EP1449965B1 - Vibreur pour compaction du sol - Google Patents

Vibreur pour compaction du sol Download PDF

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Publication number
EP1449965B1
EP1449965B1 EP03026486A EP03026486A EP1449965B1 EP 1449965 B1 EP1449965 B1 EP 1449965B1 EP 03026486 A EP03026486 A EP 03026486A EP 03026486 A EP03026486 A EP 03026486A EP 1449965 B1 EP1449965 B1 EP 1449965B1
Authority
EP
European Patent Office
Prior art keywords
unbalance
generating device
shafts
oscillation generating
shaft pair
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03026486A
Other languages
German (de)
English (en)
Other versions
EP1449965A3 (fr
EP1449965A2 (fr
Inventor
Niels Laugwitz
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.)
Bomag GmbH and Co OHG
Original Assignee
Bomag GmbH and Co OHG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Bomag GmbH and Co OHG filed Critical Bomag GmbH and Co OHG
Publication of EP1449965A2 publication Critical patent/EP1449965A2/fr
Publication of EP1449965A3 publication Critical patent/EP1449965A3/fr
Application granted granted Critical
Publication of EP1449965B1 publication Critical patent/EP1449965B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S37/00—Excavating
    • Y10S37/903—Scoop or scraper attachments
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • the invention relates to a vibration exciter device for use in a soil compaction machine, such as a vibratory plate or a roller, with a vibration exciter device, a first unbalanced shaft pair and a tilting torque balancing device.
  • Conventional soil compaction machines such as reversible vibratory plates and vibratory rollers, are equipped with an opposing imbalance shaft pair for generating directional vibrations.
  • the imbalances of the two shafts rotate synchronously but with opposite direction of rotation.
  • phase shifting By phase shifting, a desired directional vibration direction can be adjusted and directional forward or backward movement of the soil compaction machine can be created.
  • a vibration plate which has a tilting moment compensating device for suppressing such a tilting moment. It contains a central imbalance shaft between an unbalanced shaft pair.
  • the imbalance mass of Central imbalance shaft is as large as the total imbalance mass of imbalance shaft pair.
  • the central imbalance shaft rotates in opposite directions to the same direction rotating imbalance shaft pair, the rotational speed of all unbalanced shafts is synchronous. By this arrangement occurs no unwanted tilting moment occurs.
  • the object of the present invention is to improve a soil compacting machine of the type mentioned above and to provide a simple and inexpensive alternative to the previously known tilting moment compensating device for use in a soil compacting machine.
  • a second imbalance shaft pair is arranged as the tilting moment compensation device in the axial direction next to the first unbalanced shaft pair.
  • the first and second unbalanced shaft pairs rotate in opposite directions and diagonally opposite unbalanced shafts rotate in the same direction.
  • the invention has the advantage that unwanted force components and torques cancel each other, so that no tilting moments occur.
  • vibration exciter is constructed of similar components simple and symmetrical, so that cost advantages can be achieved. Since the total imbalance mass is distributed over four waves, the total imbalance mass can be increased or the imbalance waves can be made smaller.
  • the imbalance shafts do not have to be in pairs next to each other in alignment, but the unbalanced shafts of one unbalanced pair of shafts can be offset parallel to the imbalance shafts of the other pair of imbalance shafts with a crosswise symmetry.
  • crosswise symmetry is understood here an arrangement in which the diagonally opposite imbalance waves are arranged in pairs symmetrically to the intersection of their connecting lines.
  • the axis-parallel offset can occur within the same plane or out of the plane. For example, a rear left imbalance shaft could fall by a certain amount be offset above. Then, the front right unbalance shaft would have to be offset by the same amount to produce the required symmetry. It may also be advantageous that the distances of the diagonally opposite unbalanced shafts are different.
  • the diagonal imbalance shafts can be driven separately.
  • the diagonal unbalanced shafts are rotatably coupled, for example via a transmission. This has the advantage that the diagonal unbalanced shafts always maintain the same direction of rotation and the same rotational speed and thus always ensure the functionality and the tilting torque compensation.
  • the synchronization is further simplified by the fact that all unbalanced shafts are rotatably coupled.
  • the transmission has two associated crown gears and thus engaged spur gears on the unbalanced shafts.
  • the advantage here is that of relatively few, simple and known components, a transmission is created, which ensures the function of the device.
  • the transmission is operatively connected to a single drive. This has the advantage that the functions of the same direction of rotation and the same rotational speeds of the imbalance shafts can be maintained and additional drives can be saved.
  • each unbalanced shaft pair has an imbalance shaft with a variable phase position.
  • a synchronization device for synchronous adjustment of the phase position is preferably present. It can be designed either for the same direction, common phase adjustment of both unbalanced shaft pairs or for independent phase adjustment.
  • a particularly preferred development consists in that the synchronizing device has a hydraulically operating flow divider.
  • FIG. 1 a driven by a drive 1 first vibration exciter device of a soil compacting machine in the parallel to a first unbalanced shaft pair 2 in the axial direction laterally offset a similar second unbalanced shaft pair 3 is arranged as a tilting torque balancing device.
  • Each unbalanced shaft pair 2, 3 comprises two successively and axially parallel aligned, counter-rotating unbalanced shafts 4, 5 and 4 ', 5' with the same imbalance masses 9, 10, wherein the imbalance masses 9, 10 of an unbalanced shaft pair 2, 3 arranged to produce phase-shifted centrifugal forces angularly offset are.
  • the imbalance shaft pairs 2, 3 are adjacent to each other in such a way that their imbalance waves are aligned in pairs.
  • unbalanced shafts are the same direction of rotation diagonally opposite.
  • Coincidentally rotating unbalanced shafts 4, 4 'on the one hand and counter-rotating unbalanced shafts 5, 5' on the other hand have the same phase position when driving straight ahead. For a steering movement, the phase angles are adjustable differently.
  • the unbalanced shafts 4, 4 ', 5, 5' are rotatably coupled together by a positive force transmission means in such a way that the directions of rotation and phase assignments are ensured.
  • the power transmission means is formed in the present example as a double crown gear 25. Its non-rotatably connected crown wheels 6 mesh on both Each side with a spur gear 7 and a counter-rotating spur gear 8.
  • the spur gears 7 and 8 are each rotatably connected to the unbalanced shafts 4, 4 'and 5, 5'.
  • the drive 1 acts on the imbalance shaft 4 on the crown gear.
  • the unbalanced shafts 9, 10 are held by bearing elements 12, for example cylindrical roller bearings.
  • the diagonally opposite imbalances of the unbalanced shafts 5, 5 ' can be changed in their phase position alone or together with respect to the other imbalances by the respective imbalance masses 10 are angularly offset on their unbalanced shafts 5, 5'.
  • Fig. 2 The operation of the vibration exciter device is illustrated in three-dimensional, schematic representation. This will be done in Fig. 2 eight phase positions a) to h) of the imbalances in the course of a complete wave circulation shown. Filled black dots represent the respective angular positions of the unbalanced masses 9, 10 again.
  • the unbalanced masses 9 rotate in a clockwise direction, indicated by the curved direction of rotation arrow 13, and the unbalanced masses 10 rotate counterclockwise, indicated by the direction of rotation arrow 14.
  • the imbalance masses 9, 10 of an unbalanced pair of shafts 2 and 3 are respectively phase-shifted by 90 °. Diagonally opposite imbalance masses have the same phase.
  • the centrifugal forces of a pair of unbalanced shafts are combined to form a respective centrifugal force and shown as a filled black arrow 15, 16.
  • the arrows 15, 16 are each applied at the point of application of the resulting centrifugal force and each point in the direction in which the resulting centrifugal force acts.
  • the length of the arrow represents the magnitude of the force.
  • the arrow 15 designates the resulting centrifugal force 15 one unbalanced shaft pair 2 and the arrow 16, the resulting centrifugal force 16 of the other unbalanced shaft pair.
  • the starting position according to Fig. 2a shows the beginning of the rotational movement.
  • the unbalance 9 rotates clockwise about the transverse axis 19.
  • the unbalance 10 rotates counterclockwise about the transverse axis 20.
  • the resulting centrifugal force 15 of the rear unbalanced shaft pair 2 attacks at the intersection of the longitudinal connecting axes 18 and 19 and acts obliquely downwards in the xz direction, ie in the direction of the ground.
  • the resulting centrifugal force 16 is also directed at the imbalances 9 and 10 of the second imbalance shaft pair 3 located on the front longitudinal axis 17.
  • the resulting centrifugal force 16 acts at the intersection of the longitudinal connecting shafts 17 and 20. Since both resulting centrifugal forces 15 and 16 are the same size and directed in parallel, no tilting moment occurs.
  • Fig. 2b is a second phase of the rotational movement shown, in which the imbalance masses are offset by 45 ° in the direction of rotation.
  • the centrifugal forces within each unbalanced shaft pair 2, 3 are exactly opposite.
  • there are two equal torques 23, 24 about an imaginary horizontal center axis 22. arise, however, because they are directed opposite because of the opposite directions of rotation of the unbalanced shaft pairs 2, 3. As a result, therefore no tilting moment occurs parallel to the axes of rotation of the imbalances.
  • the unbalanced shafts 4, 5 of a pair of unbalanced shafts 2 to the unbalanced shafts 4 ', 5' of the other unbalanced shaft pair 3 are axially parallel in crosswise symmetry.
  • the cross-symmetry results from the fact that the diagonally opposite imbalance waves 4,4 '; 5, 5 'to the intersection point 30 of their connecting lines 31, 32 are arranged in pairs symmetrically.
  • Fig. 3 illustrates a spatially upwardly or downwardly axially offset arrangement of the diagonally opposite unbalanced shafts 5, 5 'to lying in a plane other diagonally opposite unbalanced shafts 4, 4'.
  • the offset Vo up and the offset Vu down are the same.
  • Fig. 4 are all unbalanced shafts in a plane and it is the distances of the respective diagonally opposite unbalanced shafts 5, 5 '; and 4, 4 'different.

Landscapes

  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Paleontology (AREA)
  • General Engineering & Computer Science (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Agronomy & Crop Science (AREA)
  • Civil Engineering (AREA)
  • Soil Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Road Paving Machines (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Consolidation Of Soil By Introduction Of Solidifying Substances Into Soil (AREA)
  • Soil Working Implements (AREA)
  • Excavating Of Shafts Or Tunnels (AREA)

Claims (15)

  1. Dispositif générateur de vibrations utilisable dans une dameuse pour sols avec une première paire d'arbres déséquilibrés (2) et avec un dispositif de compensation du moment d'inclinaison (3) caractérisé en ce que le dispositif de compensation du moment d'inclinaison (3) est formé par une deuxième paire d'arbres déséquilibrés (3) disposée près de la première dans le sens de l'axe et en ce que les paires d'arbres déséquilibrés (3, 4) tournent en sens opposé et les arbres déséquilibrés (4, 4' ; 5, 5') se faisant face en diagonale tournent dans le même sens.
  2. Dispositif générateur de vibrations selon la revendication 1, caractérisé en ce que les arbres déséquilibrés (4, 5) d'une paire d'arbres déséquilibrés (2) sont alignés par paire avec les arbres déséquilibrés (4', 5') de l'autre paire d'arbres déséquilibrés (3).
  3. Dispositif générateur de vibrations selon la revendication 1, caractérisé en ce que les arbres déséquilibrés (4, 5) d'une paire d'arbres déséquilibrés (2) sont décalés par rapport aux arbres déséquilibrés (4', 5') de l'autre paire d'arbres déséquilibrés (3) de manière parallèle à l'axe dans une symétrie croisée.
  4. Dispositif générateur de vibrations selon la revendication 3, caractérisé en ce que les distances entre les arbres déséquilibrés (4, 4' ; 5, 5') opposés en diagonale sont différentes.
  5. Dispositif générateur de vibrations selon la revendication 3 ou 4, caractérisé en ce que les arbres déséquilibrés (4, 4' ; 5, 5') se trouvent dans le même plan.
  6. Dispositif générateur de vibrations selon la revendication 3 ou 4, caractérisé en ce que les arbres déséquilibrés (4, 4' ; 5, 5') sont décalés dans l'espace les uns par rapport aux autres.
  7. Dispositif générateur de vibrations selon l'une des revendications précédentes, caractérisé en ce que chaque paire d'arbres déséquilibrés (3, 4) présente un arbre déséquilibré (10) ayant une position de phase modifiable.
  8. Dispositif générateur de vibrations selon la revendication 7, caractérisé en ce qu'il est prévu un dispositif de synchronisation pour le réglage synchronie de la position de phase.
  9. Dispositif générateur de vibrations selon la revendication 7 ou 8, caractérisé en ce que le dispositif de synchronisation est conçu en vue d'un réglage commun et dans le même sens de la phase des deux paires d'arbres déséquilibrés (3, 4).
  10. Dispositif générateur de vibrations selon la revendication 7 ou 8, caractérisé en ce qu'il est prévu un dispositif pour le réglage indépendant de la phase.
  11. Dispositif générateur de vibrations selon l'une des revendications 8 à 10, caractérisé en ce que le dispositif de synchronisation comprend un diviseur de courant à action hydraulique.
  12. Dispositif générateur de vibrations selon l'une des revendications précédentes, caractérisé en ce que les arbres déséquilibrés (4, 4' ; 5, 5') en diagonale au moins sont couplés de façon solidaire en rotation.
  13. Dispositif générateur de vibrations selon la revendication 12, caractérisé en ce que tous les arbres déséquilibrés (4, 4' ; 5, 5') sont couplés de façon solidaire en rotation.
  14. Dispositif générateur de vibrations selon la revendication 12 ou 13, caractérisé en ce que le couplage solidaire en rotation se compose d'un engrenage (25) avec deux couronnes (6) et des roues droites (7, 8) se mettant en prise avec celles-ci sur les arbres déséquilibrés (4, 4') et (5, 5').
  15. Dispositif générateur de vibrations selon la revendication 14, caractérisé en ce que l'engrenage (25) est en liaison active avec un seul entraînement (1).
EP03026486A 2003-02-18 2003-11-20 Vibreur pour compaction du sol Expired - Lifetime EP1449965B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10306791A DE10306791A1 (de) 2003-02-18 2003-02-18 Schwingungserregervorrichtung
DE10306791 2003-02-18

Publications (3)

Publication Number Publication Date
EP1449965A2 EP1449965A2 (fr) 2004-08-25
EP1449965A3 EP1449965A3 (fr) 2005-12-28
EP1449965B1 true EP1449965B1 (fr) 2008-05-07

Family

ID=32731038

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03026486A Expired - Lifetime EP1449965B1 (fr) 2003-02-18 2003-11-20 Vibreur pour compaction du sol

Country Status (5)

Country Link
US (1) US7302871B2 (fr)
EP (1) EP1449965B1 (fr)
AT (1) ATE394550T1 (fr)
DE (2) DE10306791A1 (fr)
ES (1) ES2301747T3 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007018353A1 (de) * 2007-04-18 2008-10-30 Wacker Construction Equipment Ag Schwingungserreger für Bodenverdichtungsvorrichtungen
CA2734851A1 (fr) * 2008-08-21 2010-02-25 Surinder Singh Parmar Systeme et procede pour la production d'electricite a petite/grande echelle de maniere ecologique sans utilisation de quelconques matieres premieres
DE102011112316B4 (de) * 2011-09-02 2020-06-10 Bomag Gmbh Schwingungserreger zur Erzeugung einer gerichteten Erregerschwingung
DE102012025378A1 (de) * 2012-12-27 2014-07-03 Wacker Neuson Produktion GmbH & Co. KG Schwingungserreger für bodenverdichtungsvorrichtungen
DE102012025376A1 (de) * 2012-12-27 2014-07-03 Wacker Neuson Produktion GmbH & Co. KG Schwingungserreger für lenkbare bodenverdichtungsvorrichtungen
US20160349143A1 (en) * 2015-06-01 2016-12-01 Peter S. Aronstam Systems, Methods, and Apparatuses For a Vibratory Source
EP3357589A1 (fr) * 2017-02-03 2018-08-08 BAUER Maschinen GmbH Générateur de vibrations et procédé de production de vibrations
RU2654892C1 (ru) * 2017-02-20 2018-05-23 Акционерное общество "Всероссийский научно-исследовательский институт гидротехники имени Б.Е. Веденеева" Валец вибрационного катка
GB2570351B (en) 2018-01-23 2021-03-31 Terex Gb Ltd Vibration generating mechanism for a vibrating screen box
CN108636746A (zh) * 2018-05-24 2018-10-12 中国矿业大学(北京) 对角四踏步型振动系统
DE102018006902A1 (de) 2018-08-30 2020-03-05 Forschungs- Und Transferzentrum Leipzig E.V. An Der Hochschule Für Technik, Wirtschaft Und Kultur Leipzig Schwingungserreger für Walzenvorrichtung zur Bodenverdichtung

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL6818522A (fr) * 1968-01-15 1969-07-17
FR2647705B1 (fr) * 1989-06-02 1991-08-30 Balbinot Ets Installation a table vibrante pour la fabrication de produits en beton
DE4301368A1 (de) * 1992-07-03 1994-01-05 Gedib Ingbuero Innovation Vorrichtung und Verfahren zur Schwingungserregung
DE19547043C2 (de) * 1995-12-18 1997-10-02 Wacker Werke Kg Schwingungserreger zum Erzeugen einer gerichteten Schwingung
DE19714555C2 (de) * 1997-04-09 2001-06-21 Wacker Werke Kg Arbeitsgerät, insbesondere Stampfgerät zur Bodenverdichtung oder Hammer
DE29723617U1 (de) * 1997-05-27 1998-11-26 AMMANN Verdichtung GmbH, 53773 Hennef Vibrationsplatte zur Verdichtung des Bodens
DE19920348A1 (de) * 1998-05-08 2000-01-13 Gedib Ingbuero Innovation Verstelleinrichtung zur Verstellung des resultierenden statischen Momentes von Unwucht-Vibratoren
DE19943391A1 (de) * 1999-09-10 2001-04-12 Wacker Werke Kg Schwingungserreger für Bodenverdichtungsgeräte
AUPQ931200A0 (en) * 2000-08-09 2000-08-31 Ludowici Mineral Processing Equipment Pty Ltd Exciter apparatus
US20020104393A1 (en) * 2001-02-07 2002-08-08 Van Es J. R. Variable moment vibrator
US6749365B2 (en) * 2002-03-18 2004-06-15 M-B-W Inc. Vibration isolation for a percussion rammer

Also Published As

Publication number Publication date
US7302871B2 (en) 2007-12-04
DE10306791A1 (de) 2004-08-26
EP1449965A3 (fr) 2005-12-28
ATE394550T1 (de) 2008-05-15
DE50309774D1 (de) 2008-06-19
US20040173040A1 (en) 2004-09-09
ES2301747T3 (es) 2008-07-01
EP1449965A2 (fr) 2004-08-25

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