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EP2599919B1 - Dispositif de réglage du levage d'une barre de compactage d'un finisseur de route - Google Patents

Dispositif de réglage du levage d'une barre de compactage d'un finisseur de route Download PDF

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Publication number
EP2599919B1
EP2599919B1 EP20120007935 EP12007935A EP2599919B1 EP 2599919 B1 EP2599919 B1 EP 2599919B1 EP 20120007935 EP20120007935 EP 20120007935 EP 12007935 A EP12007935 A EP 12007935A EP 2599919 B1 EP2599919 B1 EP 2599919B1
Authority
EP
European Patent Office
Prior art keywords
cam
shaft
cam shaft
camshaft
carrier
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.)
Not-in-force
Application number
EP20120007935
Other languages
German (de)
English (en)
Other versions
EP2599919A1 (fr
Inventor
Jens Wagner
Karl-Hermann Mötz
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.)
Bomag GmbH and Co OHG
Original Assignee
Bomag GmbH and Co OHG
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 Bomag GmbH and Co OHG filed Critical Bomag GmbH and Co OHG
Publication of EP2599919A1 publication Critical patent/EP2599919A1/fr
Application granted granted Critical
Publication of EP2599919B1 publication Critical patent/EP2599919B1/fr
Not-in-force legal-status Critical Current
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
    • E01C19/48—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 laying-down the materials and consolidating them, or finishing the surface, e.g. slip forms therefor, forming kerbs or gutters in a continuous operation in situ
    • E01C19/4833—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 laying-down the materials and consolidating them, or finishing the surface, e.g. slip forms therefor, forming kerbs or gutters in a continuous operation in situ with tamping or vibrating means for consolidating or finishing, e.g. immersed vibrators, with or without non-vibratory or non-percussive pressing or smoothing means
    • E01C19/4853—Apparatus designed for railless operation, e.g. crawler-mounted, provided with portable trackway arrangements
    • E01C19/486—Apparatus designed for railless operation, e.g. crawler-mounted, provided with portable trackway arrangements with non-vibratory or non-percussive pressing or smoothing means; with supplemental elements penetrating the paving to work the material thereof

Definitions

  • the invention relates to a device according to the preamble of claim 1.
  • Road pavers are known to be used for the production of traffic areas on a planum.
  • the paving material for example, asphalt
  • a tamping strip also called tamper
  • the tamping bar is connected via push rods with a rotating drive in such a way that with each revolution of the drive an oscillating vertical movement is generated, which is referred to as the amplitude or stroke of the tamping bar.
  • the drive consists in known ramming strips, for example, a crankshaft.
  • the compaction by a tamping bar of a paver usually does not replace a subsequent compaction by a roller, which is why in the compression by a tamping strip is also spoken of a pre-compaction.
  • a high pre-compaction by a tamping bar is advantageous because a better flatness of the built-in surface is achieved. It is also particularly efficient as it is done at the highest possible temperature of the paving material and minimizes the risk of material shedding during subsequent roll compaction. In addition, the compaction performance of the rolls can be reduced.
  • the known tamping strips have a flat base with a width of about 2 to 3 cm and an inlet slope at its front of about 60 °.
  • This geometry has been chosen so that all installation materials and standard layer thicknesses used can be installed, without that damage to the installation material or to the built-in appliance occurs. It is a compromise that does not affect all thicknesses and materials equally well.
  • the material is compressed only slightly in the vertical direction (compressed), but mainly pushed forward. It is based on the material that is already under the screed, which supports the further flow of material under the screed something.
  • a generic drive for a tamping bar is off DE 1459670 B known.
  • the eccentric shaft is arranged on a pivot lever whose pivot angle is adjustable.
  • an eccentric bushing is twisted, wherein it can assume two positions, which are defined by angularly offset stops and allow two different ram stripe amplitudes.
  • a reversal of direction of the eccentric shaft is required.
  • the stoppers or the follower engaged therewith can be circumferentially offset at predetermined intervals to set different strokes. The stroke can be adjusted in this way only gradually.
  • the EP 2325392 A2 describes a screed with a tamper, in which the stroke is adjusted automatically depending on a built-in parameters, such as the installation speed or the lining thickness.
  • the eccentric bushing is adjusted for this purpose by means of an adjusting mechanism, which may comprise, for example, a cam mechanism.
  • One embodiment includes a toggle mechanism that transmits the oscillation of the eccentric to the tamper such that only the top dead center of the tamper shifts during stroke adjustment.
  • the height of the eccentric shaft In contrast, relative to the screed plate of the screed is adjustable only via a plurality of adjusting screws.
  • the invention is therefore based on the object to provide a device of the type mentioned, with which a simple stroke adjustment with compensating position adjustment of the camshaft can be made without interrupting the operation.
  • the object is achieved in that the device comprises a Hubverstellvortechnisch and a position adjustment for the camshaft in the vibration plane and a forced coupling for the Exzenterverstellvortechnisch and the Wellenpositionsstellstellvortechnisch with which compensates for a change in the eccentricity by an equal displacement of the camshaft in such a way is that only the top dead center is adjusted and the bottom dead center is kept unchanged, that the cam is arranged radially displaceable on the camshaft, that the camshaft is arranged on a cam carrier which is pivotally or slidably mounted on a base frame of a screed of the paver, and that the coupling consists of two series-connected cam gears, with which a linear relative movement between the cam carrier and the base frame on the one hand to a relative movement between the cam and the camshaft is transmitted on the other hand.
  • Preferred developments are described in the dependent claims.
  • the invention has the advantage that the bottom surface of the ram strip remains at bottom dead center with a change in the stroke regardless of the set stroke in a plane with the base surface of the screed. This makes it possible that the width of the base of the tamping bar can be increased so far in comparison to conventional tamping that even high layer thicknesses can be compacted well vertically. If thinner layers are to be compacted, a suitable stroke can readily be set. A readjustment after a stroke change is therefore not required. A stroke change can therefore be carried out quickly. Another advantage is that the stroke can be kept basically small, which reduces the wear and working noise.
  • the cam and the camshaft can be adjusted with separate drives, which are controlled in dependence on each other.
  • a preferred development of the invention is that the offset of the cam rotation axis by changing the camshaft position is carried out.
  • the forced displacement of the camshaft takes place in that a coupling with the cam takes place through a mechanical or hydrostatic transmission. In this way, the required for the coupling conversion of a translational movement in a rotational movement can be carried out appropriate.
  • Another preferred embodiment of the invention is that for adjusting the shaft position, two cams, each with a Exzenterverstellvorraum spaced from each other are arranged on the camshaft, and that the Wellenpositionsverstellvortechnische is operatively connected to both cams.
  • connection of the two cam gears is particularly simple in that they are connected via a coaxially mounted in the camshaft adjusting.
  • the adjusting shaft is designed as a spindle or as axially displaceable, non-rotatably mounted in the camshaft shaft, and in each case a cam mechanism is connected to the cam or the camshaft carrier.
  • Fig. 1 and 2 is a tamping strip 10 of a paver (not shown) via two push rods 11 with a device 12 for stroke adjustment of the ram 10 is connected.
  • the device 12 has a cam drive with a camshaft 13, which is fastened via bearing blocks 14 to a camshaft carrier 15.
  • the camshaft carrier 15 is height-displaceably arranged on a base frame 16 of a known screed (not shown) of the paver.
  • the camshaft 13 is provided with two eccentric cams 19 (FIG. Fig. 2 ), each cooperating with a joint head 20 on the push rods 11.
  • the rod ends 20 are provided with concentric bearing eyes.
  • the screed has a sliding plate 17 whose base 18 is substantially flat and rests on the material to be installed.
  • the tamping bar 10 is in the direction of travel of the finisher in front of the slide plate 17.
  • the tamping bar 10 driven by the camshaft 13 performs oscillating vertical oscillations according to arrow h between a top dead center TO and a bottom dead center TU.
  • the cam drive generates a constant stroke of the tamping bar 10, which by the eccentricity of the cam 19 (FIG. Fig. 2 ).
  • the two cams of the camshaft 13 are covered by the rod ends 20, which in each case have a cam and in each case an eccentric adjusting device 21 a, 21 b (FIG. Fig. 2 .
  • Fig. 3 take up. At maximum deflection of the cam, the tamping bar 10 is deflected so far down into the bottom dead center TU, that the bottom of the tamping bar 10 is flat to the base 18 of the slide plate 17. This condition is in the Fig. 1 illustrated.
  • a stepwise stroke change of the ram 10 is achieved by a change in the eccentricity of the cam 19 (see Fig. 2 ) generated.
  • the tamping bar 10 of the bottom dead center TU remains unchanged and it is only the top dead center TO according to arrow .DELTA.h adjusted according to up or down.
  • the displacement of the camshaft rotational axis is effected by a change in the height position of the camshaft 13 by means of a Wellenpositionsverstellvorraum 9 characterized in that the cam carrier 15 according to arrow .DELTA.s on the base frame 16 by the same Amount and in the same direction as the stroke change is moved.
  • the base 18 thus serves as a reference plane for the adjustment of the top dead center TO and the height position of the camshaft, which in turn is dependent on the set stroke of the ram 10th
  • the shaft position adjusting device 9 consists in that the camshaft carrier 15 is designed as a slide which is arranged displaceably on the base frame 16. It further comprises a double-acting hydraulic actuating cylinder 22, which is operatively disposed between the camshaft carrier 15 and the base frame 16.
  • the actuator cylinder 22 may be operated manually by an operator or via a controller.
  • Fig. 2 and Fig. 3 further show, between the Wellenpositionsverstellvortechnisch 9 and each of the two similar Exzenterverstellvortechnischen 21 a, 21 b designed as a mechanical transmission forcible coupling available. It comprises a coupling rod 24, an adjusting shaft 27, and three cam gears 25, 26a, 26b.
  • the coupling rod 24 is located between the base frame 16 and the first cam gear 25.
  • the adjusting shaft 27 connects functionally the first cam gear 25 with the two similar but opposite second cam gears 26a, 26b in such a way that both cam gears 26a, 26b are operated in the same way.
  • the first cam gear 25 and one of the two second cam gears 26a and 26b are connected in series.
  • the adjusting shaft 27 is mounted coaxially in the form of a hollow shaft camshaft 13 and has a flat surface 28, via which a non-rotatable and axially and radially displaceable connection to the cam 19 and the camshaft 13 is produced.
  • the first cam mechanism consists of a first helical groove 31, which is formed in a bush 23, and in which a first pin (not shown) engages on the coupling rod 24 serving as a slide.
  • the bushing 23 is rotatably mounted on the camshaft carrier 15 and serves as a bearing for the camshaft 13.
  • the bushing 23 is slidably mounted on the camshaft 13 and is non-slidingly connected to radial driving pin 32 on the adjusting shaft 27.
  • the driving pins 32 are rotatably guided in an annular groove 34 on the inside of the sleeve 23, so that the adjusting shaft 27 can rotate with the camshaft 13. According to Fig.
  • the camshaft 13 is provided with axially extending oblong holes 35 through which the driving pins 32 are guided by the adjusting shaft 27 to the sleeve 23.
  • the second cam gears 26a, 26b each consist of a second helical groove 29 in the cam 19 and each of a radial second pin 30 on the turn serving as a slide adjusting shaft 27th
  • the first cam gear 25 operates in such a way that the coupling rod 24 axially displaces the sleeve 23 on the camshaft 13 during a height adjustment of the camshaft carrier 15, by the vertical force component exerted by the pin on the coupling rod 24 on the first helical groove 31 by the inclination of the first Spiral groove 31 is converted into a horizontal force component.
  • the adjusting shaft 27 is moved together with the sleeve 23.
  • the adjusting shaft 27 may also be provided with a spindle thread, and the sleeve 23 may be formed as a spindle nut.
  • a displacement of the adjusting shaft 27 leads to an actuation of the second cam gears 26a, 26b in such a way that the second pin 30 act on the second helical grooves 29 and lead to a radial displacement of the two cams 19 on the camshaft 13, which is an adjustment of the eccentricity the cam 19 corresponds.
  • the transmission ratios of the three cam gears 25, 26a, 26b are selected so that the displacement according to arrow .DELTA.s of the camshaft carrier 15 in the direction of vibration of the tamping bar 10 is just as large as the change in the eccentricity of the cam 19, which corresponds to the change of the stroke according to the arrow .DELTA.h of the tamping strip 10.
  • the two second cam gears 26a, 26b are further designed for this purpose so that the eccentricity of the cam 19 is reduced when the cam carrier 15 is displaced downward, and is increased when the cam carrier 15 is displaced upward.
  • the bottom dead center TU of the tamping bar 10 will always be independent of the set stroke of the tamping bar on the reference plane, which is formed by the base 18 of the slide plate 17 and the screed, and the change of the stroke is compensated with respect to the bottom dead center TU , Only the top dead center TO changed the Hub selectedung according to its location.
  • the eccentric adjusting device 21 can also be actuated directly, for example by the adjusting shaft 27 being displaced directly by an operator or by means of a control (not shown). Then, the eccentric cam 21 kinematicly reverses the shaft position adjuster 9 with the above-described positive coupling acting in the opposite direction.
  • the offset of the cam carrier 15 and thus the offset of the cam rotation axis in the ratio of 1: 1 to the stroke change the tamping bar 10. If instead, height position of the camshaft carrier 15, for example, adjusted along a pivoting cam, because the camshaft carrier is arranged for example on a pivot arm or the camshaft according to Fig. 4 is mounted eccentrically, and / or the transmission ratios of the thrust gear are not linear, a corresponding adjustment must be made so that compensation takes place in the sense described above.
  • a double eccentric for compensating for the change in amplitude is provided according to the arrow ⁇ h of the cam 13.
  • a double eccentric for compensating for the change in amplitude is provided according to the arrow ⁇ h of the cam 13.
  • the bearing eye 36 ' is eccentrically in a disc 37 which is arranged rotatably in a bearing ring 38.
  • the push rod 11 is attached to the bearing ring 38.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)

Claims (6)

  1. Dispositif de réglage de la course d'une poutre de damage (10) d'un finisseur dans lequel la poutre de damage (10) est mise en vibrations oscillatoires verticales ayant un point mort supérieur et un point mort inférieur (TO, TU) dans un plan de vibration au moyen d'un arbre à came(s) (13) ayant une came excentrique (19), comprenant un dispositif (21) de réglage excentrique et un dispositif (9) de réglage de position pour l'arbre à came(s) (13) dans le plan de vibration,
    caractérisé en ce que
    un couplage forcé pour le dispositif de réglage excentrique (21) et le dispositif (9) de réglage de position de l'arbre est prévu, par lequel un changement dans l'excentricité est compensé par un décalage tout aussi important de l'arbre à came(s) (13) d'une manière telle que seul le point mort supérieur (TO) soit réglé et que le point mort bas (TU) demeure inchangé, en ce que la came (19) est montée déplaçable radialement sur l'arbre à came(s) (13), en ce que l'arbre à came(s) (13) est monté sur un support (15) d'arbre à came(s) qui est monté pivotant ou déplaçable sur une structure (16) de châssis d'un profileur de revêtement du finisseur et en ce que le couplage est constitué de deux mécanismes d'entraînement à came(s) raccordés en série (25, 26), avec lesquels un déplacement linéaire relatif entre le support (15) d'arbre à came(s) et la structure (16) de châssis d'une part, est transféré en un déplacement relatif entre la came (19) et l'arbre à came(s) (13) d'autre part.
  2. Dispositif selon la revendication 1,
    caractérisé en ce que
    le couplage est conformé en transmission mécanique ou hydraulique.
  3. Dispositif selon la revendication 1 ou 2,
    caractérisé en ce que
    les deux mécanismes d'entraînement (25, 26a, 26b) à came(s) sont reliés via un arbre de réglage (27) monté de manière coaxiale dans l'arbre à came(s) (13).
  4. Dispositif selon la revendication 3,
    caractérisé en ce que
    l'arbre de réglage (27) est conformé en broche ou en arbre déplaçable axialement monté sans torsion dans l'arbre à came(s) (13), et en ce que respectivement un mécanisme d'entraînement (25, 26a, 26b) à came(s) est relié à la came (19) ou au support (15) d'arbre à came(s).
  5. Dispositif selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que
    deux cames (19) possédant chacune un dispositif de réglage excentrique (21 a, 21 b) sont disposées à une certaine distance l'une de l'autre sur l'arbre à came(s) (13) et en ce que le dispositif (9) de réglage de position de l'arbre est relié opérationnellement aux deux cames (19).
  6. Dispositif selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce que
    le support (15) d'arbre à came(s) est placé sur un chariot déplaçable linéairement.
EP20120007935 2011-12-01 2012-11-26 Dispositif de réglage du levage d'une barre de compactage d'un finisseur de route Not-in-force EP2599919B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011119938A DE102011119938A1 (de) 2011-12-01 2011-12-01 Verfahren und Vorrichtung zur Hubverstellung einer Stampfleiste eines Straßenfertigers

Publications (2)

Publication Number Publication Date
EP2599919A1 EP2599919A1 (fr) 2013-06-05
EP2599919B1 true EP2599919B1 (fr) 2014-12-31

Family

ID=47227428

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20120007935 Not-in-force EP2599919B1 (fr) 2011-12-01 2012-11-26 Dispositif de réglage du levage d'une barre de compactage d'un finisseur de route

Country Status (4)

Country Link
EP (1) EP2599919B1 (fr)
JP (1) JP2013117161A (fr)
CN (1) CN103132441B (fr)
DE (1) DE102011119938A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10060086B2 (en) 2015-12-23 2018-08-28 Bomag Gmbh Tamping beam device of a paving screed, paving screed, road paver, and method for changing the stroke of a tamping beam device

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103590309B (zh) * 2013-11-08 2015-11-25 中联重科股份有限公司 用于摊铺机的夯锤机构和熨平装置以及摊铺机
RU2554639C1 (ru) * 2014-04-10 2015-06-27 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Сибирская государственная автомобильно-дорожная академия (СибАДИ)" Устройство для уплотнения асфальтобетонных смесей
EP3170938B1 (fr) 2015-11-18 2019-03-13 BOMAG GmbH Finisseuse de route, tige de piston pour une finisseuse de route et procédé de fabrication d'un ensemble tige de piston et barre à damer
EP3170937B1 (fr) 2015-11-18 2018-09-19 BOMAG GmbH Finisseur de route, barre à damer pour un finisseur de route, et procédé de fabrication d'une telle barre
EP3249101B1 (fr) * 2016-05-23 2019-05-15 Caterpillar Paving Products Inc. Dispositif de damage lissoir d'une finisseuse
DE102016010071A1 (de) 2016-08-19 2018-02-22 Bomag Gmbh Einbaubohle für einen Straßenfertiger und Straßenfertiger mit einer Einbaubohle
CN109112933B (zh) * 2018-10-31 2024-01-23 徐工集团工程机械股份有限公司 一种熨平板振捣机构及摊铺机
EP4029991B1 (fr) 2021-01-14 2023-05-10 Joseph Vögele AG Réglage de la course du dameur
EP4029992B1 (fr) 2021-01-14 2023-03-29 Joseph Vögele AG Finisseur de route et procédé de réglage de la course de dameur
CN113897842A (zh) * 2021-10-21 2022-01-07 徐工集团工程机械股份有限公司道路机械分公司 一种振捣机构、熨平板与摊铺机

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Publication number Priority date Publication date Assignee Title
DE1459670A1 (de) 1964-11-26 1968-11-21 Abg Werke Gmbh Einbaumaschine fuer den Strassenbau
US6669435B2 (en) 2001-03-28 2003-12-30 Vishay Intertechnology, Inc. Precision resistor tube feeder
DE102006046250A1 (de) * 2006-09-28 2008-04-03 Dynapac Gmbh Einbaubohle für einen Straßenfertiger
EP3138961B1 (fr) * 2009-11-20 2018-08-22 Joseph Vögele AG Poutre lisseuse
PL2325391T3 (pl) * 2009-11-20 2013-08-30 Joseph Voegele Ag Ubijak z wybieralnym skokiem
PL2366832T3 (pl) 2010-03-18 2016-03-31 Joseph Voegele Ag Sposób i wykańczarka do wbudowywania zagęszczonej warstwy wierzchniej

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10060086B2 (en) 2015-12-23 2018-08-28 Bomag Gmbh Tamping beam device of a paving screed, paving screed, road paver, and method for changing the stroke of a tamping beam device

Also Published As

Publication number Publication date
JP2013117161A (ja) 2013-06-13
EP2599919A1 (fr) 2013-06-05
CN103132441A (zh) 2013-06-05
CN103132441B (zh) 2016-06-15
DE102011119938A1 (de) 2013-06-06

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