JPH093891A - Method for controlling vibratory force for eccentric weight and eccentric weight mechanism for vibration - Google Patents
Method for controlling vibratory force for eccentric weight and eccentric weight mechanism for vibrationInfo
- Publication number
- JPH093891A JPH093891A JP15947995A JP15947995A JPH093891A JP H093891 A JPH093891 A JP H093891A JP 15947995 A JP15947995 A JP 15947995A JP 15947995 A JP15947995 A JP 15947995A JP H093891 A JPH093891 A JP H093891A
- Authority
- JP
- Japan
- Prior art keywords
- eccentric weight
- fixed
- weight
- state
- movable
- 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.)
- Granted
Links
Abstract
Description
【０００１】[0001]
【産業上の利用分野】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 type vibration exciter for driving a pile and controlling a vibration generation function, and a mechanism for the same.
【０００２】[0002]
【従来の技術】土木建設工事に用いられる振動装置は一
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。図３はこの種のロータリ式起振機
の模式的な説明図であって、ケース１に対して４本の回
転軸２Ａ，２Ｂ，２Ｃ，２Ｄが配置され、それぞれ偏心
重錘３Ａ，３Ｂ，３Ｃ，３Ｄが取り付けられるととも
に、それぞれ歯車４Ａ，４Ｂ，４Ｃ，４Ｄが取り付けら
れて相互に噛合して同期回転するように拘束されてい
る。2. Description of the Related Art In general, a vibration device used for civil engineering construction has a structure in which a plurality of pairs of rotating shafts each having an eccentric weight attached thereto are arranged in parallel. According to such a configuration, the centrifugal excitation force of the eccentric weight rotating in the opposite direction can be added in the desired direction and can be canceled in the unnecessary direction. FIG. 3 is a schematic explanatory view of this type of rotary type vibration exciter, in which four rotating shafts 2A, 2B, 2C, 2D are arranged for a case 1, and eccentric weights 3A, 3B, 3C and 3D are attached, and gears 4A, 4B, 4C and 4D are respectively attached and restrained so as to mesh with each other and rotate synchronously.
【０００３】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、第４図，第５図について振動公害に関する
技術的問題を説明する。[0003] 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 regarding vibration pollution will be described with reference to FIGS.
【０００４】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１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
相当する音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 grasped by the chuck 6a of the vibration device 6, and the pile 7 is vibrated and placed in the ground. Is drawn. When the lower end of the pile 1 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 surface at the pile driving point is hardly attenuated and the nearby private house 8 , Causing vibration pollution problems. Here, if the exciting force of the vibration device 6 can be arbitrarily adjusted, the pile driving work may be started while giving a slight vibration in addition to the weight of the pile 7, and the vibration may be gradually strengthened after driving for several meters. . If the sound source position corresponding to the lower end of the pile 7 is deepened, the underground wave b is attenuated on the way to the private house 8, so that the vibration pollution is negligible.
【０００５】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 and 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-mentioned frequency increase, the natural frequency n 1 of the ground and the natural frequency n 2 of the crane boom are passed. However, since the rotation speed increasing period T 1 at the start of operation is generally short (for example, about 3 seconds), the problem of resonance when the vibration frequency of the vibration device matches the natural frequency can be usually ignored. it can. However, from the time point t 2 when the motor (not shown) of the vibration device 6 is stopped to the time point t 3 when the rotation shaft stops, the rotation shaft continues to rotate due to inertia and gradually decelerates as shown by the arrow d. . The rotational speed reduction period T
Since 2 is a relatively long time (for example, about 50 seconds), when the natural frequency n 2 of the crane boom is passed on the way, the crane boom may resonate and be damaged. Further, when passing through the natural frequency n 1 of the ground, vibration of the ground may cause vibration pollution. The time t
If it is possible to stop the energization of the motor in 2 and change the rotational phase of the rotary weight of the vibration device to make the exciting force zero, prevent problems related to resonance at the time of operation stop of the vibration device. You can
【０００６】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、定格運
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。
定格運転数に達した後は、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 the 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 increases, a large-capacity motor and a large-capacity power supply facility are required to drive this. . In this case, if the vibrating device starts the operation in a state where the vibrating force is reduced to zero by changing the rotation phase of the eccentric weight, if the vibrating force can be exerted after reaching the rated number of operations,
It is economical because the motor capacity and power supply capacity can be reduced.
This is because, after reaching the rated operation number, 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.
【０００７】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は前掲の図３に示した４軸４重錘式の起振機の
作用を説明するための模式図であって、（Ａ）は図３に
おけると同様に偏心重錘が下降している状態を表し、
（Ｂ）は約９０度回転した状態を表し、（Ｃ）はさらに
約９０度回転して重錘が上昇した状態を表している。図
６（Ａ）に比して（Ｂ）においては、４個の偏心重錘３
Ａ〜３Ｄの重心位置が寸法ｈだけ上昇している。このた
め、該偏心重錘を持ち上げる力の反力によってケース１
は押し下げられる。このようにして４個の偏心重錘それ
ぞれの重心位置は上昇するが、偏心重錘３Ａと同３Ｂを
対照し、偏心重錘３Ｃと同３Ｄとを対照して観察する
と、（Ａ）図の状態に比して（Ｂ）図の状態において
は、 〇 偏心重錘３Ａと同３Ｂとは離間して、その距離がＬ
2に拡大し、 〇 偏心重錘３Ｃと同３Ｄとは接近して、その距離がＬ
1に縮小しているが、 偏心重錘３Ａと同３Ｂとの総合重心位置は左右方向に移
動しておらず、偏心重錘３Ｃと同３Ｄとの総合重心位置
も左右方向に移動していない。従って、左右方向には起
振力を生じない。起振装置は以上のように、複数の偏心
重錘を設けて、左右方向の起振力を相殺させながら上下
方向の起振力を取り出すように構成されているが、先に
述べたように振動公害防止のために起振力を増減制御す
るため、１対の偏心重錘について上下方向起振力を一部
ないし全部相殺させることもできる。図７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７（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い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７（Ａ）に
おける２個の偏心重錘９，１０の相対的位置は、先に説
明した図６（Ａ）における偏心重錘３Ｂと同３Ｃとの相
対的位置と同様である。従って、この図７（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、図６について説明したようにし
て起振力が発生する。図７（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。図７（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７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′を同期伝動歯車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８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。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ｉ−ｊ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８に描かれている状態は前掲の図
７（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ｉ方向に回動さ
せて固定すると図７（Ｄ）の状態に近づいて起振力が減
少する。また矢印ｊ方向に回動させると図７（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９は上掲の図８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２
Ａ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１０は前掲の図９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１０（Ａ）に示した２３ａ，２３ｂ，２３
ｃ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１０（Ｂ）に
示したように、可動偏心重錘が３つの角位置をとり、１
０ａ，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１０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。[0007] 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 or decreasing the exciting force of the exciter will be described. FIG. 6 is a schematic view for explaining the operation of the four-shaft, four-weight type exciter shown in FIG. 3 described above. FIG. 6A shows a case where the eccentric weight is lowered as in FIG. State,
(B) shows a state rotated by about 90 degrees, and (C) shows a state in which the weight is further rotated by about 90 degrees. In FIG. 6B, as compared with FIG. 6A, four eccentric weights 3
The positions of the centers of gravity of A to 3D are raised by the dimension h. For this reason, the case 1
Is depressed. In this way, the center of gravity of each of the four eccentric weights rises, but when the eccentric weights 3A and 3B are compared and the eccentric weights 3C and 3D are compared and observed, (A) of FIG. Compared to the state, in the state of FIG. (B), the eccentric weights 3A and 3B are separated from each other and the distance is L.
Expanded to 2 , and the distance between the eccentric weight 3C and 3D is close, and the distance is L
Although reduced to 1 , the total center of gravity of eccentric weights 3A and 3B has not moved to the left and right, and the total center of gravity of eccentric weights 3C and 3D has not moved to the left and right. . Therefore, no vibrating force is generated in the left-right direction. As described above, the oscillating device is configured to provide a plurality of eccentric weights and to take out the oscillating force in the vertical direction while canceling the oscillating force in the lateral direction, but as described above. Since the exciting force is controlled to be increased or decreased in order to prevent vibration pollution, it is possible to partially or completely cancel the upward and downward exciting forces of the pair of eccentric weights. FIG. 7 is a view for explaining a known technique of changing an exciting force by a combination of two eccentric weights, and (A) shows two eccentric weights exhibiting maximum exciting force. A schematic diagram showing the state,
(B) is a schematic diagram showing a state in which the excitation force is medium, (C)
Is a schematic diagram showing a state where the vibrating force is slightly small, and (D) is a schematic diagram showing a state where the vibrating force is zero. Of the two eccentric weights shown in FIG. 7A, 9 is a fixed eccentric weight fixed to the rotary shaft 2B ', and 10 is rotatable relative to the rotary shaft 2C'. It is a movable eccentric weight. In the present invention, the fixed eccentric weight is an eccentric weight that is locked against relative rotation with respect to the rotation shaft, and is a member that rotates together with the rotation shaft. is not. The relative positions of the two eccentric weights 9 and 10 in FIG. 7A are the same as the relative positions of the eccentric weights 3B and 3C in FIG. 6A described above. Therefore, when the two eccentric weights 9 and 10 are rotated in synchronization with the gears 4B 'and 4C' in the state of FIG. 7A, a vibrating force is generated as described with reference to FIG. . In the state of FIG. 7D, the center of gravity of each of the two eccentric weights 9 and 10 is always the reference line MM.
Since it is located symmetrically with respect to the vertical bisector of the line segment that connects the two rotary shafts 2B 'and 2C', the vertical excitation force is zero. 7 (B) and 7 (C) are intermediate states between (A) and (D), respectively, and therefore, the vertical vibration force is smaller than that in FIG. 7A and larger than that in FIG. 7D. To occur. Then, since the state of (B) is closer to the state of (A) than that of (C), when the vibration forces are listed in order from (A), (B), (C), (D ). In order to show the principle of the excitation force increase / decrease control in FIG.
The rotary shafts 2B 'and 2C' are connected to the synchronous transmission gears 4B 'and 4C.
Although it is drawn so as to rotate synchronously at C ′, two eccentric weights may be provided on one rotation shaft for simplifying the structure. FIG. 8 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. 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 rotary shaft 2 as indicated by arc arrows i-j, and can be maintained in the adjusted state. The state illustrated in FIG. 8 corresponds to the state illustrated in FIG. 7B described above, and the vibrating force is moderate. From this state, when the movable eccentric weight is rotated and fixed in the direction of arrow i, the state of FIG. 7D is approached and the vibrating force decreases. Further, when it is rotated in the direction of arrow j, the state of FIG. The exciting force is adjusted as described above. As shown in FIG. 8 above, FIG. 9 shows a vibration generator in which a fixed eccentric weight and a movable eccentric weight are arranged on a common one axis so that the vibration force can be increased or decreased. It is a perspective view showing the conventional example of a machine. The two rotating shafts 2A and 2B are arranged in the horizontal direction and are synchronously rotated in the opposite direction (clockwise and counterclockwise) by the drive pulley 11 and the synchronous rotation transmission gears 4A and 4B. This is to offset the vibration force. The fixed eccentric weight 9A is the rotary shaft 2
A. The movable eccentric weight 10A is rotatably supported by the rotary shaft 2A, and the rotation of the fixed eccentric weight 9A can be adjusted and fixed. That is, the movable eccentric weight 10A has a plurality of adjusting female screw holes (only one is shown in this figure).
12 is worn. When the set bolt 14 is screwed into the female screw hole 12 and tightened with the hexagon wrench 15 and detented with the knock pin 13, the angular position of the movable eccentric weight 10A is fixed. FIG. 10 is provided for explaining the relationship between the rotary shaft, the fixed eccentric weight, and the movable eccentric weight in the vibration generator equipped with the conventional adjustment mechanism shown in FIG.
(A) is an external perspective view drawn by partially cutting,
(B) is a schematic diagram illustrating a view seen in a direction parallel to the rotation axis. 23a, 23b, 23 shown in FIG.
c is a scale, and the unit is kg · cm. By aligning the scales and screwing the set bolt, the movable eccentric weight takes three angular positions as shown in FIG.
As shown in 0a, 10b, and 10c, they are relatively rotated to change the exciting force. The exciter according to the related art shown in FIGS. 7 to 10 can increase or decrease the excitation force as described above.
【０００８】[0008]
【発明が解決しようとする課題】図７ないし図１０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９に表されている光像から
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１０において符号２３ａ
〜２３ｃ）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７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７（Ａ）の状態と図７（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、起振力調
節作動の応答性が悪く、調節のための回動操作に多大の
回転トルクを要するので、未だ実用化されていない。When an attempt is made to increase or decrease the exciting force in the conventional exciter described with reference to FIGS. 7 to 10, it is easy to obtain the optical image shown in FIG. As you can see, stop driving, knock pin 13
, The set bolt 14 is extracted, and the movable eccentric weight 10 is manually turned to read the scale (reference numeral 23a in FIG. 10).
After the adjustment of (c) to (c), the set bolt 14 must be screwed again, tightened, and detented with the knock pin 13. In order to increase or decrease the excitation force in the prior art,
The above operations are required. 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 for adjustment, and then lifted by the crane boom 5 again to be suspended at the upper end of the pile 7. Installation work must be time-consuming and labor-intensive. As shown in FIG. 7 mentioned above as a principle diagram, the structure in which the fixed eccentric weight 9 and the movable eccentric weight 10 are attached to different rotating shafts is configured by actual members, and the operation of the vibration generator is continued. Although it is conceivable to increase / decrease the oscillating force, the movable eccentric weight 10 is set to 180 degrees between the state of FIG. 7 (A) and the state of FIG. Since it has to be rotated relatively, the responsiveness of the excitation force adjustment operation is poor, and a large amount of rotational torque is required for the rotation operation for adjustment, so it has not been put to practical use.
【０００９】本発明は上述の事情に鑑みて為されたもの
であって、可動偏心重錘と固定偏心重錘とを共通の回転
中心軸に対して配設された構造の起振機を適用の対象と
し、 イ．起振力増減調節操作の応答性が良く、 ロ．起振力の増減調節に必要な駆動トルクの小さい、 偏心重錘の起振力制御方法、および、起振用偏心重錘機
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 employs a vibration exciter having a structure in which a movable eccentric weight and a fixed eccentric weight are disposed with respect to a common rotation center axis. And b. Good responsiveness of the vibrating force increase / decrease adjustment operation. It is an object of the present invention to provide an eccentric weight excitation force control method and an eccentric weight for eccentric weight mechanism that require a small drive torque for increasing and decreasing the excitation force.
【００１０】[0010]
【課題を解決するための手段】上記の目的（応答性向上
・駆動力小）を達成するため本発明に係る偏心重錘の起
振力制御方法は、回転中心軸に対して、慣性モーメント
のほぼ等しい２個の偏心重錘を配設して、上記２個の偏
心重錘のうちの片方を、回転軸部材に対する相対的な回
動を係止して取り付けて固定偏心重錘を構成するととも
に、上記の固定偏心重錘に対して他方の偏心重錘が回転
中心軸まわりに相対的に回動し得るように取り付けて可
動偏心重錘を構成し、前記２個の偏心重錘それぞれの重
心が回転中心軸に対して対称に位置する状態を基準状態
と名付け、上記の可動偏心重錘を、基準状態から鋭角θ
の範囲内で、固定偏心重錘に対して相対的に回動させる
ことによって、前記２個の偏心重錘よりなる起振機構の
起振力の大小を調節し、かつ、前記可動偏心重錘を固定
偏心重錘に対して、相対的に鋭角θ以上に回動させない
ことを特徴とする。上記の発明方法により実用的価値の
高い効果を発揮させる実施の態様として、偏心重錘より
成る振動杭打装置をクレーンブームで吊持し、上記振動
杭打装置に把持されている杭を地盤中に貫入する際、上
記の杭を地表に接せしめた杭打開始時点においては前記
可動偏心重錘を固定偏心重錘に対して基準状態もしくは
基準状態に近い状態として起振力を小ならしめ、起振力
の小さい状態で前記の回転軸部材を回転駆動して、杭の
打ち込みを進行させつつ次第に回転速度を上昇させて振
動周波数を増加させながら、比較的に基準状態に近くて
起振力の小さい状態で地盤の固有振動数およびクレーン
ブームの固有振動数を通過した後、可動偏心重錘を固定
偏心重錘に対して、基準状態から鋭角θまで相対的に回
動させ、定格状態で杭打作業を続行することが推奨され
る。In order to achieve the above-mentioned object (improvement of responsiveness / small driving force), an eccentric weight exciting force control method according to the present invention is designed to control the moment of inertia with respect to the rotation center axis. Two eccentric weights which are substantially equal to each other are arranged, and one of the two eccentric weights is attached by locking relative rotation with respect to the rotary shaft member to form a fixed eccentric weight. At the same time, the other eccentric weight is attached to the fixed eccentric weight so that the other eccentric weight can rotate relatively around the rotation center axis to form a movable eccentric weight. The state in which the center of gravity is located symmetrically with respect to the rotation center axis is called the reference state, and the movable eccentric weight described above is set at an acute angle θ from the reference state.
Within the range described above, the magnitude of the vibrating force of the vibrating mechanism composed of the two eccentric weights is adjusted by rotating relative to the fixed eccentric weight, and the movable eccentric weight is Are not rotated relative to the fixed eccentric weight at an acute angle θ or more. As an embodiment of exhibiting a high practical value effect by the above-mentioned method of the invention, a vibrating pile driving device composed of an eccentric weight is suspended by a crane boom, and a pile grasped by the vibrating pile driving device is grounded. At the time of starting the pile contacting the pile with the surface of the ground, the movable eccentric weight is set to a standard state or a state close to the standard state with respect to the fixed eccentric weight to reduce the vibration force. The rotary shaft member is rotationally driven in a state where the vibration force is small, and the rotation speed is gradually increased while increasing the vibration frequency while driving the pile, and the vibration force is relatively close to the reference state. After passing the natural frequency of the ground and the natural frequency of the crane boom in a small state, the movable eccentric weight is rotated relative to the fixed eccentric weight from the reference state to the acute angle θ, and Continue stakeout work It is recommended.
【００１１】以上に説明した発明方法を実施するに好適
なように創作した本発明に係る起振用偏心重錘機構は、
ほぼ等しい慣性モーメントを有する２個の偏心重錘が、
回転軸部材に取り付けられており、上記２個の偏心重錘
の内の片方は回転軸に対して回動しないように固着され
た固定偏心重錘であり、前記の２個の偏心重錘の他方は
上記固定偏心重錘に対して所定角度範囲内で相対的に回
動し得る可動偏心重錘であって、上記固定偏心重錘と可
動偏心重錘とが回転中心軸に関して対称に位置した状態
を基準状態として、可動偏心重錘が固定偏心重錘に対し
て、鋭角θ以上に回動できないようなストッパ手段が設
けられていることを特徴とする。The eccentric weight mechanism for vibration generation according to the present invention, which is created so as to be suitable for carrying out the above-described invention method, comprises:
Two eccentric weights having substantially equal moments of inertia,
One of the two eccentric weights is a fixed eccentric weight fixed to the rotary shaft member so as not to rotate with respect to the rotary shaft, and one of the two eccentric weights is a fixed eccentric weight. The other is a movable eccentric weight that can relatively rotate within a predetermined angle range with respect to the fixed eccentric weight, wherein the fixed eccentric weight and the movable eccentric weight are symmetrically positioned with respect to a rotation center axis. With the state as a reference state, a stopper means is provided so that the movable eccentric weight cannot rotate with respect to the fixed eccentric weight at an acute angle θ or more.
【００１２】[0012]
【作用】前述の方法によると、起振力最大の状態と起振
力ゼロの状態との間で、可動偏心重錘を鋭角だけ相対的
に回動させれば足りるので、調節作動の応答性が速く、
しかも、基準状態を中心として鋭角θの範囲内において
は、運転中に可動偏心重錘を調節回動させるに要する駆
動トルクが小さいので、運転を継続しつつ調節操作を行
なうことができる。本発明の機構は、ほぼ等しい慣性モ
ーメントを有する２個の偏心重錘が、回転軸部材に取り
付けられており、上記２個の偏心重錘の内の片方は回転
軸に対して回動しないように固着された固定偏心重錘で
あり、前記の２個の偏心重錘の他方は上記固定偏心重錘
に対して所定角度範囲内で相対的に回動し得る可動偏心
重錘であって、上記固定偏心重錘と可動偏心重錘とが回
転中心軸に関して対称に位置した状態を基準状態とし
て、可動偏心重錘が固定偏心重錘に対して、鋭角θ以上
に回動できないようなストッパ手段が設けられているの
で、前記の発明方法を実施するに好適である。特に、可
動偏心重錘の回動をフリーにしても固定偏心重錘に対し
て鋭角θ以上回らないようにストッパ手段が設けられて
いるので、該可動偏心重錘をフリーにすると「回転する
剛体は、慣性モーメントが最大になる姿勢をとろうとす
る」という法則に従って、基準状態から遠ざかる方向に
回動してストッパ手段に当接する。このため、ストッパ
を利かせた状態で固定偏心重錘を回転駆動すると、可動
偏心重錘を直接的に回転駆動しなくても起振機としての
機能を発揮する。このため、振動杭打用の回転エネルギ
ーの伝動が容易である。その上、共通の回転軸に対して
２個の偏心重錘（固定偏心重錘と可動偏心重錘）を配設
する構造であるため、起振機の全体的形状をコンパクト
に構成することができる。According to the above-mentioned method, it is sufficient to relatively rotate the movable eccentric weight by an acute angle between the state where the vibrating force is maximum and the state where the vibrating force is zero. Is fast,
In addition, within the range of the acute angle θ centered on the reference state, the driving torque required to adjust and rotate the movable eccentric weight during operation is small, so that the adjustment operation can be performed while the operation is continued. In the mechanism of the present invention, two eccentric weights having substantially equal moments of inertia are attached to the rotating shaft member, and one of the two eccentric weights is prevented from rotating with respect to the rotating shaft. A fixed eccentric weight fixed to the other, the other of the two eccentric weights is a movable eccentric weight that can relatively rotate within a predetermined angle range with respect to the fixed eccentric weight, A stopper means such that the movable eccentric weight cannot be rotated at an acute angle θ or more with respect to the fixed eccentric weight with reference to a state in which the fixed eccentric weight and the movable eccentric weight are positioned symmetrically with respect to the rotation center axis. Is provided, which is suitable for carrying out the above-described invention method. In particular, since the stopper means is provided so that the movable eccentric weight does not rotate more than the acute angle θ with respect to the fixed eccentric weight even if the rotation of the movable eccentric weight is free, when the movable eccentric weight is released, a “rotating rigid body” According to the rule that the moment of inertia is maximized, and contacts the stopper means in a direction away from the reference state. For this reason, when the fixed eccentric weight is rotationally driven in a state where the stopper is used, the function as a vibration exciter is exhibited without directly rotating the movable eccentric weight. Therefore, transmission of rotational energy for driving the vibrating pile is easy. In addition, since two eccentric weights (a fixed eccentric weight and a movable eccentric weight) are provided for a common rotating shaft, the overall shape of the exciter can be made compact. it can.
【００１３】[0013]
【実施例】次に、図１および図２を順次に参照しつつ、
本発明の実施例を説明する。図１は本発明に係る偏心重
錘の起振力制御方法を実施するために構成した本発明の
起振用偏心重錘機構の１実施例を示し、（Ａ）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位置とな
って起振力がゼロになる基準状態を描いた模式図であ
り、（Ｂ）は可動偏心重錘が基準状態から鋭角θだけ回
動して起振力最大となった状態を描いた模式図であり、
（Ｃ）は起振力を中等度に調節された状態を描いた模式
図である。固定偏心重錘１６と可動偏心重錘１７とは、
これを回転軸２と平行な方向に見たとき、ほぼ同形同寸
の扇形状をなし、かつ、紙面の奥行方向に厚さを有する
平板状をなしている。ただし、扇形の半径寸法よりも大
きい厚さ寸法を有しているので、外観についての印象は
板状というよりは柱状をなしている。Next, referring to FIGS. 1 and 2 sequentially,
An embodiment of the present invention will be described. FIG. 1 shows one embodiment of an eccentric weight mechanism for excitation according to the present invention configured to carry out the method of controlling the oscillating force of an eccentric weight according to the present invention, and FIG. FIG. 7B is a schematic diagram illustrating a reference state in which the eccentric weight and the eccentric weight are symmetrical with respect to the rotation axis and the vibrating force is zero. FIG. It is a schematic diagram depicting a state where the vibration force is maximum,
(C) is a schematic diagram illustrating a state in which the vibrating force is moderately adjusted. The fixed eccentric weight 16 and the movable eccentric weight 17
When viewed in a direction parallel to the rotation shaft 2, the fan has a fan shape having substantially the same shape and the same size, and has a flat plate shape having a thickness in the depth direction of the paper surface. However, since it has a thickness dimension larger than the fan-shaped radius dimension, the appearance impression is columnar rather than plate-like.
【００１４】双方の偏心重錘１６，１７が回転軸２に関
して対称位置をなしている（Ａ）図の状態では、それぞ
れの偏心重錘Ｇ，Ｇ′の総合重心は回転軸２の中心線上
に位置している。従って、双方の偏心重錘１６，１７が
相対的な位置関係を保ったままで回転軸２まわりに回転
しても遠心力が働かず、起振力はゼロである。この状態
が先に述べた基準状態である。固定偏心重錘１６および
可動偏心重錘の端面形状である扇形の頂角ψは、 ψ＝１８０度−θ に設定されている。In the state shown in FIG. 2A where both eccentric weights 16 and 17 are symmetrical with respect to the rotation axis 2, the total center of gravity of each eccentric weight G and G ′ is on the center line of the rotation axis 2. positioned. Therefore, even if the two eccentric weights 16 and 17 rotate around the rotation axis 2 while maintaining the relative positional relationship, no centrifugal force acts and the vibrating force is zero. This state is the reference state described above. The apex angle 扇 of the sector, which is the end surface shape of the fixed eccentric weight 16 and the movable eccentric weight 16, is set to に = 180 degrees−θ.
【００１５】上記の角度θは、鋭角であることを必要条
件とするが、図示のように３０度であることが望まし
い。ただし、実際問題として製作誤差が入る上に、設計
の自由度も欲しいので ３０度±１０度に設定すること
が実用的である。The angle θ is required to be an acute angle, but is desirably 30 degrees as shown. However, it is practical to set the angle to 30 degrees ± 10 degrees because a manufacturing error is included as a practical problem and a degree of freedom in design is desired.
【００１６】上記のように構成され、かつ、固定偏心重
錘１６の紙面手前側の扇形状の面と可動偏心重錘１７の
紙面手前側の扇形状の面とがほぼ同一面（紙面と平行）
に揃えられている。紙面奥行側の扇形状の面も同様に同
一面に揃えられている。従って、本図１（Ｂ）のように
基準状態から角θだけ可動偏心重錘１７が固定偏心重錘
１６に対して回動すると、扇形の辺に対応する面同志が
当接して回動が衝止され、角θ以上には回動できないよ
うになっている。本図１（Ｂ）の状態では、双方の偏心
重錘の重心Ｇ，Ｇ′の総合重心は回転軸２の中心線に比
して偏心しているので、本図（Ｂ）の状態で回転すると
遠心力が働いて起振力が発生する。可動偏心重錘１７は
固定偏心重錘１６に対して、これ以上（角θ以上に）回
動できないから、この（Ｂ）図の状態が、同一回転速度
では最大の起振力を発生する状態である。The fan-shaped surface of the fixed eccentric weight 16 on the front side of the drawing sheet and the fan-shaped surface of the movable eccentric weight 17 on the front side of the drawing sheet are substantially in the same plane (parallel to the drawing sheet). )
Are aligned. Similarly, the fan-shaped surface on the depth side of the paper is also aligned on the same surface. Therefore, when the movable eccentric weight 17 rotates relative to the fixed eccentric weight 16 by the angle θ from the reference state as shown in FIG. 1B, the surfaces corresponding to the fan-shaped sides come into contact with each other and the rotation is performed. And cannot rotate beyond the angle θ. In the state shown in FIG. 1B, since the total center of gravity G and G 'of both eccentric weights is eccentric compared to the center line of the rotating shaft 2, when the eccentric weight is rotated in the state shown in FIG. A centrifugal force acts to generate a vibrating force. Since the movable eccentric weight 17 cannot rotate any more (greater than the angle θ) with respect to the fixed eccentric weight 16, the state shown in FIG. It is.
【００１７】可動偏心重錘を鋭角θ以上には回動させな
い理由は次のごとくである。回転軸２の回転速度が一定
であると仮定したとき、（Ａ）図の状態では回転エネル
ギーが大きく、（Ｂ）図の状態では回転エネルギーが小
さい。従って、固定偏心重錘１６に対する可動偏心重錘
１７の位置を保持することについては、（Ａ）図の状態
は不安定であり、（Ｂ）図の状態が安定である。このた
め、（Ａ）図の基準状態から（Ｂ）図の起振力最大の状
態に変化させる操作は所要トルクが微小（摩擦力に打ち
勝つ程度で足りる）で良いが、（Ｂ）図の起振力最大の
状態から（Ａ）図の基準状態に変化させる操作は相応の
駆動トルクが必要である。しかし、基準状態からのズレ
角が鋭角θ以内に制限されているので、１８０度回動さ
せていた従来技術に比較すると、基準状態にするための
所要トルクが著しく小さい。θ≒３０度 であれば、い
っそう所要トルクが小さい。The reason why the movable eccentric weight is not rotated beyond the acute angle θ is as follows. Assuming that the rotation speed of the rotating shaft 2 is constant, the rotational energy is large in the state of FIG. 7A and small in the state of FIG. Accordingly, as for holding the position of the movable eccentric weight 17 with respect to the fixed eccentric weight 16, the state shown in FIG. 7A is unstable, and the state shown in FIG. 7B is stable. For this reason, the operation for changing the reference state of FIG. 7A to the state of the maximum vibrating force of FIG. 7B requires only a small required torque (sufficient to overcome the frictional force), but the operation of FIG. The operation of changing from the state of maximum vibration to the reference state shown in FIG. 3A requires a corresponding drive torque. However, since the deviation angle from the reference state is limited to within the acute angle θ, the required torque for setting the reference state is significantly smaller than that in the conventional technique rotated 180 degrees. If θ ≒ 30 degrees, the required torque is even smaller.
【００１８】図１（Ｃ）に示したように、可動偏心重錘
１７を基準状態から φ＜θ なる角φだけ回動させた状態では、（Ｂ）図の状態より
も小さい起振力を生じる。上記の角φは、 ０＜φ＜θ の範囲内で無段階的に変化させることができるので、起
振力をゼロから最大までの間で無段階的に、任意に調節
することができる。As shown in FIG. 1C, when the movable eccentric weight 17 is rotated from the reference state by an angle φ of φ <θ, a smaller vibrating force than the state shown in FIG. Occurs. Since the angle φ can be changed steplessly within the range of 0 <φ <θ, the excitation force can be arbitrarily adjusted steplessly from zero to the maximum.
【００１９】先に述べたように本発明は、可動偏心重錘
が基準状態に比して相対的に回動する角度θを鋭角に
（望ましくは約３０度に）制約することによって起振力
制御に必要な操作トルクを著しく減少させるとともに、
制御応答性を著しく改善したのであるが、その反面、可
動偏心重錘の調整操作における回動角をθ以内に制限し
たため、同一回転速度における最大起振力も制限を受け
ることになる。しかし乍ら、この短所については、回転
軸２を高速回転させることによって補い得るので、高速
回転駆動技術が発達した今日、解消し得ない欠点ではな
くなっている。図２は上掲の図１に模式図として示した
起振用偏心重錘機構の１実施例を描いた断面図である。
管状の外軸１８は、ベアリング２０によって軸受ブラケ
ット２１に対して回転自在に支承されている。上記管状
外軸１８に対して相対的回動可能なように内軸２２が挿
通されている。固定偏心重錘１６はキー１９を介して前
記の内軸２２に固着され、可動偏心重錘１７は前記の管
状外軸１８を嵌着されている。上記の内軸２２に回転駆
動力を与えて回転させながら、管状外軸１８を上記内軸
２２と同期させて回転させることによって起振力を発生
させることができる。さらに、管状外軸１８の回転位相
を内軸２２に対して若干進めたり遅らせたりすることに
よって、図１について先に説明した「固定偏心重錘１６
に対する可動偏心重錘１７の角位置を調節して、起振力
の増減調節を、遠隔的に、しかも起振機の運転を中止す
ることなく、速やかな応答性をもって行なうことができ
るので、図４，図５について説明した振動公害防止の原
理と組み合わせて実施することにより、ロータリ式起振
機を用いる杭打工事における振動公害を格段に抑制する
ことができる。As described above, the present invention restricts the angle θ at which the movable eccentric weight relatively rotates relative to the reference state to an acute angle (preferably about 30 degrees) to thereby generate a vibrating force. The operating torque required for control is significantly reduced,
Although the control responsiveness was remarkably improved, on the other hand, since the rotation angle in the adjusting operation of the movable eccentric weight was limited to within θ, the maximum vibration force at the same rotation speed was also limited. However, this disadvantage can be compensated for by rotating the rotating shaft 2 at high speed, and this is no longer an inevitable disadvantage in today's development of high-speed rotation driving technology. FIG. 2 is a cross-sectional view illustrating one embodiment of the eccentric weight mechanism for excitation shown schematically in FIG. 1 described above.
The tubular outer shaft 18 is rotatably supported by a bearing 20 on a bearing bracket 21. An inner shaft 22 is inserted so as to be rotatable relative to the tubular outer shaft 18. The fixed eccentric weight 16 is fixed to the inner shaft 22 via a key 19, and the movable eccentric weight 17 is fitted to the tubular outer shaft 18. An exciting force can be generated by rotating the tubular outer shaft 18 in synchronization with the inner shaft 22 while applying a rotational driving force to the inner shaft 22 to rotate the inner shaft 22. Further, by slightly advancing or retarding the rotational phase of the tubular outer shaft 18 with respect to the inner shaft 22, the “fixed eccentric weight 16 described above with reference to FIG.
Since the angular position of the movable eccentric weight 17 with respect to can be adjusted to increase / decrease the exciter force remotely and without stopping the operation of the exciter, a quick response can be achieved. 4. By carrying out in combination with the principle of preventing vibration pollution described with reference to FIGS. 4 and 5, it is possible to significantly suppress vibration pollution in pile driving work using a rotary exciter.
【００２０】[0020]
【発明の効果】本発明方法によると、起振力最大の状態
と起振力ゼロの状態との間で、可動偏心重錘を鋭角だけ
相対的に回動させれば足りるので、調節作動の応答性が
速く、しかも、基準状態を中心として鋭角θの範囲内に
おいては、運転中に可動偏心重錘を調節回動させるに要
する駆動トルクが小さいので、運転を継続しつつ調節操
作を行なうことができる。本発明の機構は、ほぼ等しい
慣性モーメントを有する２個の偏心重錘が、回転軸部材
に取り付けられており、上記２個の偏心重錘の内の片方
は回転軸に対して回動しないように固着された固定偏心
重錘であり、前記の２個の偏心重錘の他方は上記固定偏
心重錘に対して所定角度範囲内で相対的に回動し得る可
動偏心重錘であって、上記固定偏心重錘と可動偏心重錘
とが回転中心軸に関して対称に位置した状態を基準状態
として、可動偏心重錘が固定偏心重錘に対して、鋭角θ
以上に回動できないようなストッパ手段が設けられてい
るので、前記の発明方法を実施するに好適である。特
に、可動偏心重錘の回動をフリーにしても固定偏心重錘
に対して鋭角θ以上回らないようにストッパ手段が設け
られているので、該可動偏心重錘をフリーにすると「回
転する剛体は、慣性モーメントが最大になる姿勢をとろ
うとする」という法則に従って、基準状態から遠ざかる
方向に回動してストッパ手段に当接する。このため、ス
トッパを利かせた状態で固定偏心重錘を回転駆動する
と、可動偏心重錘を直接的に回転駆動しなくても起振機
としての機能を発揮する。このため、振動杭打用の回転
エネルギーの伝動が容易である。その上、共通の回転軸
に対して２個の偏心重錘（固定偏心重錘と可動偏心重
錘）を配設する構造であるため、起振機の全体的形状を
コンパクトに構成することができる。以上の各作用が総
合されて振動杭打工事の施工コスト低減と、振動公害防
止とに貢献するところ多大である。According to the method of the present invention, it is sufficient that the movable eccentric weight is relatively rotated by an acute angle between the state where the vibrating force is maximum and the state where the vibrating force is zero. Since the responsiveness is fast and the driving torque required to adjust and rotate the movable eccentric weight during operation is small in the range of the acute angle θ around the reference state, the adjustment operation must be performed while the operation is continued. Can be. In the mechanism of the present invention, two eccentric weights having substantially equal moments of inertia are attached to the rotating shaft member, and one of the two eccentric weights is prevented from rotating with respect to the rotating shaft. A fixed eccentric weight fixed to the other, the other of the two eccentric weights is a movable eccentric weight that can relatively rotate within a predetermined angle range with respect to the fixed eccentric weight, With the fixed eccentric weight and the movable eccentric weight being symmetrical with respect to the rotation center axis as a reference state, the movable eccentric weight has an acute angle θ with respect to the fixed eccentric weight.
Since the stopper means which cannot rotate above is provided, it is suitable for carrying out the method of the invention. In particular, since the stopper means is provided so that the movable eccentric weight does not rotate more than the acute angle θ with respect to the fixed eccentric weight even if the rotation of the movable eccentric weight is free, when the movable eccentric weight is released, a “rotating rigid body” According to the rule that the moment of inertia is maximized, and contacts the stopper means in a direction away from the reference state. For this reason, when the fixed eccentric weight is rotationally driven in a state where the stopper is used, the function as a vibration exciter is exhibited without directly rotating the movable eccentric weight. Therefore, transmission of rotational energy for driving the vibrating pile is easy. In addition, since two eccentric weights (a fixed eccentric weight and a movable eccentric weight) are provided for a common rotating shaft, the overall shape of the exciter can be made compact. it can. The above actions are combined to contribute to the reduction of the construction cost of the vibrating pile construction and the prevention of vibration pollution.
【図面の簡単な説明】[Brief description of drawings]
【図１】本発明に係る偏心重錘の起振力制御方法を実施
するために構成した本発明の起振用偏心重錘機構の１実
施例を示し、（Ａ）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位置となって起振力がゼロになる基
準状態を描いた模式図であり、（Ｂ）は可動偏心重錘が
基準状態から鋭角θだけ回動して起振力最大となった状
態を描いた模式図であり、（Ｃ）は起振力を中等度に調
節された状態を描いた模式図である。FIG. 1 shows an embodiment of an eccentric weight mechanism for excitation according to the present invention configured to carry out a method of controlling the excitation force of an eccentric weight according to the present invention, wherein FIG. FIG. 9B is a schematic diagram illustrating a reference state in which the movable eccentric weight and the movable eccentric weight become symmetrical positions with respect to the rotation axis and the vibrating force becomes zero. FIG. It is the schematic diagram which drew the state where the excitation force became maximum, and (C) is the schematic diagram which drew the state where the excitation force was moderately adjusted.
【図２】上掲の図１に模式図として示した起振用偏心重
錘機構の１実施例を描いた断面図である。FIG. 2 is a cross-sectional view illustrating one embodiment of the eccentric weight mechanism for excitation shown schematically in FIG. 1 described above.
【図３】４本の回転軸のそれぞれに偏心重錘を取り付け
たロータリ式起振機の説明図である。FIG. 3 is an explanatory view of a rotary type vibration exciter in which eccentric weights are attached to each of four rotating shafts.
【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 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 diagram showing time-rotation speed for explaining a resonance phenomenon in a vibrating pile driving work.
【図６】前掲の図３に示した４軸４重錘式の起振機の作
用を説明するための模式図であって、（Ａ）は図３にお
けると同様に偏心重錘が下降している状態を表し、
（Ｂ）は約９０度回転した状態を表し、（Ｃ）はさらに
約９０度回転して重錘が上昇した状態を表している。6A and 6B are schematic views for explaining the operation of the four-shaft, four-weight exciter shown in FIG. 3 described above, and FIG. 6A is a diagram in which the eccentric weight descends as in FIG. Represents the state of
(B) shows a state rotated by about 90 degrees, and (C) shows a state in which the weight is further rotated by about 90 degrees.
【図７】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。FIG. 7 is a view for explaining a known technique of changing the vibrating force by a combination of two eccentric weights, where (A) shows that the two eccentric weights exert the maximum vibrating force. (B) is a schematic diagram showing a state where the vibrating force is medium, (C) is a schematic diagram showing a state where the vibrating force is slightly small, and (D) is a schematic diagram showing a state where the vibrating force is slightly small. It is a schematic diagram showing a state.
【図８】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. 8 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９】上掲の図８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. 9 shows a fixed eccentric weight and a movable eccentric weight arranged on a common axis so as to increase or decrease the vibrating force as shown in FIG. 8 described above. It is a perspective view which shows the conventional example of a shaker.
【図１０】前掲の図９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。10 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. 9 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…同期回転用の伝
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、１６…固定偏心重錘、１７…可
動偏心重錘、１８…管状外軸、１９…キー、２０…ベア
リング、２１…軸受ブラケット、２２…内軸、２３ａ〜
２３ｃ…目盛。1 ... Exciter case, 2, 2A-2D ... Rotating shaft, 3, 3
A to 3D: eccentric weight, 4, 4A to 4D: transmission gear for synchronous rotation, 5: crane boom, 6: vibrating device (vibrator), 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 ... Driving pulley,
12 ... female screw hole, 13 ... knock pin, 14 ... set bolt, 15 ... hexagon wrench, 16 ... fixed eccentric weight, 17 ... movable eccentric weight, 18 ... tubular outer shaft, 19 ... key, 20 ... bearing, 21 ... bearing Bracket, 22 ... inner shaft, 23a-
23c: Scale.
Claims (15)
ほぼ等しい２個の偏心重錘を配設して、 上記２個の偏心重錘のうちの片方を、回転軸部材に対す
る相対的な回動を係止して取り付けて固定偏心重錘を構
成するとともに、 上記の固定偏心重錘に対して他方の偏心重錘が回転中心
軸まわりに相対的に回動し得るように取り付けて可動偏
心重錘を構成し、 前記２個の偏心重錘それぞれの重心が回転中心軸に対し
て対称に位置する状態を基準状態と名付け、 上記の可動偏心重錘を、基準状態から鋭角θの範囲内
で、固定偏心重錘に対して相対的に回動させることによ
って、前記２個の偏心重錘よりなる起振機構の起振力の
大小を調節し、かつ、 前記可動偏心重錘を固定偏心重錘に対して、相対的に鋭
角θ以上に回動させないことを特徴とする、偏心重錘の
起振力制御方法。1. An eccentric weight having substantially the same moment of inertia is arranged with respect to a central axis of rotation, and one of the two eccentric weights is rotated relative to a rotary shaft member. A fixed eccentric weight is configured by locking the movement to form a fixed eccentric weight, and the other eccentric weight is attached to the fixed eccentric weight so that the other eccentric weight can rotate relative to the rotation center axis. A weight is configured, and a state in which the center of gravity of each of the two eccentric weights is symmetrically located with respect to the rotation center axis is referred to as a reference state, and the movable eccentric weight is set within a range of an acute angle θ from the reference state. By rotating the movable eccentric weight with respect to the fixed eccentric weight, the magnitude of the oscillating force of the oscillating mechanism composed of the two eccentric weights is adjusted, and the movable eccentric weight is fixed. It is characterized in that it is not rotated relative to the weight by more than an acute angle θ, Excitation force control method for eccentric weight.
を回転中心軸方向に見たときの形状を、頂角が（１８０
度−θ）の扇形をなす厚板状に構成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。2. The shape of the fixed eccentric weight and the movable eccentric weight as viewed in the direction of the rotation center axis has an apex angle of (180).
The method for controlling the vibrating force of an eccentric weight according to claim 1, wherein the vibrating member is formed in a thick plate shape having a sector shape of (−θ).
と、同じく扇形厚板状の可動偏心重錘の両面とを、それ
ぞれ回転中心軸に垂直な仮想の平面に揃えて配設し、可
動偏心重錘が固定偏心重錘に対して回動したとき、前記
扇形の辺に相当する面同志を当接せしめて回動を係止す
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。3. Both surfaces of said sector-shaped thick plate-shaped fixed eccentric weight and both surfaces of said sector-shaped thick plate-shaped movable eccentric weight are arranged in a virtual plane perpendicular to the rotation center axis. 3. The method according to claim 2, wherein when the movable eccentric weight rotates with respect to the fixed eccentric weight, the surfaces corresponding to the fan-shaped sides are brought into contact with each other to stop the rotation. Excitation weight control method for eccentric weight.
することを特徴とする、請求項１ないし請求項３の何れ
かに記載した偏心重錘の起振力制御方法。4. The method for controlling the vibrating force of an eccentric weight according to claim 1, wherein the acute angle θ is set to 30 degrees ± 10 degrees.
しめた状態で回転軸部材に回転駆動力を与えて固定偏心
重錘を回転せしめつつ、可動偏心重錘に対しては別段の
回転駆動力を伝動することなく従動回転せしめることに
よって、調節可能範囲内における最大起振力を発生させ
ることを特徴とする、請求項３に記載した偏心重錘の起
振力制御方法。5. A movable eccentric weight is separated from a movable eccentric weight by applying a rotational driving force to a rotating shaft member in a state in which surfaces corresponding to the fan-shaped sides are in contact with each other to rotate the fixed eccentric weight. The method according to claim 3, wherein the maximum oscillating force within the adjustable range is generated by causing the driven rotator to rotate without transmitting the rotational driving force.
軸を挿通して前記の回転軸部材を構成するとともに、 前記の固定偏心重錘および可動偏心重錘のそれぞれを、
上記外軸と内軸とのそれぞれに取り付けることを特徴と
する、請求項１ないし請求項５の何れかに記載した偏心
重錘の起振力制御方法。6. The rotary shaft member is formed by inserting an inner shaft into a tubular outer shaft so as to be relatively rotatable, and each of the fixed eccentric weight and the movable eccentric weight is
6. The method for controlling the vibrating force of an eccentric weight according to any one of claims 1 to 5, wherein the method is attached to each of the outer shaft and the inner shaft.
ンブームで吊持し、上記振動杭打装置に把持されている
杭を地盤中に貫入する際、 上記の杭を地表に接せしめた杭打開始時点においては前
記可動偏心重錘を固定偏心重錘に対して基準状態もしく
は基準状態に近い状態として起振力を小ならしめ、 起振力の小さい状態で前記の回転軸部材を回転駆動し
て、杭の打ち込みを進行させつつ次第に回転速度を上昇
させて振動周波数を増加させながら、 比較的に基準状態に近くて起振力の小さい状態で地盤の
固有振動数およびクレーンブームの固有振動数を通過し
た後、 可動偏心重錘を固定偏心重錘に対して、基準状態から鋭
角θまで相対的に回動させ、定格状態で杭打作業を続行
することを特徴とする、請求項１ないし請求項６の何れ
かに記載した偏心重錘の起振力制御方法。7. A vibrating pile driving device comprising an eccentric weight is suspended by a crane boom, and when the pile gripped by the vibrating pile driving device penetrates into the ground, the pile is brought into contact with the ground surface. At the time of starting the pile driving, the movable eccentric weight is set in a reference state or a state close to the reference state with respect to the fixed eccentric weight to reduce the vibrating force, and rotate the rotary shaft member in a state where the vibrating force is small. While driving, the driving speed of the pile is gradually increased and the vibration frequency is increased, and the natural frequency of the ground and the natural frequency of the crane boom are relatively close to the reference state and the vibration force is small. After passing the frequency, the movable eccentric weight is rotated relative to the fixed eccentric weight from the reference state to the acute angle θ, and the pile driving operation is continued in the rated state. 7. A method according to claim 1, wherein: Method for controlling the vibrating force of an eccentric weight.
基準状態から鋭角θ相対的に回動させた状態で杭打作業
中に、前記回転軸部材の回転駆動エネルギ供給を遮断し
て、回転系を慣性回転させながら次第に減速させる際、 回転速度および振動周波数が低下してクレーンブームの
共振周波数または地盤の共振周波数に差しかかる以前
に、可動偏心重錘を固定偏心重錘に対して相対的に回動
させて、基準状態もしくは基準状態に近い状態ならしめ
て、前記共振周波数域を通過することを特徴とする、請
求項１ないし請求項７の何れかに記載した偏心重錘の起
振力制御方法。8. The movable eccentric weight is fixed relative to the fixed eccentric weight.
During a pile driving operation in a state of being relatively rotated at an acute angle θ from the reference state, when the rotation driving energy supply of the rotation shaft member is cut off and the rotation system is gradually decelerated while rotating inertia, the rotation speed and the vibration are increased. If the movable eccentric weight is rotated relatively to the fixed eccentric weight before the frequency drops and reaches the resonance frequency of the crane boom or the ground, The method for controlling the vibrating force of an eccentric weight according to any one of claims 1 to 7, further comprising passing the resonance frequency range.
動偏心重錘を鋭角θだけ回動させた起振力最大の状態と
の中間の、所望の大きさの起振力を発生する状態で、可
動偏心重錘の固定偏心重錘に対する相対的回動を阻止
し、この所望の起振力を発生する状態で可動偏心重錘と
固定偏心重錘とを同期回転させることを特徴とする、請
求項１ないし請求項８の何れかに記載した偏心重錘の起
振力制御方法。9. A vibrating force having a desired magnitude, which is intermediate between the reference state where the vibrating force is zero and the state where the movable eccentric weight is rotated by an acute angle θ is the maximum. In such a state, the relative rotation of the movable eccentric weight with respect to the fixed eccentric weight is prevented, and the movable eccentric weight and the fixed eccentric weight are synchronously rotated in a state where the desired vibrating force is generated. 9. The method for controlling the vibrating force of an eccentric weight according to any one of claims 1 to 8, wherein:
ーンブームで吊持し、上記振動杭打装置に把持されてい
る杭を地盤中に貫入する際、 上記の杭を地表に接せしめた杭打開始時点においては前
記可動偏心重錘を固定偏心重錘に対して基準状態もしく
は基準状態に近い状態として起振力を小ならしめ、 起振力の小さい状態で前記の回転軸部材を回転駆動し
て、杭の打ち込みを進行させつつ次第に回転速度を上昇
させて振動周波数を増加させながら、 比較的に基準状態に近くて起振力の小さい状態で地盤の
固有振動数およびクレーンブームの固有振動数を通過し
た後、 可動偏心重錘を固定偏心重錘に対して、基準状態から鋭
角θまでの範囲内で回動させ、打込み途中の杭の下端部
が到達している地層の状態に応じて上記回動の角度を増
減させて起振力を調節することを特徴とする、請求項１
ないし請求項６の何れかに記載した偏心重錘の起振力制
御方法。10. A vibrating pile driving device comprising an eccentric weight is suspended by a crane boom, and when the pile gripped by the vibrating pile driving device penetrates into the ground, the pile is brought into contact with the ground surface. At the time of starting the pile driving, the movable eccentric weight is set in a reference state or a state close to the reference state with respect to the fixed eccentric weight to reduce the vibrating force, and rotate the rotary shaft member in a state where the vibrating force is small. While driving, the driving speed of the pile is gradually increased and the vibration frequency is increased, and the natural frequency of the ground and the natural frequency of the crane boom are relatively close to the reference state and the vibration force is small. After passing the frequency, the movable eccentric weight is rotated relative to the fixed eccentric weight within the range from the reference state to the acute angle θ, and the stratum in which the lower end of the pile being driven has reached is reached. Increase or decrease the angle of rotation 2. The method according to claim 1, wherein the vibrating force is adjusted.
7. The method for controlling the vibrating force of an eccentric weight according to claim 6.
個の偏心重錘が、回転軸部材に取り付けられており、 上記２個の偏心重錘の内の片方は回転軸に対して回動し
ないように固着された固定偏心重錘であり、前記の２個
の偏心重錘の他方は上記固定偏心重錘に対して所定角度
範囲内で相対的に回動し得る可動偏心重錘であって、 上記固定偏心重錘と可動偏心重錘とが回転中心軸に関し
て対称に位置した状態を基準状態として、可動偏心重錘
が固定偏心重錘に対して、鋭角θ以上に回動できないよ
うなストッパ手段が設けられていることを特徴とする、
起振用偏心重錘機構。11. 2 having substantially equal moments of inertia
One of the two eccentric weights is a fixed eccentric weight that is fixed so as not to rotate with respect to the rotation axis, The other of the two eccentric weights is a movable eccentric weight that can rotate relative to the fixed eccentric weight within a predetermined angle range, and the fixed eccentric weight and the movable eccentric weight rotate. With the state symmetrically positioned with respect to the central axis as a reference state, a stopper means is provided such that the movable eccentric weight cannot rotate with respect to the fixed eccentric weight at an acute angle θ or more.
Eccentric weight mechanism for vibration excitation.
錘と可動偏心重錘とが、回転軸部材に対する取付個所を
除いてほぼ同形同寸の扇形厚板状に構成されていて、上
記扇形の頂角が（１８０度−θ）に設定されていること
を特徴とする、請求項１１に記載した起振用偏心重錘機
構。12. The fixed eccentric weight and the movable eccentric weight, which are the two eccentric weights, are formed in the shape of a fan-shaped thick plate having substantially the same shape and the same size except for a mounting position with respect to a rotating shaft member. The eccentric weight mechanism for vibration generation according to claim 11, wherein the vertical angle of the sector is set to (180 degrees-?).
心重錘とが、それぞれの両面を相互に、回転中心軸と直
交する仮想の面に沿って揃えられており、 可動偏心重錘が固定偏心重錘に対して、基準状態から角
θだけ回動したとき、 扇形の２辺に相当する面同志が当接して回動を阻止され
るようになっていることを特徴とする、請求項１２に記
載した起振用偏心重錘機構。13. The movable eccentric weight, wherein the fan-shaped plate-shaped fixed eccentric weight and the movable eccentric weight are aligned with each other along an imaginary plane orthogonal to a rotation center axis. Are rotated relative to the fixed eccentric weight by an angle θ from the reference state, and the surfaces corresponding to the two sides of the sector come into contact with each other and are prevented from rotating. An eccentric weight mechanism for vibration generation according to claim 12.
の何れかに記載した起振用偏心重錘機構。14. The rotation limiting angle θ is set to 20 ° <θ <40 °, and preferably θ ≒ 30 °. 13
The eccentric weight mechanism for vibration generation according to any one of the above.
れた管状の外軸と、上記管状外軸の中に回転自在に挿通
された内軸とよりなる回転軸部材を具備しており、 前記の固定偏心重錘および可動偏心重錘はそれぞれ上記
管状外軸と内軸との何れかに固着されていることを特徴
とする、請求項１１ないし請求項１４の何れかに記載し
た起振用偏心重錘機構。15. A fixed eccentric comprising a rotary shaft member comprising a tubular outer shaft rotatably supported by a bearing and an inner shaft rotatably inserted into the tubular outer shaft. The eccentric weight for vibration generation according to any one of claims 11 to 14, wherein the weight and the movable eccentric weight are fixed to one of the tubular outer shaft and the inner shaft, respectively. mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15947995A JP2813319B2 (en) | 1995-06-26 | 1995-06-26 | Oscillating force control method for eccentric weight and eccentric weight mechanism for oscillating weight |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15947995A JP2813319B2 (en) | 1995-06-26 | 1995-06-26 | Oscillating force control method for eccentric weight and eccentric weight mechanism for oscillating weight |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH093891A true JPH093891A (en) | 1997-01-07 |
| JP2813319B2 JP2813319B2 (en) | 1998-10-22 |
Family
ID=15694678
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15947995A Expired - Lifetime JP2813319B2 (en) | 1995-06-26 | 1995-06-26 | Oscillating force control method for eccentric weight and eccentric weight mechanism for oscillating weight |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2813319B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012007315A (en) * | 2010-06-23 | 2012-01-12 | Chowa Kogyo Kk | Pile/wall placing device, intermediate vibration hammer, and placing method |
| CN106638597A (en) * | 2017-03-05 | 2017-05-10 | 李沛 | Piling machine for containing river dike break |
-
1995
- 1995-06-26 JP JP15947995A patent/JP2813319B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012007315A (en) * | 2010-06-23 | 2012-01-12 | Chowa Kogyo Kk | Pile/wall placing device, intermediate vibration hammer, and placing method |
| CN106638597A (en) * | 2017-03-05 | 2017-05-10 | 李沛 | Piling machine for containing river dike break |
| CN106638597B (en) * | 2017-03-05 | 2018-10-26 | 李沛 | A kind of piling machine contained sill may and burst |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2813319B2 (en) | 1998-10-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2813319B2 (en) | Oscillating force control method for eccentric weight and eccentric weight mechanism for oscillating weight | |
| JP2923240B2 (en) | Eccentric weight type vibration generation / control method and eccentric weight type vibration exciter | |
| JPH0938575A (en) | Rotary vibration generator and control method therefor | |
| JP3731169B2 (en) | Vibration pile punching control method | |
| JP2724296B2 (en) | Excitation weight control method and control mechanism for eccentric weight | |
| JP5315295B2 (en) | Pile or wall placing device, intermediate vibrator hammer and placing method | |
| JP2607377B2 (en) | Exciter for structural test | |
| JP3212250B2 (en) | Method for supporting eccentric weight for exciter and support structure for eccentric weight for exciter | |
| JP3120064B2 (en) | Exciting force generator | |
| JP2680797B2 (en) | Excitation force control method and excitation force control device | |
| JPH0220263Y2 (en) | ||
| SU1187890A1 (en) | Vibration exciter | |
| WO2011056910A1 (en) | Vibratory pile driving apparatus | |
| JP3144774B2 (en) | Exciting force generator | |
| JPS6120115Y2 (en) | ||
| JP2872871B2 (en) | Drive / control method and drive / control device for exciter | |
| JPH0639782B2 (en) | Shaker | |
| JP2733493B2 (en) | Vibration device | |
| JP2664957B2 (en) | Variable eccentricity vibrator | |
| JPH07285638A (en) | Variable type vibrator | |
| SU1209313A1 (en) | Vibration exciter | |
| JP3384689B2 (en) | Exciting force control method | |
| JPS59183140A (en) | Variable output type vibration damper | |
| JPH0293138A (en) | Suppression of vibration of structure | |
| JPH03275180A (en) | Centrifugal force generator for which nonuniform speed gear is used |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080807 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090807 Year of fee payment: 11 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100807 Year of fee payment: 12 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110807 Year of fee payment: 13 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110807 Year of fee payment: 13 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120807 Year of fee payment: 14 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120807 Year of fee payment: 14 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130807 Year of fee payment: 15 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| EXPY | Cancellation because of completion of term | ||
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |