EP1534439B1 - Oscillateur destine a des engins de compactage du sol - Google Patents

Oscillateur destine a des engins de compactage du sol Download PDF

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Publication number
EP1534439B1
EP1534439B1 EP03793804A EP03793804A EP1534439B1 EP 1534439 B1 EP1534439 B1 EP 1534439B1 EP 03793804 A EP03793804 A EP 03793804A EP 03793804 A EP03793804 A EP 03793804A EP 1534439 B1 EP1534439 B1 EP 1534439B1
Authority
EP
European Patent Office
Prior art keywords
unbalanced
vibration exciter
imbalance
masses
shafts
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
EP03793804A
Other languages
German (de)
English (en)
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EP1534439A1 (fr
Inventor
Franz Riedl
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.)
Wacker Construction Equipment AG
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Wacker Construction Equipment AG
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Publication date
Application filed by Wacker Construction Equipment AG filed Critical Wacker Construction Equipment AG
Publication of EP1534439A1 publication Critical patent/EP1534439A1/fr
Application granted granted Critical
Publication of EP1534439B1 publication Critical patent/EP1534439B1/fr
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Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase

Definitions

  • the invention relates to a vibration exciter for a soil compaction device according to the preamble of patent claim 1.
  • vibration exciters are mainly used in vibration plates advantageous and z. B. from EP 0 358 744 B1.
  • a similar vibration exciter is described in DE 100 38 206 A1. It has two form-fitting counter-rotatably coupled unbalanced shafts, each carrying a fixed unbalanced mass and a relative to the fixed imbalance mass and thus rotatably movable with the imbalance shaft unbalanced mass.
  • the position of the movable imbalance masses can be changed by adjusting active in a wider range.
  • Upon rotation of the imbalance waves results from the interaction of the various imbalance masses a resulting total force, which may be directed depending on the operator in forward or reverse direction.
  • the change of the direction of travel is effected by the adjusting means which drive the movable imbalance masses. If the operator desires a standstill of the soil compactor, the resulting force of the centrifugal weights is set in the vertical direction. This also means that a targeted compaction of the soil in the state of the machine can be achieved.
  • the operator does not always desire such a high degree of compaction at a localized point of the ground.
  • an excessively strong and thus disadvantageous compaction of the soil can be achieved, since the force acting on the ground in this position is the greatest, while they are in the forward or Reverse movement of the vibrating plate and the associated pivoting of the resulting force vector by, for example, 45 ° forwards or back to 1 / ⁇ 2 of the maximum value reduced.
  • a vibration generator is described in DE 199 43 391 A1, in which the phase position of the flyweights is adjustable so that cancel the vertical components of the centrifugal forces generated by the flyweights in each rotational position, while the horizontal components of the centrifugal forces add up accordingly rectified ,
  • the invention is therefore based on the object of further developing a vibration exciter of the aforementioned type such that an excessively strong compaction of the soil during standstill due to strong Vertikalschwinguhgen can be avoided without the operator or the soil to be compacted in turn is exposed to strong horizontal vibrations.
  • a vibration exciter preferably has two imbalance shafts, which can be driven in opposite directions and are driven in opposite directions, each carrying a stationary imbalance mass and an imbalance mass which is rotatable relative to the stationary imbalance mass or the respective imbalance shaft.
  • Each of the unbalanced shafts is associated with an adjusting device with which the relative position of the respective movable imbalance mass with respect to the imbalance shaft carrying it can be adjusted.
  • the relative positions of the movable imbalance masses with respect to the unbalanced shafts carrying them adjustable by the adjusting so that cancel the centrifugal forces generated by the imbalance masses upon rotation of the unbalanced shafts in their entirety in each rotational position of the unbalanced shafts.
  • the relative position on each of the unbalanced shafts is adjustable so that cancel the centrifugal forces carried by this unbalance shaft imbalance masses in each rotational position of the imbalance shaft. This means that already in the operation with only one imbalance shaft, a relative position can be achieved, in which there is no vibration effect.
  • the relative positions can be changed such that the centrifugal forces of the unbalanced masses do not cancel, but that a resulting total centrifugal force has a horizontal component. This can cause a movement of the vibrating plate, as known from the prior art effect.
  • a forward and a reverse direction is temporarily the already described stand position in which no vibration acts in the ground. This can be avoided even when changing direction in the reversing unwanted vertical or horizontal vibrations. Because the adjustment of the movable imbalance masses is sufficient to produce the resulting centrifugal force with the desired direction and size, it is not necessary in a preferred embodiment that the phase position of the unbalanced shafts must be mutually variable, as z. B. in the vibration generator described in DE 100 38 206 A1 is the case.
  • axle mass is meant abstractly in the context of this description.
  • an imbalance mass also consist of several imbalance elements, which are distributed on the respective imbalance shaft.
  • vibration exciters are known in many forms. Likewise are - such. B. in DE 199 43 391 A1 set forth - so-called "Phaseneinstell Tooen", ie adjusting means for adjusting relative positions between imbalance masses and unbalanced shafts known. Since the invention does not relate to the detailed and specific design of a particular vibration exciter or a particular adjustment device, but rather a relative position (phase position) which is particularly suitable but hitherto unknown, a detailed description of the vibration exciter is not required.
  • two imbalance shafts 2, 3 are rotatably mounted, wherein the imbalance shaft 2 is driven in rotation by a drive, not shown.
  • the imbalance shaft 2 carries unbalance elements 4 and 5, with the imbalance shaft. 2 are firmly connected and form a fixed imbalance mass.
  • a rotatably movable imbalance mass 6 is arranged on the imbalance shaft 2, which is rotatable relative to the imbalance shaft 2 via a hub 7 and bearing 8.
  • the relative position between the movable imbalance mass 6 and the imbalance shaft 2 is determined by means of an adjustment 9.
  • the operating principle of such an adjustment has long been known and z.
  • the adjusting device 9 essentially has a piston 10, which is axially adjustable under hydraulic action and which is axially reciprocable in a hollow region of the imbalance shaft 2.
  • the piston 10 carries a transverse pin 11, which penetrates two formed in the wall of the imbalance shaft 2 longitudinal grooves 12 and engages in spiral grooves 13 which are formed on the inside of the hub 7.
  • the hub 7 and the movable imbalance mass 6 supported by it thus rotate relative to the imbalance shaft 2.
  • the imbalance shaft 2 further carries a gear 14 which meshes with a gear 15 which is mounted on the imbalance shaft 3.
  • a gear 14 which meshes with a gear 15 which is mounted on the imbalance shaft 3.
  • the rotational movement of the driven imbalance shaft 2 is positively transmitted to the imbalance shaft 3, which thus rotates in opposite directions, but at the same speed.
  • the imbalance shaft 3 carries two imbalance elements 16, 17, which together form a fixed imbalance mass. Furthermore, an imbalance mass 18 rotatably movable on the imbalance shaft 3 is provided, whose relative position with respect to the imbalance shaft 3 can be adjusted by means of an adjusting device 19. Since the adjuster 19 has the same structure as the adjuster 9, a detailed description will be omitted.
  • the position of the imbalance mass shown in the section of FIG. 1 corresponds to the relative position according to the invention, in which the individual centrifugal forces generated by the respective imbalance masses or elements cancel in their entirety (standing position).
  • the associated mr values (products of mass m x radius r of the unbalance center of gravity) must be matched to one another accordingly.
  • the unbalanced shafts 2 and 3 can rotate without causing an outward unbalance and thus a vibration.
  • this equilibrium state is canceled, so that the desired vertical and horizontal vibrations can arise for soil compaction.
  • FIG. 2 shows highly schematic side views from the right in FIG. 1.
  • the hatched semicircles correspond to the movable, ie adjustable unbalanced masses 6, 18, while the non-hatched semicircles should correspond to the imbalance waves 2, 3 fixed imbalance masses 4, 5 and 16, 17, as z. B. in the field a) "state" of Fig. 2 can be seen.
  • the movable imbalance mass 6 has been rotated by 90 ° relative to the stationary imbalance elements 4, 5 and to the imbalance shaft 2.
  • the movable imbalance mass 18 was rotated with respect to the fixed imbalance elements 16, 17 on the imbalance shaft 3 by 90 ° in the same direction as the movable imbalance mass 6.
  • the corresponding state is in Fig. 2a) in the column "forward” shown.
  • different rotational states of the imbalance shafts 2, 3 are shown in the "forward" column under a) to d).
  • Fig. 2c creates a corresponding counteraction to the bottom right.
  • the vibration plate is supported on the ground and introduces the vibration energy into the ground.
  • a backward movement of the vibrating plate (to the right in FIG. 2) is shown in the right-hand column of FIG.
  • the movable imbalance masses 6 and 18 with respect to the unbalanced shafts 2, 3 carrying them in opposite direction to the forward direction and with respect to the position have been rotated by 90 °, as shown in Fig. 2a) in the column "backwards" recognizable.
  • the positions of the imbalance masses shown in Fig. 2 are extreme positions. Depending on the configuration of the adjusting devices 9, 19, any intermediate positions, ie. H. reach other adjustment angle than 90 °, so that a continuous change between forward drive, stationary operation and reverse drive can be achieved.
  • the setting devices 9, 19 it is possible for the setting devices 9, 19 to resort to known means, such as hydraulic control, electric motors, electromechanical actuators, etc.
  • a control of the movable imbalance masses using simple train-pressure cables can be carried out, which can be controlled by the operator via a common encoder. This can save considerable costs even with simpler vibratory plates.
  • the adjustment of the relative positions by the adjusting means 9, 19 should be carried out synchronously.
  • vibration exciter according to the invention to assume other relative positions than those shown in FIG.
  • adjustment means 9, 19 can be z. B. achieve relative positions in which, although no vertical vibrations, but strong horizontal vibrations are generated at standstill of the vibrating plate, as known in DE 199 43 391 A1.

Claims (10)

  1. Oscillateur destiné à des engins de compactage du sol avec des arbres à balourd (2, 3) placés parallèlement ou coaxialement l'un par rapport à l'autre, pouvant être entraînés en sens inverse à la même vitesse de rotation, chacun des arbres à balourd (2, 3) portant un balourd (4, 5 ; 16, 17) fixé sur lui et un balourd (6, 18) mobile en rotation par rapport à lui, et un dispositif de réglage (9, 19) étant associé à chacun des arbres à balourd (2, 3) pour le réglage de la position relative du balourd mobile (6, 18) par rapport à l'arbre à balourd respectif (2, 3) qui le porte, caractérisé en ce que
    - les positions relatives sont réglables au moyen des dispositifs de réglage (9, 19) pendant le fonctionnement de telle manière que les forces centrifuges générées par les balourds (4, 5 ; 16, 17 ; 6, 18) lors de la rotation des arbres à balourd (2, 3) s'équilibrent dans chaque position de rotation des arbres à balourd (2, 3) dans leur ensemble, et en ce que
    - une modification des positions relatives est réalisable de telle manière que la valeur d'une force centrifuge totale résultant des balourds est proportionnelle à une vitesse de déplacement de l'engin de compactage du sol.
  2. Oscillateur selon la revendication 1, caractérisé en ce que la position relative est ajustable sur chacun des arbres à balourd (2, 3) de telle manière que les forces centrifuges des balourds (4, 5 ; 16, 17 ; 6, 18) portés par cet arbre à balourd s'équilibrent dans chaque position de rotation de l'arbre à balourd.
  3. Oscillateur selon la revendication 1 ou 2, caractérisé en ce que, pour provoquer un déplacement de l'engin de compactage du sol dans une première direction horizontale, les positions relatives peuvent être modifiées de telle manière que les forces centrifuges des balourds ne s'équilibrent pas, mais qu'une force centrifuge totale résultant des forces centrifuges présente une composante horizontale.
  4. Oscillateur selon la revendication 3, caractérisé en ce que, lors d'un changement entre la première direction et une deuxième direction opposée, les positions relatives définies dans la revendication 1 peuvent être prises temporairement.
  5. Oscillateur selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la modification des positions relatives est réalisable en continu.
  6. Oscillateur selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les arbres à balourd (2, 3) sont couplés mécaniquement l'un à l'autre en rotation dans le sens opposé.
  7. Oscillateur selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la relation des phases des arbres à balourd (2, 3) l'un par rapport à l'autre n'est pas modifiable.
  8. Oscillateur selon l'une quelconque des revendications 1 à 7, caractérisé en ce que le réglage des positions relatives au moyen des dispositifs de réglage (9, 19) sur les arbres à balourd (2, 3) est réalisable de manière synchrone.
  9. Oscillateur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les dispositifs de réglage (9, 19) sont actionnables électriquement, hydrauliquement, pneumatiquement ou mécaniquement.
  10. Oscillateur selon l'une quelconque des revendications 1 à 9, caractérisé en ce qu'au moins une partie des balourds est constituée de plusieurs éléments de balourd (4, 5 ; 16, 17).
EP03793804A 2002-09-05 2003-09-04 Oscillateur destine a des engins de compactage du sol Expired - Lifetime EP1534439B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10241200A DE10241200A1 (de) 2002-09-05 2002-09-05 Schwingungserreger für Bodenverdichtungsgeräte
DE10241200 2002-09-05
PCT/EP2003/009822 WO2004022250A1 (fr) 2002-09-05 2003-09-04 Oscillateur destine a des engins de compactage du sol

Publications (2)

Publication Number Publication Date
EP1534439A1 EP1534439A1 (fr) 2005-06-01
EP1534439B1 true EP1534439B1 (fr) 2007-01-03

Family

ID=31895679

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03793804A Expired - Lifetime EP1534439B1 (fr) 2002-09-05 2003-09-04 Oscillateur destine a des engins de compactage du sol

Country Status (7)

Country Link
US (1) US20060067796A1 (fr)
EP (1) EP1534439B1 (fr)
JP (1) JP4314194B2 (fr)
CN (1) CN100348339C (fr)
DE (2) DE10241200A1 (fr)
HK (1) HK1082458A1 (fr)
WO (1) WO2004022250A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022127864A1 (de) 2022-10-21 2024-05-02 Inecosys Gmbh Schwingungserzeuger

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005029432A1 (de) * 2005-06-24 2006-12-28 Wacker Construction Equipment Ag Bodenverdichtungsvorrichtung mit automatischer oder bedienerintuitiver Verstellung des Vorschubvektors
FR2971571B1 (fr) 2011-02-15 2013-02-08 Renault Sas Moteur a combustion interne equipe d'arbres d'equilibrage et procede de pilotage d'un tel moteur
DE102011112316B4 (de) 2011-09-02 2020-06-10 Bomag Gmbh Schwingungserreger zur Erzeugung einer gerichteten Erregerschwingung
EP2669436B1 (fr) * 2012-05-30 2014-12-31 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Dispositif de battage et de traction
DE102013021494B4 (de) 2012-12-28 2023-11-30 Bomag Gmbh Vibrationsplatte mit einem Schwingungserreger
US20160349143A1 (en) * 2015-06-01 2016-12-01 Peter S. Aronstam Systems, Methods, and Apparatuses For a Vibratory Source
AT523034A3 (de) * 2019-09-18 2024-02-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Maschine und Verfahren zum Stabilisieren eines Gleises

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1095752B (de) * 1959-03-19 1960-12-22 Losenhausenwerk Duesseldorfer Unwuchtruettler, insbesondere fuer Bodenverdichter, mit gegenlaeufig umlaufenden Unwuchtwellen
DE3806897A1 (de) * 1988-03-03 1989-09-14 Wacker Werke Kg Schwingungserreger
US5177386A (en) * 1990-08-30 1993-01-05 Kencho Kobe Co., Ltd. Vibration generator adjustable during operation
CN2111143U (zh) * 1991-07-10 1992-07-29 龙天民 椭圆轨迹高效振动筛新型激振器
DE10038206C2 (de) * 2000-08-04 2002-09-26 Wacker Werke Kg Regelbarer Schwingungserreger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022127864A1 (de) 2022-10-21 2024-05-02 Inecosys Gmbh Schwingungserzeuger

Also Published As

Publication number Publication date
JP2006501049A (ja) 2006-01-12
CN100348339C (zh) 2007-11-14
CN1678410A (zh) 2005-10-05
JP4314194B2 (ja) 2009-08-12
EP1534439A1 (fr) 2005-06-01
US20060067796A1 (en) 2006-03-30
DE50306207D1 (de) 2007-02-15
WO2004022250A1 (fr) 2004-03-18
DE10241200A1 (de) 2004-03-25
HK1082458A1 (en) 2006-06-09

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