JP2724296B2 - Excitation weight control method and control mechanism for eccentric weight - Google Patents
Excitation weight control method and control mechanism for eccentric weightInfo
- Publication number
- JP2724296B2 JP2724296B2 JP23669595A JP23669595A JP2724296B2 JP 2724296 B2 JP2724296 B2 JP 2724296B2 JP 23669595 A JP23669595 A JP 23669595A JP 23669595 A JP23669595 A JP 23669595A JP 2724296 B2 JP2724296 B2 JP 2724296B2
- Authority
- JP
- Japan
- Prior art keywords
- eccentric weight
- fixed
- rotation
- eccentric
- phase difference
- 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 - Lifetime
Links
Landscapes
- Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
Description
【0001】[0001]
【発明の属する技術分野】本発明は、杭打ち用のロータ
リ式起振機を回転駆動するとともに、起振機能を制御す
る方法、および同機構に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for driving a rotary exciter for driving a pile and for controlling a vibrating function, and a mechanism therefor.
【0002】[0002]
【従来の技術】土木建設工事に用いられる振動装置(起
振機)は一般に、偏心重錘を取りつけた複数対の回転軸
を平行に配設した構造である。このような構成によれ
ば、反対方向に回転する偏心重錘の遠心起振力を所望の
方向については相加せしめるとともに、不要の方向につ
いては相殺せしめることができる。上述した起振機を用
いて杭打作業を行う場合、振動公害の防止と騒音公害の
防止とが重要な問題となる。次に、図4,図5について
振動公害に関する技術的問題を説明する。2. Description of the Related Art In general, a vibration device (vibrator) used for civil engineering construction has a structure in which a plurality of pairs of rotating shafts having eccentric weights mounted thereon are arranged in parallel. According to such a configuration, the centrifugal vibrating force of the eccentric weight rotating in the opposite direction can be added in a desired direction and can be offset in an unnecessary direction. When a pile driving operation is performed using the above-described exciter, prevention of vibration pollution and prevention of noise pollution are important issues. Next, a technical problem relating to vibration pollution will be described with reference to FIGS.
【0003】図4は杭打ち作業における振動公害を説明
するための模式図である。本図は、クレーンブーム5で
振動装置6を吊持するとともに、該振動装置6のチャッ
ク6aで杭7の上端を把持し、この杭7に振動を与えて
地中に打設している状態を描いてある。杭7の下端を地
表に接せしめて杭打作業を開始する際、最初から振動装
置6をフル稼働させると、杭打ち地点の地表で発生する
地表波aが殆ど減衰せずに付近の民家8に到達するので
振動公害の問題を生じる。ここで、振動装置6の起振力
を任意に調節できるならば、杭7の自重に加えて僅かな
振動を与えながら杭打ち作業を開始し、数メートル打ち
込んでから次第に振動を強くすれば良い。杭7の下端に
相当する震源位置が深くなれば、地中波bは民家8に到
達する途中で減衰するので振動公害は軽微である。FIG. 4 is a schematic diagram for explaining vibration pollution in a pile driving operation. This figure shows a state in which the vibration device 6 is suspended by the crane boom 5, the upper end of the pile 7 is gripped by the chuck 6 a of the vibration device 6, and the pile 7 is vibrated and driven into the ground. Is drawn. When the lower end of the pile 7 is brought into contact with the ground surface to start the pile driving operation, if the vibration device 6 is fully operated from the beginning, the surface wave a generated on the ground at the pile driving point is hardly attenuated and the nearby private house 8 , Causing vibration pollution problems. Here, if the vibrating force of the vibrating device 6 can be adjusted arbitrarily, the pile driving operation is started while giving a slight vibration in addition to the weight of the pile 7, and after driving several meters, the vibration may be gradually increased. . If the hypocenter position corresponding to the lower end of the pile 7 becomes deeper, the underground wave b attenuates on the way to the private house 8, so that the vibration pollution is negligible.
【0004】図5は振動装置の運転開始時および運転停
止時における振動数の変化を示す図表で、横軸は時間で
ある。運転開始時点t0から、定格運転状態に到達する
時点t1までの間、振動数は矢印cの如く急激に上昇す
る。上記の振動数上昇中に、地盤の固有振動数n1、及
びクレーンブームの固有振動数n2を通過する。しか
し、運転開始時における回転数上昇期間T1は一般に短
時間(例えば約3秒間)であるから、振動装置の振動数
が固有振動数に一致したときの共振の問題は、通常無視
することができる。しかし、振動装置6のモータ(図示
せず)の通電を停止した時点t2から回転軸が停止する
時点t3までの間は、回転軸が慣性で回転を続けながら
矢印dの如く次第に減速する。上記の回転数低下期間T
2は比較的長時間(例えば約50秒間)であるから、そ
の途中でクレーンブームの固有振動数n2を通過する
際、該クレーンブームが共振して損傷を被る虞れが有
る。また、地盤の固有振動数n1を通過する際、地盤の
共振により振動公害を生じる虞れが有る。前記の時刻t
2でモータの通電を停止するとともに、振動装置の回転
重錘の回転位相を変化させて起振力を零にすることがで
きれば、振動装置の運転停止操作の際の共振に関する問
題を防止することができる。FIG. 5 is a table showing changes in the vibration frequency at the time of starting operation and at the time of stopping the operation of the vibration device. The horizontal axis represents time. Start of operation time t 0, between time t 1 to reach the rated operating state, frequency rises sharply as shown by arrow c. During the above frequency rise, the natural frequency of the ground n 1 and the natural frequency of the crane boom n 2 are passed. However, since the rotational speed increase period T 1 at the start operation is generally short (e.g., about 3 seconds), the resonance problem when frequency of the vibration device matches the natural frequency, can be usually ignored it can. However, between the time t 2 of stopping the energization of the motor of the vibrating device 6 (not shown) to the time t 3 when the rotary shaft is stopped is gradually decelerated as indicated by the arrow d while continuing to rotate at a rotational axis of inertia . The above-mentioned rotation speed reduction period T
Since 2 is a relatively long time (for example, about 50 seconds), there is a possibility that the crane boom will resonate and be damaged when passing the natural frequency n 2 of the crane boom on the way. Further, when passing through the natural frequency n 1 of the ground, there is a possibility that vibration pollution may occur due to resonance of the ground. The time t
If the motor could be de-energized in step 2 and the vibrating device could change the rotational phase of the vibrating device's rotating weight to zero the vibrating force, it would be possible to prevent problems related to resonance during the operation of stopping the vibrating device. Can be.
【0005】次に、振動装置に供給されるエネルギー量
について見ると、前記の時刻t0からt1まで振動装置6
の回転数が上昇する間、該振動装置の偏心重錘(図示せ
ず)によって振動を発生させつつ増速すると、これを駆
動するために大容量のモータや大容量の電源設備が必要
になる。この場合、振動装置の偏心重錘の回転位相を変
化させて起振力を零にした状態で運転を開始し、定格回
転数に達した後に起振力を発揮させることが出来れば、
モータ容量や電源容量を縮少できるので経済的である。
定格回転数に達した後は、回転部材にそれ以上回転エネ
ルギーを蓄積する必要が無く、振動の減衰を補うだけの
エネルギーを補充することによって運転を継続できるか
らである。Next, looking at the amount of energy supplied to the vibrating device, the vibrating device 6 from time t 0 to t 1 described above.
If the speed is increased while the vibration is generated by the eccentric weight (not shown) of the vibration device while the rotation speed of the vibration device is increasing, a large-capacity motor or a large-capacity power supply facility is required to drive the vibration. . In this case, the operation is started in a state where the vibration force is reduced to zero by changing the rotation phase of the eccentric weight of the vibration device, and if the vibration force can be exerted after reaching the rated rotation speed,
It is economical because the motor capacity and power supply capacity can be reduced.
This is because, after reaching the rated rotation speed, there is no need to store any more rotational energy in the rotating member, and the operation can be continued by replenishing energy sufficient to compensate for the attenuation of vibration.
【0006】以上の事情に鑑みて、起振機の起振力を増
減させる調節技術が開発され、公知になっている。次
に、起振機の起振力を増減調節する原理について述べ
る。図6は2個の偏心重錘の組み合わせによって起振力
を変化させる公知技術を説明するために示したものであ
って、(A)は2個の偏心重錘が最大起振力を発揮する
状態を表す模式図、(B)は起振力中程度である状態を
表す模式図、(C)は起振力がやや小さい状態を表す模
式図、(D)は起振力がゼロの状態を表す模式図であ
る。図6(A)に示した2個の偏心重錘のうち、9は回
転軸2B′に固着された固定偏心重錘であり、10は回
転軸2C′に対して相対的に回動し得る可動偏心重錘で
ある。本発明において固定偏心重錘とは回転軸に対する
相対的回動を係止された偏心重錘の意であって、回転軸
と一緒に回転する部材であるから、固定とは静止の意で
はない。図6(A)における2個の偏心重錘9,10の
相対的位置は、位相差ゼロの状態である。[0006] In view of the above circumstances, an adjustment technique for increasing or decreasing the vibrating force of a vibrator has been developed and is known. Next, the principle of increasing and decreasing the vibrating force of the vibrator will be described. FIG. 6 is a view for explaining a known technique for changing a vibrating force by a combination of two eccentric weights, and FIG. 6A shows two eccentric weights exhibiting a maximum vibrating force. FIG. 3B is a schematic diagram illustrating a state in which the vibrating force is medium, FIG. 3C is a schematic diagram illustrating a state in which the vibrating force is slightly small, and FIG. FIG. Of the two eccentric weights shown in FIG. 6A, 9 is a fixed eccentric weight fixed to the rotating shaft 2B ', and 10 can rotate relatively to the rotating shaft 2C'. It is a movable eccentric weight. In the present invention, the fixed eccentric weight is an eccentric weight that is locked with respect to the rotation axis and is a member that rotates together with the rotation axis. . The relative positions of the two eccentric weights 9 and 10 in FIG. 6A are in a state where the phase difference is zero.
【0007】従って、この図6(A)の状態で、2個の
偏心重錘9,10を歯車4B′,4C′で同期させて回
転させると起振力が発生する。図6(D)の状態では、
2個の偏心重錘9,10それぞれの重心が、常に参考線
M−M(2本の回転軸2B′,2C′を結ぶ線分の垂直
2等分線)に関して対称位置に在るので上下方向の起振
力はゼロである。説明の便宜上、本図6(D)のように
2個の偏心重錘の位相差が180度になって該2個の偏
心重錘の総合偏心モーメントがゼロの状態を基準状態と
名付ける。図6(B),(C)は、それぞれ前記
(A),(D)の中間的状態であるから(A)図の場合
よりも小さく(D)図の場合よりも大きい上下方向起振
力を発生する。そして、(B)図の方が(C)図よりも
(A)図の状態に近いから、起振力の大きい方から順番
に挙げると(A),(B),(C),(D)となる。前
掲の図6において起振力増減制御の原理を示すため、2
本の回転軸2B′,2C′を同期回転歯車4B′,4
C′で同期回転させる形に描かれているが、構造を簡単
にするため1本の回転軸に2個の偏心重錘を配設するこ
ともできる。図7は共通の回転軸に対して固定偏心重錘
を固着するとともに可動偏心重錘を上記共通の回転軸に
対する相対的な回動角位置を調節できるようにした機構
の模式図である。Therefore, when the two eccentric weights 9 and 10 are rotated in synchronization with the gears 4B 'and 4C' in the state shown in FIG. 6A, a vibrating force is generated. In the state of FIG.
Since the center of gravity of each of the two eccentric weights 9 and 10 is always symmetric with respect to the reference line MM (vertical bisector of the line connecting the two rotation axes 2B 'and 2C'), The excitatory force in the direction is zero. For convenience of explanation, a state where the phase difference between the two eccentric weights is 180 degrees and the total eccentric moment of the two eccentric weights is zero as shown in FIG. 6D is referred to as a reference state. 6 (B) and 6 (C) are intermediate states of the above (A) and (D), respectively, so that the vertical vibrating force is smaller than in the case of (A) and larger than in the case of FIG. Occurs. (B) is closer to the state of (A) than that of (C), so that (A), (B), (C), (D) ). In order to show the principle of the vibrating force increase / decrease control in FIG.
The two rotating shafts 2B ', 2C' are connected to the synchronous rotating gears 4B ', 4B.
Although it is depicted as being rotated synchronously at C ', two eccentric weights can be arranged on one rotating shaft to simplify the structure. FIG. 7 is a schematic diagram of a mechanism in which a fixed eccentric weight is fixed to a common rotating shaft and the movable eccentric weight can adjust the relative rotation angle position with respect to the common rotating shaft.
【0008】固定偏心重錘9は回転軸2に固着されて一
緒に回転する。可動偏心重錘10は回転軸2に対する取
付角位置を円弧矢印α−βのごとく変化させて調節する
ことと、調節した状態を維持することとが出来るように
なっている。本図7に描かれている状態は前掲の図6
(B)に示した状態に対応し、起振力が中等度である。
この状態から、可動偏心重錘を矢印α方向に回動させて
固定すると図6(D)の状態に近づいて起振力が減少す
る。また矢印β方向に回動させると図6(A)の状態に
近づいて起振力が増大する。以上のようにして起振力が
調節される。図8は上掲の図7に原理を示したように、
共通の1軸に対して固定偏心重錘と可動偏心重錘とを配
設して起振力を増減調節できるようにした起振機の従来
例を示す斜視図である。2本の回転軸2A,2Bを水平
方向に並べて駆動用プーリ11および同期回転用伝動歯
車4A,4Bによって反対方向に(時計周りと反時計回
りに)同期回転させているのは、水平方向の起振力を相
殺させるためである。固定偏心重錘9Aは回転軸2Aに
固着されている。そして可動偏心重錘10Aは上記回転
軸2Aに対して回動自在に支承されるとともに、固定偏
心重錘9Aに対する回動を調節・固定できるようになっ
ている。すなわち、可動偏心重錘10Aには複数個の調
節用メネジ穴(本図において1個のみ現れている)12
が穿たれている。セットボルト14を上記メネジ穴12
に螺合して六角レンチ15で締めつけ、ノックピン13
で回り止めを施すと可動偏心重錘10Aの角位置が固定
される。図9は前掲の図8に示した従来例の調節機構を
備えた起振機における回転軸と固定偏心重錘と可動偏心
重錘との関係を説明するために示したもので、(A)は
部分的に切断して描いた外観斜視図であり、(B)は回
転軸と平行な方向に見たところを描いた模式図である。
図9(A)に示した23a,23b,23cは目盛であ
って、単位はkg・cmである。目盛を合わせてセットボル
トを螺合することにより、図9(B)に示したように、
可動偏心重錘が3つの角位置をとり、10a,10b,
10cのように相対的に回動して起振力を変化させる。
図7ないし図9に示した従来技術に係る起振機は、以上
に説明したようにして起振力の増減調節を行なうことが
できる。The fixed eccentric weight 9 is fixed to the rotating shaft 2 and rotates together. The movable eccentric weight 10 can be adjusted by changing the mounting angle position with respect to the rotating shaft 2 as shown by the arc arrows α-β, and can maintain the adjusted state. The state depicted in FIG. 7 is shown in FIG.
Exciting force is moderate, corresponding to the state shown in (B).
When the movable eccentric weight is rotated and fixed in the direction of the arrow α from this state, the state approaches the state of FIG. 6A, the vibrating force is increased by approaching the state shown in FIG. The vibrating force is adjusted as described above. FIG. 8 shows the principle in FIG.
FIG. 11 is a perspective view showing a conventional example of a vibration exciter in which a fixed eccentric weight and a movable eccentric weight are arranged with respect to one common axis so that a vibration force can be increased or decreased. The reason why the two rotating shafts 2A and 2B are arranged in the horizontal direction and are synchronously rotated in the opposite directions (clockwise and counterclockwise) by the driving pulley 11 and the synchronous rotation transmission gears 4A and 4B is the horizontal direction. This is to offset the vibrating force. The fixed eccentric weight 9A is fixed to the rotating shaft 2A. The movable eccentric weight 10A is rotatably supported on the rotary shaft 2A, and can adjust and fix the rotation with respect to the fixed eccentric weight 9A. That is, the movable eccentric weight 10A has a plurality of adjusting female screw holes (only one is shown in the figure) 12
Is pierced. Set bolt 14 into female screw hole 12
And tighten it with a hexagon wrench 15
When the rotation is stopped by the above, the angular position of the movable eccentric weight 10A is fixed. FIG. 9 illustrates the relationship between the rotating shaft, the fixed eccentric weight, and the movable eccentric weight in the conventional exciter having the adjusting mechanism shown in FIG. FIG. 2 is an external perspective view partially cut and drawn, and FIG. 2B is a schematic view illustrating a portion viewed in a direction parallel to a rotation axis.
Reference numerals 23a, 23b, and 23c shown in FIG. 9A are scales, and the unit is kg · cm. By setting the scale and screwing the set bolts together, as shown in FIG.
The movable eccentric weight takes three angular positions, 10a, 10b,
The vibrating force is changed by relatively rotating as shown in 10c.
The exciter according to the prior art shown in FIGS. 7 to 9 can increase or decrease the excitatory force as described above.
【0009】[0009]
【発明が解決しようとする課題】図7ないし図9を参照
して説明した従来技術に係る起振機において起振力を増
減調節しようとすると、図8に表されている構造から容
易に理解されるように、運転を止め、ノックピン13を
抜き取ってセットボルト14を抜き出し、可動偏心重錘
10を手動で回して目盛(図9において符号23a〜2
3c)を合わせた後、再びセットボルト14を螺合し緊
定してノックピン13で回り止めを施さねばならない。
従来技術において起振力の増減調節を行なうには、以上
のような操作を必要とする。図4について既に述べたよ
うに、起振装置6は杭7の上端に取り付けられているの
で、これをクレーンブーム5で吊り降して調節した後、
再びクレーンブーム5で吊り上げて杭7の上端に取りつ
ける作業は多大の時間と労力とを費さねばならない。原
理図として先に掲げた図6のように固定偏心重錘9と可
動偏心重錘10とをそれぞれ異なる回転軸に取り付けた
構造を実際の部材によって構成して、起振機の運転を継
続しながら起振力の増減調節を行なうことも考えられる
が、図6(A)の状態と図6(D)の状態との間で可動
偏心重錘10を180度(固定偏心重錘9に対して相対
的に)回動させなければならないので構造が複雑にな
る。特に、固定偏心重錘の回転位相と可動偏心重錘の回
転位相とを検出しつつ、これらの偏心重錘を相互に連繋
させつつサーボ制御するための機構が複雑,高価とな
り、そのメイティナンスに高度の熟練と多大の労力とを
必要とする。When an attempt is made to increase or decrease the excitation force in the conventional exciter described with reference to FIGS. 7 to 9, it is easily understood from the structure shown in FIG. As shown in FIG. 9, the operation is stopped, the knock pin 13 is pulled out, the set bolt 14 is pulled out, and the movable eccentric weight 10 is manually turned to indicate the scale (reference numerals 23a to 23 in FIG. 9).
After setting 3c), the set bolt 14 must be screwed again, tightened, and detented with the knock pin 13.
In the prior art, the above operations are required to adjust the increase and decrease of the vibrating force. As already described with reference to FIG. 4, since the vibrating device 6 is attached to the upper end of the pile 7, it is suspended by the crane boom 5 and adjusted.
The work of lifting up the crane boom 5 and attaching it to the upper end of the pile 7 again requires a lot of time and labor. The structure in which the fixed eccentric weight 9 and the movable eccentric weight 10 are respectively mounted on different rotating shafts as shown in FIG. It is also conceivable to increase or decrease the vibrating force while adjusting the movable eccentric weight 10 by 180 degrees between the state shown in FIG. 6A and the state shown in FIG. (Relatively) and the structure becomes complicated. In particular, the mechanism for performing servo control while detecting the rotational phase of the fixed eccentric weight and the rotational phase of the movable eccentric weight while connecting these eccentric weights to each other becomes complicated and expensive. Requires great skill and great effort.
【0010】本発明は上述の事情に鑑みて為されたもの
であって、偏心重錘の回転位相を検出したり偏心重錘の
回転駆動をサーボ制御したりする必要が無く、しかも、
起振機の運転を中断することなく継続しつつ、該起振機
の起振力を増減調節して杭打作業における振動公害を未
然に防止し得る制御方法および制御機構を提供すること
を目的とする。The present invention has been made in view of the above circumstances, and there is no need to detect the rotational phase of an eccentric weight or to servo-control the rotational drive of an eccentric weight.
It is an object of the present invention to provide a control method and a control mechanism capable of preventing vibration pollution in a pile driving operation by increasing or decreasing the vibrating force of the vibration exciter while continuing the operation of the vibration exciter without interruption. And
【0011】[0011]
【課題を解決するための手段】上記の目的(制御機構の
簡素化)を達成するために創作した本発明の基本的原理
について、前掲の図9を参照して略述すると次のとおり
である。すなわち、運転開始の際、公害防止およびクレ
ーンブーム保護のために必要なことは、起振機の回転を
開始する点oにおいて偏心重錘の総合偏心モーメントを
零にしてスタートし、定常運転に移行する点iにおいて
上記の総合偏心モーメントを最大ならしめれば良い。換
言すれば2系列の起振ユニット相互の回転位相差を18
0度にして起振力零の状態でスタートし(点o)、定常
運転に移行する点iで回転位相差を0度にして最大起振
力を発揮させれば良い。同様に、運転終了の際に公害防
止およびクレーンブーム保護のために必要なことは、定
常運転から慣性運転に移行する点jで回転位相差を18
0度にして起振力零にすれば良い。さらに要約して言う
ならば、地盤の固有振動数n1とクレーンブームの固有
振動数n2とに相当する回転数領域を、回転位相差18
0度で通過すれば良い。点iから点jまでの定常運転中
には、回転位相差を0度に保持して最大起振力を発揮さ
せなければならないことは言うまでも無い。以上の考察
から明らかになったことは、2系列の起振ユニット相互
の回転位相差の制御は、0度の状態と180度の状態と
の切り替え操作が行なわれれば足り、回転数範囲の全域
にわたって精密にサーボ制御することは省略可能だとい
うことである。The basic principle of the present invention created to achieve the above object (simplification of the control mechanism) is briefly described below with reference to FIG. . That is, at the time of starting operation, what is necessary for pollution prevention and crane boom protection is to set the total eccentric moment of the eccentric weight to zero at the point o where the rotation of the exciter starts, and to start the steady operation. At the point i, the above total eccentric moment may be maximized. In other words, the rotational phase difference between the two vibration units is 18
It is sufficient to start at 0 degree and start at zero excitation force (point o), and at point i where the operation shifts to the steady operation, set the rotational phase difference to 0 degree to exhibit the maximum excitation force. Similarly, what is necessary to prevent pollution and protect the crane boom at the end of the operation is that the rotational phase difference is 18 at the point j at which the operation shifts from the steady operation to the inertia operation.
What is necessary is just to set it to 0 degree and to make excitation force zero. If say further summarize, the speed range corresponding to the natural frequency n 2 of the natural frequency n 1 and a crane boom of the ground, the rotational phase difference 18
It only has to pass at 0 degrees. It goes without saying that during the steady operation from the point i to the point j, the rotational phase difference must be maintained at 0 degree to exert the maximum vibrating force. From the above considerations, it is clear that the control of the rotational phase difference between the two series of excitation units is sufficient if the operation of switching between the 0-degree state and the 180-degree state is performed. It means that precise servo control over the whole can be omitted.
【0012】本願発明の基本は、A,B両系統の偏心重
錘式振動発生機構を設けて、該A,B両系統の回転部材
相互の回転位相差が0度よりも小さくならず、180度
よりも大きくならないように、許容角度180度以内に
機械的に拘束し、上記A,B両系統をそれぞれモータで
回転駆動する。ただし、以上に述べたのは基本原理であ
って、起振力を減少させたとき必ずしも起振力を零にす
る必要は無い。実際問題としては、振動公害やクレーン
ブームの共振破損を招かない程度の起振力を残しておか
ないと、杭は自重だけでは地中に沈み込んでゆかない。The basic principle of the present invention is to provide an eccentric weight type vibration generating mechanism for both the A and B systems so that the rotational phase difference between the rotating members of the A and B systems does not become smaller than 0 degree, and 180 degrees. In order not to exceed the degree, mechanical restraint is performed within an allowable angle of 180 degrees, and both the A and B systems are rotationally driven by motors. However, what has been described above is the basic principle, and it is not always necessary to make the excitation force zero when the excitation force is reduced. As a practical matter, the pile will not sink into the ground by its own weight alone unless a vibrating force that does not cause vibration pollution or resonance damage of the crane boom is left.
【0013】前記のA系統,B系統とは説明の便宜上の
呼称であって、名称を入れ替えることも可能である。た
だし、本発明においてはA,B両系統の偏心重錘相互の
回転位相差が零となるように揃えた状態から、相対的に
約180度進相することが出来るが上記のように揃った
状態から遅相出来ない方をA系統とし、上記のように位
相差零に揃えた状態から相対的に約180度遅相可能
で、この揃えられた状態から進相出来ない方をB系統と
する。すなわち、回転位相差零の状態から、A系統は約
180度進相可能、B系統は180度遅相可能である。
A系統がB系統に比して相対的に約180度進むという
ことと、B系統がA系統に比して相対的に約180度遅
れるということとは同意である。従って、A,B両系統
の内の何れか一方が他方を押しながら回っているとき
は、該A,B両系統の位相の関係は、(イ)A系統がB
系統よりも約180度進んで総合偏心モーメント最小に
なっているか、(ロ)A,B両系統の回転位相差が零に
なって総合偏心モーメントが最大になっているか、何れ
かである。The above-mentioned A system and B system are names for convenience of explanation, and the names can be interchanged. However, in the present invention, the phase can be relatively advanced by about 180 degrees from the state where the rotational phase difference between the eccentric weights of both the A and B systems is adjusted to be zero. The system that can not be delayed from the state is defined as system A, and the system that can be relatively delayed by about 180 degrees from the state where the phase difference is adjusted to zero as described above, and the system that cannot be advanced from the aligned state is defined as system B. I do. That is, from the state where the rotational phase difference is zero, the system A can be advanced by about 180 degrees, and the system B can be delayed by 180 degrees.
It is agreed that the A system leads by about 180 degrees relative to the B system, and that the B system lags by about 180 degrees relative to the A system. Therefore, when one of the two systems A and B is rotating while pressing the other, the phase relationship between the two systems A and B is as follows.
Either about 180 degrees ahead of the system and the total eccentric moment is minimum, or (ii) the rotational phase difference between both the A and B systems is zero and the total eccentric moment is maximum.
【0014】以上に述べた原理に基づいて本発明に係る
起振機の駆動・制御装置の具体的構成は(図1参照)、
A系統とB系統との2系統よりなる駆動・伝動系を具備
し、A系統回転軸(21)にA系統固定偏心重錘(2
6)が固定されるとともに、該B系統回転軸にA系統可
動偏心重錘(29)が相対的回動可能に嵌着され、前記
A系統固定偏心重錘(26)とA系統可動偏心重錘(2
9)とを常に等しい回転速度で反対方向に回転せしめる
連動手段が設けられるとともに、前記B系統固定偏心重
錘(28)とB系統可動偏心重錘(27)とを常に等し
い回転速度で反対方向に回転せしめる連動手段が設けら
れており、かつ、前記A系統の回転位相とB系統の回転
位相との位相差を、0度以上180度以下の所定角度範
囲内に拘束する機械的手段が設けられており、前記A系
統回転軸(21)を回転駆動するA系統駆動モータ(M
a)と、B系統回転軸(22)を回転駆動するB系統駆
動モータ(Mb)とが設けられるとともに、上記A,B
両系統の駆動モータ(Ma,Mb)がそれぞれ個別に制
御できるようになっていることを特徴とする。Based on the principle described above, a specific configuration of the drive / control device of the vibration exciter according to the present invention is shown in FIG.
A drive and transmission system consisting of two systems, A system and B system, is provided, and the A system fixed eccentric weight (2
6) is fixed, and the A-system movable eccentric weight (29) is rotatably fitted to the B-system rotating shaft, so that the A-system fixed eccentric weight (26) and the A-system movable eccentric weight are rotated. Weight (2
9) is provided at all times in the opposite direction at the same rotational speed, and the B-system fixed eccentric weight (28) and the B-system movable eccentric weight (27) are always rotated in the opposite direction at the same rotational speed. And a mechanical means for restricting the phase difference between the rotation phase of the system A and the rotation phase of the system B within a predetermined angle range of 0 degree or more and 180 degrees or less. And an A-system drive motor (M) that rotationally drives the A-system rotation shaft (21).
a) and a B-system drive motor (Mb) for rotating and driving the B-system rotary shaft (22).
It is characterized in that the drive motors (Ma, Mb) of both systems can be individually controlled.
【0015】上記の構成においては、A系統の固定偏心
重錘とA系統の可動偏心重錘とが常に一定の位相差(1
80度)を保持するとともに、B系統の固定偏心重錘と
B系統の可動偏心重錘とが常に一定の位相差(180
度)を保持しており、かつ、A系統の固定,可動両偏心
重錘とB系統の固定,可動両偏心重錘との位相差は所定
角度範囲内となるように拘束されている。このため、A
系統の駆動モータによってA系統の固定,可動両偏心重
錘を回転駆動すると、A系統よりも所定角度以上には遅
相できないB系統の固定,可動両偏心重錘は所定角度範
囲の最大角度だけ遅れて(A系統に引っ張られる形で)
A系統と同じ回転速度で同じ方向に回転して最大偏心モ
ーメントの状態で作動し、最大起振力を発生させる。ま
た、B系統の駆動モータによってB系統の固定,可動両
偏心重錘を回転駆動すると、B系統よりも所定角度以上
には進相できないA系統の固定,可動両偏心重錘は所定
角度範囲内の最小角度だけ進んで(B系統に押される形
で)B系統と同じ回転速度で同じ方向に回転して最小偏
心モーメントの状態で作動し、最小起振力を発生させ
る。以上の作働を要約すると、A,B両系統の回転位相
を検出したりサーボ制御したりすることなく、かつ、起
振機の運転を中断することなく、2個の駆動用モータの
内の何れによって起振機を回転駆動するかという単純な
操作によって、最大起振力を発生する状態と最小起振力
を発生する状態との何れかを任意に選定することができ
る。In the above configuration, the fixed eccentric weight of the system A and the movable eccentric weight of the system A always have a constant phase difference (1).
80 degrees), and the fixed phase difference between the fixed eccentric weight of the B system and the movable eccentric weight of the B system is always constant (180 degrees).
), And the phase difference between the fixed and movable eccentric weights of the system A and the fixed and movable eccentric weights of the system B is constrained to be within a predetermined angle range. Therefore, A
When the fixed and movable eccentric weights of the system A are rotationally driven by the drive motor of the system, the fixed and movable eccentric weights of the system B cannot be delayed more than a predetermined angle from the system A, and the weights of the fixed and movable eccentric weights of the system B are limited to a maximum angle within a predetermined angle range. Late (pulled by system A)
It rotates in the same direction at the same rotational speed as the A-system and operates in the state of the maximum eccentric moment to generate the maximum vibrating force. When the fixed and movable eccentric weights of the B system are rotationally driven by the drive motor of the B system, the fixed and movable eccentric weights of the A system which cannot advance more than a predetermined angle than the B system are within a predetermined angle range. (In the form of being pushed by the B system) and rotating in the same direction at the same rotational speed as the B system to operate in the state of the minimum eccentric moment and generate the minimum vibrating force. To summarize the above operation, without detecting the rotational phases of the A and B systems or performing servo control, and without interrupting the operation of the vibration exciter, one of the two drive motors is used. By a simple operation of which one causes the exciter to be rotationally driven, it is possible to arbitrarily select one of a state in which the maximum excitation force is generated and a state in which the minimum excitation force is generated.
【0016】[0016]
【発明の実施の形態】次に、図1ないし図3を順次に参
照しつつ、本発明の実施形態を説明する。図1は、本発
明の起振力制御方法を実施するために構成した本発明に
係る偏心重錘の起振力制御機構の1実施形態を備えた起
振機を示し、模式的に描いた水平断面図である。ケース
1によって2本の水平な軸、すなわちA系統回転軸21
とB系統回転軸22とが回転自在に支承されている。そ
してA系統駆動歯車23がキー24を介して前記A系統
回転軸21に固着されている。本図1には7個のキーが
描かれていて、符号は1個のみ付されているが、キーの
図形が描かれていることは回転軸に対して相対的に回動
不能に嵌合されていることを表わしている。そして、キ
ーの図形が描かれていない個所は相対的な回動可能に嵌
合されていることを表している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of the present invention will be described with reference to FIGS. FIG. 1 schematically shows an exciter provided with one embodiment of an eccentric weight excitation force control mechanism according to the present invention configured to carry out the excitation force control method of the present invention. It is a horizontal sectional view. Depending on the case 1, two horizontal shafts, that is, the A-system rotating shaft 21
And the B-system rotary shaft 22 are rotatably supported. An A-system drive gear 23 is fixed to the A-system rotary shaft 21 via a key 24. In FIG. 1, seven keys are drawn, and only one symbol is attached. However, the drawing of the key means that the key is fitted so that it cannot rotate relative to the rotation axis. It shows that it is done. A portion where the key graphic is not drawn indicates that the key is fitted so as to be relatively rotatable.
【0017】A系統の被動歯車25は前記A系統駆動歯
車23と歯数が等しく、B系統の回転軸22に対して回
動自在に嵌合されて支承されている。同様に、歯数の等
しいB系統の1対の歯車のうち、B系統駆動歯車34は
B系統回転軸22に対して回動不可能に固着され、B系
統被動歯車31はA系統回転軸21に対して回動可能に
嵌合され、支承されている。前記A系統回転軸21に対
して、A系統固定偏心重錘26が相対的回動不可能に、
B系統可動偏心重錘27が相対的回動可能に、それぞれ
嵌合されて支持されるとともに、上記B系統可動偏心重
錘27は前記B系統被動歯車31に対して同期連結杆3
3を介して一体的に連結されて一緒に回転する。これに
より該B系統可動偏心重錘27はB系統回転軸22と反
対方向に、同じ回転速度で回転せしめられる。前記B系
統回転軸22に対して、B系統固定偏心重錘28が相対
的回動不可能に、A系統可動偏心重錘29が相対的回動
可能に、それぞれ嵌合されて支持されるとともに、上記
A系統可動偏心重錘29は前記A系統被動歯車25に対
して同期連結杆30を介して一体的に連結されて一緒に
回転する。これにより該A系統可動偏心重錘29はA系
統回転軸21と反対方向に、同じ回転速度で回転せしめ
られる。前記A系統回転軸21にA系統被動プーリ35
が固着されるとともに、A系統駆動モータMaにA系統
駆動プーリ38が固着されており、上記A系統被動プー
リ35とA系統駆動プーリ38とに巻掛伝動手段37が
巻き掛けられて伝動している。前記B系統回転軸22に
B系統被動プーリ36が固着されるとともに、B系統駆
動モータMbにB系統駆動プーリ39が固着されてお
り、上記B系統被動プーリ36とA系統駆動プーリ39
とに巻掛伝動手段37が巻き掛けられて伝動している。
図2は、前掲の図1に示した実施態様に係る起振機の水
平断面図であって、その輪郭線並びに符号および部材の
名称は図1と同様であるが、A系統の回転部材に平行斜
線を付するとともにB系統の回転部材に斑点を付して系
統区分および伝動経路を表してある。The A-system driven gear 25 has the same number of teeth as the A-system drive gear 23, and is rotatably fitted and supported on the B-system rotary shaft 22. Similarly, among a pair of gears of the B system having the same number of teeth, the B system drive gear 34 is fixed to the B system rotation shaft 22 so as not to rotate, and the B system driven gear 31 is connected to the A system rotation shaft 21. And are rotatably fitted to and supported by. The A-system fixed eccentric weight 26 cannot rotate relative to the A-system rotation shaft 21,
The B-system movable eccentric weight 27 is fitted and supported so as to be relatively rotatable, and the B-system movable eccentric weight 27 is connected to the B-system driven gear 31 by the synchronous connecting rod 3.
3 and are connected together and rotate together. As a result, the B-system movable eccentric weight 27 is rotated at the same rotational speed in the direction opposite to the B-system rotating shaft 22. The B-system fixed eccentric weight 28 is fitted to and supported by the B-system rotating shaft 22 so that the B-system fixed eccentric weight 28 cannot rotate relatively and the A-system movable eccentric weight 29 can rotate relatively. The A-system movable eccentric weight 29 is integrally connected to the A-system driven gear 25 via a synchronous connection rod 30 and rotates together. As a result, the A-system movable eccentric weight 29 is rotated at the same rotational speed in the direction opposite to the A-system rotating shaft 21. The A-system driven pulley 35 is attached to the A-system rotating shaft 21.
Is fixed, and the A-system drive pulley 38 is fixed to the A-system drive motor Ma, and the wrapping transmission means 37 is wound around the A-system driven pulley 35 and the A-system drive pulley 38 to transmit power. I have. A B-system driven pulley 36 is fixed to the B-system rotating shaft 22, and a B-system drive pulley 39 is fixed to the B-system drive motor Mb.
Then, the wrapping transmission means 37 is wrapped and transmitted.
FIG. 2 is a horizontal cross-sectional view of the vibration exciter according to the embodiment shown in FIG. 1, which has the same outlines, symbols, and names of members as those in FIG. 1. Rotational members of the B system are indicated by parallel diagonal lines and spots are added to indicate system divisions and transmission paths.
【0018】図示を省略するが、A系統の回転部材とB
系統の回転部材とは所定角度範囲の位相差を許容して、
相互の回動が拘束されている。A,B両系統の相対的回
動は、A,B両系統間の回転位相差の増減を意味してい
る。本発明を実施する際、回動の拘束手段すなわち位相
差の制限手段は任意に設定することができるが、同一回
転軸(例えば符号21)に嵌着されている固定偏心重錘
(26)の一部と可動偏心重錘(27)の一部とを、ガ
タを伴って当接せしめるように構成すると好都合であ
る。この種の技術は、例えば特願平7−159479号
出願の明細書及び図面に開示されている。Although not shown, the A-system rotating member and B
Allowing a phase difference within a predetermined angle range with the rotating member of the system,
Mutual rotation is restricted. The relative rotation between the A and B systems means an increase or decrease in the rotational phase difference between the A and B systems. In practicing the present invention, the means for restricting the rotation, that is, the means for limiting the phase difference can be set arbitrarily, but the fixed eccentric weight (26) fitted on the same rotating shaft (for example, reference numeral 21) can be used. Conveniently, a part and a part of the movable eccentric weight (27) are configured to contact with play. This type of technique is disclosed, for example, in the specification and drawings of Japanese Patent Application No. 7-159479.
【0019】本例においては、A系統偏心重錘とB系統
偏心重錘との位相差制限範囲を次のように設定した。B
系統駆動モータMbを作動させてB系統回転軸22を回
転させると、図2に斑点を付して示したB系統の回転部
材が回転する。平行斜線を付して示したA系統の回転部
材は、B系統よりも遅れることができないので、B系統
で押される形に、B系統よりも微小角度だけ進相した状
態で一緒に回転する。この状態は、A,B両系統の偏心
モーメントが零になる基準状態に近い状態である。ただ
し、偏心モーメントを完全に零とはせず、重力加速度g
とほぼ等しい振動加速度を生じるように前記微小角度を
設定してある。重力加速度とほぼ等しい振動加速度を生
じさせるに適正な位相差の値は、計算で求めることもで
きるが、実機について試験的に実測して求めることも容
易である。また、A系統駆動モータMaを作動させると
A系統の回転部材が回転せしめられ、A系統よりも所定
角度以上に遅れることのできないB系統は、該A系統に
引っ張られる形に、許容角度範囲の最大位相差角だけ遅
れて一緒に回転する(一緒に回転している時は、A,B
両系統の回転速度は等しい)。この状態は、A,B両系
統の位相差が180度である基準状態に比して位相差が
約30度だけ小さくなるように設定してある。その理由
は、位相差が180度−30度=150度よりも小さい
状態で回転している場合、これを標準状態に戻すように
操作するには、非常に大きい操作力を必要とするからで
ある。本発明者の試験研究によれば、基準状態からの位
相差を約30度に設定することが最も好都合である。In this embodiment, the phase difference limiting range between the A-system eccentric weight and the B-system eccentric weight is set as follows. B
When the system drive motor Mb is operated to rotate the B-system rotation shaft 22, the B-system rotating member indicated by spots in FIG. 2 rotates. Since the rotating members of the A system indicated by the parallel diagonal lines cannot be delayed from the B system, the rotating members rotate together with the shape pushed by the B system by a smaller angle than the B system. This state is a state close to the reference state where the eccentric moments of both the A and B systems become zero. However, the eccentric moment is not completely set to zero, and the gravitational acceleration g
The minute angle is set so as to generate a vibration acceleration substantially equal to. The value of the phase difference appropriate for causing the vibration acceleration substantially equal to the gravitational acceleration can be obtained by calculation, but it is also easy to obtain the value by experimentally measuring the actual machine. Further, when the A-system drive motor Ma is operated, the rotating member of the A-system is rotated, and the B-system, which cannot be delayed more than a predetermined angle from the A-system, is pulled by the A-system to have an allowable angle range. Rotate together with a delay of the maximum phase difference angle (when rotating together, A, B
Both systems have the same rotation speed). This state is set so that the phase difference is reduced by about 30 degrees as compared with the reference state in which the phase difference between the A and B systems is 180 degrees. The reason is that, when the phase difference is rotating in a state smaller than 180 degrees−30 degrees = 150 degrees, an extremely large operation force is required to return the phase difference to the standard state. is there. According to tests conducted by the present inventors, it is most convenient to set the phase difference from the reference state to about 30 degrees.
【0020】本実施形態の装置を用いて杭打ち作業を行
なうためには、(図5を併せて参照)作業開始点oで、
B系統駆動モータMbを作動させて、偏心モーメント最
小(起振力最小,振動加速度約g)で回転を始め、矢印
cのように回転数を上昇させつつ、地盤固有地動数
n1、およびクレーンブーム固有振動数n2を偏心モーメ
ント最小の状態で通過する。通過し終えると、B系統駆
動モータMbの通電を断ち、もしくは通電を弱めて、A
系統駆動モータMaを作動させる。この場合、偏心重錘
の回転数(回転速度)と発生する振動の振動数とは等し
い。回転数が定格回転数に達すると(点i)、定常運転
に移行する。この状態では、A系統が基準状態よりも約
30度進相して最大偏心モーメントとなり、最大起振力
を発揮しつつ杭打作業を遂行する。この定常運転は、A
系統がB系統を引っ張る形で、B系統は約30度遅れて
追随する。この定常状態の運転期間中、B系統駆動モー
タMbは通電を断っておいても良い。また、B系統がA
系統に追いつかない程度に、B系統駆動モータMbに電
気エネルギーを供給しても良い。杭打ち作業を遂行し終
えたとき(点j)A,B両系統の駆動モータMa,Mb
の給電を停止するとともに、A系統駆動モータMaに電
気制動を掛ける。これにより、偏心モーメント最小の状
態となり、クレーンブーム固有振動数n2,地盤固有振
動数n1を順次に通過して矢印mのごとく減速し、停止
(点m)するに至る。In order to perform a pile driving operation using the apparatus of this embodiment, (see also FIG. 5)
The B-system drive motor Mb is operated to start rotating with the minimum eccentric moment (minimum vibrating force, vibration acceleration about g), while increasing the number of rotations as indicated by the arrow c, the ground-specific ground motion number n 1 and the crane It passes through the boom natural frequency n 2 with the minimum eccentric moment. When the passage is completed, the energization of the B-system drive motor Mb is cut off or the energization is reduced, and A
The system drive motor Ma is operated. In this case, the rotation frequency (rotation speed) of the eccentric weight is equal to the vibration frequency of the generated vibration. When the rotation speed reaches the rated rotation speed (point i), the operation shifts to a steady operation. In this state, the system A is advanced by about 30 degrees from the reference state to become the maximum eccentric moment, and performs the pile driving work while exhibiting the maximum vibration force. This steady operation is A
The system pulls the system B, and the system B follows with a delay of about 30 degrees. During this steady state operation period, the B-system drive motor Mb may be de-energized. In addition, B system is A
Electric energy may be supplied to the B-system drive motor Mb to such an extent that it cannot catch up with the system. When the pile driving operation is completed (point j), the drive motors Ma and Mb of both the A and B systems
Is stopped, and electric braking is applied to the A-system drive motor Ma. As a result, the eccentric moment is minimized, and sequentially passes through the crane boom natural frequency n 2 and the ground natural frequency n 1 , decelerates as indicated by an arrow m, and stops (point m).
【0021】図3は、前掲の図1および図2の実施形態
と異なる実施形態を示し、模式的に描いた水平断面図で
ある。前記実施態様と異なる点は次の通りである。A系
統駆動モータMaに固着したA系統原動歯車40をA系
統駆動歯車23に噛合せしめるとともに、B系統駆動モ
ータMbに固着したB系統原動歯車41をB系統駆動歯
車34に噛合させる。本実施形態(図3)によれば前記
実施形態(図1,図2)に比して装置の横幅寸法Lが小
さくなるという長所が有る。ただし、前記実施形態(図
1,図2)の方は、歯車騒音が少ないという長所を有し
ている。FIG. 3 is a horizontal sectional view schematically showing an embodiment different from the embodiments shown in FIGS. 1 and 2 described above. The differences from the above embodiment are as follows. The A-system drive gear 40 fixed to the A-system drive motor Ma is meshed with the A-system drive gear 23, and the B-system drive gear 41 fixed to the B-system drive motor Mb is meshed with the B-system drive gear 34. According to the present embodiment (FIG. 3), there is an advantage that the lateral width L of the device is smaller than that of the embodiment (FIGS. 1 and 2). However, the embodiment (FIGS. 1 and 2) has an advantage that the gear noise is small.
【0022】[0022]
【発明の効果】固定偏心重錘と可動偏心重錘とよりなる
起振機の制御に本発明を適用すると、A系統の固定偏心
重錘とA系統の可動偏心重錘とが常に一定の位相差(1
80度)を保持するとともに、B系統の固定偏心重錘と
B系統の可動偏心重錘とが常に一定の位相差(180
度)を保持しており、かつ、A系統の固定,可動両偏心
重錘とB系統の固定,可動両偏心重錘との位相差は所定
角度範囲内となるように拘束されている。このため、A
系統の駆動モータによってA系統の固定,可動両偏心重
錘を回転駆動すると、A系統よりも所定角度以上には遅
相できないB系統の固定,可動両偏心重錘は所定角度範
囲内の最大角度だけ遅れて(A系統に引っ張られる形
で)同じ方向に回転して最大偏心モーメントの状態で作
動し、最大起振力を発生させる。また、B系統の駆動モ
ータによってB系統の固定,可動両偏心重錘を回転駆動
すると、B系統よりも所定角度以上には進相できないA
系統の固定,可動両偏心重錘は所定角度範囲内の最小角
度だけ進んで(B系統で押される形で)B系統と同じ回
転速度で同じ方向に回転して最小偏心モーメント状態で
作動し、最小起振力を発生させる。以上の作働を要約す
ると、A,B両系統の回転位相を検出したりサーボ制御
したりすることなく、かつ、起振機の運転を中断するこ
となく、2個の駆動用モータの内の何れによって起振機
を回転駆動するかという単純な操作によって、最大起振
力を発生する状態と最小起振力を発生する状態との何れ
かを任意に選定することができる。When the present invention is applied to the control of an exciter composed of a fixed eccentric weight and a movable eccentric weight, the fixed eccentric weight of the A system and the movable eccentric weight of the A system are always in a fixed position. Difference (1
80 degrees), and the fixed phase difference between the fixed eccentric weight of the B system and the movable eccentric weight of the B system is always constant (180 degrees).
), And the phase difference between the fixed and movable eccentric weights of the system A and the fixed and movable eccentric weights of the system B is constrained to be within a predetermined angle range. Therefore, A
When the fixed and movable eccentric weights of the system A are rotationally driven by the drive motor of the system, the fixed and movable eccentric weights of the system B cannot be delayed more than a predetermined angle from the system A, and the weights of the fixed and movable eccentric weights of the system B are within a predetermined angle range. Only after a delay (in the form of being pulled by the A system) it rotates in the same direction and operates at the maximum eccentric moment, generating the maximum vibrating force. Further, when the fixed and movable eccentric weights of the B system are driven to rotate by the drive motor of the B system, the phase cannot be advanced beyond a predetermined angle than the B system.
Both the fixed and movable eccentric weights of the system advance by the minimum angle within the predetermined angle range (in a form pushed by the system B), rotate in the same direction at the same rotational speed as the system B, operate in the state of the minimum eccentric moment, Generate minimum vibration force. To summarize the above operation, without detecting the rotational phases of the A and B systems or performing servo control, and without interrupting the operation of the vibration exciter, one of the two drive motors is used. By a simple operation of which one causes the exciter to be rotationally driven, it is possible to arbitrarily select any one of a state in which the maximum vibration is generated and a state in which the minimum vibration is generated.
【図1】本発明の起振力制御方法を実施するために構成
した本発明に偏る偏心重錘の起振力制御機構の1実施形
態を備えた起振機を示し、模式的に描いた水平断面図で
ある。FIG. 1 schematically shows an exciter provided with an embodiment of an eccentric weight excitatory force control mechanism biased to the present invention configured to carry out an excitatory force control method of the present invention. It is a horizontal sectional view.
【図2】前掲の図1に示した実施形態に係る起振機の水
平断面図であって、その輪郭線並びに符号および部材の
名称は図1と同様であるが、A系統の回転部材に平行斜
線を付するとともにB系統の回転部材に斑点を付して系
統区分および伝動経路を表してある。FIG. 2 is a horizontal cross-sectional view of the vibration exciter according to the embodiment shown in FIG. 1 described above, in which the outlines, symbols and names of members are the same as those in FIG. Rotational members of the B system are indicated by parallel diagonal lines and spots are added to indicate system divisions and transmission paths.
【図3】前掲の図1および図2の実施形態と異なる実施
形態を示し、模式的に描いた水平断面図である。FIG. 3 is a schematic cross-sectional view showing an embodiment different from the embodiments of FIGS. 1 and 2 described above.
【図4】振動装置を用いる杭打工事における地上波およ
び地中波の伝達を示す説明図である。FIG. 4 is an explanatory diagram showing transmission of ground waves and underground waves in a pile driving work using a vibration device.
【図5】振動杭打工事における共振現象を説明するため
の、時間−回転速度を表わした図表である。FIG. 5 is a table showing time-rotation speed for explaining a resonance phenomenon in a vibrating pile driving work.
【図6】2個の偏心重錘の組み合わせによって起振力を
変化させる公知技術を説明するために示したものであっ
て、(A)は2個の偏心重錘が最大起振力を発生する状
態を示す模式図、(B)は起振力中程度である状態を表
す模式図、(C)は起振力がやや小さい状態を表す模式
図、(D)は起振力がゼロの状態を表す模式図である。FIG. 6 is a view for explaining a known technique for changing a vibrating force by a combination of two eccentric weights, in which (A) shows that two eccentric weights generate a maximum vibrating force; (B) is a schematic diagram showing a state in which the vibrating force is moderate, (C) is a schematic diagram showing a state in which the vibrating force is slightly small, and (D) is a schematic diagram showing a state in which the vibrating force is zero. It is a schematic diagram showing a state.
【図7】共通の回転軸に対して固定偏心重錘を固着する
とともに可動偏心重錘を上記共通の回転軸に対する相対
的な回動角位置を調節できるようにした機構の模式図で
ある。FIG. 7 is a schematic diagram of a mechanism in which a fixed eccentric weight is fixed to a common rotation shaft and a movable eccentric weight can adjust a relative rotation angle position with respect to the common rotation shaft.
【図8】上掲の図7に原理を示したように、共通の1軸
に対して固定偏心重錘と可動偏心重錘とを配設して起振
力を増減調節できるようにした起振機の従来例を示す斜
視図である。FIG. 8 shows a fixed eccentric weight and a movable eccentric weight arranged on a common axis so as to be able to increase and decrease the vibrating force as shown in FIG. It is a perspective view which shows the conventional example of a shaker.
【図9】前掲の図8に示した従来例の調節機構を備えた
起振機における回転軸と固定偏心重錘と可動偏心重錘と
の関係を説明するために示したもので、(A)は部分的
に切断して描いた外観斜視図であり、(B)は回転軸と
平行な方向に見たところを描いた模式図である。FIG. 9 is a view for explaining the relationship between the rotating shaft, the fixed eccentric weight, and the movable eccentric weight in the conventional exciter having the adjusting mechanism shown in FIG. 1) is an external perspective view partially cut and drawn, and FIG. 2B is a schematic view illustrating a portion viewed in a direction parallel to the rotation axis.
1…起振機のケース、2,2A〜2D…回転軸、3,3
A〜3D…偏心重錘、4,4A〜4D…同期伝動用の伝
動歯車、5…クレーンブーム、6…振動装置(起振
機)、7…杭、8…民家、9,9A,9B…固定偏心重
錘、10,10A,10B…可動偏心重錘、10a〜1
0c…可動偏心重錘の調整位置、11…駆動用プーリ、
12…メネジ穴、13…ノックピン、14…セットボル
ト、15…六角レンチ、21…A系統回転軸、22…B
系統回転軸、26…A系統固定偏心重錘、27…B系統
可動偏心重錘、28…B系統固定偏心重錘、29…A系
統可動偏心重錘、Ma…A系統駆動モータ、Mb…B系
統駆動モータ。1: Exciter case, 2, 2A to 2D: Rotating shaft, 3, 3
A to 3D: eccentric weight, 4, 4A to 4D: transmission gear for synchronous transmission, 5: crane boom, 6: vibration device (exciter), 7: pile, 8: private house, 9, 9A, 9B ... Fixed eccentric weight, 10, 10A, 10B ... movable eccentric weight, 10a-1
0c: Adjustable position of movable eccentric weight, 11: Drive pulley,
12: female screw hole, 13: knock pin, 14: set bolt, 15: hexagon wrench, 21: rotary shaft of A system, 22: B
System rotating shaft, 26 ... A system fixed eccentric weight, 27 ... B system movable eccentric weight, 28 ... B system fixed eccentric weight, 29 ... A system movable eccentric weight, Ma ... A system drive motor, Mb ... B System drive motor.
Claims (14)
の偏心重錘回転駆動系とを設け、 A系統回転軸(21)にA系統固定偏心重錘(26)を
固定するとともに、該A系統回転軸にB系統可動偏心重
錘(27)を相対的回動可能に取り付け、 B系統回転軸(22)にB系統固定偏心重錘(28)を
固定するとともに、該B系統回転軸にA系統可動偏心重
錘(29)を相対的回動可能に取り付け、 前記A系統固定偏心重錘(26)とA系統可動偏心重錘
(29)とを常に等しい回転速度で反対方向に回転する
ように連動させるとともに、 前記B系統固定偏心重錘(28)とB系統可動偏心重錘
(27)とを常に等しい回転速度で反対方向に回転する
ように連動させ、かつ、 前記A系統の回転位相とB系統の回転位相との位相差
が、0度以上180度以下の所定角度範囲以上とならな
いように、両系統の回転部材相互を機械的に拘束して、 前記A系統回転軸(21)とB系統回転軸(22)と
を、それぞれ別個に制御し得るモータによって回転駆動
することを特徴とする、偏心重錘の起振力制御方法。An eccentric weight rotation drive system of system A and an eccentric weight rotation drive system of system B are provided, and an A system fixed eccentric weight (26) is fixed to an A system rotation shaft (21). The B-system movable eccentric weight (27) is attached to the A-system rotating shaft so as to be relatively rotatable, and the B-system fixed eccentric weight (28) is fixed to the B-system rotating shaft (22). The A-system movable eccentric weight (29) is attached to the rotating shaft so as to be relatively rotatable, and the A-system fixed eccentric weight (26) and the A-system movable eccentric weight (29) are always rotated at the same rotational speed in opposite directions. And the B-system fixed eccentric weight (28) and the B-system movable eccentric weight (27) are interlocked so as to always rotate in the opposite direction at the same rotation speed; The phase difference between the rotation phase of the system and the rotation phase of the system B is 0 degree or more. The rotating members of the two systems are mechanically constrained so as not to exceed a predetermined angle range of 80 degrees or less, and the A system rotating shaft (21) and the B system rotating shaft (22) are separately controlled. A method for controlling the vibrating force of an eccentric weight, characterized in that it is driven to rotate by a motor capable of being driven.
A系統駆動歯車(23)と、B系統回転軸(22)に対
して回動可能に取り付けたA系統被動歯車(25)とを
噛合させるとともに、該A系統被動歯車とA系統可動偏
心重錘(29)とを相対的回動不能に連結し、 前記のB系統回転軸(22)に固着したB系統駆動歯車
(34)と、A系統回転軸(21)に対して回動可能に
取り付けたB系統被動歯車(31)とを噛合させるとと
もに、該B系統被動歯車とB系統可動偏心重錘(27)
とを相対的回動不能に連結したことを特徴とする、請求
項1に記載した偏心重錘の起振力制御方法。2. An A-system drive gear (23) fixed to the A-system rotation shaft (21), and an A-system driven gear (25) rotatably mounted on the B-system rotation shaft (22). And the A-system driven gear and the A-system movable eccentric weight (29) are non-rotatably connected to each other, and the B-system drive gear (34) fixed to the B-system rotation shaft (22). And a B-system driven gear (31) rotatably attached to the A-system rotation shaft (21), and the B-system driven gear and the B-system movable eccentric weight (27)
2. The method according to claim 1, wherein the eccentric weight and the eccentric weight are connected to each other so that they cannot rotate relative to each other.
プーリ(35)を固着するとともに、A系統駆動プーリ
(38)を取り付けたA系統駆動用のモータ(Ma)に
より、巻掛伝動手段(37)を介して回転駆動し、か
つ、 前記B系統回転軸(22)にB系統被動プーリ(39)
を固着するとともに、B系統駆動プーリ(39)を取り
付けたB系統駆動用のモータ(Mb)により、巻掛伝動
手段(37)を介して回転駆動することを特徴とする、
請求項2に記載した偏心重錘の起振力制御方法。An A-system driven pulley (35) is fixed to the A-system rotating shaft (21), and a winding transmission is performed by an A-system driving motor (Ma) to which an A-system drive pulley (38) is attached. A driving pulley (39) on the B-system rotating shaft (22) through the means (37);
And driven by a B-system drive motor (Mb) to which a B-system drive pulley (39) is attached via a winding transmission means (37).
An eccentric weight excitation force control method according to claim 2.
けたA系統原動歯車(40)を、A系統回転軸(21)
に固着されたA系統駆動歯車(23)に噛合せしめてA
系統の回転部材を回転駆動し、 B系統駆動用のモータ(Mb)に取り付けたB系統原動
歯車(41)を、B系統回転軸(22)に固着したB系
統駆動歯車(34)に噛合せしめてB系統の回転部材を
回転駆動することを特徴とする、請求項2に記載した偏
心重錘の起振力制御方法。4. An A-system driving gear (40) attached to an A-system driving motor (Ma) is connected to an A-system rotating shaft (21).
Meshed with the A-system drive gear (23) fixed to
The rotating member of the system is rotationally driven, and the B system driving gear (41) attached to the B system driving motor (Mb) is engaged with the B system driving gear (34) fixed to the B system rotating shaft (22). 3. The method for controlling the vibrating force of an eccentric weight according to claim 2, wherein the rotating member of the B system is driven to rotate.
範囲の最大値を、下記のように設定することを特徴とす
る、請求項1ないし請求項4の何れかに記載した偏心重
錘の起振力制御方法。A系統固定偏心重錘(26)とB
系統可動偏心重錘(27)とがA系統回転軸(21)に
関して対称に位置したとき、B系統固定偏心重錘(2
8)とA系統可動偏心重錘(29)とがB系統回転軸
(22)に関して対称に位置するように、 前記A系統駆動歯車(23)とA系統被動歯車(25)
との噛合関係を設定するとともにB系統駆動歯車(3
4)とB系統被動歯車(31)との噛合関係を設定し
て、これら4個の偏心重錘を回転させたときの総合偏心
モーメントが零となる状態を想定して、これをA,B両
系統の回転位相差180度の状態と定義し、 A,B両系統の回転位相差が約180度であって、前記
4個の偏心重錘の回転によって発生する振動加速度が重
力加速度とほぼ等しくなる位相差に相当する角度をもっ
て、前記所定角度範囲の最大値とする。5. The eccentric weight according to claim 1, wherein a maximum value of the predetermined angle range from 0 to 180 degrees is set as follows. Exciting force control method. A system fixed eccentric weight (26) and B
When the system movable eccentric weight (27) is positioned symmetrically with respect to the system A rotation axis (21), the system B fixed eccentric weight (2)
8) and the A-system drive gear (23) and the A-system driven gear (25) such that the A-system movable eccentric weight (29) is symmetrically positioned with respect to the B-system rotation axis (22).
And the B-system drive gear (3
4) and the B-system driven gear (31) are set in meshing relationship, and assuming a state where the total eccentric moment when these four eccentric weights are rotated becomes zero, this is defined as A, B. The rotation phase difference between the two systems is defined as 180 degrees, and the rotation phase difference between the A and B systems is about 180 degrees, and the vibration acceleration generated by the rotation of the four eccentric weights is substantially equal to the gravitational acceleration. An angle corresponding to the equal phase difference is defined as the maximum value in the predetermined angle range.
範囲の最小値を、下記のように設定することを特徴とす
る、請求項5に記載した偏心重錘の起振力制御方法。前
記の回転位相差180度の状態を基準状態とし、この基
準状態に比して回転位相差を約30度小さく設定する。6. The method according to claim 5, wherein the minimum value in the predetermined angle range from 0 ° to 180 ° is set as follows. The state where the rotation phase difference is 180 degrees is set as a reference state, and the rotation phase difference is set to be smaller than the reference state by about 30 degrees.
相との位相差を、所定角度範囲内の最大値として4個の
偏心重錘の総合偏心モーメントを最小ならしめて杭打作
業の運転を開始し、 A系統の回転速度およびB系統の回転速度が、杭打作業
現場の地盤の固有振動数に相当する回転速度および杭打
作業用クレーンブームの固有振動数に相当する回転速度
を通過して上昇した後、 A系統の回転位相とB系統の回転位相との位相差を、所
定角度範囲内の最小値として前記4個の偏心重錘の総合
偏心モーメントを最大ならしめて定常的な運転状態に移
行することを特徴とする、請求項1に記載した偏心重錘
の起振力制御方法。7. A pile driving operation in which the phase difference between the rotation phase of the system A and the rotation phase of the system B is set to a maximum value within a predetermined angle range to minimize the total eccentric moment of the four eccentric weights. The rotation speed of the A system and the rotation speed of the B system pass through the rotation speed corresponding to the natural frequency of the ground at the pile driving work site and the rotation speed corresponding to the natural frequency of the crane boom for the pile driving operation. After that, the phase difference between the rotation phase of the A-system and the rotation phase of the B-system is set to the minimum value within a predetermined angle range, and the total eccentric moment of the four eccentric weights is maximized to perform steady operation. The method according to claim 1, wherein the state shifts to a state.
相との位相差を、所定角度範囲内の最小値として前記4
個の偏心重錘の総合偏心モーメントを最大ならしめて定
常的な運転を遂行した後、 前記の位相差を所定角度範囲内の最大値として前記4個
の偏心重錘の総合偏心モーメントを最小ならしめた状態
で、A,B両系統の回転速度を減速せしめて停止に至ら
しめることを特徴とする、請求項7に記載した偏心重錘
の起振力制御方法。8. A phase difference between the rotation phase of the A-system and the rotation phase of the B-system as a minimum value within a predetermined angle range.
After performing the steady operation by maximizing the total eccentric moment of the four eccentric weights, minimizing the total eccentric moment of the four eccentric weights by setting the phase difference to a maximum value within a predetermined angle range. 8. The method according to claim 7, wherein the rotational speeds of both the A and B systems are reduced to stop the system.
と、B系統の偏心重錘およびその回転駆動系とよりな
り、 A系統回転軸(21)にA系統固定偏心重錘(26)が
固定されるとともに、該A系統回転軸にB系統可動偏心
重錘(27)が相対的回動可能に嵌着され、 B系統回転軸(22)にB系統固定偏心重錘(28)が
固定されるとともに、該B系統回転軸にA系統可動偏心
重錘(29)が相対的回動可能に嵌着され、 前記A系統固定偏心重錘(26)とA系統可動偏心重錘
(29)とを常に等しい回転速度で反対方向に回転せし
める連動手段が設けられるとともに、 前記B系統固定偏心重錘(28)とB系統可動偏心重錘
(27)とを常に等しい回転速度で反対方向に回転せし
める連動手段が設けられており、かつ、 前記A系統の回転位相とB系統の回転位相との位相差
を、0度以上180度以下の所定角度範囲内に拘束する
機械的手段が設けられており、 前記A系統回転軸(21)を回転駆動するA系統駆動モ
ータ(Ma)と、B系統回転軸(22)を回転駆動する
B系統駆動モータ(Mb)とが設けられるとともに、上
記A,B両統の駆動モータ(Ma,Mb)がそれぞれ個
別に制御できるようになっていることを特徴とする、偏
心重錘の起振力制御機構。9. An eccentric weight of system A and its rotary drive system, an eccentric weight of system B and its rotary drive system, and an A system fixed eccentric weight (26) on the A system rotating shaft (21). Is fixed, and a B-system movable eccentric weight (27) is rotatably fitted to the A-system rotation shaft, and a B-system fixed eccentric weight (28) is fitted to the B-system rotation shaft (22). The A-system movable eccentric weight (29) is fixed to the B-system rotating shaft so as to be relatively rotatable. The A-system fixed eccentric weight (26) and the A-system movable eccentric weight (29) ) Is always provided in the opposite direction at the same rotational speed, and the B-system fixed eccentric weight (28) and the B-system movable eccentric weight (27) are always rotated in the opposite direction at the same rotational speed. Interlocking means for rotating is provided, and A mechanical means is provided for restraining the phase difference between the rotation phase and the rotation phase of the B system within a predetermined angle range of 0 degree or more and 180 degrees or less, and A for rotating and driving the A system rotation shaft (21). A system drive motor (Ma) and a B system drive motor (Mb) for rotating and driving the B system rotation shaft (22) are provided, and the A and B drive motors (Ma, Mb) are individually controlled. A vibrating force control mechanism for an eccentric weight, characterized in that it can be driven.
(23)とA系統被動歯車(25)とが設けられるとと
もに、相互に歯数の等しいB系統駆動歯車(34)とB
系統被動歯車(31)とが設けられており、 A系統駆動歯車(23)はA系統回転軸(21)に固着
され、 A系統被動歯車(25)は前記A系統駆動歯車(23)
と噛合するとともに前記B系統回転軸(22)と相対的
回動可能に嵌合され、かつ、前記A系統可動偏心重錘
(29)に対して一体的に連結されており、 B系統被動歯車(31)は前記B系統駆動歯車(34)
と噛合するとともに前記A系統回転軸(21)と相対的
回動可能に嵌合され、かつ、前記B系統可動偏心重錘
(27)に対して一体的に連結されていることを特徴と
する、請求項9に記載した偏心重錘の起振力制御機構。10. An A-system drive gear (23) and an A-system driven gear (25) having the same number of teeth, and a B-system drive gear (34) and a B-system drive gear having the same number of teeth.
A system driven gear (31), an A system drive gear (23) is fixed to the A system rotation shaft (21), and an A system driven gear (25) is the A system drive gear (23).
And is integrally connected to the A-system movable eccentric weight (29) so as to be rotatable relative to the B-system rotating shaft (22), and is connected to the B-system movable eccentric weight (29). (31) The B-system drive gear (34)
And is fitted so as to be relatively rotatable with the A-system rotating shaft (21), and is integrally connected to the B-system movable eccentric weight (27). An eccentric weight vibrating force control mechanism according to claim 9.
動プーリ(35)が固着されるとともに、A系統駆動プ
ーリ(38)を取り付けたA系統駆動用のモータ(M
a)により、巻掛伝動手段(37)を介して回転駆動さ
れるようになっており、かつ、 前記B系統回転軸(22)にB系統被動プーリ(39)
を固着されるとともに、B系統駆動プーリ(39)を取
り付けたB系統駆動用のモータ(Mb)により、巻掛伝
動手段(37)を介して回転駆動されるようになってい
ることを特徴とする、請求項10に記載した偏心重錘の
起振力制御機構。11. An A-system driving motor (M) having an A-system driven pulley (35) fixed to the A-system rotating shaft (21) and having an A-system driving pulley (38) attached thereto.
a) is driven to rotate via the wrapping transmission means (37), and the B-system driven pulley (39) is attached to the B-system rotation shaft (22).
And a rotary drive via a winding transmission means (37) by a B-system drive motor (Mb) to which a B-system drive pulley (39) is attached. The oscillating force control mechanism for an eccentric weight according to claim 10.
付けたA系統原動歯車(40)が、A系統回転軸(2
1)に固着されたA系統駆動歯車(23)に噛合されて
おり、 B系統駆動用のモータ(Mb)に取り付けたB系統原動
歯車(41)が、B系統回転軸(22)に固着されたB
系統駆動歯車(34)に噛合されていて、 前記A系統駆動用のモータ(Ma)とB系統駆動用のモ
ータ(Mb)とが、それぞれ独立に制御できるようにな
っていることを特徴とする、請求項10に記載した偏心
重錘の起振力制御機構。12. An A-system driving gear (40) attached to an A-system driving motor (Na) includes an A-system rotating shaft (2).
The B-system drive gear (41), which is engaged with the A-system drive gear (23) fixed to 1) and is attached to the B-system drive motor (Mb), is fixed to the B-system rotary shaft (22). B
A system drive gear (34) meshes with the A system drive motor (Ma) and the B system drive motor (Mb) so that they can be independently controlled. An eccentric weight vibrating force control mechanism according to claim 10.
重錘との回転位相差が最大値となったとき、これらの偏
心重錘の総合偏心モーメントが最小値となり、かつ、偏
心モーメント最小の状態で前記偏心重錘が定格回転速度
で回転したときに発生する振動の振動加速度が、ほぼ重
力加速度と等しいように構成されていることを特徴とす
る、請求項9に記載した偏心重錘の起振力制御機構。13. When the rotational phase difference between the eccentric weight of the system A and the eccentric weight of the system B has a maximum value, the total eccentric moment of these eccentric weights has a minimum value, and The eccentric weight according to claim 9, wherein a vibration acceleration of a vibration generated when the eccentric weight rotates at a rated rotation speed in a minimum state is configured to be substantially equal to a gravitational acceleration. Vibration force control mechanism of the weight.
相との位相差に関する所定角度範囲の最小値は、 固定偏心重錘と可動偏心重錘とが回転軸に関して対称に
位置して180度の位相差を有す仮想の状態を基準の状
態とし、上記の基準状態における位相差よりも約30度
小さい値に設定されていることを特徴とする、請求項9
に記載した偏心重錘の起振力制御機構。14. A minimum value in a predetermined angle range regarding a phase difference between the rotation phase of the A-system and the rotation phase of the B-system is 180 degrees when the fixed eccentric weight and the movable eccentric weight are symmetrically positioned with respect to the rotation axis. 10. A virtual state having a phase difference of the reference state is set as a reference state, and is set to a value smaller by about 30 degrees than the phase difference in the reference state.
The vibration force control mechanism of the eccentric weight described in [1].
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP23669595A JP2724296B2 (en) | 1995-09-14 | 1995-09-14 | Excitation weight control method and control mechanism for eccentric weight |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP23669595A JP2724296B2 (en) | 1995-09-14 | 1995-09-14 | Excitation weight control method and control mechanism for eccentric weight |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0978579A JPH0978579A (en) | 1997-03-25 |
JP2724296B2 true JP2724296B2 (en) | 1998-03-09 |
Family
ID=17004406
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Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP23669595A Expired - Lifetime JP2724296B2 (en) | 1995-09-14 | 1995-09-14 | Excitation weight control method and control mechanism for eccentric weight |
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Country | Link |
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JP (1) | JP2724296B2 (en) |
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SG11201507746WA (en) * | 2013-04-15 | 2015-10-29 | Kinki Kk | Vibration generation device |
CN108472689B (en) * | 2015-12-08 | 2021-09-21 | 株式会社近畿 | Operation control method of vibrating screen machine |
-
1995
- 1995-09-14 JP JP23669595A patent/JP2724296B2/en not_active Expired - Lifetime
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JPH0978579A (en) | 1997-03-25 |
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