間に拘束力が発生
した。換言すれば各加振機は制御偏差が残ったままで停
止することとなり、この状態で加振すると、加振波形の
歪の増大、周波数特性の低下を引き起こしていた。Conventional vibration testing machines of this type have not been equipped with a zero point drift detection device and an automatic adjustment device. (
(For example, Japanese Patent Application Laid-Open No. 54-108656) Therefore, if the zero point of the vibrator drifts, the displacement of the vibrator will be restrained because the position of the vibrating table is restrained by another vibrator or guide device. A restraining force was generated between each vibrator. In other words, each vibrator is stopped with the control deviation remaining, and if vibrated in this state, the distortion of the excitation waveform increases and the frequency characteristics deteriorate.
このため、振動台を使用する場合、所定の性能を維持す
るためには頻繁に零点の再調整を行なう必要があった。Therefore, when using a shaking table, it is necessary to frequently readjust the zero point in order to maintain a predetermined performance.
さらに、この調整には等間的な技術を必要とするため振
動台の維持、管理を困難なものにしていた。Furthermore, this adjustment requires a uniform technique, making it difficult to maintain and manage the shaking table.
本発明の目的は、加振機の零点のドリフトが発生しても
簡単な操作で自動的に弊害を取り除くことができること
により維持、管理が簡単で、かつ長期間所定の性能を維
持できる振動試験機を提供することにある。The purpose of the present invention is to provide a vibration test that is easy to maintain and manage, and can maintain a specified performance for a long period of time, by automatically removing the negative effects with a simple operation even if the zero point drift of the vibrator occurs. The aim is to provide the opportunity.
本発明は、二次元振動台に於て加振機の零点のドリフト
が発生し、前述の不具合が発生したためその解決手段と
して生まれたものである。加振機の零点のドリフトは現
在の油圧サーボ技術では避けら−れない。従って、零点
ドリフトそのものを除去することは不可能であり９本発
明の様に、簡単な操作で現象的な弊害を取り除く機能を
付加する方法が現実的かつ最善の方法である。The present invention was developed as a solution to the above-mentioned problem caused by the occurrence of zero point drift of the vibrator in a two-dimensional vibration table. Drift in the zero point of the shaker is unavoidable with current hydraulic servo technology. Therefore, it is impossible to eliminate the zero point drift itself, and the best and most practical method is to add a function to eliminate the phenomenonal adverse effects with a simple operation, as in the present invention.
以下本発明の一実施例を第１図により説明する。 An embodiment of the present invention will be described below with reference to FIG.
第１図は三次元振動台の平面図である。振動台１に供試
体を搭載して加振し供試体の耐震性に関する実験を行な
う装置である。Ｘ方向の振動はＸ１加振機２及びｘ２２
加振３によって与えられ、各各静圧継手４を介して振動
台ｌに伝達される。Ｙ方向の振動も同様にしてＹ１１加
振５及び￥２２加振６によって与えられ静圧軸受３によ
って振動台１に伝達される。また、Ｚ方向の振動も４台
のＺ加振機１８によって与えられ静圧継手（図示してい
ない）によって振動台１に伝達される。ここで、Ｘ１加
振機２及びＸ２加振機３には第２図に示す様な制御系が
構成されている。また、Ｙｌ加振機５及びＹ２２加振６
には第３図に示す制御系を構成する。第３図に於て、圧
力変換器７，８、差圧用増幅器９、圧力表示計１０、演
算器１１、零点＋１１１１用増幅器１２．零点変換用ボ
リュームＩ３が本発明により付加された部分である。今
。FIG. 1 is a plan view of the three-dimensional shaking table. This is an apparatus for carrying out experiments regarding the seismic resistance of a specimen by mounting a specimen on a vibration table 1 and shaking it. Vibration in the X direction is performed by X1 vibrator 2 and x22
It is applied by the excitation 3 and transmitted to the vibration table l via each static pressure joint 4. Vibration in the Y direction is similarly given by the Y11 vibration 5 and the Y22 vibration 6, and is transmitted to the vibration table 1 by the static pressure bearing 3. Further, vibrations in the Z direction are also applied by the four Z vibration exciters 18 and transmitted to the vibration table 1 by a static pressure joint (not shown). Here, the X1 vibrator 2 and the X2 vibrator 3 are configured with a control system as shown in FIG. In addition, Yl vibration exciter 5 and Y22 vibration exciter 6
The control system shown in FIG. 3 is constructed. In FIG. 3, pressure transducers 7, 8, differential pressure amplifier 9, pressure indicator 10, arithmetic unit 11, zero point +1111 amplifier 12. The zero point conversion volume I3 is a part added according to the present invention. now.
第１ｌｉＩに於て、ＸＩ、Ｘ２．Ｙｌ、Ｘ’２のいずれ
かの加振機のサーボ弁１４の零点がドリフトした場合を
考える。サーボ弁１４がドリフトした加振機はそのドリ
フト量に応じて位置がずれようとするが、振動台１は他
の３台の加振機によって位置が決められているため変化
することができない。In 1liI, XI, X2. Let us consider a case where the zero point of the servo valve 14 of either the vibrator Yl or X'2 drifts. The position of the vibration exciter whose servo valve 14 has drifted tends to shift according to the amount of drift, but the position of the vibration table 1 cannot be changed because its position is determined by the other three vibration exciters.
従ってドリフトした加振機も変位することができず、制
御偏差が残った状態となる。このときドリフトした加振
機には差圧が発生し振動台に力を加えることになるため
、この力と対向するため他の３台の加振機にも差圧が発
生する。この現象はとの加振機がドリフトしても同じ現
象となり、結局全ての加振機に差圧が発生することにな
る。また。Therefore, the drifted exciter cannot be displaced, and a control deviation remains. At this time, a differential pressure is generated in the drifting exciter, which applies force to the vibration table, and a differential pressure is also generated in the other three vibrators to counter this force. This phenomenon will be the same even if the two vibrators drift, and eventually a differential pressure will occur in all the vibrators. Also.
２台以上の加振機が同時にドリフトしても現象は同じと
なる。この状態で振動台を加振すると、各加振機間に拘
束力が発生した状態で加振することになるため、十偏と
一側の加振振幅が一致しない。Even if two or more exciters drift at the same time, the phenomenon will be the same. If the vibration table is vibrated in this state, it will be vibrated while a restraining force is generated between each vibrator, so the excitation amplitude on one side and the one side will not match.
出力波形の歪が増大する。各方向の加振機の同期が狂う
０周波数特性が低下する。という不具合が発生する。本
発明によれば、この不具合を簡単な操作で除去できる。Distortion of the output waveform increases. The 0 frequency characteristics deteriorate as the vibration exciters in each direction become out of synchronization. This problem occurs. According to the present invention, this problem can be eliminated with a simple operation.
以下本発明の機能について説明する。まず、４台の加振
機のいずれかに、シリンダ内の圧力を測定することがで
きる様に２台の圧力変換器７，８を取付ける。さらにこ
の圧力変換器７，８の出力の差を増幅する増幅器９及び
差圧を表示する表示計１０を設ける。これにより。The functions of the present invention will be explained below. First, two pressure transducers 7 and 8 are attached to one of the four vibrators so that the pressure inside the cylinder can be measured. Furthermore, an amplifier 9 for amplifying the difference between the outputs of the pressure transducers 7 and 8 and a display meter 10 for displaying the differential pressure are provided. Due to this.
従来困難であった零点のドリフトの発生とその程度を容
易に把握できる。さらに、この零点のドリフトによる各
加振機間の拘束力を除去するために演算器１１、零点調
整用増幅器１２．零点変換用ボリューム１３を設ける。It is now possible to easily understand the occurrence and extent of zero point drift, which has been difficult in the past. Furthermore, in order to remove the restraining force between the vibration exciters due to the drift of the zero point, an arithmetic unit 11, a zero point adjustment amplifier 12. A volume 13 for zero point conversion is provided.
演算器１１は測定された差圧に応じた零点調整用信号を
発生する装置で例えば第４図に示す様な関数をあらかじ
め設定しておく。この関数は各振動試験機に特有のもの
で、あらかじめ、シミュレーション或いは実験等によす
最適な関数を決定しなければならない、さらに零点ｇｍ
用増幅器１２は演算器１１から出力された零点調整用信
号に応じて、変位計用アンプ１５に設けた零点変換用ボ
リューム１３を駆動し。The arithmetic unit 11 is a device that generates a zero point adjustment signal in accordance with the measured differential pressure, and a function as shown in FIG. 4, for example, is set in advance. This function is unique to each vibration testing machine, and the optimal function must be determined in advance through simulation or experiment.
The amplifier 12 drives the zero point conversion volume 13 provided in the displacement meter amplifier 15 in accordance with the zero point adjustment signal output from the arithmetic unit 11.
Ｙ２２加振６の差圧が零になる様変位計１６の零点を調
整する。但し、このｍ整機能は作動用スイッチ１７を操
作した時のみ作動する様にしなければならない、また、
この調整機能は４台の加振機のいずれに設けても良い。Adjust the zero point of the displacement meter 16 so that the differential pressure of the Y22 vibration 6 becomes zero. However, this adjustment function must be activated only when the activation switch 17 is operated, and
This adjustment function may be provided in any of the four vibration exciters.
本発明によれば、振動試験機の油圧加振機の零点のドリ
フトによる性能の低下を、容易に把握することができ、
かつ簡単な操作で所定の性能が維持できる様に調整が可
能となり、従来、メーカの技術者が約１ケ月に１回、２
〜３日調整に要していた調整作業がユーザーで２〜３時
間でできる様になる。According to the present invention, it is possible to easily understand the decrease in performance due to drift of the zero point of the hydraulic exciter of the vibration testing machine.
In addition, it is now possible to make adjustments to maintain the specified performance with simple operations.
The adjustment work that used to take 3 days can now be done by the user in 2 to 3 hours.
第１図は、三次元振動台の平面図、第２図は、Ｘ１加振
機及びＸ２加振機の制御ブロック図、第３図は、Ｙ１１
加振及びＹ２２加振の制御ブロック図、第４図は演算器
に設定すべき関数の一例を示す図である。
１・・・振動台、２・・・Ｘ１加振機、３・・・Ｘ２加
振機、４・・・静圧継手、５・・・Ｙ１１加振、６・・
・Ｙ２２加振、７・・・圧力変換器、８・・・圧力変換
器、９・・・差圧用増幅器、１０・・・圧力表示計、１
１・・・演算器、１２・・・零点調整用増幅器、１３・
・・零点変換用ボリューム。
１４・・・サーボ弁、１５・・・変位計用アンプ、１６
・・・変位計、１７・・・作動スイッチ、１８・・・Ｚ
加振機、１９・・・サーボ増幅器。
第２図Figure 1 is a plan view of the three-dimensional vibration table, Figure 2 is a control block diagram of the X1 vibration exciter and X2 vibration exciter, and Figure 3 is the Y11 vibration exciter.
FIG. 4 is a control block diagram of vibration and Y22 vibration, and is a diagram showing an example of functions to be set in the arithmetic unit. 1... Vibration table, 2... X1 shaker, 3... X2 shaker, 4... Static pressure joint, 5... Y11 shaker, 6...
・Y22 vibration, 7... Pressure transducer, 8... Pressure transducer, 9... Differential pressure amplifier, 10... Pressure indicator, 1
DESCRIPTION OF SYMBOLS 1... Arithmetic unit, 12... Zero point adjustment amplifier, 13.
...Volume for zero point conversion. 14... Servo valve, 15... Displacement meter amplifier, 16
...Displacement meter, 17...Activation switch, 18...Z
Vibrator, 19... Servo amplifier. Figure 2
Claims (1)
に構成した振動試験機において、温度変化や経年変化に
よって生ずる油圧加振機の零点のドリフトを油圧加振機
の差圧の変化を検出することによって検知し、検出した
差圧に応じて、零点を自動的に調整可能な自動調整装置
を付加したことを特徴とする振動試験機。In a vibration testing machine configured to apply vibrations to a vibration table using multiple hydraulic vibrators, the drift of the zero point of the hydraulic vibrators caused by temperature changes and secular changes can be detected using the differential pressure of the hydraulic vibrators. A vibration testing machine characterized by being equipped with an automatic adjustment device that detects changes and automatically adjusts the zero point according to the detected differential pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59222035A JPS61100632A (en) | 1984-10-24 | 1984-10-24 | Vibration tester |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59222035A JPS61100632A (en) | 1984-10-24 | 1984-10-24 | Vibration tester |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61100632A true JPS61100632A (en) | 1986-05-19 |
Family
ID=16776061
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59222035A Pending JPS61100632A (en) | 1984-10-24 | 1984-10-24 | Vibration tester |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61100632A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5544528A (en) * | 1992-04-20 | 1996-08-13 | Team Corporation | High frequency vibration test fixture with hydraulic servo valve and piston actuator |
| CN100343646C (en) * | 2004-12-11 | 2007-10-17 | 燕山大学 | Environmental experimental platform for mechanical vibration with three freedom degrees |
-
1984
- 1984-10-24 JP JP59222035A patent/JPS61100632A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5544528A (en) * | 1992-04-20 | 1996-08-13 | Team Corporation | High frequency vibration test fixture with hydraulic servo valve and piston actuator |
| CN100343646C (en) * | 2004-12-11 | 2007-10-17 | 燕山大学 | Environmental experimental platform for mechanical vibration with three freedom degrees |
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