EP1337713B1 - Appareil de compactage - Google Patents

Appareil de compactage Download PDF

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Publication number
EP1337713B1
EP1337713B1 EP01990445A EP01990445A EP1337713B1 EP 1337713 B1 EP1337713 B1 EP 1337713B1 EP 01990445 A EP01990445 A EP 01990445A EP 01990445 A EP01990445 A EP 01990445A EP 1337713 B1 EP1337713 B1 EP 1337713B1
Authority
EP
European Patent Office
Prior art keywords
pendulum
drum
oscillation
type
compactor according
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
EP01990445A
Other languages
German (de)
English (en)
Other versions
EP1337713A1 (fr
Inventor
Wolfgang Richter
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.)
Hamm AG
Original Assignee
Hamm AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hamm AG filed Critical Hamm AG
Publication of EP1337713A1 publication Critical patent/EP1337713A1/fr
Application granted granted Critical
Publication of EP1337713B1 publication Critical patent/EP1337713B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • the invention relates to a compacting device with at least one vibrating bandage according to the preamble of claim 1.
  • a generic compacting device is from the EP 0 530 546 A known.
  • the known compaction device has at least one movable bandage, which is arranged in parallel to the bandage axis and synchronously rotating unbalance exciter shafts of a vibration exciter in operative connection that the roller optionally exerts a predominantly dynamic shear or compressive load on the ground.
  • the vibration is generated by at least two exciter waves with oppositely rotating imbalance masses. This results in a directional vibration whose direction of action can be pivoted from a horizontal to a vertical direction.
  • the amplitude of the roller bandage remains constant, so that only the direction of vibration is changed.
  • vibration generation by means of circular vibrators.
  • the imbalance masses preferably sit on an axis in the center of the bandage and generate a circumferential force.
  • the amount of the resulting compaction force can be changed by the change in the phase position.
  • Another parameter for adapting to the conditions of use is the variation of the vibration frequency.
  • a method for measuring mechanical data of a soil and for adjusting the roll parameters which is based on said mechanical solution for adjusting the compression force and frequency, from the WO 98/17865 known.
  • Circular vibrators achieve higher compression values under comparable conditions than the directional vibration of the counter-vibrators.
  • the directional oscillation of the counter-vibrators produces pressure forces in the ground, which in each case act only in one direction and thus allow the compression by a shift of different layers of the compacting ground only to a limited extent. If this mode of action of the oscillation is pivoted from a vertical to a horizontal direction in order, for example, to reduce the vibration which can be transmitted to buildings, the shear stress which can be transmitted to the substrate becomes very small.
  • EP 0 053 598 can optionally be compacted with a deep-acting vibration according to the circular vibrator principle or with an oscillating bandage movement generated by torques, which generates predominantly shearing stresses in the subsurface.
  • the oscillating bandage movement reduces the vibratory load of the machine and the environment as the adjustable counter jogger, but achieved in comparison higher compression values.
  • the principle includes two exciter shafts that rotate synchronously in the same direction of rotation by 180 ° out of phase. As a result, the opposing forces generated by the exciter waves compensate for the bandage. A torque is generated on the bandage around the bandage axis.
  • the invention has for its object to simplify a compactor of the type mentioned in terms of their mechanical structure and to allow the generation of a vibrational movement, with which an introduction of force is optimized in the material to be compacted to allow rapid compaction.
  • the vibration exciter consists of a pendulum vibrator for generating an elliptical oscillation of the bandage with an oscillating housing oscillating about the bandage axis and with a single unbalance exciter shaft mounted at a radial distance from the bandage axis and parallel thereto in the pendulum housing.
  • the use of a pendulum vibrator combines the advantages of the simple construction of a Kreisrüttlers with the adjustment of a directional Gegenrüttlers, and the compaction technical advantages of an oscillating bandage movement.
  • the imbalance mass rotating on the exciter shaft generates circulating forces. Since the exciter shaft is mounted in a pendulum housing pivotable about the drum axis, only small forces are transmitted outside the direction of the longitudinal axis of the pendulum.
  • the Force components of the imbalance mass that are at an angle to the longitudinal axis of the pendulum create a moment on the pendulum housing about the drum axis causing the pendulum to deflect. Due to the high frequency of the imbalance mass and the mass inertia of the pendulum housing, the angle of the pendulum motion can be kept small.
  • the pendulum housing is preferably supported radially on the inside of the bandage via rolling bearings against the bandage.
  • the radial support can be made on the radially outer peripheral portion of the pendulum housing or on corresponding radial Genzouseabstufitch the pendulum housing on the axial side surfaces.
  • the radial bearings transmit the oscillations of the pendulum housing to the drum.
  • the angular position of the longitudinal axis of the pendulum vibrator relative to a vertical plane through the drum axis is adjustable by means of an adjusting device.
  • the orientation of the elliptical vibration is adjustable relative to a vertical plane through the drum axis by, for example ⁇ 90 °.
  • a pendulum vibrations permitting and limiting damping element is arranged between the adjusting device for adjusting the angular position of the pendulum vibrator and the pendulum housing.
  • the damping element serves as a coupling element between a control lever of the adjusting device and the oscillating pendulum housing.
  • the adjusting lever specifies the angular position of the longitudinal axis of the pendulum vibrator, wherein the damping element allows oscillation of the pendulum housing to this angular position to a certain extent.
  • the longitudinal axis of the pendulum housing lies in a plane defined by the drive shaft of the pendulum vibrator and the imbalance shaft.
  • the generated by the vibration drive elliptical waveform is on the one hand on the angular position of the pendulum housing and on the other hand on the speed of the Unbalance exciter shaft variable. In this respect, the direction of the elliptical vibration and its intensity can be adjusted.
  • the drive shaft of the pendulum vibrator is arranged coaxially to the drum axis, wherein the drive shaft is mounted in the pendulum housing.
  • the drive shaft for the pendulum vibrator is coupled via an intermediate gear with the unbalance exciter shaft.
  • the intermediate gear consist of a belt drive.
  • the unbalance exciter shaft can be driven electrically or hydrostatically directly.
  • the intermediate gear and the drive shaft of the pendulum vibrator can be omitted, so that the design effort is reduced.
  • two bandages are arranged side by side in the axial direction, which have a common pendulum vibrator.
  • the two bandages can be provided with independent bandage drives.
  • Fig. 1 is a road roller 1 with a chassis 3, a wheel drive with two rear wheels 7 and a front bandage. 4
  • Fig. 2 shows a cross section through the bandage 4, wherein the embodiment is a split bandage 4 with two bandage sections 4a, 4b.
  • the bandage sections 4a, 4b can each be provided with its own bandage drive 9a, 9b, which allow a relative movement of the two bandage sections during the steering.
  • the connecting flange 13, to which the bandage drive 9a, 9b is fastened, is elastically connected to the machine frame 3 via rubber elements 15.
  • the bandage drives 9a, 9b are fastened to the vehicle frame 3 on a connection flange 13 and drive the bandage sections 4a, 4b via an inner flange 11a, 11b.
  • the bandage 4 receives in its interior a pendulum vibrator 10 which is driven by a drive shaft 22 which extends coaxially to the drum axis 2 through the drum drive 9a.
  • the drive shaft 22 is connected to a vibration drive 6.
  • the pendulum vibrator 10 consists essentially of a pendulum housing 8 with a single mounted in the pendulum housing 8 unbalance exciter shaft 12.
  • the unbalance exciter shaft 12 is fixedly mounted on the unbalance exciter shaft 12 unbalanced masses 16 provided.
  • the drive shaft 22 is connected to the unbalance exciter shaft 12 via an arranged in the pendulum housing 8, e.g. connected from a belt drive 24 existing intermediate gear.
  • the belt drive 24 may have a toothed belt 34 which rotates via gears 36, 38 on the drive shaft 22 or the unbalance exciter shaft 12 in order to transmit the drive energy to the unbalance exciter shaft 12. Since no synchronous running of the masses is required, V-belts can also be used.
  • the pendulum housing 8 is in the embodiment of Fig. 2 pivotable about a pivot axis, which is coaxial with the drum axis 2.
  • the pendulum housing 8 is supported radially via a roller bearing 30 on its outer circumference against the drum portions 4a, 4b.
  • the drive shaft 22 for the pendulum vibrator 10 is in turn mounted in the pendulum housing 8 by means of a rolling bearing 32.
  • the vibration drive 6 can directly drive the unbalance exciter shaft 12, wherein the vibration drive 6 can consist of an electric motor or a hydraulic motor.
  • the drive shaft 22 and the existing of a belt drive 24 intermediate gear between the drive shaft 22 and the unbalance exciter shaft 12 accounts.
  • An adjusting device 5 which preferably consists of a piston-cylinder unit, is fixed on one side to the frame member 13 and actuates a in Fig. 2 invisible by the shaft 21 concealed adjusting lever, with the help of which passed through the bandage drive 9b shaft 21 is rotatable.
  • the shaft 21 is connected to a control lever 23 which is connected via at least one damping element 20 at its radial end to the pendulum housing 8.
  • the adjusting lever 23 may also consist of a disc, on whose outer circumference a plurality of damping elements 20 are coupled to the pendulum housing 8. With the help of the adjusting device 5 thus the pendulum vibrator 10 is adjustable relative to a vertical plane through the drum axis 2.
  • the pendulum housing 8 can be adjusted continuously by ⁇ 90 ° from its vertical rest position by means of the adjusting device 5.
  • At least one imbalance mass 16 is mounted on an unbalance exciter shaft and generated upon rotation centrifugal forces whose size depends on the size of the imbalance and the speed of the exciter shaft. The centrifugal forces act in every direction with equal strength.
  • the unbalance exciter shaft 12 is mounted in a pendulum housing 8, which in turn is suspended parallel to the unbalance exciter shaft 12 about the hinge center axis 2 pendulum.
  • centrifugal forces can only in the direction of the axis unbalance exciter shaft - Bandagenmitte be fully transmitted. Forces perpendicular to this plane cause a deflection of the pendulum housing from its rest position (pendulum oscillation).
  • the mass of the pendulum vibrator 10 must be pivoted against its inertia about the drum axis 2. This produces reaction forces in the drum axis 2 which are orthogonal to the above-mentioned directly transmitted centrifugal forces.
  • the forces acting transversely to the main vibration plane depend on the position of the center of gravity of the pendulum housing and on the distance of the unbalance exciter shaft 12 from the center of the drum or pendulum suspension.
  • the position of the oscillation ellipse is adjustable by means of the adjusting device 5, with which the oscillating pendulum housing 8 is pivotable in its angular position.
  • Fig. 3 For example, three marked with a, b and c angular positions of the pendulum housing 8 are shown with the associated elliptical bandage vibrations.
  • the position a shows the vertical position of the pendulum vibrator 10 with an elliptical bandage vibration whose major axis is vertical.
  • a bandage vibration is generated, the Main axis at an angle of, for example, 45 ° to the vertical.
  • the pendulum housing can also be pivoted through an angle of 90 °, whereby an elliptical band vibration can be adjusted, in which the main axis is horizontal.
  • Each position between the angular positions a, b, c is adjustable.
  • the angle of the pendulum housing oscillation can be kept small. For example, oscillates or oscillates the pendulum housing 8 relative to the set by means of the adjusting device 5 angular position as a central position by ⁇ 3 °.
  • the optimum vibration direction for the compression intensity can be done by measuring the waveform during compression.
  • the change in the form of vibration with increasing compaction of the ground compared to oscillation in uncompacted ground represents a measured value for the compaction.
  • This measured value serves as a reference variable for the regulation of the oscillation direction.
  • the road roller 1 can thus adapt to the background conditions.
  • the adjusting device 5 can be operated automatically or by manual control. During the automatic operation, the oscillation shape or the change of the elliptical oscillation movement of the roller bandage is monitored. During the crossing of the road roller 1, the condition of the ground is determined by the vibration analysis.
  • the results of the vibration analysis can be used to automatically adjust the vibration direction via a machine control. It can also be a speed control for the Unbalance exciter shaft 12 are carried out via the hydrostatic vibration drive 6.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Road Paving Machines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Dry Formation Of Fiberboard And The Like (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)

Claims (12)

  1. Appareil de compactage comprenant au moins un cylindre déplaçable (4, 4a, 4b) rotatif autour un axe de cylindre (2), comprenant un générateur de vibrations logé dans le cylindre (4, 4a, 4b), dont la position angulaire par rapport à un plan vertical passant par l'axe du cylindre (2) est ajustable pour un angle de pivotement réglable,
    caractérisé en ce
    que le générateur de vibrations est un secoueur oscillant (10), que le secoueur oscillant comprend un boîtier oscillant (8) pivotable autour d'un axe de pivotement s'étendant coaxialement à l'axe du cylindre (2) et un seul arbre générateur de vibrations à balourd (12) logé dans le boîtier oscillant (8) à distance radiale parallèle de l'axe du cylindre (2), et que le boîtier oscillant (8) oscille autour de la position angulaire réglée, le secoueur oscillant (10) génère des vibrations elliptiques du cylindre dans la position angulaire respective du secoueur oscillant (10).
  2. Appareil de compactage selon la revendication 1, caractérisé en ce que le boîtier oscillant est logé coaxialement par rapport à l'axe du cylindre (2).
  3. Appareil de compactage selon une des revendications 1 ou 2, caractérisé en ce que le boîtier oscillant (8) a un moment d'inertie résultant de la masse non équilibrée (16) rotative, le moment s'opposant au couple autour de l'axe de pivotement pour générer une forme d'oscillation elliptique du cylindre (4, 4a, 4b).
  4. Appareil de compactage selon une des revendications 1 à 3, caractérisé en ce que le boîtier oscillant (8) est logé radialement au sein du cylindre (4, 4a, 4b) par des paliers à roulement (30).
  5. Appareil de compactage selon une des revendications 1 à 4, caractérisé en ce que des éléments amortisseurs (20) sont prévus entre un moyen d'ajustage (5), pour ajuster la position angulaire du secoueur oscillant (10) par rapport au plan vertical passant par l'axe du cylindre (2), et le boîtier oscillant (8), les éléments amortisseurs permettant des mouvements oscillant du boîtier oscillant (8).
  6. Appareil de compactage selon une des revendications 1 à 5, caractérisé en ce que l'intensité de la compactage par l'oscillation elliptique est variable par la position du boîtier oscillant (8) et la vitesse de l'arbre générateur de vibrations à balourd (12).
  7. Appareil de compactage selon une des revendications 1 à 6, caractérisé en ce que l'arbre d'entraînement (22) du secoueur oscillant (10) est disposé coaxialement par rapport à l'axe du cylindre (2) et logé dans le boîtier oscillant (8).
  8. Appareil de compactage selon la revendication 7, caractérisé en ce que l'arbre d'entraînement (22) du secoueur oscillant (10) est relié l'arbre générateur de vibrations à balourd (12) par une transmission intermédiaire.
  9. Appareil de compactage selon la revendication 8, caractérisé en ce que la transmission intermédiaire est une transmission à courroie (24).
  10. Appareil de compactage selon une des revendications 1 à 9, caractérisé en ce que l'arbre générateur de vibrations à balourd (12) peut être entraîné directement par électricité ou hydrostatiquement.
  11. Appareil de compactage selon une des revendications 1 à 10, caractérisé en ce que deux cylindres (4, 4a, 4b) sont prévus l'un à coté de l'autre dans la direction axiale, les cylindres comprenant un secoueur oscillant (10) commun.
  12. Appareil de compactage selon une des revendications 1 à 11, caractérisé en ce que un moyen de mesurage contrôle le changement de la forme d'oscillation elliptique pendant la compactage et commande, en fonction du résultat de l'analyse des oscillations et par un moyen de commande de l'appareil, la position angulaire du secoueur oscillant (10) et, par cela, l'amplitude de l'oscillation agissant sur le substrat.
EP01990445A 2000-11-29 2001-11-27 Appareil de compactage Expired - Lifetime EP1337713B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10059245 2000-11-29
DE10059245 2000-11-29
PCT/EP2001/013806 WO2002044475A1 (fr) 2000-11-29 2001-11-27 Appareil de compactage

Publications (2)

Publication Number Publication Date
EP1337713A1 EP1337713A1 (fr) 2003-08-27
EP1337713B1 true EP1337713B1 (fr) 2009-01-07

Family

ID=7665098

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01990445A Expired - Lifetime EP1337713B1 (fr) 2000-11-29 2001-11-27 Appareil de compactage

Country Status (6)

Country Link
US (1) US6829986B2 (fr)
EP (1) EP1337713B1 (fr)
JP (1) JP4131433B2 (fr)
AT (1) ATE420245T1 (fr)
DE (1) DE50114647D1 (fr)
WO (1) WO2002044475A1 (fr)

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US8190338B2 (en) 2008-09-02 2012-05-29 The Board Of Regents Of The University Of Oklahoma Method and apparatus for compaction of roadway materials
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US7857544B2 (en) * 2008-10-03 2010-12-28 Caterpillar Inc Extension plate for a compactor
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DE976405C (de) * 1951-12-23 1963-08-22 Losenhausenwerk Duesseldorfer Unwuchtruettler mit pendelnd gelagertem Schwingungserzeuger
US3486427A (en) * 1967-03-10 1969-12-30 Losenhausen Maschinenbau Ag Vibratory rollers
DE1634450A1 (de) * 1967-03-10 1971-11-18 Losenhausen Maschb Ag Ruettelwalze

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JP4131433B2 (ja) 2008-08-13
US20040028472A1 (en) 2004-02-12
ATE420245T1 (de) 2009-01-15
JP2004514811A (ja) 2004-05-20
DE50114647D1 (de) 2009-02-26
US6829986B2 (en) 2004-12-14
WO2002044475A1 (fr) 2002-06-06
EP1337713A1 (fr) 2003-08-27

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