EP1342849B1 - Rouleau de compactage - Google Patents

Rouleau de compactage Download PDF

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Publication number
EP1342849B1
EP1342849B1 EP03003966A EP03003966A EP1342849B1 EP 1342849 B1 EP1342849 B1 EP 1342849B1 EP 03003966 A EP03003966 A EP 03003966A EP 03003966 A EP03003966 A EP 03003966A EP 1342849 B1 EP1342849 B1 EP 1342849B1
Authority
EP
European Patent Office
Prior art keywords
unbalance
piston
compaction roller
roller according
cylinder
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
EP03003966A
Other languages
German (de)
English (en)
Other versions
EP1342849A2 (fr
EP1342849A3 (fr
Inventor
Richard Stelbrink
Steffen Wachsmann
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.)
ABG Allgemeine Baumaschinen GmbH
Original Assignee
ABG Allgemeine Baumaschinen GmbH
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Filing date
Publication date
Application filed by ABG Allgemeine Baumaschinen GmbH filed Critical ABG Allgemeine Baumaschinen GmbH
Publication of EP1342849A2 publication Critical patent/EP1342849A2/fr
Publication of EP1342849A3 publication Critical patent/EP1342849A3/fr
Application granted granted Critical
Publication of EP1342849B1 publication Critical patent/EP1342849B1/fr
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
    • E01C19/286—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 compaction roller according to the preamble of claim 1.
  • the US-A-4105356 shows such a compaction roller.
  • the aim is to compress unbonded and hydraulically or bituminously bound materials in earthworks or road construction as quickly as possible to the prescribed Proctor or Marshallêt, but at the same time to prevent over-compression and to minimize grain erosion of the mineral constituents, especially in wear layers.
  • bituminous road surfaces In the case of bituminous road surfaces, a smoothing of the surface during compaction is to be avoided in order to ensure either a good layer composite or, in the case of wear layers, a high level of traction.
  • the setting of optimum system sizes for short compaction times is imperative for bituminous materials, as the material can be compacted by cooling the material shrinks and in the worst case, the prescribed final density can not be achieved.
  • compacting drainage asphalt open-pored asphalt
  • the pores in the near-surface area must not be closed in order to achieve the desired water drainage and reduce the so-called "air pumping" effect when rolling tires in the contact zone between the tire and the road surface.
  • a directional oscillator consists of at least two oppositely running exciter waves, the resulting force torque-free continuously from a horizontal direction in a vertical direction can be rotated.
  • the nominal amplitude or imbalance is not changed in this system. Again, unwanted waves, smoothing and pore closures can occur especially in horizontal vibrations.
  • a vibration exciter for a soil compaction machine in which an exciter shaft is provided with an imbalance, wherein a radially arranged to the exciter shaft cylinder with spring-loaded piston is used to effect an automatic adjustment of the imbalance due to changing the rotational speed of the changing centrifugal force.
  • each frequency is assigned exactly one amplitude.
  • the imbalance shaft can be accelerated from the state only with great imbalance.
  • the object of the invention is to provide a compaction roller according to the preamble of claim 1, which allows an optimal adaptation of the vibration to the respective road construction materials or to the local conditions such as bridges and vibration-sensitive structures and facilities.
  • an actuating cylinder is provided, whose communicating with the unbalance cylinder space of the adjusting cylinder is connected to a hydraulic source for leakage oil replacement via a controllable valve in an intermediate or intermediate position between the two end positions of the unbalance piston, from which the nominal amplitude can be increased or decreased , locks.
  • tandem compaction roller comprises a superstructure 1 with the driver's cab, below the front and rear, respectively, a rolling body 2 or 3 is mounted on steerable turntable 4. Between the two rolling elements 2, 3 is an engine compartment 5, which houses a drive motor, usually a diesel engine.
  • the front and / or rear roller body 2, 3 comprises two axially adjacent to each other arranged drum halves 6a, 6b and in each case a radially extending drum base 7 with a central passage opening. At the drum floors 7 each have a bearing flange 8 is attached.
  • the two bandage halves 6a, 6b are rotatably connected to one another about the two bearing flanges 8 and a spacer tube 9 about the roller body axis by a bearing 10, such as a roller bearing, is arranged between a bearing flange 8 and the spacer tube 9.
  • the turntable 4 which is steerably connected to the upper structure 1 is elastically connected on both sides via damping elements 11, such as rubber-metal elements, and a flange plate 11a, each with a hollow hydraulic traction motor 12.
  • the traction motors 12 are connected on the output side via a flange 13 with the adjacent bearing flange 8 and thus each drive the bandage halves 6a, 6b.
  • an exciter shaft 14 which is driven by a hydraulic vibration motor 15 and is mounted on the bearing flanges 8 via bearings.
  • An unbalance cylinder 16 is mounted centrally in a bore of the exciter shaft 14.
  • the unbalance cylinder 16 has a corresponding collar and on the opposite side a threaded portion for clamping by means of a clamping ring and a pair of nuts.
  • the unbalance cylinder 16 takes radially to the rolling body axis hydraulically adjustable an unbalanced piston 17.
  • the unbalance in the exciter shaft 14, which is sufficient to achieve the smallest nominal amplitude of the rolling element, are added continuously.
  • the unbalance piston 17 may be filled with lead in order to achieve the largest possible adjustment range of the nominal amplitude with minimum installation space.
  • the unbalance piston 17 is equipped with guide belts and a piston sealing ring. Deformation of the exciter shaft 14 (bending due to centrifugal forces) is not transmitted to the unbalance cylinder 16 by a sufficient clearance. The required amount of oil to move the unbalance piston 17 is provided by a bore 18 in the exciter shaft 14. The oil pressure is transmitted via a taper of the unbalance piston 17 and holes 19 to the piston crown.
  • bearing flanges 8 In one of the bearing flanges 8 is an oil inlet and outlet nipple 20 to lubricate the space within the spacer tube 9, the adjacent bearings, etc.
  • Fig. 3 the pressurization of the unbalance piston 17 by means of a precisely metered amount of oil to move the unbalance piston 17 via a rotary feedthrough 21, which is suspended due to rubber springs 22 and an additional oscillating mass 23 low vibration on one of the traction motors 12.
  • the oscillating mass 23 receives an adapter 24 which slidably supports a piston 25, which is connected via a pipe 26 with another, received by the exciter shaft 14 piston 27.
  • Radial and axial displacements between rotary feedthrough 21 and exciter shaft 14 due to thermal expansion are compensated by seals 28 of the pistons 25, 27.
  • Pins 29 prevent rotational slippage between the seals 28 and the exciter shaft 14 and the adapter 24 of the rotary feedthrough 21st
  • the required oil volume for changing the position of the unbalanced piston 17 is metered by displacing an adjusting piston 34 of an actuating cylinder 34a.
  • the piston rod 30 of the adjusting piston 34 is connected to a trapezoidal or ball screw 31 whose spindle is not displaceable under tensile or compressive stress (self-locking).
  • the screw drive 31 is driven by an electric or hydraulic motor 32.
  • An incremental travel measurement on the piston rod or optionally angle measurement on the screw drive 31 (preferably integrated therein and therefore not shown) is used to adjust the eccentricity of the unbalance piston 17 and the nominal amplitude.
  • the 2/2-way valve 33 can be automatically switched depending on the operating status in position flow.
  • the required oil volume for changing the position of the unbalance piston 17 using the adjusting piston 34 and its piston rod 30 is changed on the piston rod side by a variable oil volume.
  • electromagnets of a 3/3-way valve 35 are cyclically so controlled that the adjusting 34 can be moved in very small distances.
  • the adjusting piston 34 moves in the pressure circuit of the 3/3-way valve 35 in the direction of the piston side, at tank switching due to the centrifugal force of the unbalanced piston 17 in the direction of the piston rod side.
  • the blocking zero position of the 3/3-way valve 35 replaces the self-locking action of the screw 31 of Fig.
  • the function of the adjusting piston 34 with piston rod 30 is here exclusively the incremental displacement measurement for adjusting the eccentricity of the unbalanced piston 17 or the nominal amplitude.
  • the calibration and the leakage compensation are the same as those of Fig. 4a ,
  • the unbalance piston 17 is located in the in Fig. 5b shown position only at maximum manually or automatically set nominal amplitude and minimum working frequency.
  • the 2/2-way valve 33 is switched to flow and the oil pressure corresponds to the inlet pressure of the directional control valve. In this mode, leak oil can be replaced and the system calibrated.
  • the adjusting piston 34 the position of the Fig. 5b has reached, the 2/2-way valve 33 is immediately locked automatically. Subsequently, the nominal amplitude can be reduced continuously from this operating state.
  • the operating frequency is subsequently controlled in the direction of a smaller nominal amplitude, for example by means of characteristic map control, in order to avoid exceeding the permissible centrifugal force of the unbalanced piston 17.
  • the 2/2-way valve 33 is locked and leak oil replacement or calibration are not possible.
  • the nominal amplitude can be increased continuously from this operating state or be reduced. In the direction of smaller nominal amplitude, the operating frequency and in the direction of larger nominal amplitude, the position of the unbalanced piston 17 is subsequently controlled.
  • the vibration frequency is adjusted to the nominal amplitude as described above.
  • the optimum rolling speed can be automatically set as a function of the vibration frequency or displayed to the roller driver.
  • the position of the unbalance piston 17 can either be adjusted manually or automatically regulated depending on the density (rigidity) of the substrate.
  • tandem vibratory rollers either only the front, only the rear one or both rolling bodies 2, 3 can be equipped with an unbalance adjustable in the above manner.
  • a directional control valve 35 instead of the hydraulic motor 32 of Fig. 5a to 5c provided, which is connected to the piston rod side space of the adjusting cylinder 34, while in this case three-way directional control valve 33 is in turn connected to the space of the adjusting cylinder 34 a in front of the adjusting piston 34.
  • the unbalance cylinder 16 filled with oil from the hydraulic source via a pump 37.
  • the directional control valve 33 switched.
  • a pressure relief valve 36 is connected to the line from the pump 37 to the directional control valve 33. If the latter responds, this means the complete oil filling of the unbalance cylinder 16.
  • the directional control valve 33 Upon reaching the full oil filling of the unbalance cylinder 16, see. Fig. 6b , the directional control valve 33 is switched so that from the adjusting cylinder 34a, and indeed from the space in front of the adjusting piston 34, oil can flow back to the hydraulic source via a pressure relief valve 38, while the previously closed directional valve 35 is opened, so that hydraulic oil the adjusting 34th can adjust. As a result, the amount of oil in the adjusting cylinder 34a is completely returned to the hydraulic source, whereby at the same time the system is calibrated.
  • the directional valves 33, 35 are disabled and the vibration can be turned on, cf. Fig. 6c . Then, when a certain frequency, for example, 28 Hz, is reached, the amplitude adjustment of the in Fig. 6c shown position smallest amplitude made by appropriately opening the directional control valve 35.

Landscapes

  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (12)

  1. Rouleau de compactage comportant au moins un corps de rouleau (2, 3) avec un entraînement à vibrations qui comprend un arbre d'excitation (14) avec un balourd, susceptible d'être entraîné et monté dans le corps de rouleau (2, 3) axialement par rapport à celui-ci, le balourd présentant un cylindre de balourd (16) agencé au milieu par rapport à l'axe du corps de rouleau (2, 3) et maintenu par l'arbre d'excitation (14) avec un piston de balourd (17) réglable hydrauliquement, radialement à l'axe du corps de rouleau (2, 3), et au balourd du liquide hydraulique peut être amené de manière commandée depuis l'extérieur par un dispositif de réglage externe via un perçage (18) ménagé dans l'arbre d'excitation (14), en adaptant de manière continue l'amplitude nominale aux particularités de revêtement, le dispositif de réglage présentant un vérin (34a) avec un piston de réglage (34) et une chambre du vérin (34a) communiquant avec le cylindre de balourd, caractérisé en ce que la chambre du vérin (34a), qui communique avec le cylindre de balourd (16), est reliée à une source d'huile hydraulique pour remplacer l'huile de fuite via une soupape (33) commandable qui se ferme dans une position médiane du piston de balourd (17) depuis laquelle l'amplitude nominale peut être augmentée ou réduite.
  2. Rouleau de compactage selon la revendication 1, caractérisé en ce que la soupape (33) se ferme lorsque la fréquence de travail minimale est atteinte.
  3. Rouleau de compactage selon la revendication 1 ou 2, caractérisé en ce que, après avoir arrêté l'entraînement à vibrations via la soupape (33) commandable, on peut effectuer un échange d'huile hydraulique entre le contenu du cylindre de balourd (16) et la source d'huile hydraulique.
  4. Rouleau de compactage selon la revendication 3, caractérisé en ce que, après avoir arrêté l'entraînement à vibrations via la soupape (33) commandable, on peut effectuer un échange d'huile hydraulique entre le contenu du vérin (34a) et la source d'huile hydraulique.
  5. Rouleau de compactage selon la revendication 3 ou 4, caractérisé en ce que la soupape (33) commandable peut être reliée à la source d'huile hydraulique lorsque le piston de réglage (34) est rentré.
  6. Rouleau de compactage selon la revendication 5, caractérisé en ce que, lorsque le piston de réglage (34) est rentré et le cylindre de balourd (16) est rempli, la soupape (33) commandable peut être reliée à la source d'huile hydraulique et le piston de réglage (24) peut être sorti.
  7. Rouleau de compactage selon l'une des revendications 1 à 6, caractérisé en ce que le cylindre de balourd (16) est relié au dispositif de réglage par un passage tournant (21) qui est soutenu sur le corps de rouleau (2, 3) via un élément d'amortissement (22).
  8. Rouleau de compactage selon la revendication 7, caractérisé en ce qu'entre le passage tournant (21) et l'arbre d'excitation (14) est agencé un tube (26) qui est relié par un piston (25, 27) aux extrémités respectives de façon solidaire en rotation et avec jeu axial.
  9. Rouleau de compactage selon l'une des revendications 1 à 8, caractérisé en ce que le piston de réglage (34) est réglable mécaniquement ou hydrauliquement.
  10. Rouleau de compactage selon la revendication 9, caractérisé en ce que la position du piston de réglage (34) peut être surveillée par capteur.
  11. Rouleau de compactage selon la revendication 9 ou 10, caractérisé en ce que le dispositif de réglage peut être commandé en fonction d'une mesure des performances de compactage du corps de rouleau (2, 3).
  12. Rouleau de compactage selon l'une des revendications 1 à 11, caractérisé en ce que le piston de balourd (17) est rempli d'un métal lourd.
EP03003966A 2002-03-07 2003-02-22 Rouleau de compactage Expired - Lifetime EP1342849B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10210049A DE10210049B4 (de) 2002-03-07 2002-03-07 Verdichtungswalze
DE10210049 2002-03-07

Publications (3)

Publication Number Publication Date
EP1342849A2 EP1342849A2 (fr) 2003-09-10
EP1342849A3 EP1342849A3 (fr) 2004-12-01
EP1342849B1 true EP1342849B1 (fr) 2008-07-02

Family

ID=27740680

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03003966A Expired - Lifetime EP1342849B1 (fr) 2002-03-07 2003-02-22 Rouleau de compactage

Country Status (5)

Country Link
US (1) US20030223817A1 (fr)
EP (1) EP1342849B1 (fr)
JP (1) JP4203725B2 (fr)
CN (1) CN100529263C (fr)
DE (2) DE10210049B4 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021200285A1 (de) 2021-01-14 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Verdichtungsfahrzeug, bei welchem ein Fahrantrieb und eine Vibrationseinheit von einer gemeinsamen Versorgungstelle her mit Druckfluid versorgt werden

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006030628B4 (de) * 2006-07-03 2021-03-04 F. Weyhausen Ag & Co. Kg Maschinenfabrik Vorrichtung zur Verdichtung eines Baugrundes
US20110158745A1 (en) * 2009-12-31 2011-06-30 Caterpillar Paving Products Inc. Vibratory system for a compactor
CN105268621B (zh) * 2015-11-11 2018-06-05 王存伟 无级变幅振动器
CN113846540B (zh) * 2021-10-22 2024-02-09 李亚辉 一种道路桥梁工程路面修复装置
CN115157717B (zh) * 2022-06-29 2024-02-09 中化工程沧州冷却技术有限公司 一种冷却塔用玻璃钢管道的生产工艺
CN115369720B (zh) * 2022-07-29 2024-08-16 许慧保 一种无极变频定向液压振动压路机

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US3059483A (en) * 1960-05-31 1962-10-23 Continental Oil Co Vibrator with hydraulically controlled eccentricity
US3656419A (en) * 1969-04-01 1972-04-18 American Hoist & Derrick Co Vibratory roller
US4105356A (en) * 1977-05-19 1978-08-08 Koehring Corporation Vibratory roller
SE426719B (sv) * 1980-12-03 1983-02-07 Thurner Geodynamik Ab Forfarande och anordning for packning av ett materialskikt
AU570233B2 (en) * 1983-02-18 1988-03-10 Bowater Tutt Industries Pty. Ltd. Vibratory mechanism
US4759659A (en) * 1987-07-01 1988-07-26 Fernand Copie Variable vibrator system
DE4129182A1 (de) * 1991-09-03 1993-03-04 Bomag Gmbh Verdichtungsgeraet
AU692479B2 (en) * 1993-11-30 1998-06-11 Sakai Heavy Industries, Ltd. Vibrating mechanism and apparatus for generating vibrations for a vibration compacting roller with a variable amplitude
FI107365B (fi) * 1998-04-27 2001-07-13 Nokia Mobile Phones Ltd Menetelmä ja järjestelmä muuttuvan datankäsittelyn ilmaisemiseksi tiedonsiirtoyhteydessä
US6460006B1 (en) * 1998-12-23 2002-10-01 Caterpillar Inc System for predicting compaction performance
IT1307472B1 (it) * 1999-07-13 2001-11-06 Bitelli Spa Tamburo vibrante perfezionato per macchine compattatrici di suoli.
JP3725769B2 (ja) * 1999-10-28 2005-12-14 酒井重工業株式会社 ハンドガイドローラ
DE10031617A1 (de) * 2000-06-29 2002-01-17 Wacker Werke Kg Vibrationserreger mit Amplitudenverstellung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021200285A1 (de) 2021-01-14 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Verdichtungsfahrzeug, bei welchem ein Fahrantrieb und eine Vibrationseinheit von einer gemeinsamen Versorgungstelle her mit Druckfluid versorgt werden
WO2022152596A1 (fr) 2021-01-14 2022-07-21 Robert Bosch Gmbh Véhicule de compactage dans lequel un système d'entraînement et une unité de vibration sont alimentés en fluide sous pression par un point d'alimentation commun

Also Published As

Publication number Publication date
CN100529263C (zh) 2009-08-19
DE10210049B4 (de) 2004-03-25
DE10210049A1 (de) 2003-10-09
DE50310053D1 (de) 2008-08-14
EP1342849A2 (fr) 2003-09-10
US20030223817A1 (en) 2003-12-04
EP1342849A3 (fr) 2004-12-01
CN1445415A (zh) 2003-10-01
JP2004003296A (ja) 2004-01-08
JP4203725B2 (ja) 2009-01-07

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