EP2392413B1 - Marteaux à vibration - Google Patents

Marteaux à vibration Download PDF

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Publication number
EP2392413B1
EP2392413B1 EP11004220.7A EP11004220A EP2392413B1 EP 2392413 B1 EP2392413 B1 EP 2392413B1 EP 11004220 A EP11004220 A EP 11004220A EP 2392413 B1 EP2392413 B1 EP 2392413B1
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EP
European Patent Office
Prior art keywords
groups
shaft
imbalance
group
vibration
Prior art date
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Active
Application number
EP11004220.7A
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German (de)
English (en)
Other versions
EP2392413A2 (fr
EP2392413A3 (fr
Inventor
Christian Heichel
Albrecht Kleibl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Original Assignee
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
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Publication of EP2392413A2 publication Critical patent/EP2392413A2/fr
Publication of EP2392413A3 publication Critical patent/EP2392413A3/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses

Definitions

  • the invention relates to a method for introducing a profile into a ground by means of a vibrating hammer according to claim 1.
  • vibratory rams are used to bring objects such as profiles into the ground or to pull them out of the ground.
  • the soil is excited by vibration at a frequency above the natural frequency of the soil and thus reaches a "pseudo-liquid state". By static load the pile can then be pressed into the ground.
  • the vibration is characterized by a linear movement and is generated by pairwise counter-rotating imbalances.
  • Vibration generator with rotatably mounted imbalance masses are the expert, for example, from EP 2 105 213 A1 known.
  • the vibration generators of such vibratory rams are linearly acting vibration exciters whose centrifugal force is generated by rotating imbalances. These vibration exciters move at a variable speed.
  • the size of the unbalance is also called a static moment.
  • the course of the velocity of the linear vibration exciter corresponds to a periodically recurring function, in particular a sine function. Due to the sinusoidal course of the force generated by means of the rotating unbalanced masses a temporally offset alternately acting in and against the direction of advance drive is generated. This is ultimately determined by static forces, especially dead weight and static loads. Without the superimposition of the vibration with static forces, the pile would not move forward, but would merely swing back and forth.
  • a disadvantage of the known systems that the piling process with the aforementioned sinusoidal force curve has a considerable energy consumption, which is additionally increased by friction of the pile in the ground. The energy used for the vibrator causes virtually no propulsion.
  • the invention aims to remedy this situation.
  • the invention is based on the object to provide an energy-efficient method for introducing a profile in the ground by means of a vibrating hammer. According to the invention, this object is solved by the features of claim 1.
  • a directional characteristic in the direction of advance is generated by superposition of the sinusoidal force characteristics generated by the rotating imbalances.
  • the direction of advance there is a much greater maximum force compared to the opposite direction. Since during the ramming process the ground can not follow the large acceleration in the direction of ramming, the pile rips off the resonating ground with each forward momentum impulse. Due to this periodic decoupling of soil and pile material less energy is supplied to the ground. As a result, the vibration load of the environment is also significantly reduced.
  • the static moment of the first wave group is eight times as large as the static moment of the second wave group.
  • a pronounced force peak is effected in the advancing direction.
  • the wave groups By using three wave groups on which at least three unbalance groups are arranged, the wave groups having a speed ratio of 1: 2: 3 and the ratio of the static moments of the wave groups to each other being substantially 100: 16.64: 3.68 the maximum acting force is increased by a further pronounced force peak in the direction of advance. This results in a further increase in energy efficiency, combined with an acceleration of the piling process causes.
  • These vibratory ram has the advantages of the aforementioned embodiment of a vibrating hammer and is to operate at a speed corresponding to a frequency which is well below the natural frequency of the soil.
  • This embodiment of the vibrating ram has the advantages of the aforementioned embodiment of a vibrating hammer and is to operate at a speed corresponding to a frequency which is well below the natural frequency of the soil. Due to the specific arrangement of wave and imbalance groups a very fine adjustment of the desired force characteristic is possible.
  • means for adjusting the direction of action of the vibration generator are provided in the vibration ram. This allows adaptation of the vibrator to different process requirements such as ramming and pulling.
  • the means for adjusting the direction of action comprise a swivel motor, via which the phase position of at least two imbalance groups rotating at different rotational speeds is variable relative to one another.
  • the at least two imbalance groups are connected via gears with the pivot motor, wherein at least one imbalance group with the stator and at least one imbalance group is connected to the rotor of the swing motor.
  • the swing motor is a rotary-wing pivoting motor with a wing. This is distinguished from the 180-degree adjustable swivel motors by multiple higher torque and lower friction.
  • the swing motor may also be a swivel motor with coarse thread.
  • the vibration generator of a vibrating hammer selected as the exemplary embodiment are designed as vibrator gears.
  • Such vibrators essentially consist of a housing in which gears provided with gears are rotatably mounted.
  • the gears are each provided with imbalance masses.
  • Vibratorgetriebe with rotatably mounted imbalance masses are the expert, for example from the DE 20 2007 006 283 U1 known.
  • the following explanation of the embodiments is essentially limited to the arrangement of waves and imbalance masses.
  • the shafts 11, 12 of the shaft group 1 are provided with toothed wheels 112, 122, on which imbalance masses 111, 121 are arranged.
  • the imbalance masses 111, 121 are executed in the same embodiment.
  • the shafts 21, 22 of the shaft group 2 are as it were provided with gears 212, 222, on which similar imbalance masses 211, 221 are arranged.
  • the gears 112, 122, 212, 222 are designed such that upon rotation, the rotational speed of the shafts 21, 22 of the shaft group 2 is twice as large as the rotational speed of the shafts 11, 12.
  • the imbalance masses 111, 121, 211, 221 are arranged such that the static moment of the shaft group 1 is eight times the static moment of wave group 2.
  • a pivot motor 5 is arranged, whose stator has a gear 51 and whose rotor has a gear 52.
  • the wave groups 1, 2 are connected to each other via the swing motor 5 such that the gear 112 of the shaft 11 is engaged with the gear 52 of the swing motor 5; the gears 212, 222 of the shaft group 2 are connected to the gear 51 of the swing motor 5 in engagement.
  • the swivel motor 5 is a rotary-wing pivoting motor with a wing.
  • the wave groups 1, 2 of three shafts 11, 12, 13, 21, 22, 23 are formed, which are each provided with imbalance masses 111, 121, 131, 211, 221, 231.
  • the imbalance masses 111, 121 and 131 form the imbalance group 101
  • the imbalance masses 211, 221 and 232 form the imbalance group 201.
  • the gears 112, 122, 132, 212, 222, 232 of the shafts 11, 12, 13, 21, 22, 23 are again chosen such that during rotation, the waves of the wave group 2 have twice the speed, as the waves of the wave group 1.
  • the number of waves of the wave groups 1, 2 can also be chosen differently.
  • an additional shaft 24 is added with corresponding imbalance mass 241.
  • a compact design can be achieved (see. FIG. 4c) ).
  • a pivot motor 5 is arranged between the shafts 11, 12, 13 of the shaft group 1 and the shafts 21, 22, 23 of the shaft group 2, a pivot motor 5 is arranged.
  • the unbalanced masses 111, 121 and 131 form the imbalance group 101
  • the imbalance masses 211, 221 and 232 form the imbalance group 201.
  • the gears 112, 122, 132 of the shaft group 1 with the gear 51 of the stator of the swing motor 5 are engaged and the gears 212, 222, 232 of the shaft group 2 are engaged with the gear 52 of the rotor of the swing motor 5.
  • the pivot motor 5 is a rotary wing pivot motor with three wings.
  • FIG. 6 is a modified structure of the aforementioned arrangement according to FIG. 5 shown, which allows a significant reduction in length, but in which instead of six waves eight waves are required, but this is reflected in a lower load on the shaft bearings and advantages in terms of recoverable centrifugal force, suitability for high speeds and lower sensitivity large angular acceleration brings with it.
  • an additional speed stage whose unbalance rotate at three times speed can be used.
  • FIG. 7 is such an arrangement based on the transmission concept according to FIG. 5 shown. This falls slightly wider, since the lower large gear 132, which drives the two juxtaposed shafts 31, 32, is shifted relative to the transmission center.
  • the angular position of the slow imbalances 111, 121, 131 and rapid imbalances 311, 321 remains unchanged.
  • the pivoting motor 5 the adjustment of the imbalances 211, 221, 231 medium speed over the others is possible.
  • the ratio of the rotational speeds of the wave groups 1, 2, 3 to each other is about 1: 2: 3; the static moment of the wave groups 1, 2, 3 to each other is substantially 100: 16.64: 3.68.

Claims (4)

  1. Procédé pour faire pénétrer un profilé dans le sol au moyen d'un vibrofonceur, comprenant un générateur de vibrations qui comprend soit deux groupes d'arbres sur lesquels sont disposés deux groupes de masselottes et qui sont reliés avec au moins un entraînement qui les fait entrer en rotation, sachant que les groupes d'arbres (1, 2) sont reliés avec au moins un entraînement de sorte que la vitesse de rotation du groupe d'arbres (1) représente la moitié de la vitesse du groupe d'arbres (2) et sachant que le rapport des moments statiques des groupes d'arbres (1, 2) équipés des groupes de masselottes (101, 102) est compris entre 6 : 1 et 10 : 1, soit trois groupes d'arbres sur lesquels sont disposés au moins trois groupes de masselottes et qui sont reliés avec au moins un entraînement qui les fait entrer en rotation, sachant que les groupes d'arbres (1, 2, 3) sont reliés avec au moins un entraînement de sorte que la vitesse de rotation du groupe d'arbres (1) représente la moitié de la vitesse de rotation du groupe d'arbres (2) et un tiers de la vitesse de rotation du groupe d'arbres (3) et sachant que le rapport mutuel entre les moments statiques des groupes d'arbres (1, 2, 3) équipés des groupes de masselottes (101, 201, 301) s'élève essentiellement à 100 : 16,64 : 3,68, soit quatre groupes d'arbres sur lesquels sont disposés au moins quatre groupes de masselottes et qui sont reliés avec au moins un entraînement les faisant entrer en rotation, sachant que les groupes d'arbres (1, 2, 3, 4) sont reliés avec au moins un entraînement de sorte que le rapport mutuel entre les vitesses de rotation des groupes d'arbres (1, 2, 3, 4) s'élève essentiellement à 1 : 2 : 3 : 4 et sachant que le rapport mutuel entre les moments statiques des groupes d'arbres (1, 2, 3, 4) équipés des groupes de masselottes (101, 201, 301, 401) s'élève essentiellement à 100 : 18,72 : 5,6 : 1,38, sachant que son groupe d'arbres le plus lent est exploité à une vitesse de rotation correspondant à une fréquence inférieure à la fréquence propre du sol, ce qui permet d'éviter un état pseudo-fluide du sol, sachant que la fréquence de la courbe de force résultante développée par le générateur de vibrations est inférieure à 20 Hz.
  2. Procédé selon la revendication 1, caractérisé en ce que sont prévus sur le vibrofonceur des moyens destinés à déplacer la direction active du dispositif générateur de vibrations, lesquels moyens comprennent un moteur pivotant (5) qui permet de modifier la position réciproque des phases d'au moins deux groupes de masselottes (101, 201) tournant à des vitesses différentes.
  3. Dispositif générateur de vibrations selon la revendication 2, caractérisé en ce qu'au moins deux groupes de masselottes (101, 201) du vibrofonceur sont reliés au moteur pivotant (5) via des engrenages (232, 112), sachant qu'un groupe de masselottes (201) est relié au stator et qu'au moins un groupe de masselottes (101) est relié au rotor du moteur pivotant (5).
  4. Procédé selon l'une des revendications précédentes, caractérisé en ce que la fréquence de la courbe de force résultante développée par le générateur de vibrations est inférieure à 18 Hz.
EP11004220.7A 2010-06-02 2011-05-21 Marteaux à vibration Active EP2392413B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010022468 DE102010022468A1 (de) 2010-06-02 2010-06-02 Vibrationsramme

Publications (3)

Publication Number Publication Date
EP2392413A2 EP2392413A2 (fr) 2011-12-07
EP2392413A3 EP2392413A3 (fr) 2017-11-29
EP2392413B1 true EP2392413B1 (fr) 2019-06-26

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ID=44645298

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11004220.7A Active EP2392413B1 (fr) 2010-06-02 2011-05-21 Marteaux à vibration

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EP (1) EP2392413B1 (fr)
DE (1) DE102010022468A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2789401B1 (fr) 2013-04-10 2017-09-27 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Générateur de vibrations pour machines de construction
EP2789402B1 (fr) * 2013-04-10 2017-05-17 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Accélérateur d'oscillations
EP2789403B1 (fr) 2013-04-10 2015-12-16 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Générateur de vibrations pour machines de construction
CN113145434A (zh) * 2021-05-10 2021-07-23 无锡坤龙工程机械有限公司 两级式调矩激振器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL101663B1 (pl) * 1974-10-30 1979-01-31 Method of generating mechanical periodic impulse vibrations
DE202007006283U1 (de) 2007-05-03 2007-12-27 Sünkenberg, Bernd Stehfahrrad
EP2105213B1 (fr) * 2008-03-28 2018-01-24 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Dispositif de production de vibrations

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102010022468A1 (de) 2011-12-08
EP2392413A2 (fr) 2011-12-07
EP2392413A3 (fr) 2017-11-29

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