EP0789801B1 - Vibratory roller with at least one tyre having a built-in twin-shaft vibration generator - Google Patents

Vibratory roller with at least one tyre having a built-in twin-shaft vibration generator 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
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Expired - Lifetime
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EP96929220A
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German (de)
French (fr)
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EP0789801A1 (en
Inventor
Gülertan Vural
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Wacker Werke GmbH and Co KG
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Wacker Werke GmbH and Co KG
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    • 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)

Description

Die Erfindung bezieht sich auf eine Vibrationswalze gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a vibratory roller according to the Preamble of claim 1.

Vibrationswalzen sind aus EP 0 530 546 A1 bekannt. Bei diesen bekannten Vibrationswalzen sind die beiden Unwuchtwellen des Doppelwellen-Schwingungserregers parallel zueinander auf entgegengesetzten Seiten der Fahrachse der jeweiligen Bandage symmetrisch zu dieser in einem gemeinsamen Erregergehäuse drehbar gelagert, das wiederum in dem gemeinsamen Träger in der jeweiligen Walzenbandage verschwenkbar gelagert ist. Eine der beiden Unwuchtwellen ist über Zahnräder drehbar von einem hydraulischen Antriebsmotor angetrieben und über Zahnräder mit der anderen Antriebswelle so gekoppelt, daß die beiden Unwuchtwellen stets mit untereinander gleicher Drehzahl gegensinnig in dem Erregergehäuse umlaufen. Die Fliehgewichte der beiden Unwuchtwellen haben untereinander gleiche Masse und gleichen Schwerpunktanstand, so daß die in den beiden Bandagen befindlichen Schwingungserreger jeweils eine gerichtete Schwingung erzeugen, die sich radial zur Fahrachse der betreffenden Bandage erstreckt und deren Richtung von der räumlichen Einstellung des Gehäuses der Unwuchtwellen abhängig ist.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.

Die Lösung gemäß EP 0 530 546 A1 ist vorteilhaft anwendbar in Verbindung mit Bodenarten, die sich am besten durch die Ausübung von Scherspannungen und Kombinationen von Scher- und Druckspannungen auf sie verdichten lassen, und sie eignet sich auch sehr gut zum wirtschaftlichen Verdichten relativ großer Schichtdicken. Außerdem kann einem durch Scher- und Druckspannungskombinationen verursachten Schlupf entgegengewirkt und die Traktion der Walze unterstützt werden. The solution according to 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. One can also by shear and compressive stress combinations counteracted slippage and the traction of the roller get supported.

Die Lösung gemäß EP 0 530 546 A1 ist aber auch mit Nachteilen behaftet:However, the solution according to EP 0 530 546 A1 also has disadvantages afflicted:

In der Praxis dauert ein Fahrtrichtungswechsel, insbesondere auf bituminösem Material, ca. 10-15 Sekunden, so daß bei einer Fahrgeschwindigkeit von ca. 5 Km/h für den Abbremsvorgung und die anschließende Beschleunigung auf 5 Km/h in der Gegenrichtung eine Wegstrecke von 3,5 bis 5 Metern benötigt wird. Auf dieser Fahrstrecke werden die Erregergehäuse bezüglich der Vertikalebene spiegelbildlich verstellt. Dieser Verstellvorgang hat sich laufend verändernde Druck- und Schubspannungen auf den Boden zur Folge, wodurch eine inhomogene Verdichtung und unerwünschte Dellenbildung hervorgerufen werden. Um eine solche inhomogene Verdichtung und Dellenbildung in zulässigen Grenzen zu halten, müßte der Verstellvorgang innerhalb eines Bruchteils einer Sekunde erfolgen, was bei der bekannten Vibrationswalze praktisch nicht zu erreichen ist, weil der Schwingungserreger bezüglich der Schwenkachse ein sehr großes Trägheitsmoment (I= Σ mr2) aufweist, das durch das schwenkbare Erregergehäuse als solches und durch einen relativ großen Abstand der Unwuchtwellen von der mit der Bandagenfahrachse zusammenfallenden Schwenkachse des Erregergehäuses sowie durch die Lager- und Antriebseinheiten hervorgerufen wird. Zum verschwenken des Erregergehäuses wird ein Drehmoment Md = I * ΔW/ Δt benötigt. Dieses Drehmoment wächst also proportional mit I und der Winkelbeschleunigung ΔW/Δt. Dies bedeutet, daß umso größere Drehmomente benötigt werden, je kürzer die Schwenkzeit angesetzt wird und je größer das Trägheitsmoment I des Erregersystems ist. Je größer die benötigten Drehmomente sind, desto komplizierter gestaltet sich aber wiederum der Regelprozess.In practice, changing the direction of travel, especially on bituminous material, takes approx. 10-15 seconds, so that at a driving speed of approx. 5 km / h for braking and subsequent acceleration to 5 km / h in the opposite direction, a distance of 3 , 5 to 5 meters is needed. On this route, the exciter housing is adjusted in mirror image with respect to the vertical plane. This adjustment process results in constantly changing compressive and shear stresses on the ground, causing inhomogeneous compaction and undesirable dent formation. In order to keep such inhomogeneous compression and dent formation within permissible limits, the adjustment process would have to take place within a fraction of a second, which is practically impossible to achieve with the known vibratory roller because the vibration exciter has a very large moment of inertia with respect to the pivot axis (I = Σ mr 2 ), which is caused by the pivotable exciter housing as such and by a relatively large distance between the unbalanced shafts from the pivot axis of the exciter housing coinciding with the drum travel axis and by the bearing and drive units. A torque M d = I * ΔW / Δt is required to pivot the exciter housing. This torque therefore increases proportionally with I and the angular acceleration ΔW / Δt. 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.

Hinzu kommt, daß schwenkbare, den kompletten Aufbau des Erregersystems enthaltende Erregergehäuse und die zusätzlichen Schwenklager einen hohen technischen Aufwand bedingen und kostspielig sind.In addition, 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.

Ein weiterer Nachteil der bekannten Vibrationswalze gemäß EP 0 530 546 A1 ist ein ungünstiges Traktionsverhalten unter bestimmten Betriebsbedingungen:Another disadvantage of the known vibratory roller according to EP 0 530 546 A1 is an unfavorable traction behavior under certain Operating conditions:

Während des Verdichtungsvorgangs mit einer Vibrationswalze, die zwei hintereinander angeordnete, mit dem geschilderten Schwingungserreger ausgerüstete Walzenbandagen aufweist, hat die in Fahrtrichtung vordere Walzenbandage einen größeren Rollwiderstand als die hintere. Das für beiden Walzen vorgesehene, parallel geschaltete, hydraulische Fahrantriebssystem stellt sich auf die größeren benötigten Antriebsmomente ein. Für die hintere Walze ist das Antriebsmoment dann zu groß. Dadurch wird ein Schlüpfen der Walzen begünstigt. Eine möglicherweise vorgesehene Antischlupfregelung versucht den Schlupf durch unterschiedliche Einstellwinkel der Schwingungserreger in der vorderen und in der hinteren Bandage zu verhindern. Dies bedeutet aber, daß die beiden Walzenbandagen unterschiedliche Druck- und Schubspannungen auf den Boden ausüben, die sich wiederum während der Fahrt ständig ändern. Auch dadurch entsteht eine unerwünschte inhomogene Verdichtung. Diese inhomogene Verdichtung wird durch den Reibungskoeffizienten zwischen Walzenbandage und Boden, durch Änderungen des Rollwiderstandes und durch fehlerhaftes Fahrverhalten des Fahrers zusätzlich noch unkontrollierbarer.During the compaction process with a vibratory roller, 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.

Eine weitere bekannte Vibrationswalze (EP 053 598 A1) weist zwei parallel zur Walzenachse angeordnete Unwuchtwellen auf, die synchron mit gleichem Drehsinn umlaufen, aber um 180° in Bezug aufeinander phasenverschoben sind. Die Anordnung ist so getroffen, daß sich die von den Unwuchtwellen erzeugten Vertikalkräfte kompensieren während die entgegengesetzt gerichteten Horizontalkräfte ein Drehmoment auf die Walzenbandage um die Bandagendreh- bzw. fahrachse herum erzeugen. Dieses Drehmoment übt eine ihrer Größe nach nicht veränderbare Scherbelastung auf den Boden aus. Untersuchungen haben gezeigt, daß diese Lösung für die Verdichtung von dünnschichtigem, rolligem und bituminösem Material mit Vorteil anwendbar ist, und auch hinsichtlich der geforderten geringen Geräusch- und Schwingungsbelästigung für das Bedienungspersonal zu vorteilhaften Ergebnissen führt. Demgegenüber ist diese bekannte Vibrationswalze jedoch nicht wirtschaftlich einsetzbar generell bei größeren Schichtdicken und bei nicht rolligem Material, z.B. bei Mischböden, bindigen Böden und Felsen. Hinzu kommt, daß die bekannte Walze sehr schlupfgefährdet ist, was insbesondere bei Gefällen oder Steigungen zu Traktionsproblemen fhrt. Außerdem ist die bekannte Walze gemäß EP 053 598 A1 konstruktiv sehr aufwendig, weil die Unwuchtwellen weit entfernt von der Bandagenfahrachse gelagert werden müssen, damit sie das gewünschte Drehmoment erzeugen können.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. 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.

In der den Oberbegriff von Anspruch 1 bildenden DE 32 25 235 A1 ist ein in einer Walze angeordneter Schwingungserreger beschrieben, der zwei konzentrisch zueinander angeordnete Unwuchtwellen aufweist, die gemeinsam mittels eines Hydraulikmotors angetrieben sind. Die eine Unwuchtwelle ist achsial translatorisch bewegbar und kann außer Eingriff mit einer Keilwellenkupplung gebracht werden, um sie relativ zu der anderen Unwuchtwelle in unterschiedlichen Drehpositionen einstellen zu können. Auf diese Weise ist es möglich, die Vibrationsamplituden zu vergrößern und zu verkleinern. Dieser bekannte Vibrationsmechanismus eignet sich für die Ausübung komplexer Spannungen auf passende Bodenarten, weil die angebotene kinetische Energie in Abhängigkeit von der Amplitudenverstellung in quadratischer Funktion vergrößert und verkleinert werden kann, doch haben solche amplitudenverstellbare Lösungen unter bestimmten Betriebsbedingungen auch wesentliche anwendungstechnische Nachteile. So ist es z.B. nicht möglich, kontrollierte Druck- und Scherspannungskombinationen für eine homogene und wirtschaftliche Verdichtung bei einigen Bodenarten zu erzeugen. Ferner ist eine Dosierung der angebotenen kinetischen Energie, die sich in quadratischer Funktion zur Amplitudenverstellung verändert, problematisch, weil bei fehlerhafter Einstellung des Angebots an kinetischer Energie mit steigendem Verdichtungsgrad unerwünschte Oberflächenlockerungen und bei bituminösem Material nicht erlaubte Materialzertrümmerungen herbeigeführt werden. Hinzu kommt, daß der vorstehend geschilderte bekannte Vibrationsmechanismus nicht die im Hinblick auf einen schonenden Einsatz des Verdichtungsgerätes und eine geringe Geräuschund Schwingungsbelästigung des Bedienungspersonals und seiner Umgebung zu stellenden Anforderungen erfüllt. Außerdem ist der bekannte Schwingungserreger kompliziert aufgebaut und störanfällig.In DE 32 25 235 A1, which forms the preamble of claim 1, is a vibration exciter arranged in a roller described, the two concentrically arranged Unbalance shafts, which together by means of a Hydraulic motor are driven. One unbalanced shaft is axial Can be moved translationally and can be disengaged from a spline coupling brought to them relative to the other Adjust unbalanced shaft in different rotary positions can. In this way it is possible to increase the vibration amplitudes enlarge and reduce. This well-known vibration mechanism is suitable for exercising complex tensions on matching ones Soil types because the kinetic energy offered depends on of the amplitude adjustment in quadratic function can be enlarged and reduced, but have such amplitude adjustable Solutions under certain operating conditions too significant technical disadvantages. So it is e.g. Not possible, controlled pressure and shear stress combinations for a homogeneous and economical compaction with some types of soil to create. There is also a dosage of the kinetic offered Energy that is in quadratic function for amplitude adjustment changed, problematic, because when it is faulty Setting the supply of kinetic energy with increasing Degree of compaction undesirable surface loosening and with bituminous Material not allowed material destruction become. In addition, the known one described above Vibration mechanism is not the most gentle Use of the compactor and a low noise and Vibration nuisance to the operating personnel and their Environment to be met. In addition, the well-known vibration exciter complex and prone to failure.

In der CH-B- 271 578 ist eine Vibrationsplatte mit einem auf die Bodenkontaktplatte aufgesetzten Schwingungserreger dargestellt und beschrieben, der zwei koaxial zueinander angeordnete, also um eine gemeinsame Rotationsachse umlaufende Unwuchtwellen aufweist, die mittels eines sie für gegensinnigen Umlauf mit synchroner Drehzahl dauernd koppelnden Differentialgetriebes in ihrer gegenseitigen Phasenlage verstellbar sind, so daß es möglich ist, die Wirkungsrichtung der von den Unwuchtwellen erzeugten gerichteten Schwingung bezüglich der Bodenkontaktplatte zu verstellen. Die Vibrationsplatte kann dadurch selbstfahrend im Vorlauf und im Rücklauf betrieben werden.In 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.

Die DE- 195 39 150 A1 zeigt und beschreibt in verschiedenen Ausführungsformen Vibrationsantriebe für Schwingmaschinen, die alle zueinander koaxiale Unwuchtwellen aufweisen. Die Vibrationsantriebe sind speziell für einen Einsatz bei Schwingsieben, Fördervorrichtungen und Rüttlern vorgesehen. Bei allen Ausführungsformen bis auf eine sind die Unwuchtwellen ohne die Möglichkeit einer Verstellung der gegenseitigen Phasenbeziehung während des Betriebes zwangsweise gegensinnig angetrieben. Bei dieser einen abweichenden Ausführungsform erfordert ein Antrieb mit gleicher Drehrichtung jedoch einen gesonderten Antrieb für jede Unwuchtwelle, was einen erheblichen technischen Aufwand bedingt.DE-195 39 150 A1 shows and describes in various embodiments 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. In all embodiments except one are the unbalanced shafts without the possibility of adjusting the mutual phase relationship during operation forcibly driven in opposite directions. In 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.

Ausgehend von dem vorgenannten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine universell anwendbare Vibrationswalze zu schaffen, die es je nach Einstellung ermöglicht,

  • um die Bandagenfahrachse herum oszillierende Drehschwingungen zu erzeugen und damit auf den zu verdichtenden Boden überwiegend Scherspannungen auszuüben,
  • an der Bandagenfahrachse eine gerichtete Kraft einzuleiten und den Kraftvektor beliebig in alle Richtungen einzustellen, um auf den zu verdichtenden Boden optimal kombinierbare Druck- und Scherspannungen ausüben zu können, oder
  • eine an der Bandagenfahrachse eingeleitete und um diese rotierend wirkende sowie ihrer Größe nach veränderbare Zentrifugalkraft zu erzeugen, um auf den zu verdichtenden Boden komplexe Spannungen auszuüben.
On the basis of the aforementioned prior art, the object of the invention is to create a universally applicable vibratory roller which, depending on the setting, enables
  • to generate oscillating torsional vibrations around the drum axis and thus to exert predominantly shear stress on the soil to be compacted,
  • To initiate a directed force on the drum travel axis and to set the force vector as desired in all directions in order to be able to exert compressible and shear stresses that can be optimally combined on the soil to be compacted, or
  • a centrifugal force which is introduced on the drum travel axis and which produces a rotating centrifugal force which is variable in size in order to exert complex tensions on the soil to be compacted.

Trotz dieser vielfältigen Einstellungsmöglichkeiten soll sich die erfindungsgemäße Vibrationswalze durch einen einfachen konstruktiven Aufbau, geringe Störanfälligkeit und lange Lebensdauer auszeichnen.Despite these diverse setting options, the Vibratory roller according to the invention by a simple constructive Design, low susceptibility to failure and long service life.

Die vorstehende Aufgabe wird durch die im Patentanspruch 1 genannten Merkmale gelöst.The above object is achieved by those mentioned in claim 1 Features resolved.

Die erfindungsgemäße Vibrationswalze kann jeweils optimal an die verschiedenen Bedürfnisse des zu verdichtenden Bodens angepaßt werden, und zwar derart, daß die vorteilhaften Wirkungsweisen der verschiedenen bekannten Vibrationswalzen jeweils aufrechterhalten, deren Nachteile aber vermieden werden.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.

Ein besonderer Vorzug der erfindungsgemäßen Vibrationswalze besteht dabei auch darin, daß das Trägheitsmoment des Schwingungserregers bezüglich der Fahrachse der jeweiligen Bandage überaus gering, im Vergleich zu der Vibrationswalze gemäß EP 0 530 546 A1 z.B. praktisch mindestens um das Zehnfache kleiner, ist, so daß der Schwingungserreger in der Einstellung zum Einleiten einer gerichteten Vibrationskraft an der Bandagenfahrachse zur Veränderung der Richtung der gerichteten Schwingung eines weitaus geringeren Drehmoments als bei der bekannten Walze bedarf und demgemäß in wesentlich kürzerer Zeit in die neue Richtung verschwenkbar werden kann, so daß es möglich ist, Inhomogenitäten und Dellen im verdichteten Boden zu minimieren.There is a particular advantage of 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.

Mit dem erfindungsgemäßen Gerät ist für die verschiedenen Bodenarten und Schichtdicken durch eine aus der Vielzahl gebotener Möglichkeiten ausgewählte entsprechende Grundeinstellung des Schwingungserregungssystems und der dadurch erzeugten verschiedenen Schub- und Druckspannungskombinationen eine optimale Verdichtung erreichbar, und es können damit auch Schlupferscheinungen in einem zulässigen Bereich gehalten werden.With 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.

Die Unteransprüche 2 bis 18 betreffen bevorzugte Ausführungsformen der Vibrationswalze nach Patentanspruch 1.Subclaims 2 to 18 relate to preferred embodiments the vibratory roller according to claim 1.

Die Erfindung betrifft auch ein besonders vorteilhaftes Verfahren zum Betreiben der Vibrationswalze nach Patentanspruch 1. Dieses Verfahren ist Gegenstand der Patentansprüche 19 bis 22.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.

Die Erfindung wird nachstehend anhand der Zeichnung an einem Ausführungsbeispiel noch näher erläutert. In der Zeichnung zeigt:

Fig. 1
eine Seitenansicht einer erfindungsgemäßen Vibrationswalze mit zwei Walzenbandagen,
Fig. 2
einen axialen Querschnitt durch eine der beiden untereinander gleichen Walzenbandagen der Vibrationswalze gemäß Fig. 1,
Fig. 3
eine Stirnansicht im Querschnitt entlang der Schnittlinie III-III in Fig. 2,
Fig. 4
eine schematische Darstellung des in einer der möglichen Grundeinstellungen (Einstellung I) des Schwingungserregers in horizontaler Richtung wirkenden Kraftvektors,
Fig. 5
eine schematische Darstellung des gegenüber Fig. 4 in vertikaler Richtung wirkenden Kraftvektors,
Fig. 6
eine schematische Darstellung des unter einem Schwenkwinkel α gegenüber der Horizontalen geneigten Kraftvektors in der gleichen prinzipiellen Grundeinstellung wie in Fig. 4 und 5,
Fig. 7
eine schematische Darstellung eines Regelkreises für die automatische Korrektur des Anstellwinkels α des Kraftvektors in der prinzipiellen Einstellung gemäß Fig, 4 bis Fig. 6, und
Fig. 8a und 8b
schematische Darstellungen des in einer anderen möglichen Grundeinstellung (Einstellung II) des Schwingungserregers rotierenden Kraftvektors in verschiedenen gegenseitigen Phasenlagen der Unwuchtwellen und dementsprechend unterschiedlicher Größe der Zentrifugalkraft.
The invention is explained in more detail below with reference to the drawing using an exemplary embodiment. The drawing shows:
Fig. 1
a side view of a vibratory roller according to the invention with two roller bandages,
Fig. 2
3 shows an axial cross section through one of the two mutually identical roller bandages of the vibratory roller according to FIG. 1,
Fig. 3
3 shows an end view in cross section along the section line III-III in FIG. 2,
Fig. 4
1 shows a schematic representation of the force vector acting in one of the possible basic settings (setting I) of the vibration exciter in the horizontal direction,
Fig. 5
4 shows a schematic illustration of the force vector acting in the vertical direction compared to FIG. 4,
Fig. 6
4 shows a schematic representation of the force vector inclined at a swivel angle α with respect to the horizontal in the same basic basic setting as in FIGS. 4 and 5,
Fig. 7
a schematic representation of a control loop for the automatic correction of the angle of attack α of the force vector in the basic setting according to FIG. 4 to FIG. 6, and
8a and 8b
schematic representations of the force vector rotating in another possible basic setting (setting II) of the vibration exciter in different mutual phase positions of the unbalanced shafts and accordingly different magnitudes of the centrifugal force.

Die in Fig. 1 dargestellte Vibrationswalze weist zwei in Fahrtrichtung hintereinander angeordnete Walzenbandagen 1 und 2 auf. Auf der Walzenbandage 1 ist ein Rahmen 2a angeordnet, und auf der Walzenbandage 2 befindet sich ein Rahmen 2b mit Fahrerstand. Die Rahmen 2a und 2b sind zur Lenkbarkeit der Vibrationswalze über ein vertikales Schwenkpendellager 29 miteinander verbunden.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, and 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.

In beiden Walzenbandagen 1 und 2 ist jeweils ein Doppelwellen-Schwingungserreger S angeordnet, dessen Aufbau im einzelnen aus Fig. 2 ersichtlich ist.In both 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.

Gemäß Fig. 2 befinden sich im Innern jeder Walzenbandage 1, 2 zwei koaxial zueinander angeordnete Unwuchtwellen 3 und 4, wobei die eine - innere - Unwuchtwelle 3 mit Hilfe von Wälzlagern 3b stirnseitig in der sie ummantelnden anderen - äußeren - Unwuchtwelle 4 drehbar gelagert ist.2 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.

Die äußere Unwuchtwelle 4 ist mit Hilfe von Wälzlagern 5,6 an ihren Enden jeweils in dem einen bzw. anderen von zwei in den Walzenbandagen 1 und 2 angeordneten, diese diagonal im gegenseitigen Abstand durchquerenden Trägern 1a und 1b drehbar in einer solchen Position gelagert, daß ihre Drehachse 28, die gleichzeitig die Drehachse der inneren Unwuchtwelle 3 darstellt, mit der Bandagen-Fahrachse zusammenfällt, um die sich die Walzenbandagen 1, 2 gegenüber dem Bandagenträger 23 bzw. 24 dreht, der an dem jeweiligen Walzenrahmen 2a bzw. 2b auf der einen bzw. anderen Seite der Bandagen 1 bzw. 2 befestigt ist und stirnseitig etwas in die Bandage hineinragt.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.

An dem für den Betrachter der Fig. 2 linken Ende weist die äußere Unwuchtwelle 4 ein zur Drehachse 28 koaxiales Kegelrad 14 auf. Die innere Unwuchtwelle 3 hat eine sich durch das linke stirnseitige Ende der äußeren Unwuchtwelle 4 und durch das an dieser befestigte Kegelrad 14 hindurch erstreckende Verlängerung 13a, auf der, dem Kegelrad 14 zugewendet, im axialen Abstand hiervon ein Kegelrad 11 befestigt ist, das beim Ausführungsbeispiel den gleichen Durchmesser und die gleiche Zähnezahl aufweist wie das Kegelrad 14 an der äußeren Unwuchtwelle 4. Die beiden Kegelräder 11 und 14 bilden zusammen mit zwei bezüglich der Verlängerung 3a diametral einander gegenüberliegend angeordneten, um eine die Rotationsachse 28 senkrecht schneidende Drehachse drehbaren, in sie eingreifenden Kegelrädern 12 und 13 ein Differentialgetriebe mit einem Steg 15, der als die Verlängerung 3a rundherum umgebendes, für den Betrachter der Fig. 1 auch nach links stirnseitig geschlossenes Gehäuse ausgeführt ist und nach links in einen rohrförmigen, stirnseitig nach links offenen Ansatz ausläuft, an dem endseitig ein Zahnrad 16 befestigt ist. Der Steg 15 bildet ein verschwenkbares Gehäuse, das mittels Wälzlagern in einem koaxial zur Fahrachse 28 an dem für den Betrachter der Fig. 2 linken Träger 1b befestigten, das Differentialgetriebe umgebenden Fahrlagergehäuse 17 drehbar gelagert ist.At the left end for the viewer of FIG. 2, 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. Form the two bevel gears 11 and 14 together with two diametrically opposite each other with respect to the extension 3a arranged opposite one another about a the axis of rotation 28 perpendicular intersecting axis of rotation rotatable, meshing bevel gears 12 and 13 a differential gear with a web 15, the one surrounding the extension 3a all around, for the viewer 1 also housing closed on the left end is executed and to the left in a tubular, frontal to the left open approach runs out, at the end a gear 16 is attached. The web 15 forms a pivotable housing, that by means of roller bearings in a coaxial to the driving axis 28 on the for the viewer of Fig. 2 left carrier 1b attached, the Differential gear surrounding bearing housing 17 rotatably mounted is.

Das Fahrlagergehäuse 17 weist auf der für den Betrachter der Fig. 2 linken Seite einen zur Fahrachse 28 konzentrischen Bund auf, mit dem es über ein Wälzlager 20 in einer Lagerplatte 21 gelagert ist, die über Puffer 22 an dem Bandagenträger 23 befestigt ist. Die mit dem Bandagenträger 23 eine undrehbare Einheit bildende Lagerplatte 21 trägt einen Antriebsmotor 9 mit zur Fahrachse 28 koaxialer Antriebswelle, die über eine im rohrförmigen Ansatz am Steg 15 des Differentialgetriebes untergebrachte Kupplung 10 mit der Verlängerung 3a der inneren Unwuchtwelle 3 verbunden ist. 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. With 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.

Auf der für den Betrachter der Fig. 2 rechten Seite ist die Walzenbandage 1 bzw. 2 an dem dortigen Bandagenträger 24 über eine Lagerplatte 26 gelagert, die über Puffer 27 an dem die Bandage diagonal durchquerenden Träger 1a befestigt ist und koaxial zur Fahrachse 28 in einem in Fig. 2 im einzelnen nicht dargestellten Lager an dem Bandagenträger 24 gelagert ist. An dem Bandagenträger 24 ist ein Fahrantriebsmotor 25 befestigt, mit dem die Lagerplatte 26 gegenüber dem Bandagenträger 24 um die Fahrachse 28 in Drehung versetzbar ist.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. 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.

Der vorstehend beschriebene Schwingungserreger S mit seinen an einem Ende über das Differentialgetriebe verbundenen Unwuchtwellen 3 und 4 ist in zwei unterschiedlichen Einstellungen des Differentialgetriebes bezüglich der benachbarten Vorrichtungsteile betreibbar.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.

In einer ersten, nachstehend als Einstellung I bezeichneten Grundeinstellung ist der gehäuseartige Steg 15 des Differentialgetriebes gegenüber der Trägerplatte 21 über das Zahnrad 16 fixiert, steht also mit dieser still, wobei jedoch seine Winkelstellung gegenüber der Lagerplatte 21 mit Hilfe eines in das Zahnrad 16 eingreifenden, von einem Motor 31 verstellbaren Zahnrads 30 (Fig. 3) gesteuert koaxial zur Fahrachse 28 veränderbar ist. Da der Steg 15 des Differentialgetriebes stillsteht, wird von der vom Motor 9 in Drehung versetzten inneren Unwuchtwelle 3 über die Kegelräder 11, 12, 13 und 14 die äußere Unwuchtwelle 4 im Gegensinn zur inneren Unwuchtwelle 3 mit gleicher Drehzahl angetrieben, so daß der Schwingungserreger S eine gerichtete Schwingung erzeugt, deren Vektor wegen der koaxialen Anordnung der Unwuchtwellen 3 und 4 die Fahrachse 28 senkrecht schneidet. Durch Verdrehen des Steges 15 gegenüber der Lagerplatte 21 mittels des Stellmotors 31 über die Zahnräder 30 und 16 (Fig. 3) ist die räumliche Phasenlage der Unwuchtwellen 3 und 4 und mit dieser die Wirkungsrichtung des Vektors der gerichteten Schwingung um 360° um die Fahrachse 28 herum veränderbar, wobei jedoch von dieser Verstellmöglichkeit nur im Rahmen eines vorbestimmten Winkelbereiches Gebrauch gemacht wird. In a first basic setting, hereinafter referred to as 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. Since the jetty 15 of the differential gear is stopped by the engine 9 rotated inner unbalance shaft 3 via the bevel gears 11, 12, 13 and 14 the outer imbalance shaft 4 in the opposite direction to the inner one Unbalance shaft 3 driven at the same speed, so that Vibration exciter S generates a directional vibration, the Vector due to the coaxial arrangement of the unbalanced shafts 3 and 4 Axis 28 intersects vertically. By turning the web 15 opposite the bearing plate 21 by means of the servomotor 31 via the Gears 30 and 16 (Fig. 3) is the spatial phase position of the Unbalance shafts 3 and 4 and with this the direction of action of the Vector of the directional vibration by 360 ° around the driving axis 28 changeable around, but from this adjustment option only made use of within a predetermined angular range becomes.

Die Fig. 4, 5 und 6 zeigen verschiedene unterschiedliche Einstellungen der räumlichen Phasenlage der Unwuchtwellen 3 und 4 in der prinzipiellen Grundeinstellung I und die zugehörige Wirkungsrichtung des Vektors F2 der gerichteten Schwingung. Es ist ersichtlich, daß die räumliche Phasenlage der beiden Unwuchtwellen 3 und 4, d. h. der Schwenkwinkel α des Schwingungserregers S, so gewählt ist, daß bei der Phasenlage gemäß Fig. 4 sich die von den Unwuchten erzeugten Zentrifugalkräfte in horizontaler Richtung verstärken, in vertikaler Richtung hingegen kompensieren, bei der Phasenlage gemäß Fig. 5 die von den Unwuchten erzeugten Zentrifugalkräfte sich in vertikaler Richtung verstärken und in horizontaler Richtung kompensieren, und bei der Phasenlage gemäß Fig. 6 die von den Unwuchten erzeugten Zentrifugalkräfte sich in der vom Schwenkwinkel α des Schwingungserregers S definierten Richtung verstärken und senkrecht zu dieser Richtung kompensieren. Die von den Unwuchtwellen 3 und 4 ausgehenden Rüttelkräfte werden dabei jeweils über die Lager 5 und 6 und die Lagergehäuse 7 und 8 auf die Träger 1a und 1b und über diese auf den jeweiligen Mantel der Walzenbandagen 1 bzw. 2 übertragen.4, 5 and 6 show various different settings of the spatial phase position of the unbalanced shafts 3 and 4 in the basic setting I and the associated direction of action of the vector F 2 of the directional vibration. It can be seen that the spatial phase position of the two unbalanced shafts 3 and 4, that is to say the swivel angle α 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.

Der Motor 9 ist vorzugsweise ein Hydraulikmotor.The motor 9 is preferably a hydraulic motor.

Die Phasenverstellung mittels des Stellmotors 31 und der Zahnräder 30 und 16 kann von Hand gesteuert vorgenommen aber auch automatisch gesteuert durchgeführt werden.The phase adjustment by means of the servomotor 31 and the gears 30 and 16 can be controlled manually, but also automatically controlled.

Die Fig. 7 zeigt die Funktion eines Regelkreises zur automatischen Steuerung der Phasenlage der Unwuchtwellen 3 und 4 in solcher Weise, daß einem Schlupf der Walzenbandagen 1 und 2 auf dem zu verdichtenden Boden entgegengewirkt wird. Gemäß Fig. 7 ist in jeder Walzenbandage 1, 2 ein in der Zeichnung hinsichtlich seines Aufbaus und des Anbringungsortes nicht dargestellter Incremental-Geber 35, 36 angeordnet, der die Winkelbeschleunigung dω/dt = ξ(t) und die Winkelgeschwindigkeit ω(t) der Walzenbandagen 1 und 2 mißt. Wenn eine Walzenbandage dazu neigt, im Vergleich zu der nicht schlüpfenden Walzenbandage ihren Toleranzbereich hinsichtlich ξ(t) und ω(t) zu verlassen, werden die Differenzwerte Δξ und Δω durch ein in der Zeichnung ebenfalls nicht im einzelnen dargestelltes Vergleichselement 37 ermittelt. Liegen die Werte Δξ und Δω über einem vorgegebenen, mittels eines Sollwertgebers 40 voreinstellbaren Wert, so werden über einen Verstärker 38 die beiden Einstellmotoren 311 und 312 der Walzenbandagen 1 und 2 in solcher Weise aktiviert, daß die Winkelposition des Schwingungserregers S im Sinne einer Vergrößerung der Horizontalkomponente der resultierenden Zentrifugalkraft so lange verändert wird, bis der vom Vergleichselement 37 festegestellte Schlupf unter dem eingestellten Grenzwert liegt. Dieser neue Schwenkwinkelwert wird bei beiden Walzenbandagen 1 und 2 synchron eingestellt. Bei einem Fahrtrichtungswechsel wird der eingestellte oder einregulierte Schwenkwinkelwert der Zentrifugalkraft automatisch spiegelbildlich bezüglich der Vertikalen jeweils in Fahrtrichtung positioniert. Vorzugsweise wird die Positionierung wie folgt vorgenommen: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. According to FIG. 7, an incremental encoder 35, 36, which is not shown in the drawing with regard to its structure and the attachment location, is arranged in each roller drum 1, 2, which gives the angular acceleration dω / dt = ξ (t) and the angular velocity ω (t) Roll bandages 1 and 2 measures. If a roller drum tends to leave its tolerance range with respect to ξ (t) and ω (t) compared to the non-slipping roller drum, the difference values Δξ and Δω are determined by a comparison element 37, which is also not shown in detail in the drawing. If the values Δξ and Δω 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. When changing the direction of travel, 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:

Wenn sich der Schwenkwinkel des Erregerkraftvektors im Bereich von 0° bis 45° befindet, verstellt er sich im Uhrzeigersinn spiegelbildlich, und wenn er sich im Bereich von 45° bis 90° befindet, verstellt er sich entgegen dem Uhrzeigersinn spiegelbildlich.If 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.

Zahlreiche Untersuchungen haben zu folgenden Ergebnissen und Erkenntnissen geführt:

  • Für rollige und bituminöse Materialien werden überwiegend dynamische Scherspannungen mit einem mit steigender Schichtdicke steigenden Druckspannungsanteil benötigt.
  • Bei schwer verdichtbaren Böden braucht man für eine optimale Verdichtung überwiegend dynamische Druckspannungen, wobei mit steigender Schichtdicke wachsende Druckspannungsanteile benötigt werden.
  • Der resultierende Kraftvektor hat, je nach Einstellwinkel orientiert, eine horizontale, in Fahrtrichtung weisende Komponente, der zwei Funktionen zukommen, nämlich zum einen das Erzeugen der für die Verdichtung notwendigen Scherspannungen und zum anderen die Unterstützung der Traktion.
  • Die andere, vertikale Kraftkomponente ist auf den Boden gerichtet und erzeugt die für die Verdichtung notwendigen Druckspannungen, wobei sie gleichzeitig die Reibungskraft zwischen Walzenbandage und Boden erhöht. Dies spielt wiederum eine wichtige Rolle für die Scherspannungsübertragung zu dem zu verdichtenden Boden.
Numerous studies have led to the following results and findings:
  • For rolling and bituminous materials, dynamic shear stresses with an increasing compressive stress component with increasing layer thickness are mainly required.
  • In the case of soils that are difficult to compact, dynamic compressive stresses are predominantly required for optimal compaction, with increasing compressive stress components being required as the layer thickness increases.
  • Depending on the setting angle, the resulting force vector has a horizontal component pointing in the direction of travel, which has two functions, namely the generation of the shear stresses required for compression and the support of traction.
  • The other, vertical force component is directed towards the ground and generates the compressive stresses necessary for compaction, while at the same time increasing the frictional force between the drum and the ground. This in turn plays an important role for the shear stress transmission to the soil to be compacted.

Aus diesen Erkenntnissen heraus kann davon ausgegangen werden, daß zum Erreichen einer optimalen Verdichtung für rollige und bituminöse Materialien der Einstellwinkel α von 0° bis 45° variieren und mit wachsender Schichtdicke des Materials einen Wert von 45° erreichen sollte.From these findings it can be assumed that to achieve optimal compaction for rolled and bituminous Materials of the setting angle α vary from 0 ° to 45 ° and reach a value of 45 ° with increasing layer thickness of the material should.

Um bei schwer verdichtbaren Böden eine optimale Verdichtung zu erreichen, sollte der Einstellwinkel α im Bereich von 45° bis 90° variieren und mit wachsender Schichtdicke des Materials einen Wert von 90° erreichen.In order to achieve optimal compaction on soils that are difficult to compact should reach the setting angle α in the range of 45 ° to 90 ° vary and a value with increasing layer thickness of the material of 90 °.

Auf zahlreichen Untersuchungsergebnissen basierende Erfahrungen belegen andererseits, daß

  • erstens ein je nach Bodenart und Schichtdicke orientierter Grundwert des Einstellwinkels des Kraftvektors eine gewisse Reserve für eine Traktionsunterstützung und Reibungskrafterhöhung zwischen Walzenbandage und Boden berücksichtigen sollte, und
  • zweitens eine nach jedem Verdichtungsübergang orientierte Reduzierung des Einstellwinkels in Abhängigkeit von der Bodenart und Schichtdicke eine homogene Verdichtung innerhalb dieser zu gewährleisten vermag. Es ist, wie vorstehend bereits erwähnt, zweckmäßig, die Anpassung der Schwenkwinkel des Kraftvektors in der Grundeinstellung I zu automatisieren, damit zum einen eine optimale Verdichtung erreicht und andererseits der Schlupf zwischen Walzenbandage und Boden auf ein nicht schädliches Minimum reduziert wird.
On the other hand, experience based on numerous test results shows that
  • firstly, a basic value of the setting angle of the force vector, which is oriented according to the type of soil and layer thickness, should take into account a certain reserve for a traction support and an increase in the frictional force between the roller drum and the ground, and
  • secondly, a reduction of the setting angle based on each compaction transition, depending on the type of soil and layer thickness, can ensure homogeneous compaction within this. As already mentioned above, it is expedient to automate the adjustment of the swivel angle of the force vector in the basic setting I, so that on the one hand an optimal compaction is achieved and on the other hand the slip between the roller drum and the ground is reduced to a non-harmful minimum.

Ein hierfür an der Vibrationswalze installiertes vorprogrammiertes Kommandoinstrument kann es dem Fahrer ermöglichen, die Grundeinstellungen manuell vorzunehmen.A preprogrammed one installed on the vibratory roller for this purpose Command instrument can allow the driver to make the basic settings manually.

Wenn die anwendungsorientierte Grundeinstellung des Schwenkwinkels des Kraftvektors des Schwingungserregers S z.B. bei beiden Walzenbandagen einer Tandemwalze infolge des Rollwiderstandes und des Reibungskoeffizienten zwischen Walze und Boden insbesondere bei steigenden Gewichtsverteilungsunterschieden zwischen der in Fahrtrichtung vorderen ersten Walze und der zweiten Walze nicht ausreichen sollte, um die Rutschneigung der einen Walze zu eleminieren, dann wird vorzugsweise die vorstehend bereits erörterte einfache Regelung eingsetzt, wonach die vorprogrammierten Grundeinstellungen des Erregersystems korrigierend eingreifen, und zwar bei einer Tandemwalze bei beiden Walzenbandagen.If 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.

Gemäß der Erfindung sind die Unwuchtwellen 3 und 4 abweichend von der vorstehend geschilderten Grundeinstellung I auch in eine Grundeinstellung II einstellbar, in der sie sich gleichsinnig drehen und in der ihre relative Phasenlage zur Einstellung der Größe der resultierenden Zentrifugalkraft einstell- und fixierbar ist.According to the invention, 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.

Auch in der Grundeinstellung II wird die Unwuchtwelle 3 mittels des Hydraulikmotors 9 über die zwischen diesem und ihr installierte Kupplung 10 angetrieben. Veränderungen und Fixierungen der Phasenlage der Unwuchtwelle 3 gegenüber der Unwuchtwelle 4 werden dabei wie folgt auf einfache Weise vorgenommen:In the basic setting II, 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:

Die Unwuchtwelle 3 wird zunächst mittels des Hydraulikmotors 9 in ihrer augenblicklichen Position festgehalten und sodann der gehäuseartige Steg 15 des Differentialgetriebes manuell (zeichnerisch nicht dargestellt) oder mit einem Verstellmechanismus, z.B. dem in Fig. 3 zu sehenden, d.h. mit dem Hydraulikmotor 31 und dem Zahnradpaar 30, 16, im Bedarfsfalle in solcher Weise verstellt, bis die sich hierbei ändernde Phasenlage zwischen den Unwuchtwellen 3 und 4 einen gewünschten Wert erreicht hat. Dann wird die nunmehr voherrschende gegenseitige Phasenlage der Unwuchtwellen 3 und 4 fixiert, wofür lediglich zwischen der Abtriebswelle des Hydraulikmotors 9 und dem Steg 15 z.B. mittels einer schaltbaren Kupplung (zeichnerisch nicht dargestellt) eine starre Verbindung hergestellt und gleichzeitig die Verbindung zwischen den Zahnrädern 16 und 30 gelöst zu werden braucht. Dadurch bilden der gehäuseartige Steg 15, die Kegelräder 11, 12, 13 und 14 und die untereinander positionierten und fixierten Unwuchtwellen 3, 4 eine einzige, im gleichen Drehsinn umlaufende Vibrationseinheit und üben auf die Walzenbandage eine um Walzenfahrachse 28 rotierend wirkende Zentrifugalkräfte aus, deren Größe von der eingestellten gegenseitigen Phasenlage der Unwuchtwellen 3 und 4 abhängt. Diese Wirkungsweise ist schematisch in Fig. 8a und 8b für unterschiedliche Einstellungen der Phasenbeziehung der Unwuchtwellen 3 und 4 ersichtlich.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. This will form the housing-like Web 15, the bevel gears 11, 12, 13 and 14 and each other positioned and fixed unbalanced shafts 3, 4 a single, in same direction of rotation revolving vibration unit and practice on the Roller drum a centrifugal forces rotating about the roller axis 28 whose size is set by the mutual Phase position of the unbalanced shafts 3 and 4 depends. This mode of action is schematic in Fig. 8a and 8b for different settings the phase relationship of the unbalanced shafts 3 and 4 can be seen.

Claims (22)

  1. Vibratory roller with at least one tyre (1) and a double-shaft vibration generator (S) disposed therein, the unbalanced shafts of which vibration generator, which are driven by a common drive (9), are rotatably mounted in a common carrier (1a, 1b) located in the tyre (1) and each have an axis of rotation parallel to the axis of travel (28) of the tyre (1), wherein
    the unbalanced shafts (3, 4) are formed and disposed with respect to each other and with respect to the tyre (1) in the carrier (1a, 1b) in such a way that the one - outer-unbalanced shaft (4) surrounds the other - inner - unbalanced shaft (3) in a coaxially rotatable manner and the said common axis of rotation of the unbalanced shafts (3, 4) coincides with the axis of travel (28) of the tyre (1), and
    the unbalanced shafts for one operating state, designated second operating state, in which they act upon the tyre with a circular vibration, can be coupled to each other in such a way that they rotate in the same direction, wherein their relative phase position can be adjusted and fixed to set the magnitude of the resulting centrifugal force,
    characterised in that
    the unbalanced shafts for another operating state, designated first operating state, in which they produce a directional vibration, can be coupled to each other in such a way that they rotate in opposite directions and the angle (α or α + 180°) which the directions of maximum resulting centrifugal force form with the direction of travel of the tyre (1) can be adjusted and fixed as desired.
  2. Vibratory roller according to claim 1, characterised in that the unbalanced shafts (3, 4) are mounted in the tyre (1) in such a way that they are not influenced by the rotational movement thereof
  3. Vibratory roller according to claim 1 or 2, characterised in that the carrier is formed by two axially-spaced end-face walls (1a, 1b) of the tyre (1) which is provided with bearing housings (7, 8) having first roller bearings (5, 6) for mounting the outer unbalanced shaft (4).
  4. Vibratory roller according to claim 3, characterised in that the first roller bearings (5, 6) simultaneously serve as travel bearings by means of which the tyre (1) is mounted on the chassis (23, 24) of the vibratory roller.
  5. Vibratory roller according to claim 3 or 4, characterised in that the inner unbalanced shaft (3) is mounted in the outer unbalanced shaft (4) by means of second roller bearings (3b) which are installed into the outer unbalanced shaft (4) in the proximity of the bearing housings (7).
  6. Vibratory roller according to any one of the preceding claims characterised in that in the first operating state the angle (α or α + 180°) between the vector of the directional vibration and the plane which is parallel to the ground and contains the travel axis (28) can be changed throughout the entire range of 360°.
  7. Vibratory roller according to any one of the preceding claims, characterised in that for the second operating state the coupling of the unbalanced shafts (3, 4) for rotation in the same direction and the adjusting and fixing of the relative phase position of the unbalanced shafts (3, 4) can be carried out manually when the vibration generator is at a standstill or can be carried out automatically.
  8. Vibratory roller according to any one of the preceding claims, characterised in that at least in the second operating state, the direction of rotation of the unbalanced shafts (3, 4) can be reversed.
  9. Vibratory roller according to any one of the preceding claims, characterised in that for the first operating state the coupling of the unbalanced shafts (3, 4) for rotation in opposite directions and the adjusting and fixing of the angle (α or α + 180°) between the vector of the directional vibration and the plane which is parallel to the ground and contains the travel axis (28) can be carried out manually when the vibration generator is at a standstill.
  10. Vibratory roller according to any one of claims 1 to 8, characterised in that for the first operating state the coupling of the unbalanced shafts (3, 4) for rotation in opposite directions and the adjusting and fixing of the angle (α or α + 180°) between the vector of the directional vibration and the plane which is parallel to the ground and contains the travel axis (28) can be carried out automatically.
  11. Vibratory roller according to claim 10, characterised in that the unbalanced shafts (3, 4) can be coupled to each other at the ends by means of a differential mechanism (11-15) which comprises two oppositely-rotating central wheels (11, 14) having the same number of teeth, of which one (11) is located in a rotationally fixed and coaxial manner on the inner unbalanced shaft (3), and the other (14) is disposed in a rotationally fixed and coaxial manner on the outer unbalanced shaft (4), and of which the cross-piece (15) for changing the relative phase position of the unbalanced shafts (3, 4) can be rotated about its axis of rotation (28) by an adjusting drive (30, 31, 16) and can be fixed in each adjusted angular position against the tyre carrier (21, 22, 23, 24) of the vibratory roller.
  12. Vibratory roller according to claim 11, characterised in that the differential mechanism (11-15) is formed as a conical wheel mechanism.
  13. Vibratory roller according to claim 11 or 12, characterised in that the cross-piece (15) forms a pivot housing which engages over one end (3a) of one unbalanced shaft (3), one end-face side of which pivot housing faces the tyre carrier (21, 22, 23) and carries an adjusting toothed wheel (16) coaxial to the travel axis (28) of the tyre (1), which adjusting toothed wheel meshes with the pinion (30) or the like of a servomotor (31) of the adjusting mechanism (30, 31, 16), which servomotor is attached to the tyre carrier (21, 22, 23).
  14. Vibratory roller according to any one of claims 11 to 13, characterised in that in order to bring about the second operating state the cross-piece (15) of the differential mechanism (11-15) can be coupled to one (3) of the unbalanced shafts (3, 4) and the engagement between the pinion (30) of the servomotor (31) and the toothed wheel (16) can be discontinued.
  15. Vibratory roller according to any one of the preceding claims 11 to 14, characterised in that the cross-piece (15) is rotatably mounted in a carrier (17) which is attached to one (1b) of the roller end-face walls (1a, 1b).
  16. Vibratory roller according to claim 15, characterised in that the carrier (17) surrounds the differential mechanism (11-15) as a protective housing.
  17. Vibratory roller according to any one of the preceding claims, characterised by a comparator element (37) which is effective in the first operating state and compares with each other, on the one hand, signals which are output by a transmitting device (35 or 36), are derived from an non-slip tyre (1 or 2) and correspond to the angular velocity (ω1 or ω2) thereof and the angular acceleration (ξ1 or ξ2) thereof, and, on the other hand, signals which are output by a transmitting device (35 or 36), are derived from a tyre (1 or 2) with a tendency to slip and correspond to the angular velocity (ω1 or ω2) thereof and the angular acceleration (ξ1 or ξ2) thereof and, when a predetermined difference (Δω and Δξ) for these signals is exceeded, activates an adjusting member (31) which in turn correspondingly reduces the angle (α) which the vector of the directional vibration forms with the plane which is parallel to the ground and contains the travel axis (28).
  18. Vibratory roller according to any one of the preceding claims, characterised in that the unbalanced shafts (3, 4) have the same moment of inertia (m*r).
  19. Method of operating the vibratory roller according to any one of the preceding claims,
    characterised in that in the first operating state the angle (α) which the vector of the directional vibration forms with the plane which is parallel to the ground and contains the travel axis (28) is set in such a manner that it amounts to 0° to 45° in the case of loose or bituminous ground and 45° to 90° in the case of ground which is difficult to compact.
  20. Method according to claim 19, characterised in that the angle (α) which the vector of the directional vibration forms with the plane which is parallel to the ground and contains the travel axis (28) is set in a programme-controlled manner in dependence upon the thickness of the ground layer to be compacted.
  21. Method according to claim 19 or 20, characterised in that in the case of a change in the direction of travel the vector of the directional vibration is changed automatically in a mirror-image manner with respect to the plane which is parallel to the ground and contains the travel axis (28).
  22. Method according to claim 20 or 21, characterised in that the angle (a) which the vector of the directional vibration forms with the plane which is parallel to the ground and contains the travel axis (28) is reduced in a programme-controlled manner with each passage of the vibratory roller over the ground to be compacted.
EP96929220A 1995-08-08 1996-08-07 Vibratory roller with at least one tyre having a built-in twin-shaft vibration generator Expired - Lifetime EP0789801B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19529115A DE19529115A1 (en) 1995-08-08 1995-08-08 Vibration mechanism, particularly for use in soil compaction
DE19529115 1995-08-08
PCT/EP1996/003499 WO1997006308A1 (en) 1995-08-08 1996-08-07 Vibratory roller with at least one tyre having a built-in twin-shaft vibration generator

Publications (2)

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EP0789801A1 EP0789801A1 (en) 1997-08-20
EP0789801B1 true EP0789801B1 (en) 2001-09-26

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

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19911913A1 (en) * 1999-03-17 2000-09-21 Beissbarth Gmbh Tire inspection method and device
SE513571C2 (en) * 1999-03-18 2000-10-02 Ulf Bertil Andersson Apparatus for generating mechanical vibrations
DE19943391A1 (en) * 1999-09-10 2001-04-12 Wacker Werke Kg Vibration exciter for soil compaction equipment
JP4131433B2 (en) * 2000-11-29 2008-08-13 ハム アーゲー Tamping machine
US20120148585A1 (en) * 2001-05-01 2012-06-14 Andrew Saxon Fusion molecules and methods for treatment of immune diseases
US6558072B2 (en) 2001-05-15 2003-05-06 Caterpillar Paving Products Inc. Speed control system for a work machine
US6857816B2 (en) * 2001-06-20 2005-02-22 Sakai Heavy Industries, Ltd. Roller
US6585450B2 (en) * 2001-07-10 2003-07-01 Ingersoll-Rand Company Speed controlled eccentric assembly
US6698974B2 (en) * 2001-12-11 2004-03-02 Caterpillar Inc System for electrically powering and vibrating a compacting roller
US7938595B2 (en) * 2007-04-30 2011-05-10 Caterpillar Paving Products Inc. Surface compactor and method of operating a surface compactor
US8376655B2 (en) * 2008-10-03 2013-02-19 Caterpillar Paving Products Inc. Compactor with smooth hose routing
US7857544B2 (en) * 2008-10-03 2010-12-28 Caterpillar Inc Extension plate for a compactor
DE102008050576A1 (en) * 2008-10-06 2010-04-08 Bomag Gmbh Device for generating a circular oscillation or a directed oscillation with continuously adjustable oscillation amplitude or exciter force
WO2011137462A1 (en) * 2010-04-30 2011-11-03 Millen Works Oscillating device for generating seismic loads and compacting soil
DE102010052713A1 (en) * 2010-11-26 2012-05-31 Bomag Gmbh A traveling soil compacting device and method for detecting a layer E modulus of a topmost layer of said bottom layer structure
CN102787544B (en) * 2011-05-16 2017-08-25 池州腾虎机械科技有限公司 A kind of directional vibration wheel of road roller
US9062420B2 (en) * 2011-07-15 2015-06-23 Ammann Schweiz Ag Unbalance type exciter for a soil compaction device
CN102691248B (en) * 2012-05-24 2015-01-28 青岛科技大学 Amplitude adjustment device for intelligent vibratory roller
DE102012024104A1 (en) * 2012-12-10 2014-06-12 Bomag Gmbh compaction
CN103174085B (en) * 2013-03-07 2015-05-13 青岛科技大学 Intelligent amplitude adjustment device of vibratory roller
CN103758014B (en) * 2014-01-15 2016-02-17 柳工无锡路面机械有限公司 There is multifunctional vibration driving wheel and the control method thereof of directional vibration and circumferential oscillation
JP6214428B2 (en) * 2014-02-26 2017-10-18 大成ロテック株式会社 Compaction device and compaction ground construction method
DE102014205503A1 (en) * 2014-03-25 2015-10-01 Hamm Ag Method for correcting a measured value profile by eliminating periodically occurring measuring artifacts, in particular in the case of a soil compactor
CN104631287B (en) * 2015-02-12 2017-04-12 徐工集团工程机械股份有限公司道路机械分公司 Vibrating wheel and vibrating road roller
EP3357589A1 (en) 2017-02-03 2018-08-08 BAUER Maschinen GmbH Oscillation generator and method for generating oscillations
DE102019113947A1 (en) * 2019-05-08 2020-11-12 Liebherr-Components Biberach Gmbh Vibration generator and construction machine with such a vibration generator
US20220228328A1 (en) * 2019-05-10 2022-07-21 Volvo Construction Equipment Ab Self-balancing uni-drum compactor
RU2724157C1 (en) * 2019-05-27 2020-06-22 Федеральное государственное бюджетное образовательное учреждение высшего образования "Сибирский государственный автомобильно-дорожный университет (СибАДИ)" Vibrating pavement roller
RU2735316C1 (en) * 2019-09-13 2020-10-30 Федеральное государственное бюджетное образовательное учреждение высшего образования "Сибирский государственный автомобильно-дорожный университет (СибАДИ)" Road vibrating roller
KR102400849B1 (en) * 2021-08-20 2022-05-23 (주)대동이엔지 vibrating rotary ripper

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2803172C2 (en) * 1978-01-25 1983-01-05 Losenhausen Maschinenbau AG, 4000 Düsseldorf Vibrating roller with two-part roller drum
US4454780A (en) * 1981-07-06 1984-06-19 Ingersoll-Rand Company Vibratory mechanism
DE4129182A1 (en) * 1991-09-03 1993-03-04 Bomag Gmbh COMPRESSOR
DE4434779A1 (en) * 1994-09-29 1996-04-04 Bomag Gmbh Method and device for dynamically compacting soil

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WO1997006308A1 (en) 1997-02-20
DE59607775D1 (en) 2001-10-31
DE19529115A1 (en) 1997-03-06
CA2202132A1 (en) 1997-02-20
EP0789801A1 (en) 1997-08-20
CA2202132C (en) 2001-07-10
JP3778939B2 (en) 2006-05-24
US5934824A (en) 1999-08-10

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