JP2865934B2 - Vibration generator - Google Patents
Vibration generatorInfo
- Publication number
- JP2865934B2 JP2865934B2 JP4400192A JP4400192A JP2865934B2 JP 2865934 B2 JP2865934 B2 JP 2865934B2 JP 4400192 A JP4400192 A JP 4400192A JP 4400192 A JP4400192 A JP 4400192A JP 2865934 B2 JP2865934 B2 JP 2865934B2
- Authority
- JP
- Japan
- Prior art keywords
- phase
- shaft
- gear
- adjustment
- adjusting
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
- Road Paving Machines (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、振動杭打機，各種シェ
ーカー，ふるい装置等に適用される振動発生装置に係
り、特に、偏心重錘を回転させることにより得られる起
振力あるいは振幅を任意にかつ無段階に変更できるよう
にされたものに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration generating device applied to a vibrating pile driver, various shakers, a sieving device, etc., and more particularly to a vibrating force or an amplitude obtained by rotating an eccentric weight. The present invention relates to one that can be changed arbitrarily and steplessly.
【０００２】[0002]
【従来の技術】偏心重錘を回転させることにより発生す
る遠心力を利用した振動発生装置としては、偏心重錘が
取り付けられた対をなす偶数本の回転軸をケーシング部
材に相互に平行に軸支するとともに、各回転軸に伝動歯
車を取り付けて隣接するもの同士を噛合させ、一方の回
転軸群と他方の回転軸群とを反対方向に回転させること
により、各回転軸に取り付けられた偏心重錘に発生する
遠心力の水平分力を相殺するとともに遠心力の垂直分力
を相加し、この垂直分力によりケーシング部材に例えば
上下方向の起振力を与えるようにしたものが一般によく
知られている。2. Description of the Related Art As a vibration generator utilizing centrifugal force generated by rotating an eccentric weight, an even number of pairs of rotating shafts to which an eccentric weight is attached are parallel to a casing member. While supporting, a transmission gear is attached to each rotating shaft so that adjacent ones mesh with each other, and one of the rotating shaft groups and the other rotating shaft group are rotated in opposite directions, so that the eccentric attached to each rotating shaft. In general, the vertical component of the centrifugal force is added while the horizontal component of the centrifugal force generated in the weight is offset, and the vertical component is applied to the casing member, for example, so as to give a vertical vibration force. Are known.
【０００３】このような振動発生装置にあっては、ケー
シング部材をばねあるいはダンパーを介して支持するこ
とにより、振動発生装置全体が回転軸の回転速度に応じ
た周波数をもって振動せしめられる。従って、ケーシン
グ部材にチャック等を介して例えば鋼矢板等の杭を支持
させて振動発生装置を作動させることにより、杭打込作
業や杭引抜作業が行え、さらに、かかる振動発生装置を
シェーカーやふるい装置に組み込むことで掻き混ぜ作業
やふるい作業が行える。In such a vibration generator, the entire vibration generator is vibrated at a frequency corresponding to the rotation speed of the rotating shaft by supporting the casing member via a spring or a damper. Therefore, by operating a vibration generating device by supporting a pile such as a steel sheet pile on a casing member through a chuck or the like, a pile driving operation or a pile pulling-out operation can be performed, and further, such a vibration generating device can be shaker or sieved. Stirring work and sieving work can be performed by incorporating it into the device.
【０００４】[0004]
【発明が解決しようとする課題】上述した如くの従来の
振動発生装置においては、回転軸に偏心重錘が固定され
ているため、運転時に起振力あるいは振幅を任意に変え
ることは容易ではない。ところが、かかる振動発生装置
では、運転開始時において静止状態の偏心重錘を回転さ
せるために必要とされる駆動力は偏心重錘が定格回転速
度に達した後におけるそれより著しく大きいので、静止
状態の偏心重錘が定格回転速度に達するまでに必要とさ
れる駆動力を低減することができればモーター等の駆動
源の小型化が図れ、消費電力等のエネルギーの利用効率
を格段に向上させることができる。そのため、回転軸の
回転開始初期において、回転に必要とされる駆動力を簡
易に低減させ得る方策が要望されている。In the conventional vibration generator as described above, since the eccentric weight is fixed to the rotating shaft, it is not easy to arbitrarily change the vibrating force or the amplitude during operation. . However, in such a vibration generating device, the driving force required to rotate the eccentric weight in the stationary state at the start of operation is significantly larger than that after the eccentric weight has reached the rated rotation speed. If the driving force required until the eccentric weight of the eccentric weight reaches the rated rotation speed can be reduced, the drive source such as a motor can be reduced in size, and the efficiency of energy use such as power consumption can be significantly improved. it can. Therefore, there is a need for a measure that can easily reduce the driving force required for rotation at the beginning of the rotation start of the rotation shaft.
【０００５】また、例えば、振動杭打機に適用される振
動発生装置にあっては、杭打込作業性や杭引抜作業性を
向上させるため、打ち込まれる杭が貫入する地盤の状態
等に応じて起振力あるいは振幅を簡易に変え得る方策、
あるいは起動時、制動時に発生する共振現象を防ぐため
の方策も要望されている。上述の要望に応えるべく現在
起振力あるいは振幅可変の振動発生装置がいくつか考え
られているが、いずれも構造が複雑で部品点数が多く大
幅なコストアップが避けられない嫌いがある。Further, for example, in a vibration generator applied to a vibrating pile driving machine, in order to improve the workability of driving a pile and the work of pulling a pile, depending on the state of the ground into which the driven pile penetrates, etc. To easily change the excitation force or amplitude
Alternatively, a measure for preventing a resonance phenomenon that occurs at the time of starting or braking is also demanded. To meet the above demands, several types of vibration generators with variable vibrating force or amplitude are currently considered, but all of them have a complicated structure, a large number of parts, and a disproportionate increase in cost.
【０００６】かかる点に鑑み本発明は、運転時において
も起振力あるいは振幅を任意にかつ無段階に変えること
ができ、しかも、構造が簡素でかつ合理的で容易に製作
できる振動発生装置を提供することを目的とする。In view of the above, the present invention provides a vibration generating apparatus which can change the vibrating force or amplitude arbitrarily and steplessly even during operation, and has a simple and reasonable structure and can be easily manufactured. The purpose is to provide.
【０００７】[0007]
【課題を解決するための手段】上述の目的を達成すべ
く、本発明に係る振動発生装置は、ケーシング部材に相
互に平行に軸支され、それぞれに偏心重錘及び伝動歯車
が外嵌固定された第１の回転軸，第２の回転軸，第３の
回転軸，及び第４の回転軸と、それらの各回転軸と平行
に軸支され、位相固定歯車が相対回転不能にまた位相調
整歯車が相対回転可能にそれぞれ軸方向の移動は阻止さ
れた状態で外嵌された位相調整軸とを有し、上記第１の
回転軸及び第２の回転軸上の伝動歯車同士が噛合せしめ
られるとともに、上記第３の回転軸及び第４の回転軸上
の伝動歯車同士が噛合せしめられ、上記第３の回転軸及
び第４の回転軸のいずれかに軸方向の移動は阻止された
状態で上記位相固定歯車及び位相調整歯車のうちの一方
の回転を上記第１の回転軸及び第２の回転軸上の伝動歯
車のいずれかに伝達する媒介歯車が回転可能に外嵌さ
れ、さらに、上記第３の回転軸及び第４の回転軸上の伝
動歯車のいずれかが上記位相固定歯車及び位相調整歯車
のうちの他方に噛合せしめられ、かつ、上記位相調整軸
に関連して上記位相調整歯車を位相調整軸に対して相対
回転させる位相変更手段が設けられる。In order to achieve the above-mentioned object, a vibration generator according to the present invention is supported by a casing member in parallel with each other, and an eccentric weight and a transmission gear are externally fitted and fixed to each other. A first rotating shaft, a second rotating shaft, a third rotating shaft, and a fourth rotating shaft, which are supported in parallel with the respective rotating shafts, so that the phase-locked gears cannot rotate relative to each other and are phase-adjusted. The gears have a phase adjustment shaft fitted externally in a state where the gears are relatively rotatably prevented from moving in the axial direction, and the transmission gears on the first rotation shaft and the second rotation shaft are engaged with each other. At the same time, the transmission gears on the third rotating shaft and the fourth rotating shaft are engaged with each other, and the movement in the axial direction is prevented by any of the third rotating shaft and the fourth rotating shaft. The rotation of one of the phase locked gear and the phase adjustment gear is changed to the first An intermediate gear transmitting to any of the transmission gears on the rotation shaft and the second rotation shaft is rotatably fitted to the outside, and further, any one of the transmission gears on the third rotation shaft and the fourth rotation shaft is connected. There is provided a phase changing means which meshes with the other of the phase-locking gear and the phase-adjusting gear, and rotates the phase-adjusting gear relative to the phase-adjusting shaft in relation to the phase-adjusting shaft.
【０００８】また、本発明に係る振動発生装置の別の態
様は、ケーシング部材に相互に平行に軸支され、それぞ
れに偏心重錘及び伝動歯車が外嵌固定された第１の回転
軸，第２の回転軸，第３の回転軸，及び第４の回転軸
と、それらの各回転軸と平行に軸支され、位相固定歯車
が相対回転不能にまた位相調整歯車が相対回転可能にそ
れぞれ軸方向の移動は阻止された状態で外嵌された位相
調整軸とを有し、上記第１の回転軸及び第２の回転軸上
の伝動歯車同士が噛合せしめられるとともに、それらの
一方が上記位相固定歯車及び位相調整歯車のうちの一方
に噛合せしめられ、また、上記第３の回転軸及び第４の
回転軸上の伝動歯車同士が噛合せしめられるとともに、
それらの一方が上記位相固定歯車及び位相調整歯車のう
ちの他方に噛合せしめられ、かつ、上記位相調整軸に関
連して上記位相調整歯車を位相調整軸に対して相対回転
させる位相変更手段が設けられる。Another aspect of the vibration generating device according to the present invention is a vibration generating device comprising a first rotating shaft and a first rotating shaft each having an eccentric weight and a transmission gear externally fixedly supported by a casing member in parallel with each other. The second rotation shaft, the third rotation shaft, and the fourth rotation shaft are supported in parallel with the respective rotation shafts, so that the phase-locked gears cannot rotate relative to each other and the phase adjustment gears can rotate relative to each other. And a phase adjustment shaft fitted externally in a state where movement in the direction is prevented. The transmission gears on the first rotation shaft and the second rotation shaft are meshed with each other, and one of the transmission gears While being engaged with one of the fixed gear and the phase adjustment gear, the transmission gears on the third rotation shaft and the fourth rotation shaft are meshed with each other,
One of them is meshed with the other of the phase-locking gear and the phase-adjusting gear, and phase changing means is provided for rotating the phase-adjusting gear relative to the phase-adjusting shaft in relation to the phase-adjusting shaft. Can be
【０００９】かかる本発明に係る振動発生装置におい
て、位相変更手段としては多種多様なものが採用でき
る。例えば、位相調整軸を軸方向に強制的に移動させる
駆動手段と位相調整軸の軸方向の直線運動を位相調整歯
車の相対回転に変換する運動変換手段との組み合わせが
考えられ、具体的には、位相変更手段が、位相調整軸の
外周部に所定の旋回方向をもって設けられた螺旋状凹凸
部あるいは螺旋状の溝もしくは凸条と、位相調整歯車の
内周部に設けられ、上記螺旋状凹凸部あるいは螺旋状の
溝もしくは凸条に摺動自在に嵌合する螺旋状凹凸部ある
いは螺旋状の凸部もしくは凹部と、上記位相調整軸を軸
方向に強制的に移動させる駆動手段と、から構成される
もの、あるいは、位相変更手段が、位相調整軸に径方向
に向けて突出するように立設されたピンと、上記位相調
整歯車に連設され、上記ピンが嵌挿される螺旋長孔が形
成された延長ボス部と、上記位相調整軸を軸方向に強制
的に移動させる駆動手段と、から構成されるもの、等が
挙げられる。In the vibration generator according to the present invention, various types of phase changing means can be employed. For example, a combination of a driving unit that forcibly moves the phase adjustment shaft in the axial direction and a motion conversion unit that converts the axial linear motion of the phase adjustment shaft into a relative rotation of the phase adjustment gear can be considered. A phase changing means provided on the inner peripheral portion of the phase adjusting gear, and a spiral concave / convex portion or a spiral groove or ridge provided on the outer peripheral portion of the phase adjusting shaft with a predetermined turning direction; A spiral concave / convex portion or a spiral convex or concave portion slidably fitted into a portion or a spiral groove or convex line, and a driving means for forcibly moving the phase adjustment shaft in the axial direction. Or a phase changing means is formed with a pin which is provided upright so as to protrude radially from the phase adjustment shaft, and a helical elongated hole which is connected to the phase adjustment gear and into which the pin is inserted. Extension boss and Those composed of the phase adjustment shaft and a driving means to forcibly move axially, from, and the like.
【００１０】また、本発明に係る振動発生装置の他の態
様としては、位相調整軸を２分割構成の第１の調整軸と
第２の調整軸となし、第１の調整軸を第２の調整軸に対
して、直線運動を回転運動に変換する第１の運動変換手
段を介して軸方向に相対移動及び相対回転可能に配置し
てそれらを同一軸線上で挿脱するように移動させる構成
としてもよく、かかるもとでは、位相調整歯車が第１の
調整軸もしくは第２の調整軸に対して相対回転するよう
に構成できる。この場合、位相調整歯車を、直線運動を
回転運動に変換する第２の運動変換手段を介して第１の
調整軸及び第２の調整軸のいずれか一方に相対回転可能
に外嵌してもよく、さらに、上記第１び第２の運動変換
手段の両方を伴った構成としてもよい。In another aspect of the vibration generator according to the present invention, the phase adjustment shaft is divided into a first adjustment shaft and a second adjustment shaft having a two-part structure, and the first adjustment shaft is formed as a second adjustment shaft. A configuration in which relative movement and relative rotation are possible in the axial direction via first movement conversion means for converting a linear movement into a rotation movement with respect to the adjustment axis, and these are moved so as to be inserted and removed on the same axis. Under such circumstances, the phase adjustment gear may be configured to rotate relative to the first adjustment shaft or the second adjustment shaft. In this case, even if the phase adjustment gear is externally rotatably fitted to one of the first adjustment shaft and the second adjustment shaft via the second motion conversion means for converting the linear motion into the rotary motion. Further, the configuration may be such that both the first and second motion converting means are provided.
【００１１】さらに、本発明に係る振動発生装置の他の
別の態様としては、位相調整軸の外周部と上記位相調整
歯車の一方との間に流体作動室を形成し、該流体作動室
に対して流体の給排を行うことによりそれらが位相変更
手段として機能するようになし、もって上記位相調整歯
車を上記位相調整軸に対して相対回転させる構成として
もよい。この場合、流体作動室を位相調整軸に固定され
た固定仕切り壁部と位相調整歯車に固定された可動仕切
り壁部とで仕切り、流体作動室を回転型シリンダのよう
に構成できる。Further, as another mode of the vibration generating apparatus according to the present invention, a fluid working chamber is formed between an outer peripheral portion of a phase adjusting shaft and one of the phase adjusting gears, and the fluid working chamber is formed in the fluid working chamber. On the other hand, by supplying and discharging the fluid, they may function as phase changing means, and thus the phase adjustment gear may be rotated relatively to the phase adjustment shaft. In this case, the fluid working chamber is partitioned by a fixed partition wall fixed to the phase adjusting shaft and a movable partition wall fixed to the phase adjusting gear, and the fluid working chamber can be configured like a rotary cylinder.
【００１２】[0012]
【作用】上述の如くの構成を有する本発明に係る振動発
生装置においては、位相調整軸全体が軸方向に強制的に
移動せしめられることにより、もしくは、位相調整軸を
構成する第１の調整軸及び第２の調整軸の一方が他方に
対して軸方向に強制的に移動せしめられることにより、
あるいは、流体作動室に対して流体の給排が行われるこ
とにより、位相調整歯車が位相調整軸に対して相対回転
する。In the vibration generating apparatus according to the present invention having the above-described configuration, the entire phase adjusting shaft is forcibly moved in the axial direction, or the first adjusting shaft constituting the phase adjusting shaft. And one of the second adjustment axes is forcibly moved in the axial direction with respect to the other, so that
Alternatively, the supply and discharge of fluid to and from the fluid working chamber causes the phase adjustment gear to rotate relative to the phase adjustment shaft.
【００１３】そして、このように位相調整歯車が位相調
整軸に対して相対回転すると、位相調整歯車の回転が伝
達される第３の回転軸及び第４の回転軸上の偏心重錘が
位相固定歯車の回転が伝達される第１の回転軸及び第２
の回転軸上の偏心重錘に対して相対的に進められ又は遅
らされ、それらの偏心重錘の間に位相差が生じる。それ
により、各偏心重錘に発生する水平分力が常時相殺され
るのに対し、各偏心重錘に発生する垂直分力の合計値が
第１の回転軸及び第２の回転軸上の偏心重錘と第３の回
転軸及び第４の回転軸上の偏心重錘との間の位相差に応
じて変化せしめられ、その結果、各回転軸を介してケー
シング部材に与えられる起振力あるいは振幅が変化せし
められる。When the phase adjusting gear rotates relative to the phase adjusting shaft, the eccentric weights on the third rotating shaft and the fourth rotating shaft to which the rotation of the phase adjusting gear is transmitted are fixed in phase. A first rotation shaft to which rotation of the gear is transmitted and a second rotation shaft;
Are advanced or retarded relative to the eccentric weights on the axis of rotation, and a phase difference occurs between the eccentric weights. Thereby, while the horizontal component force generated in each eccentric weight is always canceled, the total value of the vertical component force generated in each eccentric weight is determined by the eccentricity on the first rotation axis and the second rotation axis. The weight is changed in accordance with the phase difference between the weight and the eccentric weight on the third rotary shaft and the fourth rotary shaft, and as a result, the vibrating force or the vibrating force applied to the casing member via each rotary shaft The amplitude is changed.
【００１４】[0014]
【実施例】以下、本発明の実施例を添付図面を参照しつ
つ説明する。 第１実施例：図１及び図２は本発明に係る振動発生装置
の第１実施例の主要部を示す斜視図及び展開図であり、
図３は図１及び図２に示される実施例の振動発生装置が
適用された振動杭打機の一例を示す正面図である。Embodiments of the present invention will be described below with reference to the accompanying drawings. First Embodiment FIGS. 1 and 2 are a perspective view and a development view, respectively, showing a main part of a first embodiment of a vibration generator according to the present invention.
FIG. 3 is a front view showing an example of a vibration pile driver to which the vibration generator of the embodiment shown in FIGS. 1 and 2 is applied.
【００１５】図３において、振動杭打機１は、クレーン
等の吊持手段のフック２が掛止される掛止部が設けられ
たハンガー５と、このハンガー５から垂下された４本の
ガイドロッド６及びそれに縮装された上下一対のコイル
スプリング８，９を有した緩衝装置７と、この緩衝装置
７を介してハンガー５に支持された、駆動源としての電
動モーター１４，ケーシング部材２０，ケーシング部材
２０内部に配置された起振力発生部，動力伝達用のベル
ト１７及びプーリー１８，１９等を備えた本実施例の振
動発生装置１０と、この振動発生装置１０の下側に設け
られた、鋼矢板等の杭を拘持するチャック１２等からな
っている。この振動杭打機１は、後記する起振力発生部
を除き従来公知のものであって、駆動源として電動モー
ターに限らず油圧モーター等任意の手段を用いることが
できるとともに、緩衝装置も図示のもの以外に適宜のも
のを用いうるものである。In FIG. 3, a vibrating pile driver 1 comprises a hanger 5 provided with a hook for hooking a hook 2 of a lifting means such as a crane, and four guides suspended from the hanger 5. A shock absorber 7 having a rod 6 and a pair of upper and lower coil springs 8 and 9 compressed therein, an electric motor 14 as a drive source supported by a hanger 5 via the shock absorber 7, a casing member 20, The vibration generator 10 of the present embodiment including a vibration generating unit, a power transmission belt 17, pulleys 18, 19, and the like disposed inside the casing member 20, and provided below the vibration generator 10. Further, it comprises a chuck 12 for holding a pile such as a steel sheet pile. This vibratory pile driving machine 1 is a conventionally known one except for a vibrating force generating unit described later. The driving source is not limited to an electric motor, and any means such as a hydraulic motor can be used. Other than those described above, appropriate ones can be used.
【００１６】ケーシング部材２０に設けられた起振力発
生部は、図１及び図２に詳細に示される如くに、第１の
回転軸２１と、この第１の回転軸２１の略真横にそれと
平行に配置され、電動モーター１４からの回転駆動力が
プーリー１９を介して伝達される第２の回転軸２２と、
これら第１及び第２の回転軸２１，２２の下方にそれら
と平行に配置された第３の回転軸２３及び第４の回転軸
２４と、これら第３及び第４の回転軸２３，２４の中間
位置の略真下にそれらと平行に配置された位相調整軸２
５と、を有している。As shown in detail in FIG. 1 and FIG. 2, the vibrating force generating portion provided on the casing member 20 includes a first rotating shaft 21 and the first rotating shaft 21 almost directly beside the first rotating shaft 21. A second rotating shaft 22 which is arranged in parallel and to which the rotational driving force from the electric motor 14 is transmitted via the pulley 19;
A third rotating shaft 23 and a fourth rotating shaft 24 disposed below and parallel to the first and second rotating shafts 21 and 22; A phase adjustment shaft 2 arranged substantially directly below and in parallel with the intermediate position
And 5.
【００１７】なお、この実施例では位相調整軸２５は第
３及び第４の回転軸２３，２４の下方に位置するものと
して示されているが、位相調整軸２５は各回転軸２１，
２２，２３，２４に対し平行でかつ回転可能に配置され
てさえいれば、その位置はその下方に限定されないこと
は明らかであろう。各回転軸２１〜２４は、図２に示さ
れる如く、その両端部がケーシング部材２０の側壁２０
ａ，２０ｂにベアリング２６，２７を介して軸支され、
各回転軸２１〜２４には、それぞれ第１の伝動歯車３
１，第２の伝動歯車３２，第３の伝動歯車３３，第４の
伝動歯車３４が外嵌されてキー４３により固定されてい
る。これら伝動歯車３１〜３４のうち、第１の回転軸２
１及び第２の回転軸２２上の伝動歯車３１，３２同士が
噛合せしめられるとともに、第３の回転軸２３及び第４
の回転軸２４上の伝動歯車３３，３４同士が噛合せしめ
られている。In this embodiment, the phase adjustment shaft 25 is shown as being located below the third and fourth rotation shafts 23, 24.
It will be clear that its position is not limited below it, as long as it is arranged parallel and rotatable with respect to 22, 23, 24. As shown in FIG. 2, each of the rotating shafts 21 to 24 has both ends at the side wall 20 of the casing member 20.
a, 20b via bearings 26, 27,
Each of the rotating shafts 21 to 24 has a first transmission gear 3
1, a second transmission gear 32, a third transmission gear 33, and a fourth transmission gear 34 are externally fitted and fixed by a key 43. Among these transmission gears 31 to 34, the first rotating shaft 2
The transmission gears 31 and 32 on the first and second rotating shafts 22 are engaged with each other, and the third rotating shaft 23 and the fourth
The transmission gears 33 and 34 on the rotary shaft 24 are meshed with each other.
【００１８】また、第３の回転軸２３には、上記第３の
伝動歯車３３に加えて、軸方向の移動は阻止された状態
で、後述する位相調整軸２５に固定された位相固定歯車
の回転を上記第２の回転軸２２上の第２の伝動歯車３２
に伝達する媒介歯車３７がベアリング４５を介して回転
可能に外嵌されている。さらに、第１の回転軸２１及び
第３の回転軸２３にはその中央部に偏心重錘５１Ｂ，５
２Ｂがスプライン２８により一体に外嵌固定され、ま
た、第２の回転軸２２及び第４の回転軸２４にはその両
端近傍に分割された偏心重錘５１Ａａ，５１Ａｂ（５１
Ａａと５１Ａｂとを合わせて符号５１Ａを用いる）及び
５２Ａａ，５２Ａｂ（５２Ａａと５２Ａｂとを合わせて
符号５２Ａを用いる）がスプライン２９により一体に外
嵌固定されている。The third rotating shaft 23 has, in addition to the third transmission gear 33, a phase-fixed gear fixed to a phase adjusting shaft 25, which will be described later, while being prevented from moving in the axial direction. The rotation is transmitted to the second transmission gear 32 on the second rotation shaft 22.
Gear 37 is rotatably fitted via a bearing 45. Further, the first rotating shaft 21 and the third rotating shaft 23 have eccentric weights 51B, 5B at their central portions.
2B is externally fitted and fixed integrally by a spline 28, and the eccentric weights 51Aa, 51Ab (51
Aa and 51Ab are combined and the reference numeral 51A is used, and 52Aa and 52Ab (the 52Aa and 52Ab are combined and the reference numeral 52A is used) are externally fitted and fixed integrally by the spline 29.
【００１９】なお、各回転軸２１〜２４と伝動歯車３１
〜３４及び偏心重錘５１Ａ，５２Ａ，５１Ｂ，５２Ｂと
の固定手段は、ここに示したように、キーやスプライン
による結合に限られるものではなく固定手段としての機
能を果たすものであればいかなる手段でもよいことは明
らかであろう。一方、位相調整軸２５の一端側には、そ
れを軸方向に移動させる駆動手段としての複動型で自動
ロック装置付のシリンダー５０がケーシング部材２０に
取り付けられて配されている。シリンダー５０から位相
調整軸２５への推進力の伝達は、シリンダー５０のピス
トンロッド先端に設けられた箱形連結部５５と位相調整
軸２５の一端に設けられたＴ形連結部５６との間に介装
された一対のスラストベアリング５８を介して行われる
ようにされている。なお、シリンダー５０にはその前後
の油室に外部から作動油を給排するための給排口６６，
６８が設けられている。The rotating shafts 21 to 24 and the transmission gear 31
As shown here, the fixing means to the ３４34 and the eccentric weights 51A, 52A, 51B, 52B is not limited to the connection by the key or the spline, but may be any means as long as it functions as the fixing means. It will be clear that this is acceptable. On the other hand, on one end side of the phase adjusting shaft 25, a double-acting cylinder 50 with an automatic locking device as a driving means for moving the phase adjusting shaft 25 in the axial direction is attached to the casing member 20 and disposed. The transmission of the propulsion force from the cylinder 50 to the phase adjustment shaft 25 is performed between a box-shaped connection portion 55 provided at the tip of the piston rod of the cylinder 50 and a T-shaped connection portion 56 provided at one end of the phase adjustment shaft 25. The operation is performed through a pair of interposed thrust bearings 58. The cylinder 50 has a supply / discharge port 66 for supplying / discharging hydraulic oil to / from the oil chambers before and after the cylinder 50 from outside.
68 are provided.
【００２０】また、位相調整軸２５の他端側には、位相
調整軸２３の移動量を制御するため、適宜の位置検出器
が配される。この実施例においては、ケーシング部材２
０にに取り付けられて、位相調整軸２５の他端に設けら
れた鉄心等が挿入されるようにされた差動変圧器式の位
置検出器６０が配されているが、ポテンションメータな
ども用いることも可能である。On the other end of the phase adjustment shaft 25, an appropriate position detector is disposed to control the amount of movement of the phase adjustment shaft 23. In this embodiment, the casing member 2
0, a differential transformer type position detector 60 in which an iron core or the like provided at the other end of the phase adjustment shaft 25 is inserted is provided. However, a potentiometer or the like is also provided. It is also possible to use.
【００２１】そして、上記位相調整軸２５には、その中
央より一端側寄りの外周部に比較的ゆるやかな旋回勾配
をもった螺旋状凹凸部５３が所定の旋回方向（右ねじ形
もしくは左ねじ形）をもって設けられ、また、その中央
より他端側寄りにスプライン５４が設けられている。こ
の位相調整軸２５に位相調整歯車３５と位相固定歯車３
６とが配されている。位相調整歯車３５及び位相固定歯
車３６はケーシング部材に付随して設けられたベアリン
グサドル３９，４０にベアリング４７，４８を介して回
転可能に支持されるも軸方向の移動を阻止された状態で
位相調整軸２５に外嵌されており、位相調整歯車３５
は、その内周部に位相調整軸２５設けられた螺旋状凹凸
部５３に摺動自在に嵌合する螺旋状凹凸部４６が設けら
れ、第３の回転軸２３上の第３の伝動歯車３３に噛合せ
しめられている。また、位相固定歯車３６にはその内周
部にスプライン状凹凸部４９が設けられていてそれが位
相調整軸２５に設けられたスプライン５４に外嵌固定さ
れ、第３の回転軸２３上の媒介歯車３７に噛合せしめら
れている。The phase adjusting shaft 25 is provided with a spiral concave / convex portion 53 having a relatively gentle turning gradient on the outer peripheral portion closer to one end side from the center thereof in a predetermined turning direction (right-handed screw type or left-handed screw type). ), And a spline 54 is provided closer to the other end than the center. The phase adjustment gear 35 and the phase-fixed gear 3
6 are arranged. The phase adjusting gear 35 and the phase fixing gear 36 are rotatably supported via bearings 47 and 48 on bearing saddles 39 and 40 provided in association with the casing member, but are prevented from moving in the axial direction. The phase adjustment gear 35 which is externally fitted to the adjustment shaft 25
Is provided with a spiral uneven portion 46 slidably fitted on a spiral uneven portion 53 provided on the inner surface of the phase adjusting shaft 25, and a third transmission gear 33 on the third rotary shaft 23. It is bitten by. Further, a spline-shaped uneven portion 49 is provided on the inner peripheral portion of the phase fixing gear 36, and the spline-shaped uneven portion 49 is externally fitted and fixed to a spline 54 provided on the phase adjusting shaft 25. It is meshed with the gear 37.
【００２２】なお、上述の偏心重錘５１Ａ，５２Ａ，５
１Ｂ，５２Ｂは、一例として、それぞれ中心角が１８０
°の概略扇形（半円形）であり、偏心重錘５１Ａ，５２
Ａの一つの厚みは偏心重錘５１Ｂ，５２Ｂの約半分とさ
れており、偏心重錘５１Ａ，５２Ａと偏心重錘５１Ｂ，
５２Ｂとは、偏心モーメントが同一となるようにそれら
の重量及び形状が定められるとともに、左右方向おいて
釣り合いがとれるように位置決めがなされている。The above eccentric weights 51A, 52A, 5
1B and 52B each have a center angle of 180, for example.
°, a substantially fan-shaped (semicircular) eccentric weight 51A, 52
One thickness of A is about half of the eccentric weights 51B and 52B, and the eccentric weights 51A and 52A and the eccentric weight 51B,
52B has its weight and shape determined so that the eccentric moments are the same, and is positioned so as to be balanced in the left-right direction.
【００２３】本実施例では、上述の如くに偏心重錘５１
Ａ，５２Ａ，５１Ｂ，５２Ｂの配置及び形状が設定され
ることにより、各伝動歯車３１〜３４の回転半径は偏心
重錘５１Ａ，５２Ａ，５１Ｂ，５２Ｂの回転半径より小
さくすることが可能となり、それによって、各回転軸２
１〜２４の離間距離を小さくすることができ、装置のコ
ンパクト化が図られる。In this embodiment, as described above, the eccentric weight 51
By setting the arrangement and shape of A, 52A, 51B, 52B, the turning radius of each transmission gear 31-34 can be made smaller than the turning radius of eccentric weights 51A, 52A, 51B, 52B. By each rotation axis 2
The distance between 1 to 24 can be reduced, and the device can be made compact.
【００２４】しかしながら、偏心重錘５１Ａ，５２Ａ，
５１Ｂ，５２Ｂの形状、厚み、配置などは、上記したも
のに限るものではなく、偏心モーメントが同一となるよ
うに、また、左右方向おいて釣り合いがとれるようにそ
れらの重量及び形状及び位置決めがなされればよいもの
であることはもちろんである。また、各歯車３１〜３６
の歯数等の諸元は同一で噛合状態においては等速回転す
るようにされている。However, the eccentric weights 51A, 52A,
The shapes, thicknesses, arrangements, and the like of the 51B and 52B are not limited to those described above, and their weights, shapes, and positioning are made so that the eccentric moments are the same, and are balanced in the left-right direction. Needless to say, it is only necessary. In addition, each gear 31-36
The number of teeth and the like are the same, and they rotate at a constant speed in the meshing state.
【００２５】上述の如くの構成を有する本実施例の振動
発生装置１０においては、モーター１４の回転駆動力が
ベルト１７を介してプーリー１９から第２の回転軸２２
→第２の伝動歯車３２→第１の伝動歯車３１及び媒介歯
車３７→位相固定歯車３６→位相調整軸２５→螺旋状凹
凸部５３，４６→位相調整歯車３５に順次伝達され、第
１の回転軸２１，第２の回転軸２２及び位相調整軸２５
が同期して回転するとともに、位相調整軸２３の回転が
位相調整歯車３５→第３の伝動歯車３３及び第３の回転
軸２３→第４の伝動歯車３４及び第４の回転軸２４に順
次伝達される。In the vibration generator 10 of the present embodiment having the above-described configuration, the rotational driving force of the motor 14 is transmitted from the pulley 19 via the belt 17 to the second rotary shaft 22.
→ The second transmission gear 32 → the first transmission gear 31 and the intermediate gear 37 → the phase fixing gear 36 → the phase adjustment shaft 25 → the spiral concave / convex portions 53 and 46 → the power is sequentially transmitted to the phase adjustment gear 35 to perform the first rotation. Shaft 21, second rotating shaft 22, and phase adjusting shaft 25
Rotate synchronously, and the rotation of the phase adjustment shaft 23 is sequentially transmitted to the phase adjustment gear 35 → the third transmission gear 33 and the third rotation shaft 23 → the fourth transmission gear 34 and the fourth rotation shaft 24. Is done.
【００２６】ここで、シリンダー５０により位相調整軸
２５を軸方向に強制的に移動させると、この位相調整軸
２５の外周部に設けられた螺旋状凹凸部５３と位相調整
歯車３５の内周部に設けられた螺旋状凹凸部４６とが嵌
合しているので、位相調整歯車３５が螺旋状凹凸部５３
の周方向分力によって位相調整軸２３の移動距離に応じ
て位相固定歯車３６に対して相対回転し、その位相が進
められ又は遅らされ、かかる状態で位相調整歯車３５が
位相調整軸２３と一体に回転する。Here, when the phase adjusting shaft 25 is forcibly moved in the axial direction by the cylinder 50, the spiral uneven portion 53 provided on the outer peripheral portion of the phase adjusting shaft 25 and the inner peripheral portion of the phase adjusting gear 35 are provided. Is fitted with the spiral uneven portion 46 provided on the helical uneven portion 53.
Is rotated relative to the phase-locking gear 36 in accordance with the moving distance of the phase adjustment shaft 23 by the circumferential component force of the phase adjustment shaft 23, and its phase is advanced or delayed, and in this state, the phase adjustment gear 35 They rotate together.
【００２７】そして、このように位相調整歯車３５の位
相が位相固定歯車３６に対して変化すると、第３及び第
４の回転軸２３，２４とそれに取り付けられた偏心重錘
５２Ｂ，５２Ａの位相が第１及び第２の回転軸に取り付
けられた偏心重錘５１Ｂ，５１Ａに対して同角度ずつ変
化する。それにより、各回転軸２１〜２４を介してケー
シング部材２０に与えられる起振力あるいは振幅が変化
せしめられる。When the phase of the phase adjusting gear 35 changes with respect to the phase fixed gear 36, the phases of the third and fourth rotating shafts 23 and 24 and the eccentric weights 52B and 52A attached thereto are changed. The eccentric weights 51B and 51A attached to the first and second rotating shafts change by the same angle. Thereby, the vibrating force or the amplitude applied to the casing member 20 via each of the rotating shafts 21 to 24 is changed.
【００２８】この場合、各回転軸２１〜２４に取り付け
られた偏心重錘５１Ａ，５２Ａ，５１Ｂ，５２Ｂに発生
する遠心力の水平分力が相殺されるとともに、遠心力の
垂直分力が相加され、この垂直分力によりケーシング部
材２０に上下方向の起振力あるいは振幅が与えられる。
そして、いま、図４Ａに示される如くに、偏心重錘５１
Ａ，５１Ｂと偏心重錘５２Ａ，５２Ｂの位相差θが１８
０°とされている場合には、図５Ａにおいて曲線ａ，ｂ
で示される如く、それらから得られる起振力あるいは振
幅は互いに相殺されて０となる。それに対し、位相調整
軸２５を移動させて位相調整歯車３５を位相固定歯車３
６に対して１８０°回転させると、図４Ｃに示される如
く、偏心重錘５１Ａ，５１Ｂと偏心重錘５２Ａ，５２Ｂ
の位相差θは０となり、図５Ｃに示される如く、一方の
偏心重錘だけで得られる起振力あるいは振幅の和として
の量、すなわち、一方の偏心重錘だけで得られる量の２
倍の起振力あるいは振幅（図５Ｃにおいて破線ｃで示さ
れている）が得られる。なお、図４Ｂは、位相差θが上
述の図４Ａと図４Ｃの中間の９０°の場合を示してお
り、図４Ａ、Ｃの場合と同様に起振力あるいは振幅の和
として、図５Ｂにおいてｃで示される量の起振力あるい
は振幅が得られる。In this case, the horizontal component of the centrifugal force generated in the eccentric weights 51A, 52A, 51B, 52B attached to each of the rotary shafts 21 to 24 is canceled, and the vertical component of the centrifugal force is added. The vertical component force gives the casing member 20 a vertical vibrating force or amplitude.
And now, as shown in FIG.
A, 51B and the phase difference θ between the eccentric weights 52A, 52B are 18
If it is 0 °, curves a and b in FIG.
As shown by the above, the vibrating forces or amplitudes obtained from them cancel each other out and become zero. On the other hand, the phase adjustment shaft 35 is moved to move the phase adjustment gear 35 to the phase-fixed gear 3.
6, the eccentric weights 51A and 51B and the eccentric weights 52A and 52B as shown in FIG.
Is 0, and as shown in FIG. 5C, the amount as the sum of the vibrating force or the amplitude obtained by only one eccentric weight, that is, the amount obtained by only one eccentric weight, 2
A double excitation force or amplitude (indicated by dashed line c in FIG. 5C) is obtained. FIG. 4B shows a case where the phase difference θ is 90 ° between the above-mentioned FIGS. 4A and 4C, and as in FIGS. 4A and 4C, the sum of the vibrating force or the amplitude is shown in FIG. 5B. The amount of vibrating force or amplitude indicated by c is obtained.
【００２９】従って、例えば、振動発生装置１０の起動
時においては、偏心重錘５１Ａ，５２Ｂと偏心重錘５２
Ａ，５２Ｂとの位相差θを図４Ａに示される如くに１８
０°にしておけば、釣り合いのとれたフライホイールを
起動する場合と同様な状態となり、起動後電動モーター
１４が定格回転速度に達するまでの期間にそれらの位相
差θを１８０°から０に徐々に減少させるように位相調
整軸２３を移動させれば、大なる駆動力を必要とせずに
各偏心重錘を円滑に回転させることが可能となり、その
ため、電動モーター１４は小型のもので充分にその役目
を果たすことができ、省エネルギー化が図られることに
なる。Therefore, for example, when the vibration generator 10 is started, the eccentric weights 51A and 52B and the eccentric weight 52
A, 52B, as shown in FIG.
If the angle is set to 0 °, the state becomes the same as when a balanced flywheel is started, and the phase difference θ is gradually reduced from 180 ° to 0 during the period after the start until the electric motor 14 reaches the rated rotation speed. If the phase adjustment shaft 23 is moved so as to reduce it, the eccentric weights can be smoothly rotated without requiring a large driving force. That role can be fulfilled, and energy can be saved.
【００３０】なお、上述の例においては、起振力を発生
させる動力源として電動モータを用いたものを示した
が、動力源としてはこれに限るものではなく油圧モータ
なども用いることができる。さらに、位相調整軸２５の
駆動手段としてシリンダー５０が用いられているが、そ
れに代えて、例えば、モーター，ウオームギヤ，推力軸
等から構成される駆動手段等を用いてもよい。In the above example, an electric motor is used as the power source for generating the vibrating force. However, the power source is not limited to this, and a hydraulic motor or the like may be used. Further, although the cylinder 50 is used as a driving means of the phase adjustment shaft 25, a driving means including a motor, a worm gear, a thrust shaft, and the like may be used instead.
【００３１】さらになお、各偏心重錘や歯車の配置、ま
た、各回転軸２１〜２３や位相調整軸２３の配置は適宜
変更できること勿論である。この場合、例えば、位相調
整軸２５を第１及び第２の回転軸２１，２２と第３及び
第４の回転軸２３，２４との間に配置することにより、
図６の展開図で示される如くに、位相固定歯車３６を直
接第２の伝動歯車３２に噛合させることができ、従っ
て、かかる場合には図２に示される媒介歯車３７を用い
ることなく、上述の例と略同様な作用効果が得られる。Further, the arrangement of the eccentric weights and gears, and the arrangement of the rotating shafts 21 to 23 and the phase adjusting shaft 23 can be changed as appropriate. In this case, for example, by disposing the phase adjustment shaft 25 between the first and second rotation shafts 21 and 22 and the third and fourth rotation shafts 23 and 24,
As shown in the developed view of FIG. 6, the phase locked gear 36 can be directly meshed with the second transmission gear 32, and thus, in such a case, without using the intermediate gear 37 shown in FIG. The same operation and effect as those of the example can be obtained.
【００３２】実施例２：図７は本発明に係る振動発生装
置の第２実施例の主要部を示す断面図であり、図８はそ
の部分切り欠き斜視図である。この第２実施例は、上述
の第１実施例における位相調整軸２５に相当する部分が
２分割構成の第１の調整軸７１及び第２の調整軸７２か
らなる位相調整軸７０とされており、この位相調整軸７
０とその周辺部以外は上述の第１実施例と共通であるか
らかかる部分には共通の符号を付してそれらの重複説明
を省略する。Embodiment 2 FIG. 7 is a sectional view showing a main part of a second embodiment of the vibration generator according to the present invention, and FIG. 8 is a partially cutaway perspective view thereof. In the second embodiment, a portion corresponding to the phase adjustment shaft 25 in the first embodiment is a phase adjustment shaft 70 including a first adjustment shaft 71 and a second adjustment shaft 72 having a two-part structure. , This phase adjusting shaft 7
The parts other than 0 and its peripheral parts are the same as those in the first embodiment described above.
【００３３】位相調整軸７０を構成する第１の調整軸７
１及び第２の調整軸７２のうちの第１の調整軸７１は、
図７及び図８に詳細に示される如くに管状軸とされ、そ
の外周部に軸方向に真っ直ぐに伸びるスプライン７８が
形成され、その内周部に第１の螺旋状凹凸部７３が刻設
されており、その一端側は、後述の油圧シリンダ５０の
ピストンロッド６５の先端にベアリング６９を介して回
転可能な状態でかつ軸方向の相対移動は阻止された状態
で連結されている。また、第２の調整軸７２は、一端側
の外周部に上記第１の螺旋状凹凸部７３に嵌合する第２
の螺旋状凹凸部７４が刻設され、この第２の螺旋状凹凸
部７４部分において第１の調整軸７１に連結され、他端
がベアリング４２を介してケーシング部材の側壁２０ｂ
に回転可能に支持されている。First adjustment shaft 7 constituting phase adjustment shaft 70
The first adjustment shaft 71 of the first and second adjustment shafts 72 is
As shown in detail in FIGS. 7 and 8, a tubular shaft is formed, a spline 78 extending straight in the axial direction is formed on an outer peripheral portion thereof, and a first spiral uneven portion 73 is engraved on an inner peripheral portion thereof. One end thereof is connected to a distal end of a piston rod 65 of the hydraulic cylinder 50 described later via a bearing 69 in a rotatable state and in a state where relative movement in the axial direction is prevented. The second adjustment shaft 72 has a second spiral fitting portion 73 fitted on the outer peripheral portion on one end side.
Of the casing member is connected to the first adjustment shaft 71 at the portion of the second spiral uneven portion 74, and the other end thereof is connected to the side wall 20b of the casing member via the bearing 42.
It is supported rotatably.
【００３４】上述の第１の調整軸７１を軸方向にに移動
させる駆動手段としての、複動型で自動ロック装置付の
油圧シリンダ５０がケーシング部材２０に付随して設け
られた壁部２０ｃに取り付けられている。油圧シリンダ
５０は外部に配置された油圧ユニットからの作動油を給
排するための給排口６６，６８を有し、作動油の給排量
に応じてそのピストンロッド６５を進退させるようにさ
れ、このピストンロッド６５の移動量を制御するため、
図示はされていないが、例えば、差動変圧器式等の位置
検出器が配されている。A double-acting hydraulic cylinder 50 with an automatic locking device as a driving means for moving the above-mentioned first adjusting shaft 71 in the axial direction is provided on a wall 20 c provided with the casing member 20. Installed. The hydraulic cylinder 50 has supply and discharge ports 66 and 68 for supplying and discharging hydraulic oil from a hydraulic unit disposed outside, and the piston rod 65 is advanced and retracted according to the supply and discharge amount of hydraulic oil. In order to control the amount of movement of the piston rod 65,
Although not shown, for example, a position detector such as a differential transformer type is provided.
【００３５】そして、上記第１の調整軸７１の外周側に
は、第３の伝動歯車３３に噛合する位相調整歯車３５が
スプライン７８に結合されて外嵌され、また、上記第２
の調整軸７２の外周側には、第２の伝動歯車３２に噛合
する位相固定歯車３６がキー７７により固定されてい
る。上述の如くの構成を有する本実施例の振動発生装置
１０においては、モーター１４の回転駆動力がベルト１
７を介して第２の回転軸２２→第２の伝動歯車３２→第
１の伝動歯車３２及び媒介歯車３７→位相固定歯車３６
→第２の調整軸７２→第２及び第１の螺旋状凹凸部７
４，７３→第１の調整軸７１→位相調整歯車３５に順次
伝達され、第１の回転軸２１，第２の回転軸２２及び位
相調整軸７０（第１の調整軸７１及び第２の調整軸７
２）が同期して回転するとともに、位相調整軸７０の回
転が位相調整歯車３５→第３の伝動歯車３３及び第３の
回転軸２３→第４の伝動歯車３４及び第４の回転軸２４
に順次伝達される。On the outer peripheral side of the first adjusting shaft 71, a phase adjusting gear 35 that meshes with the third transmission gear 33 is connected to a spline 78 and externally fitted thereto.
A phase fixing gear 36 meshing with the second transmission gear 32 is fixed to the outer peripheral side of the adjustment shaft 72 by a key 77. In the vibration generator 10 of the present embodiment having the above-described configuration, the rotational driving force of the motor 14 is
7, the second rotation shaft 22 → the second transmission gear 32 → the first transmission gear 32 and the intermediate gear 37 → the phase-fixed gear 36.
→ second adjustment shaft 72 → second and first spiral uneven portions 7
4, 73 → the first adjustment shaft 71 → the phase adjustment gear 35, and are sequentially transmitted to the first rotation shaft 21, the second rotation shaft 22 and the phase adjustment shaft 70 (the first adjustment shaft 71 and the second adjustment shaft). Axis 7
2) rotates in synchronization with the rotation of the phase adjustment shaft 70, and the rotation of the phase adjustment shaft 70 → the third transmission gear 33 and the third rotation shaft 23 → the fourth transmission gear 34 and the fourth rotation shaft 24
Are sequentially transmitted.
【００３６】ここで、油圧シリンダー５０により第１の
調整軸７１を軸方向に強制的に移動させると、この第１
の調整軸７１の内周部に刻設された第１の螺旋状凹凸部
７３と第２の調整軸７２の外周部に刻設された第２の螺
旋状凹凸部７４とが嵌合しているので、第１の調整軸７
１と第２の調整軸７２とが、螺旋状凹凸部７３及び７４
の周方向分力によって第１の調整軸７１の移動距離に応
じて相対回転し、第１の調整軸７１上の位相調整歯車３
５の位相が第２の調整軸７２上の固定位相歯車３６に対
して進められ又は遅らされ、かかる状態で位相調整歯車
３５及び位相固定歯車３６が位相調整軸７０と一体に回
転する。Here, when the first adjustment shaft 71 is forcibly moved in the axial direction by the hydraulic cylinder 50,
The first spiral uneven portion 73 formed on the inner peripheral portion of the adjustment shaft 71 and the second spiral uneven portion 74 formed on the outer peripheral portion of the second adjustment shaft 72 are fitted to each other. The first adjustment shaft 7
The first and second adjustment shafts 72 are spirally uneven portions 73 and 74.
Relative rotation according to the moving distance of the first adjustment shaft 71 due to the circumferential component force of the phase adjustment gear 3 on the first adjustment shaft 71.
The phase of No. 5 is advanced or delayed with respect to the fixed phase gear 36 on the second adjustment shaft 72, and in this state, the phase adjustment gear 35 and the phase fixed gear 36 rotate integrally with the phase adjustment shaft 70.
【００３７】そして、このように位相調整歯車３５と固
定位相歯車３６との間に位相差が生じると、第１及び第
２の回転軸２１，２２に対して第３及び第４の回転軸２
３，２４が相対回転し、第１及び第２の回転軸２１，２
２に取り付けられた偏心重錘５１Ｂ，５１Ａと第３及び
第４の回転軸２１，２２に取り付けられた偏心重錘５２
Ｂ，５２Ａとの間に位相差が発生し、それにより、各回
転軸２１〜２４を介してケーシング部材２０に与えられ
る起振力あるいは振幅が変化せしめられ、上述の第１実
施例と同様な作用効果が得られる。When a phase difference occurs between the phase adjusting gear 35 and the fixed phase gear 36 in this manner, the third and fourth rotating shafts 2 and 22 are moved relative to the first and second rotating shafts 21 and 22.
3 and 24 rotate relative to each other, and the first and second rotation shafts 21 and
2 and the eccentric weights 52 attached to the third and fourth rotating shafts 21 and 22.
A phase difference is generated between B and 52A, whereby the vibrating force or amplitude applied to the casing member 20 via each of the rotating shafts 21 to 24 is changed, and the same as in the first embodiment described above. An effect can be obtained.
【００３８】以上の説明において、上述の実施例におい
ては位相調整歯車３５及び位相固定歯車３６に位相差を
与えるべく、直線運動を回転運動に変換する第１の運動
変換手段として、第１の調整軸７１の内周部に第１の螺
旋状凹凸部７３を刻設するとともに、第２の調整軸７２
の外周部に上記第１の螺旋状凹凸部７３に嵌合する第２
の螺旋状凹凸部７４を刻設したものを示したが、位相調
整歯車３５及び位相固定歯車３６に位相差を与えるため
の手段はこれに限るものではない。In the above description, in the above embodiment, the first adjustment means is used as the first motion converting means for converting the linear motion into the rotary motion so as to give a phase difference to the phase adjusting gear 35 and the phase fixed gear 36. A first spiral uneven portion 73 is engraved on the inner peripheral portion of the shaft 71, and a second adjustment shaft 72 is formed.
The second spiral fitting portion 73 is fitted to the outer peripheral portion of the first spiral uneven portion 73.
Is shown, but the means for giving a phase difference to the phase adjusting gear 35 and the phase fixing gear 36 is not limited to this.
【００３９】他の態様として、図９及び図１０に示され
る如くに、第１の螺旋状凹凸部７３が刻設された第１の
調整軸７１および外周部に上記第１の螺旋状凹凸部７３
に嵌合する第２の螺旋状凹凸部７４が刻設された第２の
調整軸７２を用い、さらに、直線運動を回転運動に変換
する第２の運動変換手段として、第１の調整軸７１の外
周部に、その内周部に形成された第１の螺旋状凹凸部７
３と逆位相の第３の螺旋状凹凸部７５を刻設し、さらに
第１の調整軸７１に外嵌される第１の位相調整歯車３５
の内周部に第１の調整軸７１の外周部に刻設された第３
の螺旋状凹凸部７５に嵌合する第４の螺旋状凹凸部７６
を形成するようにしてもよい。この場合には、逆位相を
持つ２重の送り手段により位相調整歯車３５及び位相固
定歯車３６に位相差が与えられるため、上記第１の調整
軸７１及び第２の調整軸７２の少なくとも一方の軸方向
の移動量を１／２で済ますことが可能となる。As another embodiment, as shown in FIGS. 9 and 10, a first adjusting shaft 71 having a first spiral uneven portion 73 engraved thereon and the first spiral uneven portion formed on an outer peripheral portion thereof. 73
A second adjustment shaft 72 provided with a second spiral uneven portion 74 fitted to the first adjustment shaft 72 is further used as a second motion conversion means for converting a linear motion into a rotary motion. The first spiral uneven portion 7 formed on the outer peripheral portion of the
A third spiral uneven portion 75 having a phase opposite to that of the third phase adjusting gear 71 is further engraved, and a first phase adjusting gear 35 fitted externally to the first adjusting shaft 71 is also provided.
The third engraved on the outer periphery of the first adjustment shaft 71 on the inner periphery of
Of the fourth spiral uneven portion 76 fitted into the spiral uneven portion 75
May be formed. In this case, since a phase difference is given to the phase adjusting gear 35 and the phase fixing gear 36 by the double feeding means having the opposite phase, at least one of the first adjusting shaft 71 and the second adjusting shaft 72 is provided. The amount of movement in the axial direction can be reduced to half.
【００４０】さらに他の態様としては、上述の第１の運
動変換手段を設けないで、第１の調整軸７１と第２の調
整軸とを例えば軸方向に相対移動可能なスプライン結合
により連結し、第２の運動変換手段のみで一対の位相調
整歯車３５、３６に位相差を与えるようにしてもよい。 実施例３：図１１及び図１２は本発明に係る振動発生装
置の第３実施例の主要部を示す一部破断正面図及び斜視
図である。In still another embodiment, the first adjustment shaft 71 and the second adjustment shaft are connected by, for example, an axially movable spline connection without providing the above-described first motion conversion means. Alternatively, a phase difference may be given to the pair of phase adjusting gears 35 and 36 only by the second motion converting means. Third Embodiment FIGS. 11 and 12 are a partially cutaway front view and a perspective view showing a main part of a third embodiment of the vibration generator according to the present invention.
【００４１】この第３実施例においても、上述の第１実
施例及び第２実施例の各部に対応する部分には共通の符
号を付してその重複説明を省略する。この実施例の位相
調整軸９０も、第３及び第４の回転軸２３，２４の下方
にそれらと平行でかつその両端部がベアリング６９，４
７を介して側壁２０ａ，２０ｂに回転可能な状態でかつ
軸方向の相対移動は阻止された状態で軸支されており、
その内部には図１１及び図１３に詳細に示される如くに
２本の油圧通路９１，９２が形成され、その一端部に
は、シール材６７，スペーサ４８を介してカバー部材４
９が被せられている。スペーサ４８及びカバー部材４９
には、上記油圧通路９１，９２に連通する給排通路９
３，９４ が形成されるとともに、その後端にはドレー
ン通路７９が接続されている。上記給排通路９３，９４
には、外部に設置された油圧ユニットからの作動油が切
り換え弁等が介装された配管系を介して給排され、その
作動油は上記油圧通路９１，９２を通じて後述する油圧
作動室１００に供給され、またそこから排出される。Also in this third embodiment, parts corresponding to the respective parts of the above-described first and second embodiments are denoted by the same reference numerals, and redundant description is omitted. The phase adjusting shaft 90 of this embodiment is also provided below the third and fourth rotating shafts 23 and 24 in parallel with the bearings 69 and 4 at both ends.
7, and is rotatably supported by the side walls 20a and 20b in a state where relative movement in the axial direction is prevented.
As shown in detail in FIGS. 11 and 13, two hydraulic passages 91 and 92 are formed therein, and one end thereof has a cover member 4 via a seal member 67 and a spacer 48.
9 is covered. Spacer 48 and cover member 49
Is provided with a supply / discharge passage 9 communicating with the hydraulic passages 91 and 92.
3, 94 are formed, and a drain passage 79 is connected to the rear end. The supply / discharge passages 93, 94
The hydraulic oil is supplied and discharged from a hydraulic unit installed outside through a piping system provided with a switching valve and the like, and the hydraulic oil is supplied to a hydraulic operating chamber 100 described later through the hydraulic passages 91 and 92. It is supplied and discharged therefrom.
【００４２】そして、この位相調整軸９０には、第２の
伝動歯車３２に噛合する位相固定歯車３６がキー７７に
より外嵌固定されるとともに、第３の伝動歯車３３に噛
合する位相調整歯車３５が軸方向の移動を阻止された状
態で外嵌されている。位相調整歯車３５は位相調整軸９
０に対して相対回転可能とされ、その一側部には、図１
１及び図１２に詳細に示される如くに、作動室形成部材
９９が結合され、この作動室形成部材９９内には、位相
調整軸９０の外周と位相調整歯車３５の側部とで包囲さ
れたスリーブ状の油圧作動室１００が形成されている。
油圧作動室１００は、適宜のシール材等により密封され
ており、その内部は、図１３に詳細に示される如くに、
位相調整軸９０にピン１１及びボルト１３によって固定
された固定仕切り壁部９５と位相調整歯車３５にボルト
１５によって固定された可動仕切り壁部９６とで第１作
動室１０１と第２作動室１０２とに仕切られている。第
１作動室１０１の固定仕切り壁部９５側端には油圧通路
９１の一端が開口し、第２作動室１０２の固定仕切り壁
部９５側端には油圧通路９２の一端が開口している。A phase fixing gear 36 meshing with the second transmission gear 32 is externally fitted and fixed to the phase adjustment shaft 90 by a key 77, and a phase adjustment gear 35 meshing with the third transmission gear 33. Are fitted outside in a state where movement in the axial direction is prevented. The phase adjustment gear 35 is connected to the phase adjustment shaft 9.
0 is rotatable relative to 0.
As shown in detail in FIGS. 1 and 12, a working chamber forming member 99 is connected, and is surrounded by the outer periphery of the phase adjusting shaft 90 and the side of the phase adjusting gear 35 in the working chamber forming member 99. A sleeve-shaped hydraulic working chamber 100 is formed.
The hydraulic working chamber 100 is sealed with a suitable sealing material or the like, and the inside thereof is, as shown in detail in FIG.
The first working chamber 101 and the second working chamber 102 include a fixed partition wall 95 fixed to the phase adjusting shaft 90 by the pins 11 and the bolts 13 and a movable partition wall 96 fixed to the phase adjusting gear 35 by the bolts 15. It is divided into. One end of a hydraulic passage 91 is open at an end of the first working chamber 101 on the fixed partition wall 95 side, and one end of a hydraulic passage 92 is open at an end of the second working chamber 102 on the fixed partition wall 95 side.
【００４３】上述の如くの構成を有する本実施例の振動
発生装置１０においては、油圧ユニットからの作動油が
油圧通路９１，９２を介して油圧作動室内に充満されて
いる状態では、モーター１４の回転駆動力がベルト１７
を介して第２の回転軸２２→第２の伝動歯車３２→第１
の伝動歯車３１及び媒介歯車３７→位相固定歯車３６を
順次介して位相調整軸９０に伝達され、第１の回転軸２
１，第２の回転軸２２及び位相調整軸９０が同期して回
転するとともに、位相調整軸９０の回転が油圧作動室１
００→位相調整歯車３５→第３の伝動歯車３３→第４の
伝動歯車３４に順次伝達される。In the vibration generator 10 of the present embodiment having the above-described configuration, when the hydraulic oil from the hydraulic unit is filled in the hydraulic working chamber through the hydraulic passages 91 and 92, the motor 14 The rotational driving force is belt 17
Through the second rotation shaft 22 → the second transmission gear 32 → the first
Are transmitted to the phase adjusting shaft 90 via the transmission gear 31 and the intermediate gear 37 → the phase-fixed gear 36 in sequence, and the first rotating shaft 2
1, the second rotation shaft 22 and the phase adjustment shaft 90 rotate synchronously, and the rotation of the phase adjustment shaft 90
00 → the phase adjusting gear 35 → the third transmission gear 33 → the fourth transmission gear 34.
【００４４】ここで、油圧配管系の弁位置を切り換えて
例えば油圧通路９１を通じて第１作動室１０１から作動
油を排出するとともに第２作動室１０２に油圧通路９２
を通じて作動油を供給すると、可動仕切り壁部９６が位
相調整軸９０の回りを位相調整歯車３５を伴って回動す
る（例えば図１８Ａに示される状態から図１８Ｂに示さ
れる状態に）。そのため、位相調整歯車３５が位相固定
歯車３６に対して相対回転し、それらの間に位相差が生
じ、かかる状態で位相調整歯車３５，位相固定歯車３６
が位相調整軸９０と一体に回転する。Here, the valve position of the hydraulic piping system is switched to discharge hydraulic oil from the first working chamber 101 through, for example, the hydraulic passage 91 and to connect the hydraulic passage 92 to the second working chamber 102.
When the operating oil is supplied through the, the movable partition wall portion 96 rotates around the phase adjusting shaft 90 with the phase adjusting gear 35 (for example, from the state shown in FIG. 18A to the state shown in FIG. 18B). Therefore, the phase adjustment gear 35 rotates relative to the phase-fixed gear 36, and a phase difference occurs between them. In this state, the phase adjustment gear 35 and the phase-fixed gear 36
Rotate integrally with the phase adjustment shaft 90.
【００４５】そして、このように位相調整歯車３５及び
位相調整歯車３６との間に位相差が生じると、第１及び
第２の回転軸２１，２２に取り付けられた偏心重錘５１
Ｂ，５１Ａと第３及び第４の回転軸２３，２４に結合さ
れた第３及び第４の偏心重錘５２Ａ，５２Ｂとの間に位
相差が発生し、それにより、各回転軸２１〜２４を介し
てケーシング部材２０に与えられる起振力あるいは振幅
が変化せしめられ、上述の実施例と同様な作用効果が得
られる。When a phase difference is generated between the phase adjusting gear 35 and the phase adjusting gear 36 in this manner, the eccentric weight 51 attached to the first and second rotating shafts 21 and 22 will be described.
B, 51A and the third and fourth eccentric weights 52A, 52B coupled to the third and fourth rotating shafts 23, 24, respectively, and a phase difference is generated between the eccentric weights 52A, 52B. Thus, the vibrating force or amplitude applied to the casing member 20 is changed, and the same operation and effect as in the above embodiment can be obtained.
【００４６】[0046]
【発明の効果】以上の説明から明らかな如く、本発明に
係る振動発生装置によれば、位相調整軸が軸方向に強制
的に移動せしめられることにより、あるいは、第１の調
整軸に対して第２の調整軸が軸方向に強制的に移動せし
められることにより、もしくは、流体作動室に対する流
体の給排がおこなわれることにより、位相調整歯車が位
相調整軸に対して相対回転し、位相調整歯車と位相固定
歯車との間に位相差が生じた状態で位相調整軸と一体に
回転するので、位相調整歯車及び固定位相歯車うちの一
方の回転が伝達される第１及び第２の回転軸に取り付け
られた偏心重錘と、それらの他方の回転が伝達される第
３及び第４の回転軸に結合された偏心重錘との間に位相
差が生じ、それにより、各偏心重錘に発生する水平分力
が常時相殺されるのに対し、各偏心重錘に発生する垂直
分力の合計値が偏心重錘間の位相差に応じて変化せしめ
られ、その結果、各回転軸を介してケーシング部材に与
えられる起振力が変化せしめられるので、運転時におい
ても起振力を任意にかつ無段階に変えることができ、し
かも、構造が極めて簡素かつ合理的で容易に製作できる
利点が得られる。As is apparent from the above description, according to the vibration generator according to the present invention, the phase adjusting shaft is forcibly moved in the axial direction, or the phase adjusting shaft is moved with respect to the first adjusting shaft. When the second adjustment shaft is forcibly moved in the axial direction, or when the fluid is supplied to and discharged from the fluid working chamber, the phase adjustment gear relatively rotates with respect to the phase adjustment shaft, and the phase adjustment is performed. The first and second rotating shafts to which the rotation of one of the phase adjustment gear and the fixed phase gear is transmitted, since the rotation rotates integrally with the phase adjustment shaft in a state where a phase difference is generated between the gear and the phase fixed gear. A phase difference occurs between the eccentric weight attached to the eccentric weight and the eccentric weights coupled to the third and fourth rotation shafts to which the rotation of the other is transmitted. The generated horizontal component is always offset In contrast, the total value of the vertical component forces generated in each eccentric weight is changed according to the phase difference between the eccentric weights, and as a result, the vibrating force applied to the casing member via each rotating shaft changes As a result, the vibrating force can be changed arbitrarily and steplessly even during operation, and the structure is very simple, rational, and has the advantage of being easily manufactured.
【図１】本発明に係る振動発生装置の第１実施例の主要
部を示す斜視図。FIG. 1 is a perspective view showing a main part of a first embodiment of a vibration generator according to the present invention.
【図２】第１実施例の展開図。FIG. 2 is a development view of the first embodiment.
【図３】本発明に係る振動発生装置が適用された振動杭
打機の一例を示す正面図。FIG. 3 is a front view showing an example of a vibration pile driver to which the vibration generator according to the present invention is applied.
【図４】第１実施例の動作説明に供される図。FIG. 4 is a diagram used for describing the operation of the first embodiment.
【図５】第１実施例の動作説明に供される図。FIG. 5 is a diagram provided for explaining the operation of the first embodiment;
【図６】第１実施例の媒介歯車を不要とする例の展開
図。FIG. 6 is a development view of an example in which the intermediate gear of the first embodiment is not required.
【図７】本発明に係る振動発生装置の第２実施例の展開
図。FIG. 7 is a development view of a second embodiment of the vibration generator according to the present invention.
【図８】第２実施例の主要部の斜視図。FIG. 8 is a perspective view of a main part of the second embodiment.
【図９】第２実施例の変形例の説明に供される断面図。FIG. 9 is a cross-sectional view used for describing a modification of the second embodiment.
【図１０】第２実施例の変形例の説明に供される斜視
図。FIG. 10 is a perspective view used for describing a modification of the second embodiment.
【図１１】第３実施例の主要部の一部破断正面図。FIG. 11 is a partially cutaway front view of a main part of the third embodiment.
【図１２】第３実施例の主要部の斜視図。FIG. 12 is a perspective view of a main part of a third embodiment.
【図１３】第３実施例の動作説明に供される図。FIG. 13 is a diagram which is used for describing the operation of the third embodiment.
１０─振動発生装置 ５１Ａ，５２Ａ─偏心
重錘 １４─モーター ５１Ｂ，５２Ｂ─偏心
重錘 ２０─ケーシング部材 ６０−位置検出器 ２１─第１の回転軸 ７０―位相調整軸 ２２─第２の回転軸 ７１−第１の調整軸 ２３─第３の回転軸 ７２−第２の調整軸 ２４─第４の回転軸 ７３，７４，７５，７
６−螺旋状凹凸部 ２５−位相調整軸 ９０─位相調整軸 ３１〜３４─伝動歯車 ９１，９２―油圧通路 ３５─位相調整歯車 ９５―固定仕切り壁部 ３６─固定位相歯車 ９６―可動仕切り壁部 ４６，５３−螺旋状凹凸部 １００―油圧作動室 ５０−シリンダー １０１―第１の作動室 １０２−第２の作動室10─Vibration generator 51A, 52A─Eccentric weight 14─Motor 51B, 52B─Eccentric weight 20─Casing member 60-Position detector 21─First rotating shaft 70-Phase adjusting shaft 22─Second rotating shaft 71-first adjustment axis 23─third rotation axis 72-second adjustment axis 24─fourth rotation axis 73,74,75,7
6-spiral uneven portion 25-phase adjustment shaft 90 ° phase adjustment shaft 31-34─transmission gear 91,92-hydraulic passage 35─phase adjustment gear 95-fixed partition wall 36─fixed phase gear 96-movable partition wall 46,53-spiral uneven portion 100-hydraulic working chamber 50-cylinder 101-first working chamber 102-second working chamber
Claims (14)
れ、それぞれに偏心重錘及び伝動歯車が外嵌固定された
第１の回転軸，第２の回転軸，第３の回転軸，及び第４
の回転軸と、それらの各回転軸と平行に軸支され、位相
固定歯車が相対回転不能にまた位相調整歯車が相対回転
可能にそれぞれ軸方向の移動は阻止された状態で外嵌さ
れた位相調整軸とを有し、上記第１の回転軸及び第２の
回転軸上の伝動歯車同士が噛合せしめられるとともに、
上記第３の回転軸及び第４の回転軸上の伝動歯車同士が
噛合せしめられ、上記第３の回転軸及び第４の回転軸の
いずれかに軸方向の移動は阻止された状態で上記位相固
定歯車及び位相調整歯車のうちの一方の回転を上記第１
の回転軸及び第２の回転軸上の伝動歯車のいずれかに伝
達する媒介歯車が回転可能に外嵌され、さらに、上記第
３の回転軸及び第４の回転軸上の伝動歯車のいずれかが
上記位相固定歯車及び位相調整歯車のうちの他方に噛合
せしめられ、かつ、上記位相調整軸に関連して上記位相
調整歯車を位相調整軸に対して相対回転させる位相変更
手段が設けられてなる振動発生装置。1. A first rotating shaft, a second rotating shaft, a third rotating shaft, and a third rotating shaft which are supported by a casing member in parallel with each other, and each of which has an eccentric weight and a transmission gear externally fixed thereto. 4
And the phase fitted gears are rotatably supported in parallel with the respective rotating shafts, and the phase-locked gears are relatively non-rotatable and the phase adjusting gears are relatively rotatable. An adjusting shaft, and the transmission gears on the first rotating shaft and the second rotating shaft are meshed with each other;
The transmission gears on the third rotating shaft and the fourth rotating shaft are engaged with each other, and the phase shift is performed in a state where the movement in the axial direction is prevented by any of the third rotating shaft and the fourth rotating shaft. The rotation of one of the fixed gear and the phase adjustment gear
An intermediate gear that transmits to any one of the transmission gears on the rotation shaft and the second rotation shaft is rotatably fitted to the outside, and further, any one of the transmission gears on the third rotation shaft and the fourth rotation shaft. Is engaged with the other of the phase-locking gear and the phase-adjusting gear, and a phase changing means is provided for rotating the phase-adjusting gear relative to the phase-adjusting shaft in relation to the phase-adjusting shaft. Vibration generator.
れ、それぞれに偏心重錘及び伝動歯車が外嵌固定された
第１の回転軸，第２の回転軸，第３の回転軸，及び第４
の回転軸と、それらの各回転軸と平行に軸支され、位相
固定歯車が相対回転不能にまた位相調整歯車が相対回転
可能にそれぞれ軸方向の移動は阻止された状態で外嵌さ
れた位相調整軸とを有し、上記第１の回転軸及び第２の
回転軸上の伝動歯車同士が噛合せしめられるとともに、
それらの一方が上記位相固定歯車及び位相調整歯車のう
ちの一方に噛合せしめられ、また、上記第３の回転軸及
び第４の回転軸上の伝動歯車同士が噛合せしめられると
ともに、それらの一方が上記位相固定歯車及び位相調整
歯車のうちの他方に噛合せしめられ、かつ、上記位相調
整軸に関連して上記位相調整歯車を位相調整軸に対して
相対回転させる位相変更手段が設けられてなる振動発生
装置。2. A first rotating shaft, a second rotating shaft, a third rotating shaft, and a third rotating shaft which are supported by a casing member in parallel with each other and to which an eccentric weight and a transmission gear are externally fixed. 4
And the phase fitted gears are rotatably supported in parallel with the respective rotating shafts, and the phase-locked gears are relatively non-rotatable and the phase adjusting gears are relatively rotatable. An adjusting shaft, and the transmission gears on the first rotating shaft and the second rotating shaft are meshed with each other;
One of them is meshed with one of the phase fixed gear and the phase adjustment gear, and the transmission gears on the third rotating shaft and the fourth rotating shaft are meshed with each other, and one of them is meshed with the other. A vibration meshed with the other of the phase-locking gear and the phase-adjusting gear, and provided with phase changing means for rotating the phase-adjustment gear relative to the phase-adjustment shaft in relation to the phase-adjustment shaft; Generator.
直線運動を位相調整歯車の回転運動に変換する運動変換
手段と、上記位相調整軸を軸方向に強制的に移動させる
駆動手段と、から構成されていることを特徴とする請求
項１又は２に記載の振動発生装置。3. A phase changing device comprising: a motion converting device configured to convert an axial linear motion of a phase adjusting shaft into a rotational motion of a phase adjusting gear; and a driving device configured to forcibly move the phase adjusting shaft in an axial direction. The vibration generating device according to claim 1, wherein the vibration generating device is configured by:
設けられた螺旋状凹凸部と、位相調整歯車の内周部に設
けられ、上記螺旋状凹凸部に摺動自在に嵌合する螺旋状
凹凸部と、上記位相調整軸を軸方向に強制的に移動させ
る駆動手段と、から構成されていることを特徴とする請
求項１又は２に記載の振動発生装置。4. A phase changing means is provided on a spiral uneven portion provided on an outer peripheral portion of a phase adjusting shaft and an inner peripheral portion of a phase adjusting gear, and is slidably fitted to the spiral uneven portion. The vibration generator according to claim 1, further comprising: a spiral uneven portion; and a driving unit for forcibly moving the phase adjustment shaft in an axial direction.
設けられた螺旋状の溝もしくは凸条と、位相調整歯車の
内周部に設けられ、上記螺旋状の溝もしくは凸条に摺動
自在に嵌合する凸部もしくは凹部と、上記位相調整軸を
軸方向に強制的に移動させる駆動手段と、から構成され
ていることを特徴とする請求項１又は２に記載の振動発
生装置。5. A helical groove or a ridge provided on an outer peripheral portion of a phase adjustment shaft and a helical groove or a ridge provided on an inner peripheral portion of a phase adjusting gear, wherein the phase changing means slides on the helical groove or the ridge. The vibration generating device according to claim 1, further comprising: a convex portion or a concave portion that is movably fitted, and a driving unit that forcibly moves the phase adjustment shaft in an axial direction. .
向けて突出するように立設されたピンと、上記位相調整
歯車に連設され、上記ピンが嵌挿される螺旋長孔が形成
された延長ボス部と、上記位相調整軸を軸方向に強制的
に移動させる駆動手段と、から構成されていることを特
徴とする請求項１又は２に記載の振動発生装置。6. A phase change means having a pin erected on a phase adjustment shaft so as to protrude in a radial direction, and a helical elongated hole connected to the phase adjustment gear and into which the pin is inserted is formed. The vibration generating device according to claim 1, further comprising: an extending boss portion; and a driving unit for forcibly moving the phase adjustment shaft in the axial direction.
調整軸からなり、第１の調整軸が第２の調整軸に対し
て、直線運動を回転運動に変換する第１の運動変換手段
を介して軸方向に相対移動及び相対回転可能に配置さ
れ、位相変更手段が上記第１の調整軸及び第２の調整軸
の少なくとも一方を軸方向に強制的に移動させる駆動手
段を含んで構成されていることを特徴とする請求項１又
は２に記載の振動発生装置。7. A first adjustment axis, comprising a first adjustment axis and a second adjustment axis, wherein the first adjustment axis converts a linear motion into a rotary motion with respect to the second adjustment axis. A driving means which is arranged so as to be capable of relative movement and relative rotation in the axial direction via the movement converting means, and wherein the phase changing means forcibly moves at least one of the first adjusting shaft and the second adjusting shaft in the axial direction. The vibration generator according to claim 1, wherein the vibration generator is configured to include the vibration generator.
調整軸からなり、第１の調整軸が第２の調整軸に対して
軸方向に相対移動及び相対回転可能に配置されるととも
に、位相調整歯車が直線運動を回転運動に変換する第２
の運動変換手段を介して上記第１の調整軸及び第２の調
整軸のいずれか一方に相対回転可能に外嵌され、かつ、
位相変更手段が上記第１の調整軸及び第２の調整軸の少
なくとも一方を軸方向に強制的に移動させる駆動手段を
含んで構成されていることを特徴とする請求項１又は２
に記載の振動発生装置。8. A phase adjustment axis includes a first adjustment axis and a second adjustment axis, and the first adjustment axis is disposed so as to be relatively movable and rotatable in the axial direction with respect to the second adjustment axis. And the phase adjusting gear converts the linear motion into the rotary motion.
The first and second adjustment shafts are externally fitted so as to be relatively rotatable via the motion conversion means, and
The phase changing means includes a driving means for forcibly moving at least one of the first adjustment axis and the second adjustment axis in the axial direction.
The vibration generating device according to item 1.
調整軸からなり、第１の調整軸が第２の調整軸に対し
て、直線運動を回転運動に変換する第１の運動変換手段
を介して軸方向に相対移動及び相対回転可能に配置され
るとともに、位相調整歯車が直線運動を回転運動に変換
する第２の運動変換手段を介して上記第１の調整軸及び
第２の調整軸のいずれか一方に相対回転可能に外嵌さ
れ、かつ、位相変更手段が上記第１の調整軸及び第２の
調整軸の少なくとも一方を軸方向に強制的に移動させる
駆動手段を含んで構成されていることを特徴とする請求
項１又は２に記載の振動発生装置。9. A phase adjustment axis comprising a first adjustment axis and a second adjustment axis, wherein the first adjustment axis converts a linear motion into a rotary motion with respect to the second adjustment axis. The first adjusting shaft and the second adjusting shaft are arranged via a second motion converting unit which is arranged so as to be relatively movable and relatively rotatable in the axial direction via the motion converting unit, and wherein the phase adjusting gear converts the linear motion into the rotary motion. A driving means externally fitted to one of the two adjustment axes so as to be relatively rotatable, and the phase changing means for forcibly moving at least one of the first adjustment axis and the second adjustment axis in the axial direction. The vibration generator according to claim 1, wherein the vibration generator is configured to include the vibration generator.
の内周部に刻設された第１の螺旋状凹凸部と第２の調整
軸の外周に刻設されて上記第１の螺旋状凹凸部に嵌合す
る第２の螺旋状凹凸部とで構成されていることを特徴と
する請求項７又は９記載の振動発生装置。10. A first motion converting means, which is engraved on a first helical uneven portion engraved on an inner peripheral portion of a first adjustment shaft and an outer peripheral portion of a second adjustment shaft, and is provided on the first adjustment shaft. The vibration generating apparatus according to claim 7, wherein the vibration generating device includes a second helical uneven portion fitted to the helical uneven portion.
の一方の内周部に刻設された第３の螺旋状凹凸部と該位
相調整歯車が外嵌された第１の調整軸及び第２の調整軸
のいずれかの外周に刻設されて上記第３の螺旋状凹凸部
に嵌合する第４の螺旋状凹凸部とで構成されていること
を特徴とする請求項８又は９記載の振動発生装置。11. A second motion conversion means comprising: a third helical uneven portion engraved on one inner peripheral portion of the phase adjustment gear; a first adjustment shaft on which the phase adjustment gear is externally fitted; 10. A fourth spiral uneven portion which is engraved on one of the outer circumferences of the second adjusting shaft and is fitted to the third spiral uneven portion. The vibration generator as described.
手段による回転変換方向が同一とされていることを特徴
とする請求項９記載の振動発生装置。12. The vibration generator according to claim 9, wherein the rotation conversion directions of the first motion conversion means and the second motion conversion means are the same.
と位相調整歯車との間に形成された流体作動室を有し、
該流体作動室に対する流体の給排により上記位相調整歯
車を上記位相調整軸に対して相対回転させるように構成
とされていることを特徴とする請求項１又は２に記載の
振動発生装置。13. A phase changing means having a fluid working chamber formed between an outer peripheral portion of a phase adjusting shaft and a phase adjusting gear,
3. The vibration generating device according to claim 1, wherein the phase adjusting gear is configured to rotate relative to the phase adjusting shaft by supplying and discharging the fluid to and from the fluid working chamber.
固定仕切り壁部と位相調整歯車に固定された可動仕切り
壁部とで仕切られていることを特徴とする請求項１３記
載の振動発生装置。14. The vibration generation according to claim 13, wherein the fluid working chamber is partitioned by a fixed partition wall fixed to the phase adjustment shaft and a movable partition wall fixed to the phase adjustment gear. apparatus.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4400192A JP2865934B2 (en) | 1992-02-28 | 1992-02-28 | Vibration generator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4400192A JP2865934B2 (en) | 1992-02-28 | 1992-02-28 | Vibration generator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05237459A JPH05237459A (en) | 1993-09-17 |
| JP2865934B2 true JP2865934B2 (en) | 1999-03-08 |
Family
ID=12679476
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4400192A Expired - Fee Related JP2865934B2 (en) | 1992-02-28 | 1992-02-28 | Vibration generator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2865934B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017013303A1 (en) * | 2015-07-17 | 2017-01-26 | Movax Oy | Vibrator device |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8813589B2 (en) | 2010-11-22 | 2014-08-26 | Zhongsheng Tang | Eccentric moment stepless adjustable vibrating mechanism |
| CN102145333B (en) * | 2010-12-01 | 2012-11-07 | 黎凡七 | Double-vibration exciter synchronous phase locking method and device |
| KR101466640B1 (en) * | 2012-12-10 | 2014-11-28 | (주)티앤에치코퍼레이션 | Vibrator |
| JP6363667B2 (en) * | 2016-08-29 | 2018-07-25 | 調和工業株式会社 | Exciter and pile construction method |
| CN110541340B (en) * | 2019-09-26 | 2021-07-02 | 贵州焱燊机电有限公司 | Drop hammer type compacting machine |
| KR102138899B1 (en) * | 2019-12-09 | 2020-07-28 | 이민수 | Detachable vibro-hammer with vibratory rubber and construction method of drilling and ground reinforcement thereof |
| KR102138893B1 (en) * | 2019-12-09 | 2020-07-28 | 이민수 | Detachable vibro-hammer with spring and construction method of drilling and ground reinforcement thereof |
-
1992
- 1992-02-28 JP JP4400192A patent/JP2865934B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017013303A1 (en) * | 2015-07-17 | 2017-01-26 | Movax Oy | Vibrator device |
| EP3325181A4 (en) * | 2015-07-17 | 2019-03-06 | Movax Oy | Vibrator device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH05237459A (en) | 1993-09-17 |
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