EP0789801B1 - Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture - Google Patents

Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture Download PDF

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Publication number
EP0789801B1
EP0789801B1 EP96929220A EP96929220A EP0789801B1 EP 0789801 B1 EP0789801 B1 EP 0789801B1 EP 96929220 A EP96929220 A EP 96929220A EP 96929220 A EP96929220 A EP 96929220A EP 0789801 B1 EP0789801 B1 EP 0789801B1
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EP
European Patent Office
Prior art keywords
vibratory roller
tyre
unbalanced
roller according
ground
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
EP96929220A
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German (de)
English (en)
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EP0789801A1 (fr
Inventor
Gülertan Vural
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 Werke GmbH and Co KG
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Wacker Werke GmbH and Co KG
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Publication of EP0789801A1 publication Critical patent/EP0789801A1/fr
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Anticipated expiration legal-status Critical
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/288—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows adapted for monitoring characteristics of the material being compacted, e.g. indicating resonant frequency, measuring degree of compaction, by measuring values, detectable on the roller; using detected values to control operation of the roller, e.g. automatic adjustment of vibration responsive to such measurements
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll

Definitions

  • the invention relates to a vibratory roller according to the Preamble of claim 1.
  • Vibratory rollers are known from EP 0 530 546 A1.
  • At these known vibratory rollers are the two unbalanced shafts of the double-wave vibration exciter parallel to each other on opposite Symmetrical sides of the travel axis of the respective drum to this rotatably mounted in a common exciter housing, that in turn in the common carrier in the respective Roller drum is pivotally mounted.
  • One of the two unbalanced shafts is rotatable by gears from a hydraulic drive motor driven and via gears with the other drive shaft so coupled that the two unbalanced shafts always with mutually the same speed in opposite directions in the exciter housing circulate.
  • the flyweights of the two unbalanced shafts have one another same mass and same level of focus, so that the vibration exciter located in the two bandages each generate a directional vibration that is radial to the driving axis of the bandage in question and its direction from the spatial adjustment of the housing of the unbalanced shafts dependent is.
  • EP 0 530 546 A1 can advantageously be used in Association with soil types that are best through exercise of shear stresses and combinations of shear and compressive stresses have it compacted, and it is also very suitable for economical compaction of relatively large layer thicknesses.
  • This torque therefore increases proportionally with I and the angular acceleration ⁇ W / ⁇ t. This means that the greater the torques required, the shorter the pivoting time is applied and the greater the moment of inertia I of the excitation system. However, the greater the torque required, the more complicated the control process becomes.
  • the complete structure of the excitation system can be swiveled containing exciter housing and the additional swivel bearings a high technical effort and costly are.
  • the two arranged one behind the other with the described vibration exciter equipped roller drum has the in Direction of travel front roller drum a greater rolling resistance than the back one.
  • the parallel, hydraulic travel drive system turns on the larger drive torques required.
  • For the rear roller is the drive torque is then too large. This will hatch the Rolls favored.
  • a possible anti-slip regulation tries to slip through different angles the vibration exciter in the front and in the rear To prevent bandage. But this means that the two roller bandages different compressive and shear stresses on the floor exercise, which in turn change constantly while driving. Also this creates an undesirable inhomogeneous compression. This inhomogeneous compression is caused by the coefficient of friction between Roller drum and floor, due to changes in rolling resistance and additionally due to incorrect driver behavior even more uncontrollable.
  • Another known vibratory roller (EP 053 598 A1) has two unbalanced shafts arranged parallel to the roller axis, which synchronously Rotate with the same direction of rotation, but by 180 ° in relation to each other are out of phase. The order is made that the vertical forces generated by the unbalanced shafts compensate each other while the opposite horizontal forces a torque on the drum around the drum rotation or Generate travel axis around. This torque exerts one of its size after unchangeable shear stress on the floor. Investigations have shown that this solution for the compression of thin-layered, rolled and bituminous material with advantage is applicable, and also with regard to the required low Noise and vibration nuisance for the operating personnel leads to beneficial results.
  • Vibratory roller In contrast, this is known Vibratory roller, however, cannot be used economically in general with thicker layers and with non-rolled material, e.g. for mixed soils, cohesive soils and rocks. In addition, the known roller is very susceptible to slippage, which is particularly the case with Inclines or slopes lead to traction problems. Besides, is the known roller according to EP 053 598 A1 is structurally very complex, because the unbalanced shafts are far from the drum axis must be stored so that they generate the desired torque can.
  • CH-B-271 578 is a vibration plate with one on the Ground contact plate shown vibrator and described, the two coaxially arranged to one another common rotational axis revolving unbalanced shafts, the by means of a counter-rotating circuit with synchronous speed permanently coupling differential gear in their mutual Phases are adjustable so that it is possible to change the direction of action the directional vibration generated by the unbalanced shafts to adjust with respect to the ground contact plate.
  • the vibration plate can be self-propelled in forward and reverse operate.
  • Vibration drives for vibrating machines all of them have coaxial unbalanced shafts.
  • the vibration drives are specially designed for use with vibrating screens and conveyors and vibrators.
  • the unbalanced shafts without the possibility of adjusting the mutual phase relationship during operation forcibly driven in opposite directions.
  • this one different embodiment however requires a drive with the same direction of rotation a separate drive for each unbalanced shaft, which is a considerable one due to technical effort.
  • the Vibratory roller according to the invention by a simple constructive Design, low susceptibility to failure and long service life.
  • the vibratory roller according to the invention can optimally match the adapted to different needs of the soil to be compacted be, in such a way that the beneficial effects of maintain various known vibratory rollers, whose disadvantages are avoided.
  • the vibratory roller according to the invention thereby also in that the moment of inertia of the vibration exciter with regard to the driving axis of the respective drum low, compared to the vibratory roller according to EP 0 530 546 A1 e.g. is practically at least ten times smaller, so that the vibration exciter in the setting to initiate a directed vibration force on the drum travel axis for change the direction of the directional vibration of a much smaller one Torque than in the known roller and accordingly in a much shorter time in the new direction can be pivoted so that it is possible to have inhomogeneities and to minimize dents in the compacted soil.
  • the device according to the invention is for the different types of soil and layer thicknesses by one of the many offered Options selected corresponding basic setting of the Vibration excitation system and the various generated thereby Shear and compressive stress combinations an optimal compression achievable, and it can also cause slip in within a permissible range.
  • Subclaims 2 to 18 relate to preferred embodiments the vibratory roller according to claim 1.
  • the invention also relates to a particularly advantageous method to operate the vibratory roller according to claim 1. This The method is the subject of claims 19 to 22.
  • the vibrating roller shown in Fig. 1 has two in the direction of travel roller drums 1 and 2 arranged one behind the other.
  • a frame 2a is arranged on the roller drum 1
  • on the Roller drum 2 is a frame 2b with a driver's station.
  • the Frames 2a and 2b are designed to steer the vibratory roller over one vertical swivel pendulum bearing 29 connected to each other.
  • roller bandages 1 and 2 there is a double-shaft vibration exciter S arranged, the structure of which in detail Fig. 2 can be seen.
  • roller drum 1 there are two inside each roller drum 1, 2 unbalanced shafts 3 and 4 arranged coaxially to one another, the an - inner - unbalanced shaft 3 with the help of roller bearings 3b on the end face in the other - outer - unbalance shaft encasing them 4 is rotatably mounted.
  • the outer unbalanced shaft 4 is on with the help of roller bearings 5.6 their ends in one or the other of two in the Roller bandages 1 and 2 arranged, these diagonally in mutual Distance crossing carriers 1a and 1b rotatable in one such a position that its axis of rotation 28, the same time represents the axis of rotation of the inner unbalanced shaft 3, with the Bandage travel axis coincides around which the drum bandages are located 1, 2 rotates relative to the drum support 23 and 24, respectively, on the respective roller frame 2a or 2b on one or the other Side of the bandages 1 and 2 is attached and the front somewhat in the bandage protrudes.
  • the outer Unbalance shaft 4 has a bevel gear 14 coaxial with the axis of rotation 28.
  • the inner unbalanced shaft 3 has a through the left front End of the outer unbalanced shaft 4 and by the attached to this Bevel gear 14 extending extension 13a on which Bevel gear 14 turned, a bevel gear 11 at an axial distance therefrom is attached, the same diameter in the embodiment and has the same number of teeth as the bevel gear 14 the outer unbalanced shaft 4.
  • the chassis bearing 17 points to the position for the viewer of FIG. 2 left side on a collar concentric to the driving axis 28, with which it is supported in a bearing plate 21 via a roller bearing 20, which is attached to the drum support 23 via a buffer 22.
  • the drum support 23 forms a non-rotatable unit bearing plate 21 carries a drive motor 9 coaxial with the driving axis 28 Drive shaft, which has a tubular extension on the web 15 of the Differential gear housed clutch 10 with the extension 3a of the inner unbalanced shaft 3 is connected.
  • roller drum 1 or 2 On the right side for the viewer of FIG. 2 is the roller drum 1 or 2 on the bandage carrier 24 there via a Bearing plate 26 stored, the buffer on which the bandage diagonally crossing carrier 1a is fixed and coaxial to Travel axis 28 in a not shown in FIG. 2 in detail Bearing is supported on the drum support 24.
  • a drive motor 25 On the bandage support 24 a drive motor 25 is attached, with which the bearing plate 26 with respect to the drum support 24 about the driving axis 28 in rotation is relocatable.
  • the vibration exciter S described above with his unbalanced shafts connected at one end via the differential gear 3 and 4 is in two different settings of the differential gear operable with respect to the neighboring device parts.
  • setting I is the housing-like web 15 of the differential gear fixed relative to the carrier plate 21 via the gearwheel 16, stands still with this, however, its angular position opposite the bearing plate 21 with the aid of a gear 16 engaging gear 30 adjustable by a motor 31 (Fig. 3) controlled in a coaxial manner with respect to the driving axis 28.
  • the spatial phase position of the two unbalanced shafts 3 and 4 that is to say the swivel angle ⁇ of the vibration exciter S, is selected such that the centrifugal forces generated by the unbalances increase in the horizontal direction in the vertical direction in the phase direction shown in FIG. 4, in the vertical direction 5, however, compensate for the centrifugal forces generated by the imbalances in the vertical direction and compensate in the horizontal direction, and in the phase position according to FIG reinforce the defined direction and compensate perpendicular to this direction.
  • the vibrating forces emanating from the unbalanced shafts 3 and 4 are transmitted in each case via the bearings 5 and 6 and the bearing housings 7 and 8 to the carriers 1a and 1b and, via these, to the respective jacket of the roller drum 1 or 2.
  • the motor 9 is preferably a hydraulic motor.
  • phase adjustment by means of the servomotor 31 and the gears 30 and 16 can be controlled manually, but also automatically controlled.
  • Fig. 7 shows the function of a control circuit for automatic control of the phase position of the unbalanced shafts 3 and 4 in such a way that slippage of the roller bandages 1 and 2 is counteracted on the soil to be compacted.
  • the difference values ⁇ and ⁇ are determined by a comparison element 37, which is also not shown in detail in the drawing. If the values ⁇ and ⁇ are above a predetermined value that can be preset by means of a setpoint generator 40, then the two adjusting motors 31 1 and 31 2 of the roller bandages 1 and 2 are activated by an amplifier 38 in such a way that the angular position of the vibration exciter S in the sense of a Magnification of the horizontal component of the resulting centrifugal force is changed until the slip determined by the comparison element 37 is below the set limit value.
  • This new swivel angle value is set synchronously for both roller bandages 1 and 2.
  • the set or adjusted swivel angle value of the centrifugal force is automatically positioned in mirror image with respect to the vertical in the direction of travel. The positioning is preferably carried out as follows:
  • the swivel angle of the excitation force vector is in the range of 0 ° to 45 °, it adjusts clockwise as a mirror image, and if it is in the range of 45 ° to 90 °, it adjusts itself counter-clockwise as a mirror image.
  • a preprogrammed one installed on the vibratory roller for this purpose Command instrument can allow the driver to make the basic settings manually.
  • the application-oriented basic setting of the swivel angle the force vector of the vibration exciter S e.g. with both roller bandages a tandem roller due to rolling resistance and Coefficient of friction between the roller and the floor in particular increasing weight distribution differences between those in the direction of travel front first roller and the second roller are not sufficient to eliminate the slippage of one roller, then preferably the simple one already discussed above Regulation used, according to which the pre-programmed basic settings of the excitation system intervene correctively with a tandem roller with both roller drums.
  • the unbalanced shafts 3 and 4 are different from the basic setting I described above also in a Basic setting II adjustable, in which they are in the same direction turn and in their relative phase position to adjust the The size of the resulting centrifugal force can be adjusted and fixed is.
  • the unbalance shaft 3 is also of the hydraulic motor 9 on the installed between this and her Coupling 10 driven. Changes and fixations of the Phase position of the unbalanced shaft 3 relative to the unbalanced shaft 4 easily done as follows:
  • the unbalance shaft 3 is first of all driven by the hydraulic motor 9 in their current position and then the housing-like Web 15 of the differential gear manually (drawing not shown) or with an adjustment mechanism, e.g. the in 3 to be seen, i.e. with the hydraulic motor 31 and the gear pair 30, 16, if necessary adjusted in such a way until the changing phase position between the unbalanced shafts 3 and 4 has reached a desired value. Then the now prevailing mutual phase position of the unbalanced shafts 3 and 4 fixed, for which purpose only between the output shaft of the hydraulic motor 9 and the web 15 e.g. by means of a switchable clutch (not shown in the drawing) established a rigid connection and at the same time the connection between the gears 16 and 30 needs to be solved.
  • an adjustment mechanism e.g. the in 3 to be seen, i.e. with the hydraulic motor 31 and the gear pair 30, 16, if necessary adjusted in such a way until the changing phase position between the unbalanced shafts 3 and 4 has reached a desired value.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Vibration Prevention Devices (AREA)

Claims (22)

  1. Rouleau vibrant comportant au moins un bandage (1) et un générateur de vibrations (S) à double arbre disposé dans ce bandage, dont les arbres à balourd, entraínés par un dispositif d'entraínement (9) commun, sont montés tournants dans un support (1a, 1b) commun, qui se trouve dans le bandage (1) du rouleau, avec chacun un axe de rotation parallèle à l'axe de roulement (28) du bandage (1) du rouleau,
    dans lequel
    les arbres à balourd (3, 4) sont conçus et disposés dans le support (1a, 1b), l'un par rapport à l'autre, ainsi que par rapport au bandage (1), de manière qu'un arbre à balourd (4)- extérieur - entoure coaxialement en rotation l'autre arbre à balourd (3)-intérieur - et de manière que l'axe de rotation commun des arbres à balourd (3, 4) coïncide avec l'axe de roulement (28) du bandage (1) du rouleau, et
    les arbres à balourd peuvent être accouplés entre eux pour un état de fonctionnement, dit deuxième état de fonctionnement, dans lequel ils impriment au bandage du rouleau une vibration circulaire, de manière à tourner dans le même sens, leur position de phase relative pouvant être réglée et fixée en vue du réglage de la grandeur de la force centrifuge résultante,
    caractérisé en ce que
    les arbres à balourd peuvent être accouplés entre eux pour un autre état de fonctionnement, dit premier état de fonctionnement, dans lequel ils produisent une vibration dirigée, de manière à tourner en sens contraire et de manière que l'angle (α ou α + 180°) que les directions de la force centrifuge maximale résultante forment avec le sens de roulement du bandage (1) du rouleau, puisse être réglé et fixé dans une mesure quelconque.
  2. Rouleau vibrant selon la revendication 1, caractérisé en ce que les arbres à balourd (3, 4) sont montés dans le bandage (1) du rouleau, de manière à ne pas influencer son mouvement de rotation.
  3. Rouleau vibrant selon la revendication 1 ou 2, caractérisé en ce que deux parois frontales (1a, 1b) du bandage (1), situées à distance axiale, et dans lesquelles sont intégrés des boítiers de palier (7, 8) avec des premiers roulements (5, 6) destinés à supporter l'arbre à balourd extérieur (4), servent de support.
  4. Rouleau vibrant selon la revendication 3, caractérisé en ce que les premiers roulements (5, 6) servent en même temps de paliers de roulement par lesquels le bandage (1) est monté sur le train de roulement (23, 24) du rouleau vibrant.
  5. Rouleau vibrant selon la revendication 3 ou 4, caractérisé en ce que l'arbre à balourd intérieur (3) est monté dans l'arbre à balourd extérieur (4), au moyen de deuxièmes roulements (3b), qui sont intégrés dans l'arbre à balourd extérieur (4), à proximité du boítier de palier (7).
  6. Rouleau vibrant selon l'une des revendications précédentes, caractérisé en ce que dans le premier état de fonctionnement, l'angle (α ou α + 180°) peut varier sur toute la plage de 360°, entre le vecteur de la vibration orientée et le plan parallèle au sol, qui contient l'axe de roulement (28).
  7. Rouleau vibrant selon l'une des revendications précédentes, caractérisé en ce que pour le deuxième état de fonctionnement, il est possible de procéder à la main, à l'arrêt du générateur de vibrations ou automatiquement à l'accouplement des arbres à balourd (3, 4) pour la rotation dans le même sens, et au réglage ainsi qu'à la fixation de la position de phase relative des arbres à balourd (3, 4).
  8. Rouleau vibrant selon l'une des revendications précédentes, caractérisé en ce qu'au moins dans le deuxième état de fonctionnement, le sens de rotation des arbres à balourd (3, 4) peut être inversé.
  9. Rouleau vibrant selon l'une des revendications précédentes, caractérisé en ce que pour le premier état de fonctionnement, il est possible de procéder à la main à l'arrêt du générateur de vibrations, à l'accouplement des arbres à balourd (3, 4) pour la rotation en sens contraire et au réglage ainsi qu'à la fixation de l'angle (α ou α + 180°) entre le vecteur de la vibration orientée et le plan parallèle au sol, qui contient l'axe de roulement (28).
  10. Rouleau vibrant selon l'une des revendications 1 à 8, caractérisé en ce que pour le premier état de fonctionnement, il est possible de procéder automatiquement, à l'accouplement des arbres à balourd (3, 4) pour la rotation en sens contraire et au réglage ainsi qu'à la fixation de l'angle (α ou α + 180°) entre le vecteur de la vibration orientée et le plan parallèle au sol, qui contient l'axe de roulement (28).
  11. Rouleau vibrant selon la revendication 10, caractérisé en ce que les arbres à balourd (3, 4) peuvent être accouplés entre eux à leurs extrémités au moyen d'un différentiel (11 à 15), qui comporte deux roues centrales (11, 14) tournant en sens contraire et présentant un même nombre de dents, dont une (11) est calée solidairement en rotation et coaxialement sur l'arbre à balourd intérieur (3), et l'autre (14) est disposée solidairement en rotation et coaxialement sur l'arbre à balourd extérieur (4), et dont on peut faire tourner autour de son axe de rotation (28) la traverse (15), au moyen d'un mécanisme de positionnement (30, 31, 16), pour faire varier la position de phase relative des arbres à balourd (3, 4), et on peut la fixer dans toute position angulaire réglée par rapport aux supports (21, 22, 23, 24) du bandage du rouleau vibrant.
  12. Rouleau vibrant selon la revendication 11, caractérisé en ce que le différentiel (11 à 15) est réalisé en tant qu'engrenage à roues coniques.
  13. Rouleau vibrant selon la revendication 11 ou 12, caractérisé en ce que la traverse (15) forme un boítier de pivotement qui passe sur une extrémité (3a) d'un arbre à balourd (3), et dont une face frontale est tournée vers le support (21, 22, 23) du bandage et qui supporte une roue dentée de réglage (16) coaxiale à l'axe de roulement (28) du bandage (1), laquelle engrène avec le pignon (30) ou similaire d'un servomoteur (31), fixé sur le support de bandage (21, 22, 23), du mécanisme de positionnement (30, 31, 16).
  14. Rouleau vibrant selon l'une des revendications 11 à 13, caractérisé en ce que pour provoquer le deuxième état de fonctionnement, la traverse (15) du différentiel (11 à 15) peut être accouplée à l'un (3) des arbres à balourd (3, 4) et l'engagement entre le pignon (30) du servomoteur (31) et la roue dentée (16) peut être supprimé.
  15. Rouleau vibrant selon l'une des revendications 11 à 14 précédentes, caractérisé en ce que la traverse (15) est montée de manière à pouvoir tourner dans un support (17) qui est fixé à l'une (1b) des parois frontales (1a, 1b) du rouleau.
  16. Rouleau vibrant selon la revendication 15, caractérisé en ce que le support (17) entoure le différentiel (11 à 15) en tant que boítier de protection.
  17. Rouleau vibrant selon l'une des revendications précédentes, caractérisé par un élément comparateur (37), actif dans le premier état de fonctionnement, qui compare entre eux, d'une part des signaux fournis par un transmetteur (35 ou 37), dérivés d'un bandage (1 ou 2) non glissant, correspondant à sa vitesse angulaire (ω1, ω2), et à son accélération angulaire (ξ1 ou ξ2), et d'autre part des signaux fournis par un transmetteur (35 ou 36), dérivés d'un bandage (1 ou 2) tendant au glissement, correspondant à sa vitesse angulaire (ω1, ω2), et à son accélération angulaire (ξ1 ou ξ2), et en cas de dépassement d'une différence déterminée (Δω et Δξ) de ces signaux, active un organe de réglage (31) qui à son tour réduit en conséquence l'angle a que le vecteur de la vibration dirigée forme avec le plan parallèle au sol, qui contient l'axe de roulement (28).
  18. Rouleau vibrant selon l'une des revendications précédentes, caractérisé en ce que les arbres à balourd (3, 4) ont le même moment d'inertie (m*r).
  19. Procédé de conduite du rouleau vibrant selon l'une des revendications précédentes, caractérisé en ce que dans le premier état de fonctionnement, l'angle (α) que le vecteur de la vibration dirigée forme avec le plan parallèle au sol, qui contient l'axe de roulement (28), est réglé sur 0° à 45° pour un sol non cohérent ou bitumineux, et sur 45° à 90° pour un sol difficilement compactable.
  20. Procédé selon la revendication 19, caractérisé en ce l'angle (α) que le vecteur de la vibration dirigée forme avec le plan parallèle au sol, qui contient l'axe de roulement (28), est réglé de manière programmée en fonction de l'épaisseur de la couche de sol à compacter.
  21. Procédé selon la revendication 19 ou 20, caractérisé en ce que dans le cas d'un changement de sens de marche, le vecteur de la vibration dirigée est modifié automatiquement dans une symétrie en miroir par rapport au plan parallèle au sol qui contient l'axe de roulement (28).
  22. Procédé selon la revendication 20 ou 21, caractérisé en ce l'angle (α) que le vecteur de la vibration dirigée forme avec le plan parallèle au sol, qui contient l'axe de roulement (28), est réduit de manière programmée chaque fois que le rouleau vibrant passe sur le sol à compacter.
EP96929220A 1995-08-08 1996-08-07 Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture Expired - Lifetime EP0789801B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19529115A DE19529115A1 (de) 1995-08-08 1995-08-08 Vibrationsmechanismus, insbesondere zur Verwendung zur Verdichtung von Böden
DE19529115 1995-08-08
PCT/EP1996/003499 WO1997006308A1 (fr) 1995-08-08 1996-08-07 Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture

Publications (2)

Publication Number Publication Date
EP0789801A1 EP0789801A1 (fr) 1997-08-20
EP0789801B1 true EP0789801B1 (fr) 2001-09-26

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP96929220A Expired - Lifetime EP0789801B1 (fr) 1995-08-08 1996-08-07 Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture

Country Status (6)

Country Link
US (1) US5934824A (fr)
EP (1) EP0789801B1 (fr)
JP (1) JP3778939B2 (fr)
CA (1) CA2202132C (fr)
DE (2) DE19529115A1 (fr)
WO (1) WO1997006308A1 (fr)

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19911913A1 (de) * 1999-03-17 2000-09-21 Beissbarth Gmbh Reifenprüfverfahren und -Vorrichtung
SE513571C2 (sv) * 1999-03-18 2000-10-02 Ulf Bertil Andersson Anordning för alstring av mekaniska vibrationer
DE19943391A1 (de) * 1999-09-10 2001-04-12 Wacker Werke Kg Schwingungserreger für Bodenverdichtungsgeräte
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JPH10507504A (ja) 1998-07-21
WO1997006308A1 (fr) 1997-02-20
DE59607775D1 (de) 2001-10-31
DE19529115A1 (de) 1997-03-06
CA2202132A1 (fr) 1997-02-20
EP0789801A1 (fr) 1997-08-20
CA2202132C (fr) 2001-07-10
JP3778939B2 (ja) 2006-05-24
US5934824A (en) 1999-08-10

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