EP3901371B1 - Balourd pour un rouleau d'engin de compactage d'un engin de compactage de sol - Google Patents

Balourd pour un rouleau d'engin de compactage d'un engin de compactage de sol Download PDF

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Publication number
EP3901371B1
EP3901371B1 EP21163305.2A EP21163305A EP3901371B1 EP 3901371 B1 EP3901371 B1 EP 3901371B1 EP 21163305 A EP21163305 A EP 21163305A EP 3901371 B1 EP3901371 B1 EP 3901371B1
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EP
European Patent Office
Prior art keywords
spur gear
unbalance
gear
rotation
transmission
Prior art date
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Application number
EP21163305.2A
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German (de)
English (en)
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EP3901371A1 (fr
Inventor
Gerhard Wolfrum
Peter Janner
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Hamm AG
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Hamm AG
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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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/162—Making use of masses with adjustable amount of eccentricity
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • 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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/026—Improving by compacting by rolling with rollers usable only for or specially adapted for soil compaction, e.g. sheepsfoot rollers

Definitions

  • the present invention relates to an unbalanced arrangement for a compactor roller of a soil compactor, comprising a first unbalanced mass unit which can be rotated about an unbalanced axis of rotation and has a first center of gravity which is eccentric with respect to the unbalanced axis of rotation, a second unbalanced mass unit which can be rotated about the unbalanced axis of rotation and has a center of gravity which is eccentric with respect to the unbalanced axis of rotation second center of mass, an unbalance drive for jointly driving the first unbalance mass unit and the second unbalance mass unit for rotation about the axis of rotation of the unbalance, and a phase position adjustment unit for adjusting a phase position of the first center of mass with respect to the second center of gravity about the axis of rotation of the unbalance.
  • Such an unbalance arrangement is from DE 102 35 976 A1 known.
  • one of the two unbalanced mass units is coupled to the drive shaft of an unbalanced drive and can be driven directly by this to rotate about an unbalanced axis of rotation.
  • the other of the two unbalanced mass units can be driven by the unbalanced drive to rotate about the unbalanced axis of rotation via a phase position adjustment unit designed as a planetary gear.
  • the phase position adjustment unit designed as a planetary gear has an input ring gear and an output ring gear.
  • a plurality of planetary gear units following one another in the circumferential direction each has an input planetary gear which meshes with the input ring gear and an input sun gear which can be driven to rotate by the unbalance drive, and has an output planetary gear which rotates together with the output ring gear and one with the other unbalanced mass unit coupled output sun gear is in meshing engagement.
  • An unbalance arrangement according to the preamble of claim 1 is known from DD-A-29601.
  • the spur gear arrangement provided in this unbalanced arrangement comprises a transmission input spur gear coupled to an unbalanced mass unit for common rotation and a transmission output spur gear coupled to another unbalanced mass unit for common rotation.
  • Torque is transmitted between the transmission input spur gear and the transmission output spur gear via two planetary gear assemblies, each including a ring gear and a plurality of planetary gears.
  • the planet gears of the two planetary gear assemblies are carried on a common planet carrier.
  • One of the two holder wheels can be rotated with respect to the other ring gear in order to adjust the phasing of the centers of mass of the two unbalanced mass units relative to one another.
  • the unbalanced arrangement according to the invention is characterized in that the phase position adjustment unit comprises a spur gear arrangement in the torque transmission path between the unbalanced drive and the first unbalanced mass unit or the second unbalanced mass unit.
  • phase position adjustment unit in the unbalance arrangement constructed according to the invention comprises a spur gear arrangement, i.e. a gear arrangement in which all gears that are drive-connected or meshing with one another are designed as spur gears
  • a structure can be implemented with standard components that can be used to transmit large torques suitable is.
  • spur gears are gears which have teeth on their outer circumference with teeth projecting radially outwards and which are drive-connected to other spur gears in that the teeth of these spur gears are in meshing engagement and are therefore in meshing engagement connected spur gears rotate in opposite directions, or that an endless transmission element, such as a toothed belt or a chain, engages with the toothing of these spur gears and thus spur gears that are drive-connected to one another in this way rotate in the same direction.
  • an endless transmission element such as a toothed belt or a chain
  • the spur gear arrangement comprises a gear input spur gear that can be driven by the unbalance drive to rotate about a gear rotation axis, a gear output spur gear that can rotate about the gear rotation axis, and a group of gear gears meshing with the gear input spur gear and the gear output spur gear.
  • Variable spur gears wherein the gear variable spur gears are rotatably supported on a variable spur gear carrier, and wherein the variable spur gear carrier is relative to the gear input spur gear and the Transmission output spur gear is rotatable about the transmission axis of rotation.
  • the adjusting spur gear carrier can be assigned an adjusting spur gear carrier drive for pivoting the adjusting spur gear carrier about the gear rotary axis.
  • a variable spur gear drive can include a drive motor which is on the variable spur gear carrier, for example via a crank drive, a Worm wheel drive, a rack and pinion drive or a gear drive, in particular a spur gear drive, acts.
  • the axis of rotation of the gear mechanism corresponds to the axis of rotation of the imbalance.
  • the group of adjusting spur gears can have a first adjusting spur gear that can rotate about a first adjusting spur gear rotation axis parallel to the gear rotation axis and mesh with the gear input spur gear, and a first adjusting spur gear about a second adjustment spur gear that is parallel to the gear rotation axis Variable spur gear axis of rotation rotatable and second variable spur gear meshing with the first variable spur gear and the transmission output spur gear.
  • the transmission output spur gear can be coupled to the second unbalanced mass unit for common rotation.
  • the transmission input spur gear can be driven to rotate with the unbalanced drive via the first unbalanced mass unit, and/or that the first unbalanced mass unit and the second unbalanced mass unit axially between the unbalanced drive and the phase position adjustment unit are arranged.
  • the first unbalanced mass unit can be coupled in a first axial end area to the unbalanced drive for driving the first unbalanced mass unit to rotate about the unbalanced axis of rotation, and the first unbalanced mass unit can be coupled in a second axial end area by means of a gear -Transmission unit with the gear input spur gear in drive connection.
  • the first transmission intermediate spur gear can be drivingly connected to the transmission drive spur gear by means of an endless transmission organ and/or at least one connecting spur gear .
  • a single connecting spur gear meshing with the first transfer spur gear and the transfer drive spur gear it is equally ensured that the first transfer spur gear and the transfer drive spur gear rotate in the same direction of rotation.
  • Several connecting spur gears forming a gear train can also be used to produce the drive connection.
  • the second transfer intermediate spur gear can mesh with the transmission input spur gear so that these two spur gears rotate in opposite directions to each other.
  • the endless transmission element can include a toothed belt or a drive chain for a slip-free transmission of the torque. Furthermore, it can be provided for this purpose that the first transmission intermediate spur gear and the second transmission intermediate spur gear are carried on the transmission shaft in a rotationally fixed manner.
  • the transmission input spur gear can be in drive connection with a motor drive spur gear for introducing a drive torque.
  • the transmission input spur gear mesh with the motor drive spur gear.
  • the motor drive spur gear can be provided on a drive shaft of the unbalance drive.
  • the first unbalanced mass unit can be drive-connected to the motor drive spur gear by means of a transmission transmission unit.
  • the first transmission intermediate spur gear mesh with the motor drive spur gear and/or that the second transmission intermediate spur gear mesh with the transfer output spur gear.
  • the first transmission intermediate spur gear and the second transmission intermediate spur gear can be carried on the transmission shaft in a rotationally fixed manner.
  • the unbalanced drive and the phase position adjustment unit can be arranged on the same axial side with respect to the first unbalanced mass unit and the second unbalanced mass unit.
  • the present invention also relates to a compactor roller for a soil compactor, comprising a roller shell surrounding a roller axis of rotation, with an unbalanced arrangement constructed according to the invention being provided in a roller interior.
  • the roller axis of rotation correspond to the unbalanced axis of rotation.
  • the present invention further relates to a soil compactor, comprising at least one compactor roller constructed according to the invention and rotatably supported on a compactor frame about a roller axis of rotation.
  • a soil compactor is generally denoted by 10 .
  • the soil compactor 10 comprises a cab 14 on a central machine frame 12, in which an operator can sit.
  • a front machine frame 16 and a rear machine frame 18 are pivotally supported on the central machine frame 12 .
  • On the front machine frame 16 and on the rear machine frame 18, a compactor roller 20, 22 is rotatably supported about a roller axis of rotation.
  • the front machine frame 16 and the rear machine frame 18 and the compactor rollers 20, 22 rotatably supported thereon can be mutually im Essentially be identical and are below with reference to 2 explained by way of example using the rear machine frame 18 or the compactor roller 22 rotatably carried thereon about a roller axis of rotation W.
  • the soil compactor 10 can be designed in many different ways and, for example, can also have only one such compactor roller, for example in the front area thereof, while in the rear region of the soil compactor 10 a plurality of rubber wheels can then be provided.
  • the structure of a compactor roller explained below can in principle be implemented independently of the design of the soil compactor 10 .
  • the compactor roller 22 comprises a roller shell 24 which surrounds the roller axis of rotation W and which surrounds an inner space 26 of the roller.
  • the compactor roller 22 is rotatably supported about the axis of rotation W of the roller on lateral frame parts 28 , 30 of the rear machine frame 18 .
  • the compactor roller 22 can be assigned a travel drive motor 23, for example a hydraulic motor.
  • An unbalanced arrangement is provided in the interior space 26 of the roll.
  • the unbalance arrangement 32 comprises two unbalance mass units 34, 36 rotatable about an unbalance axis of rotation U, each with a center of mass M 1 , M 2 eccentric to the unbalance axis of rotation U, which corresponds to the axis of rotation W of the roller.
  • the two unbalanced mass units 34 , 36 are arranged in relation to one another in such a way that their centers of mass M 1 , M 2 are positioned in the same axial area, in particular an axial center area of the compactor roller 22 .
  • the first unbalance mass unit 34 may be rotatably supported in the compactor drum 22 on hangers 38, 40 carried therein, and the second unbalance mass unit 36 may be received in the first unbalance mass unit 34 and rotatably supported thereon.
  • An unbalanced drive 42 is assigned to the unbalanced arrangement 32 .
  • This imbalance drive 42 designed as a hydraulic motor, for example, is coupled to a shaft section 44 extending from the first imbalance mass unit 34 for common rotation and thus drives the first imbalance mass unit 34 directly to rotate about the imbalance axis of rotation U or the roller axis of rotation W.
  • directly means that no gear arrangement or the like that transmits the torque is provided between a drive shaft of the unbalance drive 42 and the shaft section 44 or the first unbalance mass unit 34 .
  • the second unbalanced mass unit 36 is driven to rotate about the unbalanced axis of rotation U by the unbalanced drive 42 via the first unbalanced mass unit 34 and a phase position adjustment unit, generally designated 46 .
  • the phase position adjustment unit 46 is coupled on the drive side to a hollow shaft section 48 of the first unbalanced mass unit 34 and on the output side to a shaft section 50 of the second unbalanced mass unit 36 passing through the hollow shaft section 48 .
  • phase position adjustment unit 46 By means of the phase position adjustment unit 46, not only is the drive torque of the unbalance drive 42 transmitted to the second unbalance mass unit 36 via the first unbalance mass unit 34, but the phase position adjustment unit 46 can also be operated to adjust the phase position of the centers of mass M 1 , M 2 of the two unbalance mass units 34, 36 to adjust the unbalance axis of rotation U with respect to each other, which means that the angular distance between the two centers of mass M 1 , M 2 around the unbalance axis of rotation U can be adjusted with respect to one another.
  • the adjustment range is preferably 180°, so that, starting from the 2 shown state, in which the two centers of mass M 1 , M 2 have an angular distance of 180° to each other and thus the imbalances provided by the two unbalance mass units 34, 36 compensate each other, the angular distance can be reduced to zero, so that the two centers of mass M 1 , M 2 have the same phase relation to one another and the imbalance arrangement 32 provides a maximum imbalance.
  • the unbalance assembly 32 Since the unbalance assembly 32 is positioned such that the Unbalanced mass units 34, 36 are driven by the unbalanced drive 42 to rotate about the roller axis of rotation V, the rotating unbalanced mass units 34, 36 generate a force that is essentially orthogonal to the roller axis of rotation W, so that a vibration acceleration is generated for the compactor roller 42, by which this is correspondingly periodically accelerated towards or away from the subsoil to be compacted.
  • phase position adjustment unit 46 The structure of the phase position adjustment unit 46 is described below with reference to FIG Figures 3 to 5 described in detail.
  • the phase position adjustment unit 46 has a splined section 52 on the input side, which can be coupled to the hollow shaft section 48 of the first unbalanced mass unit 34 for common rotation about the unbalanced axis of rotation U.
  • a transmission drive spur gear 54 of a gear transmission unit, generally designated 56, is connected in a rotationally fixed manner to the splined section 52 .
  • the transmission transmission unit 56 also includes a first transmission intermediate spur gear 60 and a second transmission intermediate spur gear 62 on a transmission shaft 58.
  • the two transmission intermediate spur gears 60, 62 are each rotatably carried on the transmission shaft 58 and with it about a transmission axis of rotation Ue rotatable.
  • the two intermediate transmission spur gears 60, 62 are spaced axially from one another. Equally, these could be designed as respective gearwheel sections of an intermediate spur gear that is continuous in the direction of the transmission shaft 58 or provides it.
  • the first intermediate transmission spur gear 60 is in drive connection with the transmission drive spur gear 54 via an endless transmission element 64, here designed as a toothed belt. Gear arrangement of the phase position adjustment unit 46 and is thus in drive connection with it.
  • a transmission output spur gear 70 of the spur gear assembly 68 is non-rotatably connected to a further splined section 72, which in turn can be coupled to the shaft section 50 of the second unbalanced mass unit 36 for common rotation.
  • the phase position adjustment unit 46 can be coupled to the first unbalanced mass unit 34 or the second unbalanced mass unit 36 both on the input side and on the output side in a manner other than by the splined sections 52, 72.
  • the spur gear arrangement 68 comprises a group of gear adjusting spur gears 78, 80 on a cassette-like housing 74, which is supported in a housing 76 of the phase position adjustment unit 76 so as to be pivotable about a gear rotation axis G.
  • the gear rotation axis corresponds G of the unbalance axis of rotation U and thus also of the roller axis of rotation W.
  • an adjusting lever mechanism 84 actuated, for example, by a hydraulic cylinder, a rack and pinion drive, a worm wheel drive or the like can be used be whose pivoting about the transmission axis of rotation G leads to a corresponding pivoting of the adjusting spur gear carrier 82 about the transmission axis of rotation G.
  • the group of gear adjustment spur gears 78, 80 includes a first gear adjustment spur gear 78, which is rotatably supported on the adjustment spur gear carrier 82 about a first adjustment spur gear axis of rotation V1, and includes a second gear adjustment spur gear 80, which is rotatably supported on the adjustment spur gear carrier 82 about a second adjustment spur gear rotation axis V2
  • the two gear adjustment spur gears 78, 80 are axially offset from one another, so that the first gear adjustment spur gear 78 meshes with a toothing section of the same with the gear input spur gear 66 and with another gear section of the same meshes with the second gear adjustment spur gear 80 stands.
  • the second gear adjusting spur gear 80 in turn meshes with the gear output spur gear 70 with a further toothing section.
  • gear adjusting spur gears 78, 80 are designed as spur gears having these toothing sections throughout.
  • the gear adjusting spur gears 78, 80 could equally well be formed by gear wheel sections which are axially separated from one another and are carried on a respective shaft in a rotationally fixed manner.
  • the unbalance drive 42 drives the first unbalance mass unit 34 to rotate about the unbalance axis U.
  • the first unbalanced mass unit 34 rotating about the unbalanced axis of rotation U drives the second unbalanced mass unit 36 to rotate about the unbalanced axis of rotation U via the phase position adjustment unit.
  • the design of the transmission transmission unit 56 and the spur gear arrangement 68 ensures that the two unbalanced mass units 34, 36 coupled to one another via the phase position adjustment unit 46 rotate in the same direction of rotation and at the same speed relative to one another about the unbalanced axis of rotation U and thus also the roll axis of rotation W rotate.
  • the adjusting spur gear carrier 82 is held in place, the phase position of the centers of mass M 1 , M 2 does not change.
  • the adjusting lever mechanism 84 and with it the adjusting spur gear carrier 82 are pivoted about the axis of rotation G of the transmission. This forces a relative rotation between the transmission input spur gear 66 and the transmission output spur gear 70.
  • imbalance drive 42 is arranged on a first axial end area 86 of first imbalance mass unit 34
  • phase position adjustment unit 46 is arranged on a second axial end area 88 of first imbalance mass unit 34, so that the first imbalance mass unit 34 and thus also the second unbalanced mass unit 36 are arranged axially between the unbalanced drive 42 and the phase position adjustment unit 46 .
  • a second embodiment of the unbalanced arrangement or the phase position adjustment unit is described below, which is characterized in that all system areas of the unbalanced arrangement, which serve to drive or to transmit torque or also to adjust the phase position, are on the same axial side of the first unbalanced mass unit or both imbalance mass units are arranged. This leads to an axially compact structure.
  • the imbalance drive 42a which can comprise a hydraulic motor, for example, drives via a motor drive spur gear 90a, which can be supported in a torque-proof manner on a motor output shaft, on the one hand the first intermediate transmission gear 60a of the transmission transmission unit 56a to rotate about the transmission axis of rotation Ue and, in turn, drives the transmission input spur gear 66a of the spur gear assembly 68a to rotate about the transmission axis of rotation G .
  • the motor drive gear 90a meshes with both the first transfer intermediate spur gear 60a and the transmission input spur gear 66a.
  • the second transmission intermediate spur gear 62a is in meshing engagement and thus in driving connection with a transmission output spur gear 92a, which is coupled to the hollow shaft section 48a of the first unbalanced mass unit 34a for common rotation about the unbalanced axis of rotation U.
  • the unbalance drive 42 drives the first unbalance mass unit 34a to rotate about the unbalance axis of rotation U via the transmission transmission unit 56a.
  • the spur gear arrangement 68a comprises the first gear adjustment spur gear 78a and the second gear adjustment spur gear 80a on the adjusting spur gear carrier 82a designed as a cassette-like housing 74a.
  • each of the two transmission adjustment spur gears 78a, 80a is formed with two spur gear sections that are formed axially separately from one another.
  • One of these spur gear portions of the first transmission variable spur gear 78a meshes with the transmission input spur gear 66a.
  • the other spur gear portion of the first gear variable spur gear 78a meshes with one of the two spur gear portions of the second gear variable spur gear 80a.
  • the unbalance drive 42 in the embodiment of Figures 6 to 10 with its motor drive spur gear 90a directly in driving connection with the input area of the spur gear arrangement 68a, namely the gear input spur gear 66a, and does not drive the first imbalance mass unit 34a directly, but via the gear transmission unit 56a.
  • the arrangement and dimensioning of the various spur gears that are drive-connected to one another is selected in such a way that the two unbalanced mass units 34a, 36a can basically rotate about the unbalanced axis of rotation U, which can also be driven in the same direction of rotation and at the same speed, corresponding to the axis of rotation of the roller.
  • This adjustment of the Verstellstirnradlys 82a can at the in the Figures 6 to 10 shown structure can be achieved by a variable displacement motor 94a, such as electric motor, hydraulic motor or the like, and a spur gear mechanism 96a.
  • the spur gear mechanism 96a includes a first spur gear 98a non-rotatably supported on a motor shaft of the servo motor 94a, and includes a second spur gear 100a non-rotatably supported on the servo spur gear carrier 82a and thus revolving therewith upon energization of the servo motor 94a about the gear Axis of rotation G rotates.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Architecture (AREA)
  • Paleontology (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Soil Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Agronomy & Crop Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)
  • Road Paving Machines (AREA)
  • Crushing And Grinding (AREA)

Claims (16)

  1. Ensemble de balourd pour un rouleau de compactage d'un compacteur de sol, comprenant :
    - une première unité de masse de balourd (34 ; 34a) pouvant tourner autour d'un axe de rotation de balourd (U) et ayant un premier centre de masse (M1) excentré par rapport à l'axe de rotation de balourd (U),
    - une deuxième unité de masse de balourd (36 ; 36a) pouvant tourner autour de l'axe de rotation de balourd (U) et ayant un deuxième centre de masse (M2) excentré par rapport à l'axe de rotation de balourd (U),
    - un entraînement de balourd (42 ; 42a) pour entraîner conjointement la première unité de masse de balourd (34 ; 34a) et la deuxième unité de masse de balourd (36, 36a) pour qu'elles tournent autour de l'axe de rotation de balourd (U),
    - une unité d'ajustement de position de phase (46 ; 46a) pour ajuster une position de phase du premier centre de masse (M1) par rapport au deuxième centre de masse (M2) autour de l'axe de rotation de balourd (U),
    dans lequel l'unité d'ajustement de position de phase (46 ; 46a) comprend un ensemble d'engrenage droit (68 ; 68a) dans le chemin de transmission de couple entre l'entraînement de balourd (42 ; 42a) et la première unité de masse de balourd (34 ; 34a) ou la deuxième unité de masse de balourd (36 ; 36a), dans lequel l'ensemble d'engrenage droit (68 ; 68a) comprend un engrenage droit d'entrée (66 ; 66a) pouvant être entraîné par l'entraînement de balourd (42 ; 42a) pour tourner autour d'un axe de rotation d'engrenage (G), un engrenage droit de sortie (70 ; 70a) pouvant tourner autour de l'axe de rotation d'engrenage (G), caractérisé en ce que l'ensemble d'engrenage droit (68 ; 68a) comprend un groupe d'engrenages droits de réglage d'engrenage (78, 80 ; 78a, 80a) en prise avec l'engrenage droit d'entrée (66 ; 66a) et l'engrenage droit de sortie (70 ; 70a), dans lequel les engrenages droits de réglage d'engrenage (78, 80 ; 78a, 80a) sont supportés de manière rotative sur un support d'engrenage droit de réglage (82 ; 82a), et dans lequel le support d'engrenage droit de réglage (82 ; 82a) peut tourner par rapport à l'engrenage droit d'entrée (66 ; 66a) et l'engrenage droit de sortie (70 ; 70a) autour de l'axe de rotation d'engrenage (G).
  2. Ensemble de balourd selon la revendication 1,
    caractérisé en ce qu'un entraînement de support d'engrenage droit de réglage (84 ; 94a, 96a) est associé au support d'engrenage droit de réglage (82 ; 82a) pour faire pivoter le support d'engrenage droit de réglage (82 ; 82a) autour de l'axe de rotation d'engrenage (G).
  3. Ensemble de balourd selon la revendication 1 ou 2,
    caractérisé en ce que l'axe de rotation d'engrenage (G) correspond à l'axe de rotation de balourd (U).
  4. Ensemble de balourd selon l'une des revendications 1, 2 ou 3,
    caractérisé en ce que le groupe d'engrenages droits de réglage d'engrenage (78, 80 ; 78a, 80a) comprend un premier engrenage droit de réglage (78 ; 78a) qui peut tourner autour d'un premier axe de rotation d'engrenage droit de réglage (V1) qui est parallèle à l'axe de rotation d'engrenage (G) et qui est en prise par engrènement avec l'engrenage droit d'entrée (66 ; 66a), et un deuxième engrenage droit de réglage (80 ; 80a) qui peut tourner autour d'un deuxième axe de rotation d'engrenage droit de réglage (V2) qui est parallèle à l'axe de rotation d'engrenage (G) et qui est en prise par engrènement avec le premier engrenage droit de réglage (78 ; 78a) et l'engrenage droit de sortie (70 ; 70a).
  5. Ensemble de balourd selon l'une des revendications précédentes,
    caractérisé en ce que l'engrenage droit de sortie (70 ; 70a) est couplé à la deuxième unité de masse de balourd (36 ; 36a) pour une rotation conjointe.
  6. Ensemble de balourd selon la revendication 5,
    caractérisé en ce que l'engrenage droit d'entrée (66) peut être entraîné en rotation avec l'entraînement de balourd (42) par l'intermédiaire de la première unité de masse de balourd (34), et/ou en ce que la première unité de masse de balourd (34) et la deuxième unité de masse de balourd (36) sont disposées axialement entre l'entraînement de balourd (42) et l'unité d'ajustement de position de phase (46).
  7. Ensemble de balourd selon la revendication 6,
    caractérisé en ce que la première unité de masse de balourd (34) est couplée dans une première zone d'extrémité axiale (86) à l'entraînement de balourd (42) pour entraîner la première unité de masse de balourd (34) en rotation autour de l'axe de rotation de balourd (U), et en ce que la première unité de masse de balourd (34) présente une liaison d'entraînement dans une deuxième zone d'extrémité axiale (88) au moyen d'une unité de transmission à engrenages (56) avec l'engrenage droit d'entrée (66).
  8. Ensemble de balourd selon la revendication 7,
    caractérisé en ce que l'unité de transmission à engrenages (56) comprend :
    - un engrenage droit d'entraînement de transmission (54) couplé à la deuxième zone d'extrémité axiale (88) de la première unité de masse de balourd (34) pour une rotation conjointe autour de l'axe de rotation de balourd (U),
    - un premier engrenage droit de renvoi de transmission (60) sur un arbre de transmission (58) pouvant tourner autour d'un axe de rotation de transmission (Ue) parallèle à l'axe de rotation de balourd (U), dans lequel le premier engrenage droit de renvoi de transmission (60) a une connexion d'entraînement à l'engrenage droit d'entraînement de transmission (54),
    - un deuxième engrenage droit de renvoi de transmission (62) sur l'arbre de transmission (58), dans lequel le deuxième engrenage droit de transmission (62) a une connexion d'entraînement avec l'engrenage droit d'entrée (66).
  9. Ensemble de balourd selon la revendication 8,
    caractérisé en ce que le premier engrenage droit de renvoi de transmission (60) a une connexion d'entraînement avec l'engrenage droit d'entraînement de transmission (54) au moyen d'un élément de transmission sans fin (64) et/ou d'au moins un engrenage droit de connexion, et/ou en ce que le deuxième engrenage droit de renvoi de transmission (62) est en prise par engrènement avec l'engrenage droit d'entrée de transmission (66),
    de préférence dans lequel l'élément de transmission sans fin (64) comprend une courroie dentée ou une chaîne d'entraînement.
  10. Ensemble de balourd selon l'une des revendications 8 ou 9,
    caractérisé en ce que le premier engrenage droit de renvoi de transmission (60) et le deuxième engrenage droit de renvoi de transmission (62) sont supportés de manière fixe en rotation sur l'arbre de transmission (58).
  11. Ensemble de balourd selon la revendication 5,
    caractérisé en ce que l'engrenage droit d'entrée (66a) a une connexion d'entraînement avec un engrenage droit d'entraînement du moteur (90a), de préférence, dans lequel l'engrenage droit d'entrée (66a) est en prise par engrènement avec l'engrenage droit d'entraînement du moteur (90a) et/ou l'engrenage droit d'entraînement du moteur (90a) est prévue sur un arbre d'entraînement de l'entraînement de balourd (42a).
  12. Ensemble de balourd selon la revendication 11,
    caractérisé en ce que la première unité de masse de balourd (34a) est reliée à l'engrenage droit d'entraînement du moteur (90a) par l'intermédiaire d'une unité de transmission à engrenages (58a).
  13. Ensemble de balourd selon la revendication 12,
    caractérisé en ce que l'unité de transmission à engrenages (58a) comprend :
    - un premier engrenage droit de renvoi de transmission (60a) sur un arbre de transmission (58a) pouvant tourner autour d'un axe de rotation de transmission (Ue) parallèle à l'axe de rotation de balourd (U), dans lequel le premier engrenage droit de renvoi de transmission (60a) a une connexion d'entraînement avec l'engrenage droit d'entraînement du moteur (90a),
    - un deuxième engrenage droit de renvoi de transmission (62a) sur l'arbre de transmission (58a),
    - un engrenage droit de sortie de transmission (92a) couplé à la première unité de masse de balourd (34a) pour une rotation conjointe autour de l'axe de rotation de balourd (U), dans lequel l'engrenage droit de sortie de transmission (92a) a une connexion d'entraînement avec le deuxième engrenage droit de renvoi de transmission (62a),
    de préférence dans lequel le premier engrenage droit de renvoi de transmission (60a) est en prise avec l'engrenage droit d'entraînement du moteur (90a), et/ou le deuxième engrenage droit de renvoi de transmission (62a) est en prise par engrènement avec l'engrenage droit de sortie de transmission (92a), ou/et le premier engrenage droit de renvoi de transmission (60a) et le deuxième engrenage droit de renvoi de transmission (62a) sont supportés de manière fixe en rotation sur l'arbre de transmission (58a).
  14. Ensemble de balourd selon l'une des revendications 11 à 13,
    caractérisé en ce que l'entraînement de balourd (42a) et l'unité d'ajustement de position de phase (46a) sont disposés sur le même côté axial par rapport à la première unité de masse de balourd (34a) et à la deuxième unité de masse de balourd (36a).
  15. Rouleau de compacteur pour un compacteur de sol, comprenant une enveloppe de rouleau (24) entourant un axe de rotation de rouleau (W), dans lequel un ensemble de balourd (10 ; 10a) selon l'une des revendications précédentes est prévu dans un intérieur de rouleau (26),
    de préférence dans lequel l'axe de rotation de rouleau (W) correspond à l'axe de rotation de balourd (U).
  16. Compacteur de sol, comprenant au moins un rouleau de compacteur (20, 22) selon la revendication 15 qui est supporté de manière rotative sur un cadre de compacteur (16, 18) autour d'un axe de rotation de rouleau (W).
EP21163305.2A 2020-04-22 2021-03-18 Balourd pour un rouleau d'engin de compactage d'un engin de compactage de sol Active EP3901371B1 (fr)

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DE102020110952A1 (de) * 2020-04-22 2021-10-28 Hamm Ag Unwuchtanordnung für eine Verdichterwalze eines Bodenverdichters
WO2023172725A1 (fr) * 2022-03-11 2023-09-14 Conn-Weld Industries, Llc Transmission elliptique

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DE29601C (de) O. HILLIG i in Berlin N., Kesselstr. 12 Stütz- und Transportir-Mechanismus j für Horden an Trockenapparaten
DD29601A1 (de) 1960-05-30 1965-03-05 Hermann Just VibrationsstraBenwalze mit im Walzenkorper angeordneter Unwucht
FR1304711A (fr) 1961-08-17 1962-09-28 Richier Sa Cylindre moteur à vibrations unidirectionnelles de direction réglable
DE2001988A1 (de) * 1970-01-17 1971-07-22 Benno Kaltenegger Strassenwalze
DE3043719A1 (de) * 1980-11-20 1982-06-24 Wacker-Werke Gmbh & Co Kg, 8077 Reichertshofen Schwingungserreger fuer bodenverdichtungsgeraete
JP2799691B2 (ja) * 1995-07-19 1998-09-21 酒井重工業株式会社 振動タイヤローラ
SE513571C2 (sv) * 1999-03-18 2000-10-02 Ulf Bertil Andersson Anordning för alstring av mekaniska vibrationer
JP4242012B2 (ja) * 1999-07-13 2009-03-18 酒井重工業株式会社 振動締固め機
US6769838B2 (en) 2001-10-31 2004-08-03 Caterpillar Paving Products Inc Variable vibratory mechanism
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CN102995521A (zh) * 2013-01-08 2013-03-27 长安大学 振动压路机用节能型激振器
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DE102020110952A1 (de) * 2020-04-22 2021-10-28 Hamm Ag Unwuchtanordnung für eine Verdichterwalze eines Bodenverdichters

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US11781278B2 (en) 2023-10-10
US20210332548A1 (en) 2021-10-28
DE102020110952A1 (de) 2021-10-28
CN113529539A (zh) 2021-10-22
CN113529539B (zh) 2023-01-31
CN216427916U (zh) 2022-05-03
EP3901371A1 (fr) 2021-10-27

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