EP4029991A1 - Tamper stroke adjustment - Google Patents

Tamper stroke adjustment Download PDF

Info

Publication number
EP4029991A1
EP4029991A1 EP21151610.9A EP21151610A EP4029991A1 EP 4029991 A1 EP4029991 A1 EP 4029991A1 EP 21151610 A EP21151610 A EP 21151610A EP 4029991 A1 EP4029991 A1 EP 4029991A1
Authority
EP
European Patent Office
Prior art keywords
eccentric shaft
eccentric
adjustment
adjusting
road finisher
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.)
Granted
Application number
EP21151610.9A
Other languages
German (de)
French (fr)
Other versions
EP4029991B1 (en
Inventor
Klaus Bertz
Ralf Weiser
Tobias Noll
Christian Pawlik
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.)
Joseph Voegele AG
Original Assignee
Joseph Voegele 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=74184474&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP4029991(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Joseph Voegele AG filed Critical Joseph Voegele AG
Priority to PL21151610.9T priority Critical patent/PL4029991T3/en
Priority to EP21151610.9A priority patent/EP4029991B1/en
Priority to JP2022000936A priority patent/JP7361808B2/en
Priority to BR102022000675-0A priority patent/BR102022000675A2/en
Priority to CN202220107328.3U priority patent/CN217266804U/en
Priority to US17/575,687 priority patent/US20220220675A1/en
Priority to CN202210056305.9A priority patent/CN114763691A/en
Publication of EP4029991A1 publication Critical patent/EP4029991A1/en
Publication of EP4029991B1 publication Critical patent/EP4029991B1/en
Application granted granted Critical
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • 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
    • E01C19/4866—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 solely non-vibratory or non-percussive pressing or smoothing means for consolidating or finishing
    • E01C19/4873—Apparatus designed for railless operation
    • 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
    • E01C2301/00—Machine characteristics, parts or accessories not otherwise provided for
    • E01C2301/20—Screed or paver accessories for paving joint or edge treatment

Definitions

  • the present invention relates to a road finisher according to claim 1 and a method for stepless tamper stroke adjustment on a road finisher according to claim 15.
  • EP 3 138 961 B1 discloses a road finisher whose screed has a tamper stroke adjustment device.
  • the tamper stroke adjustment device has an adjustment gear that is provided between an eccentric shaft that can be driven in rotation and an eccentric bushing that is rotatably mounted on the eccentric shaft. The stroke of the tamper bar is adjusted by twisting the eccentric bushing on the eccentric shaft.
  • EP 3 138 961 B1 also discloses an adjusting gear that is provided between the rotationally drivable eccentric shaft and an eccentric bushing mounted in a rotationally fixed manner on the eccentric shaft, the eccentric bushing being displaced transversely to the eccentric shaft via the adjusting gear to adjust the tamper stroke of the tamper strip.
  • EP 3 138 961 B1 a variator having a toggle mechanism.
  • adjusting the eccentric stroke during operation of the road finisher represents a technical challenge. This is particularly due to the fact that it is difficult to control or actuate the adjusting gear mounted directly on the eccentric shaft, between the eccentric bushing and the eccentric shaft.
  • the toggle lever mechanism is structurally rather complex and takes up a lot of space on the screed.
  • US 8,371,770 B1 discloses a screed with a tamper stroke adjustment device, which has a threaded rod and a threaded bushing mounted displaceably thereon. An axial adjustment of the threaded bushing along the threaded rod moves a lever arm mounted on the threaded bushing, the position and alignment of which is dependent on the tamper stroke setting on the screed of the road finisher.
  • EP 1 905 899 A2 discloses a screed for a road finisher, on which a tamper stroke adjustment device is mounted.
  • the tamper stroke adjustment device comprises a bearing block for an eccentric shaft, which is mounted so that it can be displaced horizontally along a guide carriage and on which an eccentric bushing is mounted in a rotationally fixed manner.
  • EP 2 599 918 A1 discloses a method and a device for adjusting an upper reversal point of a tamper bar of a road finisher.
  • EP 2 599 919 A1 discloses another device for adjusting the stroke of a tamper bar of a road finisher.
  • the object of the invention is to provide a road finisher with a tamper stroke adjustment device and a method for stepless tamper stroke adjustment on a road finisher, whereby the tamper stroke can be adjusted precisely and steplessly, especially during paving operation, using simple constructive technical means, in particular using fewer assemblies of the road finisher.
  • the invention relates to a road finisher with a screed for producing a paving layer, wherein the screed has at least one compacting unit for pre-compacting a paving material fed to the screed, and wherein the compacting unit has at least one eccentric bushing, which is rotatably mounted to a desired angle of rotation on an eccentric shaft carrying it , in order thereby to steplessly set a desired tamper stroke of a tamper strip of the compression unit.
  • an adjustment mechanism that is mounted at a distance from the eccentric shaft and rotates at least partially with a rotational movement of the eccentric shaft can be controlled. Since in the case of the invention, despite its spaced position from the eccentric shaft, a self-rotating adjusting mechanism controls the eccentric bushing rotating along with the eccentric shaft for adjusting the tamper stroke, there are several advantages in total, as described below.
  • the eccentric bushing on the eccentric shaft i.e. the respective eccentricities of these two components
  • the phase adjustment is advantageously controllable, in particular with little effort, by means of the adjusting mechanism which is spaced apart from the eccentric shaft and primarily rotates with the speed of the eccentric shaft itself.
  • the co-rotating adjustment mechanism can be controlled at least briefly in such a way that the torque driving it on its input side or the speed present there on its output side, on which it provides a coupling to the eccentric bushing, is exceeded or exceeded is stocky.
  • the eccentric bushing coupled to the adjusting mechanism and rotating on the eccentric shaft can be "braked” or “accelerated” relative to the rotational movement of the eccentric shaft according to the transmission ratio controlled by the adjusting mechanism, whereby the eccentric bushing rotates relative to the eccentric shaft into a new angular position, i.e. the the phase adjustment controlled by the adjustment mechanism.
  • the eccentric bush rotates at the same speed as the eccentric shaft, i.e. together with it with a constant phase angle.
  • co-rotating means that the adjustment mechanism or at least a portion of the components provided thereon rotates together with the eccentric shaft, although mounted at a distance from it, during operation of the compression unit.
  • This assembly rotating with the eccentric shaft can be sensitively controlled with little effort for the phase adjustment described above, i.e. a change in the angular position of the eccentric bushing positioned on the eccentric shaft, i.e. to vary the tamper stroke.
  • the adjustment mechanism positioned at a distance from the eccentric shaft can be controlled more precisely.
  • the tamper stroke adjustment can be carried out better automatically using such a co-rotating adjustment mechanism.
  • the adjustment mechanism can be in the form of a hydraulic and/or electromechanical phase adjustment system, for example.
  • the desired tamper stroke adjustment preferably comes about as the sum of the individual eccentricities of the eccentric shaft and the eccentric bushing mounted so as to be rotatable thereon.
  • a phase angle set in between can be changed in a fast-reacting and very precise manner by means of the co-rotating adjustment mechanism, in particular if this is designed as an electromechanical phase adjuster.
  • the adjustment mechanism can be excellently controlled for a phase adjustment between its drive and its driven side.
  • the adjustment mechanism used in the invention advantageously builds on existing components or assemblies of the screed in a compact manner, so that a large number of identical parts is possible even on different screed types. Due to its location at a distance from the eccentric shaft, the eccentric shaft itself can be of simpler construction.
  • the adjusting mechanism can preferably be driven in rotation at least partially by the eccentric shaft, there is an overall advantageous balance of forces for adjusting the tamper stroke for the phase adjustment that can be adjusted on it. This in turn means that the adjustment mechanism can be automated more easily, which means that a better paving result is possible using the road finisher.
  • the adjustment mechanism comprises at least one adjustment drive driven in rotation by the rotational movement of the eccentric shaft as such and controllable for turning the eccentric bushing and/or at least one adjustment gear drive driven in rotation by the rotational movement of the eccentric shaft and controllable for turning the eccentric bushing.
  • the rotational movement of the eccentric shaft is generally the cause of the rotation of the adjusting drive and/or the adjusting gear.
  • the adjusting drive and/or the adjusting gear is integrated into a drive train branched off from the eccentric shaft, in the power flow of which the adjusting drive and/or the adjusting gear is integrated in a rotating manner.
  • a sensitive variation of the angle of rotation between the eccentric bushing and the eccentric shaft is achieved here by actuating the adjusting drive and/or the adjusting gear with little effort.
  • the phase shift angle of the adjusting drive and/or adjusting gear rotating along in the power flow can be set more easily as a result.
  • the adjusting mechanism is thus better able to turn the eccentric bushing relative to the eccentric shaft to any desired tamper stroke setting during ongoing paving operation, i.e. to set the tamper stroke between a minimum and a maximum tamper stroke value.
  • the adjusting drive and the adjusting gear jointly form a co-rotating functional unit.
  • the functional unit is then in the form of a modular phase adjuster, which is mounted to rotate with the eccentric shaft at the same speed as the eccentric shaft, with the adjusting drive being able to control the adjusting gear for a desired phase adjustment, so that the eccentric bushing rotates in response to the eccentric shaft to vary the tamper stroke.
  • the rotating eccentric shaft can function as an actuator for the co-rotating adjusting drive coupled to it and/or the co-rotating adjusting gear, with the co-rotating adjusting drive and/or the co-rotating Adjusting gear as such is also controlled in addition to their rotation.
  • the torque picked off by the eccentric shaft can be changed at least briefly in the drive train branched off from the eccentric shaft by means of the adjusting drive and/or the adjusting gear driven in rotation therein in order to set the desired phase shift angle, so that the resulting forces decelerate or accelerate the eccentric bushing on the eccentric shaft, i.e. twist it.
  • the eccentric shaft preferably serves both to drive the tamper strip and can also function as a drive shaft for the co-rotating adjusting drive and/or the co-rotating adjusting gear, so to speak fulfills a double function, an adjusting force, possibly acting from the outside, can arise the adjusting drive and/or the adjusting gear for turning the eccentric bushing can be significantly reduced.
  • the components used for adjusting the tamper stroke can also be structurally reduced, with the result that manufacturing costs can be reduced.
  • the torque which is preferably continuously tapped off from the eccentric shaft during paving operation, can be manipulated in the branched-off power flow using the co-rotating adjustment drive and/or the co-rotating adjusting gear arranged therein in such a way that an adjustment movement of the eccentric bushing on the eccentric shaft rotating by means of the drive speed is possible without any problems and without a large additional force input is.
  • the eccentric bushing is rotated relative to the rotational movement of the eccentric shaft in or counter to a direction of rotation of the eccentric shaft until the eccentric bushing assumes a desired angular position on the eccentric shaft that is shifted from its starting position.
  • the co-rotating adjusting drive and/or the co-rotating adjusting gear can preferably be controlled to adjust a rotation angle of a machine element rotatably mounted on the eccentric shaft.
  • the machine element enables the adjustment drive and/or the adjustment gear to be coupled in a structurally simple manner to the eccentric shaft mounted eccentric bush.
  • the machine element can for example be in the form of a toothed wheel or a pulley for a synchronous belt.
  • One embodiment provides that the machine element itself forms the eccentric bushing or is connected to the eccentric bushing by means of a positive coupling, for example by means of a claw coupling.
  • the former alternative results in an assembly with a reduced part count.
  • the second alternative can be advantageous for service and/or repair measures.
  • At least one additional machine element is provided, which is designed to transmit a rotary motion of the eccentric shaft to the adjusting drive and/or the adjusting gear.
  • the further machine element is preferably mounted in a rotationally fixed manner on the eccentric shaft. This is preferably a toothed wheel or a pulley for a synchronous belt.
  • a complementary coupling element for example in the form of a gear wheel or a belt pulley for the synchronous belt, can be mounted non-rotatably on the adjustment drive and/or on the adjustment gear, for example on a gear housing of the adjustment gear or on a housing of the adjustment drive.
  • the motion or forces can be transmitted from the eccentric shaft to the adjustment mechanism by means of the additional machine element.
  • the first machine element has assumed the desired angular position, ie the target tamper stroke has been set, the aforementioned separate activation of the rotary-driven adjustment mechanism is terminated.
  • An actual angle of rotation between the eccentric bushing and the eccentric shaft that is thus set on the compression unit can then be easily detected by means of suitable sensors.
  • the adjustment mechanism which rotates continuously during the operation of the compression unit, can be controlled again for a subsequently desired phase adjustment, so that a new switching moment occurs on its output side coupled to the eccentric bushing compared to its drive side.
  • the machine elements described above for coupling the eccentric shaft to the adjusting mechanism and for coupling the same to the eccentric bushing can be in the form of gearwheels, belt pulleys and/or sprockets and thus form standardized, primarily cost-effective machine components.
  • the adjusting drive and/or the adjusting gear makes sense for the adjusting drive and/or the adjusting gear to be driven in rotation at the same speed as the eccentric shaft during operation of the compression unit.
  • gear wheels/chain wheels or belt pulleys of the same dimensions are used for this purpose in the drive train between the eccentric shaft and the adjustment mechanism that is driven in rotation with it.
  • the adjusting drive and/or the adjusting gear can have a different speed than the eccentric shaft.
  • a desired tamper stroke can be achieved in that there is the same translation between the eccentric shaft and the adjusting gear and between the adjusting gear and the eccentric bushing.
  • the eccentric shaft and the adjusting shaft on which the adjusting gear is mounted can have different speeds; the eccentric shaft and the eccentric bushing do not.
  • the adjusting drive and/or the adjusting gear can be actuated hydraulically, electrically and/or mechanically. Above all, large adjusting forces could be generated by means of a hydraulic adjusting drive and/or adjusting gear.
  • An electrical or electromechanical adjustment mechanism would allow the tamper stroke to be adjusted with shorter reaction times, i.e. independently of a hydraulic temperature.
  • the adjusting gear is preferably a continuously adjustable mechanical, hydrostatic or electric gear.
  • the adjusting gear can preferably be controlled to set a desired transmission ratio by means of a mechanical, hydraulic or electric drive that is already present on the screed, i.e. by means of a drive that is also used to operate another working component of the screed. This further contributes to a reduction in the number of components or assemblies used.
  • the adjusting drive has a controllable servo motor and/or a servo motor is provided for the adjusting gear.
  • the servomotor together with the adjusting gear can form a functional unit rotating with the eccentric shaft, the servomotor being controllable for a desired phase adjustment in such a way that it changes the power flow transmitted to the eccentric bushing via the adjusting mechanism rotating with it through the adjusting gear connected to it.
  • the eccentric bushing rotates on the eccentric shaft to the desired angular position.
  • the adjusting mechanism is preferably designed as a cam mechanism and/or has a pair of rotating deflection rollers.
  • the adjustment gear can be designed to be particularly robust.
  • the cam mechanism it is conceivable for the cam mechanism to have two cam disks which are mounted so as to be adjustable in relation to one another and can be displaced linearly and/or rotationally in relation to one another. A movement of the cam discs relative to each other can cause the deflection rollers mounted thereon to be adjusted along curved paths formed thereon, which results in a phase adjustment.
  • the adjustment mechanism provides at least one stationary cam and at least one movably mounted cam for shifting the deflection rollers mounted thereon and rotating in the power flow. This is mounted on the stationary cam disk for translational and/or rotational displacement, in order thereby to set a displacement of the axes of rotation of the deflection rollers that rotate along for a phase adjustment.
  • the pair of rotating deflection rollers for rotating the eccentric bushing is mounted on the eccentric shaft so as to be displaceable transversely to the eccentric shaft, i.e. transversely to its axis of rotation.
  • the co-rotating deflection rollers can be mounted adjacent to a toothed belt or a drive chain, which is connected to the machine element mounted rotatably on the eccentric shaft.
  • the two co-rotating deflection rollers can be rotatably mounted with respect to mutually spaced, parallel mounted axes of rotation.
  • a change in the positioning of the co-rotating deflection rollers in particular a change in the distance between the axes of rotation, can be used to influence the phase adjustment angle, based on which the eccentric bushing lies on the eccentric shaft.
  • a translational displacement of the deflection rollers that rotate along transversely to the axis of rotation of the eccentric shaft on one side of the synchronous belt guided around the deflection rollers or of the drive chain leads to a lengthening of the track, which is simultaneously compensated for by a shortening of the track on the opposite side of the synchronous belt or the drive chain.
  • the eccentric bushing can be rotated on the eccentric shaft with little effort, so that the eccentric bushing assumes a desired angle of rotation on the eccentric shaft for setting the tamper stroke.
  • the adjusting drive and/or the adjusting gear is designed for the synchronous adjustment of several eccentric bushings that are rotatably mounted along the eccentric shaft (overall stroke adjustment) or the adjusting mechanism includes several adjusting drives and/or adjusting gears for the separate adjustment of several eccentric bushings that are rotatably mounted along the eccentric shaft ( single stroke adjustment).
  • the eccentric bushings installed along several unit sections can be adjusted together, i.e. synchronously with one another, or independently of one another, i.e. individually.
  • eccentric bushings that can be controlled independently of one another, different tamper strokes can be set during one paving journey over the paving width that can be created using the screed.
  • the adjustment mechanism can be coupled to an adjustment shaft on its output side.
  • the adjustment shaft can transmit a phase adjustment set centrally by means of the adjustment mechanism synchronously to a number of unit sections of the compression unit, i.e. to eccentric bushings mounted thereon.
  • the adjusting shaft or the shaft is preferably mounted parallel to the eccentric shaft.
  • the adjusting drive and/or the adjusting gear can be controlled by means of a control device in order to set the desired angle of rotation of the eccentric bushing.
  • the control device regardless of whether it is used for a total stroke adjustment or an individual stroke adjustment, can be present as an integral part of the adjustment mechanism.
  • the control device can be connected via a CAN bus system to a vehicle controller of the road finisher, from which the setpoint tamper stroke or the respective setpoint tamper strokes can be maintained.
  • control device for the dynamic adjustment of the angle of rotation of the eccentric bushing has at least one control loop that responds to at least one process parameter that can be detected during operation of the road finisher.
  • a measured material-specific value of the paving material to be paved for example a measured temperature of the paving material transported from the goods bunker of the road finisher to the paving screed, and/or the paving layer produced, for example a measured temperature of the paving layer, be reacted accordingly with an adjustment of the angle of rotation between the eccentric bushing and the eccentric shaft in order to produce an optimal installation result.
  • a preferred embodiment of the invention provides that the control circuit is able to control a dynamic angle of rotation adjustment between the eccentric bushing and the eccentric shaft in response to a disturbance variable, for example an ambient temperature, for the continuous adjustment of the tamper stroke.
  • a disturbance variable for example an ambient temperature
  • the adjustment mechanism preferably includes at least one sensor unit, which is designed to detect a set phase angle between the eccentric bushing and the eccentric shaft that carries it and/or to detect a stroke of the tamper strip.
  • the adjustment drive especially when it is in the form of a servo motor, has at least one sensor unit suitable for this purpose, for example one or more angle sensors. This would allow the phase shift between the eccentric bushing and the eccentric shaft to be derived on the basis of the detected angular position of the motor shaft of the servomotor.
  • the control device can calculate the actual tamper stroke based on the detected phase setting. It is conceivable that the control device derives the corresponding actual tamper stroke based on the measured phase setting, for example by means of phase characteristics.
  • a phase setting detected or varying by means of the sensor unit can be transmitted to the control unit in a timely manner, so that based on a target/actual tamper stroke comparison, it may output a corresponding control signal to the adjustment drive, in particular the servo motor, in order to quickly rotate the eccentric bushing for a to control tamper stroke adjustment.
  • the sensor unit could have at least one distance sensor, which is designed to directly measure a set actual tamper stroke of the tamper strip.
  • the adjustment mechanism is designed to be manually adjustable. Above all, this can be used to calibrate the tamper strip at the beginning of the paving journey be helpful. Automated operation of the adjustment mechanism, on the other hand, can be used excellently during the paving journey.
  • the invention also relates to a method for stepless adjustment of the tamper stroke on a compacting unit of a road finisher, with at least one eccentric bush being rotated on an eccentric shaft supporting it in order to adjust the taper stroke.
  • an adjusting mechanism is controlled which is mounted at a distance from the eccentric shaft and rotates at least partially with a rotational movement of the eccentric shaft.
  • the relative rotation between the eccentric bushing and the eccentric shaft is brought about by the fact that a flow of force derived from the eccentric shaft, which causes the adjustment mechanism or at least parts of it to rotate, is at least briefly reduced or increased by means of the adjustment mechanism in such a way that the angle of rotation between the eccentric bushing and the eccentric shaft changed.
  • the torque is derived from the eccentric shaft and transmitted to the adjustment mechanism as drive torque.
  • an adjustment gear that is connected to it and also rotates along with it can be controlled for torque adjustment by means of an adjustment drive.
  • the eccentric bush rotates uniformly on the eccentric shaft, i.e. at the same speed, without additional control of the adjustment drive.
  • a differential speed can be generated via the adjusting gear coupled to it between the eccentric bushing and the eccentric shaft supporting it, as a result of which the eccentric bushing rotates into a new angular position on the eccentric shaft.
  • This adjusts the tamper stroke.
  • the compression unit can manage overall with a reduced number of mechanical, electrical and/or hydraulic components in order to vary the tamper stroke. This results in a practical adjustment device that can be produced inexpensively and works essentially autonomously for varying the tamper stroke on the road finisher.
  • figure 1 shows a road finisher 1 with a screed 2 for producing a paving layer 3 in the paving direction of travel R.
  • the screed 2 has at least one compacting unit 4 for pre-compacting paving material 5 fed to the screed 2.
  • the compacting unit 4 has a tamper strip 6, which has a variable tamper stroke H and/or a variable frequency F for pre-compacting the paving material 5 fed to the screed 2.
  • FIG 2 shows the compression unit 4 separately in an enlarged perspective view.
  • the compression unit 4 has a bearing block 7 fastened to the screed body and an eccentric shaft 8 rotatably mounted thereon.
  • the eccentric shaft 8 drives a connecting rod 9 to which the tamper bar 6 is fastened.
  • FIG figure 2 also shows an adjusting mechanism 10 which is driven in rotation by means of the eccentric shaft 8 .
  • the adjusting mechanism 10 can be controlled to set a target tamper stroke 11 that can be varied for the tamper strip 6 .
  • the co-rotating adjustment mechanism 10 includes an adjustment drive 12 and/or an adjustment gear 13.
  • the adjusting drive 12 and the adjusting gear 13 are designed as a functional unit. This functional unit is coupled to a rotary motion of the eccentric shaft 8 by means of a timing belt 14 .
  • the adjustment mechanism 10 can, without being additionally controlled, return the torque driving it by means of the synchronous belt 14 on its input side and setting it into rotation to a machine element 16 rotatably mounted on the eccentric shaft 8 by means of a further synchronous belt 15 provided on its output side.
  • a phase angle of the machine element 16 mounted on the eccentric shaft 8 can be changed by an additional activation of the adjustment mechanism 10 .
  • an eccentric bushing 17 (see Fig Figure 2C ) adjust. According to figure 2 is thus for rotating the eccentric bushing 17 on the eccentric shaft 8 of the eccentric shaft 8 mounted spaced, with the rotational movement of the eccentric shaft 8 co-rotating adjustment mechanism 10 can be controlled.
  • Figure 2B has the adjustment mechanism 10 opposite Figure 2A a phase adjustment 26 performed. This is shown on the basis of the two markings A, B that are now shown shifted relative to one another.
  • the machine element 16 has moved in relation to the Figure 2A shown position on the eccentric shaft 8 according to the phase adjustment 26 rotated. This has the effect that the eccentric bushing 17 coupled to the machine element 16 also assumes an angular position on the eccentric shaft 8 that has been changed by the phase adjustment 26 , so that the sum of the eccentricity of the eccentric shaft 8 results in a new target tamper stroke 11 .
  • Figure 2C shows a first variant of the in figure 2 embodiment shown for a total stroke adjustment on the compression unit 4. This means that a plurality of eccentric bushings 17 positioned along the eccentric shaft 8 can be rotated synchronously by means of the adjustment mechanism 10.
  • the eccentric shaft 8 is driven by a motor 20.
  • the one in the figure 2 Belt drives shown for coupling the eccentric shaft 8 to the adjustment mechanism 10 and for coupling the adjustment mechanism 10 to the machine element 16 are in the Figures 2C and 2D replaced by drive wheels 21, 22 and adjusting wheels 23, 24.
  • the drive wheel 21 is mounted on the eccentric shaft 8 in a torque-proof manner.
  • the drive wheel 22 is seated on the housing 19 of the adjustment mechanism 10 in a rotationally fixed manner.
  • the adjustment mechanism 10 is mounted on a shaft 25 in a rotationally fixed manner.
  • the adjustment mechanism 10 is configured to carry out the phase adjustment 26 between the drive wheel 22 mounted on its housing 19 and the adjustment wheel 23 mounted on its wear side.
  • the phase adjustment 26 carried out by means of the adjustment mechanism 10 is transmitted from the adjustment wheel 23 to the adjustment wheel 24 and the machine element 16 .
  • the adjustment wheel 24 and the machine element 16 are formed in one piece.
  • the in Figure 2C twisted by means of a claw coupling 27 connected thereto eccentric bushing 17 on the eccentric shaft 18 . This results in a change in the (desired) tamper stroke 11 of the tamper bar 6 .
  • the adjustment mechanism 10 has a sensor unit 28 which is configured to detect the phase adjustment 26 and thus also the angular position of the eccentric bushing 17 on the eccentric shaft 8 .
  • the sensor unit 28 continuously transmits its measurement results to a control device 29 connected to it.
  • the control device 29 can be provided with the setpoint tamper stroke 11, with the control device 29 being configured to calculate an actual tamper stroke from the measured phase adjustment 26 and to compare this with the provided To compare target tamper stroke 11, based on which the control device 29 sends a control signal 30 to the Adjustment drive 12 of the adjustment mechanism 10 emits.
  • the adjustment drive 12 for example a co-rotating synchronous motor M, can then adjust the phase adjustment 26 based on the control signal 20.
  • the control device 29 can have a control circuit RK, which responds to a process parameter P measured during operation of the road finisher 1, on the basis of which a dynamic angle of rotation adjustment, ie a dynamic phase adjustment 26 for varying the tamper stroke 11, is possible.
  • the functional principle of the control device 29 and/or the control circuit RK can also be used in connection with all of the following embodiments.
  • FIG. 12 further shows that the adjustment mechanism 10 has an adjustment shaft 31 on its output side.
  • the adjustment wheel 23 is mounted on the adjustment shaft 31 in a rotationally fixed manner. This makes it possible to Figure 2C to transmit the phase adjustment 26 set by means of the adjustment mechanism 10 synchronously to another unit section 32 via the adjustment shaft 31 .
  • an eccentric bushing which is not shown on the unit section 32, is rotated synchronously with the eccentric bushing 17 in an analogous manner.
  • Figure 2C thus shows that the adjustment mechanism 10 is designed via the adjustment shaft 31 for the synchronous adjustment of a plurality of eccentric bushings 17 that are rotatably mounted along the eccentric shaft 8 .
  • Figure 2D 12 shows a device which is designed for the separate adjustment of a plurality of eccentric bushings 17 which are rotatably mounted along the eccentric shaft 8 . A single stroke adjustment is thus possible by means of this device.
  • the compression unit 4 includes the adjustment mechanism 10 for varying the target tamper stroke 11 of the tamper strip 6 and also an additional adjustment mechanism 10' for the further unit section 32.
  • the adjustment mechanism 10' is driven via the shaft 25 and has a sensor unit 28', by means of which a phase adjustment 26' set on the unit section 32 can be measured, on the basis of which the eccentric bushing 17' mounted on the unit section 32 is rotated on the eccentric shaft 8.
  • the two adjusting wheels 23, 33 they are rotatably mounted on the shaft 25. This makes it possible to set the desired tamper stroke 11, 11' for the respective tamper strips 6, 6' on the respective unit sections of the compression unit 4 independently of one another.
  • FIG 3 shows a second embodiment of the compression unit 4.
  • the compression unit 4 has an adjustment mechanism 35.
  • the adjustment mechanism 35 can be controlled to rotate the machine element 16, which is rotatably mounted on the eccentric shaft 8, in such a way that the target tamper stroke 11 is set on the tamper bar 6 leaves.
  • the adjustment mechanism 35 off figure 3 has a pair of co-rotating deflection rollers 36a, 36b.
  • the two deflection rollers 36a, 36b are mounted so as to be displaceable back and forth transversely to the eccentric shaft 8, as shown by the double arrows v1, v2.
  • the adjustment mechanism 35 is connected to the rotational movement of the eccentric shaft 8 by means of drive pulleys 37, 38, 39 mounted in a rotationally fixed manner by means of synchronous belts 40, 41 guided thereon.
  • Drive pulleys 38, 39 shown separately could also be designed as one component.
  • a displacement of the two deflection rollers 36a, 36b transversely to the eccentric shaft 8 causes the machine element 16, which is connected to the adjustment mechanism 35 via the synchronous belt 41, to rotate on the eccentric shaft 8.
  • the eccentric bushing 17 attached thereto also changes its angular position on the eccentric shaft 8 as a result, so that the (set) tamper stroke 11 is adjusted.
  • FIG. 3B shows a potential structure for the adjustment mechanism 35.
  • the adjustment mechanism 35 has an adjustably mounted cam 42 with a first cam track 43 for the deflection roller 36a and with a second cam track 44 for the deflection roller 36b. Furthermore, the adjustment mechanism 35 has a stationary cam 45 with a guide track 46 for the deflection rollers 36a, 36b.
  • the two deflection rollers 36a, 36b in the guide track 46 are moved together in the direction F by means of a displacement of the cam disk 42 in direction E.
  • the phase adjustment 26 takes place on the machine element 16, as a result of which the eccentric bushing 17 rotates on the eccentric shaft 8.
  • FIG. 3B shows Figure 3B in the right half of the picture a section AA.
  • the deflection roller 36a is mounted on a bolt 47 .
  • the deflection roller 36a is attached to the bolt 47 by means of a roller bearing 48 .
  • the Figures 3C and 3D show variants of the adjustment mechanism 35, with the in Figure 3C Variant shown for the synchronous adjustment of a plurality of eccentric bushings 17 rotatably mounted along the eccentric shaft 8 (overall stroke adjustment) and wherein the in Figure 3D shown variant are configured for a single stroke adjustment on respective adjacent unit sections of the compression unit 4.
  • the adjustment mechanism 35 is mounted between the drive wheel 37 and an adjustment wheel 50 .
  • a using the adjustment mechanism 35 in Figure 3C set phase adjustment 26 acts via the timing belt 40 on the adjusting wheel 50, wherein the adjusting wheel 50 carrying the adjusting shaft 31 'can transmit the torque synchronously to other unit sections of the compression unit 4 to eccentric bushings stored there corresponding to the eccentric bushing 17 Figure 3C set.
  • the schematic diagram Figure 3D shows that the adjustment mechanism 35 according to figure 3 is arranged, so between the drive wheel 39 and the machine element 16, the phase adjustment 26 can generate.
  • a separate adjustment mechanism 35 can be arranged for each unit section of the compression unit 4, so that the respective tamper strokes 11 of the unit sections can be controlled independently of one another.

Landscapes

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

Abstract

Die Erfindung betrifft einen Straßenfertiger (1) mit einer Einbaubohle (2) zum Herstellen einer Einbauschicht (3), wobei die Einbaubohle (2) mindestens ein Verdichtungsaggregat (4) zum Vorverdichten eines der Einbaubohle (2) zugeführten Einbaumaterials (5) aufweist, wobei das Verdichtungsaggregat (4) mindestens eine Exzenterbuchse (17) aufweist, die auf einer sie tragenden Exzenterwelle (8) in einen gewünschten Drehwinkel verdrehbar gelagert ist, um dadurch stufenlos einen Soll-Tamperhub einer Tamperleiste (6) des Verdichtungsaggregats (4) einzustellen, wobei zum Verdrehen der Exzenterbuchse (17) auf der Exzenterwelle (8) ein zur Exzenterwelle (8) beabstandet gelagerter, zumindest teilweise mit einer Drehbewegung der Exzenterwelle (8) mitrotierender Verstellmechanismus (10, 35) ansteuerbar ist. Ferner betrifft die Erfindung ein Verfahren zur stufenlosen Tamperhubverstellung an einem Verdichtungsaggregat (4) eines Straßenfertigers (1).The invention relates to a road finisher (1) with a screed (2) for producing a paving layer (3), the screed (2) having at least one compacting unit (4) for pre-compacting a paving material (5) fed to the screed (2), wherein the compression unit (4) has at least one eccentric bushing (17), which is mounted on an eccentric shaft (8) that supports it so that it can be rotated to a desired angle of rotation, in order to continuously adjust a target tamper stroke of a tamper strip (6) of the compression unit (4), wherein for rotating the eccentric bushing (17) on the eccentric shaft (8), an adjusting mechanism (10, 35) mounted at a distance from the eccentric shaft (8) and rotating at least partially with a rotational movement of the eccentric shaft (8) can be controlled. The invention also relates to a method for continuously adjusting the tamper stroke on a compacting unit (4) of a road finisher (1).

Description

Die vorliegende Erfindung betrifft einen Straßenfertiger gemäß dem Anspruch 1 sowie ein Verfahren zur stufenlosen Tamperhubverstellung an einem Straßenfertiger gemäß dem Anspruch 15.The present invention relates to a road finisher according to claim 1 and a method for stepless tamper stroke adjustment on a road finisher according to claim 15.

EP 3 138 961 B1 offenbart einen Straßenfertiger, dessen Einbaubohle eine Tamperhubverstelleinrichtung aufweist. Die Tamperhubverstelleinrichtung verfügt über ein Verstellgetriebe, das zwischen einer drehantreibbaren Exzenterwelle und einer auf der Exzenterwelle drehbar gelagerten Exzenterbuchse vorgesehen ist. Der Hub der Tamperleiste wird durch eine Verdrehung der Exzenterbuchse auf der Exzenterwelle eingestellt. EP 3 138 961 B1 offenbart außerdem ein Verstellgetriebe, das zwischen der drehantreibbaren Exzenterwelle und einer auf der Exzenterwelle drehfest gelagerten Exzenterbuchse vorgesehen ist, wobei zum Verstellen des Tamperhubs der Tamperleiste die Exzenterbuchse über das Verstellgetriebe quer zur Exzenterwelle verschoben wird. Schließlich offenbart EP 3 138 961 B1 ein Verstellgetriebe, das einen Kniehebelmechanismus aufweist. EP 3 138 961 B1 discloses a road finisher whose screed has a tamper stroke adjustment device. The tamper stroke adjustment device has an adjustment gear that is provided between an eccentric shaft that can be driven in rotation and an eccentric bushing that is rotatably mounted on the eccentric shaft. The stroke of the tamper bar is adjusted by twisting the eccentric bushing on the eccentric shaft. EP 3 138 961 B1 also discloses an adjusting gear that is provided between the rotationally drivable eccentric shaft and an eccentric bushing mounted in a rotationally fixed manner on the eccentric shaft, the eccentric bushing being displaced transversely to the eccentric shaft via the adjusting gear to adjust the tamper stroke of the tamper strip. Finally revealed EP 3 138 961 B1 a variator having a toggle mechanism.

Bei den vorangehend beiden erstgenannten Lösungen stellt die Exzenterhubverstellung während des Betriebs des Straßenfertigers eine technische Herausforderung dar. Dies liegt insbesondere daran, dass eine Ansteuerung bzw. Betätigung des direkt auf der Exzenterwelle, zwischen der Exzenterbuchse und der Exzenterwelle gelagerten Verstellgetriebes schwierig durchführbar ist. Der Kniehebelmechanismus ist konstruktiv eher aufwändig und nimmt an der Einbaubohle viel Platz ein.In the first two solutions mentioned above, adjusting the eccentric stroke during operation of the road finisher represents a technical challenge. This is particularly due to the fact that it is difficult to control or actuate the adjusting gear mounted directly on the eccentric shaft, between the eccentric bushing and the eccentric shaft. The toggle lever mechanism is structurally rather complex and takes up a lot of space on the screed.

US 8,371,770 B1 offenbart eine Einbaubohle mit einer Tamperhubverstelleinrichtung, die eine Gewindestange sowie eine darauf verschiebbar gelagerte Gewindebuchse aufweist. Eine Axialverstellung der Gewindebuchse entlang der Gewindestange bewegt einen an der Gewindebuchse gelagerten Hebelarm, von dessen Position und Ausrichtung die Tamperhubeinstellung an der Einbaubohle des Straßenfertigers abhängig ist. US 8,371,770 B1 discloses a screed with a tamper stroke adjustment device, which has a threaded rod and a threaded bushing mounted displaceably thereon. An axial adjustment of the threaded bushing along the threaded rod moves a lever arm mounted on the threaded bushing, the position and alignment of which is dependent on the tamper stroke setting on the screed of the road finisher.

EP 1 905 899 A2 offenbart eine Einbaubohle für einen Straßenfertiger, auf welcher eine Tamperhubverstelleinrichtung montiert ist. Die Tamperhubverstelleinrichtung umfasst einen horizontal entlang eines Führungsschlittens verschiebbar gelagerten Lagerbock für eine Exzenterwelle, auf der eine Exzenterbuchse drehfest montiert ist. Durch eine horizontale Verlagerung des Lagerbocks kann manuell ein Abstand zwischen der daran gelagerten Exzenterwelle und einer auf der Einbaubohle vorgesehenen Kippachse eingestellt werden, wodurch eine Tamperhubeinstellung erfolgt. EP 1 905 899 A2 discloses a screed for a road finisher, on which a tamper stroke adjustment device is mounted. The tamper stroke adjustment device comprises a bearing block for an eccentric shaft, which is mounted so that it can be displaced horizontally along a guide carriage and on which an eccentric bushing is mounted in a rotationally fixed manner. By horizontally shifting the bearing block, a distance between the eccentric shaft mounted on it and a tilting axis provided on the screed can be set manually, as a result of which the tamper stroke is set.

EP 2 599 918 A1 offenbart ein Verfahren sowie eine Vorrichtung zur Einstellung eines oberen Umkehrpunkts einer Stampferleiste eines Straßenfertigers. EP 2 599 919 A1 offenbart eine weitere Vorrichtung zur Hubverstellung einer Stampferleiste eines Straßenfertigers. EP 2 599 918 A1 discloses a method and a device for adjusting an upper reversal point of a tamper bar of a road finisher. EP 2 599 919 A1 discloses another device for adjusting the stroke of a tamper bar of a road finisher.

Aufgabe der Erfindung ist es, einen Straßenfertiger mit einer Tamperhubverstelleinrichtung sowie ein Verfahren zur stufenlosen Tamperhubverstellung an einem Straßenfertiger zur Verfügung zu stellen, wodurch sich der Tamperhub anhand einfach konstruktiver technischer Mittel, insbesondere unter Verwendung weniger Baugruppen, präzise und stufenlos, vor allem während des Einbaubetriebs des Straßenfertigers, einstellen lässt.The object of the invention is to provide a road finisher with a tamper stroke adjustment device and a method for stepless tamper stroke adjustment on a road finisher, whereby the tamper stroke can be adjusted precisely and steplessly, especially during paving operation, using simple constructive technical means, in particular using fewer assemblies of the road finisher.

Diese Aufgabe wird gelöst anhand eines Straßenfertigers gemäß dem Anspruch 1 oder mittels eines Verfahrens gemäß dem Anspruch 15. Vorteilhafte Weiterbildungen der Erfindung sind durch die jeweiligen Unteransprüche angegeben.This object is achieved using a road finisher according to claim 1 or by means of a method according to claim 15. Advantageous developments of the invention are specified by the respective dependent claims.

Die Erfindung betrifft einen Straßenfertiger mit einer Einbaubohle zum Herstellen einer Einbauschicht, wobei die Einbaubohle mindestens ein Verdichtungsaggregat zum Vorverdichten eines der Einbaubohle zugeführten Einbaumaterials aufweist, und wobei das Verdichtungsaggregat mindestens eine Exzenterbuchse aufweist, die auf einer sie tragenden Exzenterwelle in einen gewünschten Drehwinkel verdrehbar gelagert ist, um dadurch stufenlos einen Soll-Tamperhub einer Tamperleiste des Verdichtungsaggregats einzustellen.The invention relates to a road finisher with a screed for producing a paving layer, wherein the screed has at least one compacting unit for pre-compacting a paving material fed to the screed, and wherein the compacting unit has at least one eccentric bushing, which is rotatably mounted to a desired angle of rotation on an eccentric shaft carrying it , in order thereby to steplessly set a desired tamper stroke of a tamper strip of the compression unit.

Erfindungsgemäß ist zum Verdrehen der Exzenterbuchse zur Exzenterwelle ein von der Exzenterwelle beabstandet gelagerter, zumindest teilweise mit einer Drehbewegung der Exzenterwelle mitrotierender Verstellmechanismus ansteuerbar. Da bei der Erfindung, trotz seiner beabstandeten Lage zur Exzenterwelle, ein selbst rotierender Verstellmechanismus die auf der Exzenterwelle mitdrehende Exzenterbuchse für eine Tamperhubverstellung ansteuert, ergeben sich in Summe, wie im Folgenden beschrieben, gleich mehrere Vorteile.According to the invention, in order to rotate the eccentric bushing relative to the eccentric shaft, an adjustment mechanism that is mounted at a distance from the eccentric shaft and rotates at least partially with a rotational movement of the eccentric shaft can be controlled. Since in the case of the invention, despite its spaced position from the eccentric shaft, a self-rotating adjusting mechanism controls the eccentric bushing rotating along with the eccentric shaft for adjusting the tamper stroke, there are several advantages in total, as described below.

Das Verdrehen der Exzenterbuchse auf der Exzenterwelle, sprich der jeweiligen Exzentrizitäten dieser beiden Bauteile, führt zu einer Phasenverstellung, womit sich der Soll-Tamperhub an der Einbaubohle einstellen lässt. Die Phasenverstellung ist vorteilhaft, insbesondere unter geringem Kraftaufwand, anhand des von der Exzenterwelle beabstandeten, vornehmlich mit der Drehzahl der Exzenterwelle, selbst mitrotierenden Verstellmechanismus ansteuerbar. Zum Einstellen der Phasenverstellung zwischen der Exzenterbuchse und der Exzenterwelle kann der mitrotierende Verstellmechanismus zumindest kurzzeitig derart angesteuert werden, dass das ihn an seiner Eingangsseite antreibende Drehmoment bzw. die dort anliegende Drehzahl an seiner Abtriebsseite, an welcher er eine Kopplung zur Exzenterbuchse vorsieht, über- oder untersetzt wird.Turning the eccentric bushing on the eccentric shaft, i.e. the respective eccentricities of these two components, leads to a phase adjustment, with which the target tamper stroke on the screed can be set. The phase adjustment is advantageously controllable, in particular with little effort, by means of the adjusting mechanism which is spaced apart from the eccentric shaft and primarily rotates with the speed of the eccentric shaft itself. To set the phase adjustment between the eccentric bushing and the eccentric shaft, the co-rotating adjustment mechanism can be controlled at least briefly in such a way that the torque driving it on its input side or the speed present there on its output side, on which it provides a coupling to the eccentric bushing, is exceeded or exceeded is stocky.

Dadurch kann die mit dem Verstellmechanismus gekoppelte, auf der Exzenterwelle mitdrehende Exzenterbuchse entsprechend des mittels des Verstellmechanismus angesteuerten Übersetzungsverhältnisses relativ zur Drehbewegung der Exzenterwelle "gebremst" oder "beschleunigt" werden, wodurch sich die Exzenterbuchse relativ zur Exzenterwelle in eine neue Winkelposition verdreht, d.h. die mittels des Verstellmechanismus angesteuerte Phasenverstellung durchführt. Ohne eine gesonderte Ansteuerung des mitrotierenden Verstellmechanismus dreht die Exzenterbuchse mit derselben Drehzahl wie die Exzenterwelle, d.h. zusammen mit dieser mit einem gleichbleibenden Phasenwinkel.As a result, the eccentric bushing coupled to the adjusting mechanism and rotating on the eccentric shaft can be "braked" or "accelerated" relative to the rotational movement of the eccentric shaft according to the transmission ratio controlled by the adjusting mechanism, whereby the eccentric bushing rotates relative to the eccentric shaft into a new angular position, i.e. the the phase adjustment controlled by the adjustment mechanism. Without a separate control of the co-rotating adjustment mechanism, the eccentric bush rotates at the same speed as the eccentric shaft, i.e. together with it with a constant phase angle.

Der Begriff "mitrotierend" bedeutet, dass der Verstellmechanismus oder zumindest ein Anteil der daran vorgesehenen Komponenten gemeinsam mit der Exzenterwelle, allerdings von dieser beabstandet gelagert, während des Betriebs des Verdichtungsaggregats rotiert. Diese mit der Exzenterwelle mitrotierende Baugruppe kann feinfühlig, unter geringem Kräfteaufwand für die vorangehend beschriebene Phasenverstellung, sprich eine Änderung der Winkelposition der auf der Exzenterwelle positionierten Exzenterbuchse, d.h. zum Variieren des Tamperhubs, angesteuert werden. Außerdem lässt sich das Ansteuern des von der Exzenterwelle beabstandet positionierten Verstellmechanismus präziser durchführen. Ferner lässt sich anhand eines solchen mitrotierenden Verstellmechanismus die Tamperhubverstellung besser automatisiert durchführen.The term "co-rotating" means that the adjustment mechanism or at least a portion of the components provided thereon rotates together with the eccentric shaft, although mounted at a distance from it, during operation of the compression unit. This assembly rotating with the eccentric shaft can be sensitively controlled with little effort for the phase adjustment described above, i.e. a change in the angular position of the eccentric bushing positioned on the eccentric shaft, i.e. to vary the tamper stroke. In addition, the adjustment mechanism positioned at a distance from the eccentric shaft can be controlled more precisely. Furthermore, the tamper stroke adjustment can be carried out better automatically using such a co-rotating adjustment mechanism.

Insbesondere kann vorgesehen sein, dass ein für die relative Verdrehung der Exzenterbuchse zur Exzenterwelle, von der Exzenterwelle selbst auf den Verstellmechanismus abgezweigter, diesen in Abhängigkeit einer Drehbewegung der Exzenterwelle zumindest teilweise in Rotation versetzender Kraftfluss vorliegt, wobei der dadurch in Rotation versetzte Verstellmechanismus derart ansteuerbar ist, dass er den auf ihn geleiteten Kraftfluss zwischen seinem Eingang und seinem Ausgang so manipuliert, dass dadurch eine Phasenverschiebung an seinem Abtrieb zustande kommt, worauf basierend die Exzenterbuchse auf der Exzenterwelle dementsprechend verdreht wird. Der Verstellmechanismus kann beispielsweise als hydraulisches und/oder elektromechanisches Phasenverstellsystem vorliegen.In particular, it can be provided that for the relative rotation of the eccentric bushing to the eccentric shaft, there is a flow of force that is branched off from the eccentric shaft itself to the adjustment mechanism and sets it at least partially in rotation as a function of a rotational movement of the eccentric shaft, the adjustment mechanism set in rotation thereby being controllable in this way that he manipulates the power flow directed to him between his input and his output in such a way that a phase shift occurs at his output, based on which the eccentric bushing on the eccentric shaft is twisted accordingly. The adjustment mechanism can be in the form of a hydraulic and/or electromechanical phase adjustment system, for example.

Bei der Erfindung kommt die gewünschte Tamperhubeinstellung vorzugsweise als Summe der Einzelexzentrizitäten der Exzenterwelle und der darauf verdrehbar gelagerten Exzenterbuchse zustande. Ein dazwischen eingestellter Phasenwinkel kann mittels des mitrotierenden Verstellmechanismus, insbesondere, wenn dieser als elektromechanischer Phasenversteller ausgebildet ist, reaktionsschnell und sehr präzise geändert werden. Als rotierende Baugruppe kann der Verstellmechanismus hervorragend für eine Phasenverstellung zwischen seiner Antriebs- und seiner Abtriebsseite angesteuert werden.In the case of the invention, the desired tamper stroke adjustment preferably comes about as the sum of the individual eccentricities of the eccentric shaft and the eccentric bushing mounted so as to be rotatable thereon. A phase angle set in between can be changed in a fast-reacting and very precise manner by means of the co-rotating adjustment mechanism, in particular if this is designed as an electromechanical phase adjuster. As a rotating assembly, the adjustment mechanism can be excellently controlled for a phase adjustment between its drive and its driven side.

Der bei der Erfindung eingesetzte Verstellmechanismus baut als solcher vorteilhaft in kompakter Weise auf bereits existierenden Komponenten bzw. Baugruppen der Einbaubohle auf, sodass damit sogar an verschiedenen Bohlentypen ein hohes Maß an Gleichteilen möglich ist. Aufgrund seiner zur Exzenterwelle beabstandeten Lage kann die Exzenterwelle selbst in konstruktiver Hinsicht einfacher gebaut sein.As such, the adjustment mechanism used in the invention advantageously builds on existing components or assemblies of the screed in a compact manner, so that a large number of identical parts is possible even on different screed types. Due to its location at a distance from the eccentric shaft, the eccentric shaft itself can be of simpler construction.

Dadurch, dass bei der Erfindung vorzugsweise der Verstellmechanismus zumindest teilweise von der Exzenterwelle drehangetrieben werden kann, ergibt sich insgesamt für die an ihm einstellbare Phasenverstellung eine vorteilhafte Kräftebilanz zum Einstellen des Tamperhubs. Dies wiederum führt dazu, dass der Verstellmechanismus einfacher automatisierbar ist, wodurch ein besseres Einbauergebnis mittels des Straßenfertigers möglich ist.Due to the fact that in the invention the adjusting mechanism can preferably be driven in rotation at least partially by the eccentric shaft, there is an overall advantageous balance of forces for adjusting the tamper stroke for the phase adjustment that can be adjusted on it. This in turn means that the adjustment mechanism can be automated more easily, which means that a better paving result is possible using the road finisher.

Vorzugsweise umfasst der Verstellmechanismus mindestens einen mittels der Drehbewegung der Exzenterwelle als solchen drehangetriebenen, zum Verdrehen der Exzenterbuchse ansteuerbaren Verstellantrieb und/oder mindestens ein mittels der Drehbewegung der Exzenterwelle drehangetriebenes, zum Verdrehen der Exzenterbuchse ansteuerbares Verstellgetriebe. Die Drehbewegung der Exzenterwelle ist bei dieser Ausführungsform allgemein ursächlich für das Rotieren des Verstellantriebs und/oder des Verstellgetriebes. Bei dieser Variante ist der Verstellantrieb und/oder das Verstellgetriebe in einen von der Exzenterwelle abgezweigten Antriebsstrang integriert, in dessen Kraftfluss der Verstellantrieb und/oder das Verstellgetriebe mitrotierend eingebunden ist. Ein feinfühliges Variieren des Drehwinkels zwischen der Exzenterbuchse und der Exzenterwelle wird hier durch eine Betätigung des Verstellantriebs und/oder des Verstellgetriebes schon unter geringem Kraftaufwand erreicht. Insbesondere lässt sich dadurch der Phasenverschiebungswinkel des im Kraftfluss mitrotierenden Verstellantriebs und/oder Verstellgetriebes leichter einstellen. Damit ist der Verstellmechanismus besser in der Lage, die Exzenterbuchse bei laufendem Einbaubetrieb gegenüber der Exzenterwelle in jede gewünschte Tamperhubeinstellung zu verdrehen, d.h. den Tamperhub zwischen einem minimalen und einem maximalen Tamperhubwert einzustellen.Preferably, the adjustment mechanism comprises at least one adjustment drive driven in rotation by the rotational movement of the eccentric shaft as such and controllable for turning the eccentric bushing and/or at least one adjustment gear drive driven in rotation by the rotational movement of the eccentric shaft and controllable for turning the eccentric bushing. In this embodiment, the rotational movement of the eccentric shaft is generally the cause of the rotation of the adjusting drive and/or the adjusting gear. In this variant, the adjusting drive and/or the adjusting gear is integrated into a drive train branched off from the eccentric shaft, in the power flow of which the adjusting drive and/or the adjusting gear is integrated in a rotating manner. A sensitive variation of the angle of rotation between the eccentric bushing and the eccentric shaft is achieved here by actuating the adjusting drive and/or the adjusting gear with little effort. In particular, the phase shift angle of the adjusting drive and/or adjusting gear rotating along in the power flow can be set more easily as a result. The adjusting mechanism is thus better able to turn the eccentric bushing relative to the eccentric shaft to any desired tamper stroke setting during ongoing paving operation, i.e. to set the tamper stroke between a minimum and a maximum tamper stroke value.

Für eine kompakte Bauweise ist es von Vorteil, wenn der Verstellantrieb und das Verstellgetriebe gemeinsam eine mitrotierende Funktionseinheit ausbilden. Die Funktionseinheit liegt dann als modularer Phasenversteller vor, der mit der Drehzahl der Exzenterwelle zu dieser mitrotierend gelagert ist, wobei der Verstellantrieb das Verstellgetriebe für eine gewünschte Phasenverstellung ansteuern kann, damit sich in Reaktion darauf die Exzenterbuchse zur Exzenterwelle zum Variieren des Tamperhubs verdreht.For a compact design, it is advantageous if the adjusting drive and the adjusting gear jointly form a co-rotating functional unit. The functional unit is then in the form of a modular phase adjuster, which is mounted to rotate with the eccentric shaft at the same speed as the eccentric shaft, with the adjusting drive being able to control the adjusting gear for a desired phase adjustment, so that the eccentric bushing rotates in response to the eccentric shaft to vary the tamper stroke.

Wie vorangehend beschrieben wurde, kann bei der Erfindung die rotierende Exzenterwelle in Funktion eines Aktuators für den daran gekoppelten, mitrotierenden Verstellantrieb und/oder das mitrotierende Verstellgetriebe vorliegen, wobei zum Durchführen der Phasenverstellung zwischen der Exzenterbuchse und der Exzenterwelle der mitrotierende Verstellantrieb und/oder das mitrotierende Verstellgetriebe als solches außer ihrer Rotation zusätzlich ansteuerbar ist. Das von der Exzenterwelle abgegriffene Drehmoment kann im von der Exzenterwelle abgezweigten Antriebsstrang anhand des darin drehangetriebenen Verstellantriebs und/oder das Verstellgetriebes zumindest kurzzeitig zum Einstellen des gewünschten Phasenverschiebungswinkels geändert werden, sodass daraus resultierende Kräfte die Exzenterbuchse auf der Exzenterwelle ausbremsen oder beschleunigen, sprich verdrehen.As described above, in the invention the rotating eccentric shaft can function as an actuator for the co-rotating adjusting drive coupled to it and/or the co-rotating adjusting gear, with the co-rotating adjusting drive and/or the co-rotating Adjusting gear as such is also controlled in addition to their rotation. The torque picked off by the eccentric shaft can be changed at least briefly in the drive train branched off from the eccentric shaft by means of the adjusting drive and/or the adjusting gear driven in rotation therein in order to set the desired phase shift angle, so that the resulting forces decelerate or accelerate the eccentric bushing on the eccentric shaft, i.e. twist it.

Dadurch, dass bei der Erfindung bevorzugt die Exzenterwelle sowohl zum Antreiben der Tamperleiste dient als auch in Funktion einer Antriebswelle für den mitrotierenden Verstellantrieb und/oder das mitrotierende Verstellgetriebe vorliegen kann, sozusagen eine Doppelfunktion erfüllt, kann eine, ggf. von außen wirkende, Verstellkraft auf den Verstellantrieb und/oder das Verstellgetriebe zum Verdrehen der Exzenterbuchse erheblich reduziert werden. Dadurch können auch die für die Tamperhubverstellung eingesetzten Komponenten konstruktiv reduziert werden, womit sich Herstellungskosten verringern lassen.Due to the fact that, in the case of the invention, the eccentric shaft preferably serves both to drive the tamper strip and can also function as a drive shaft for the co-rotating adjusting drive and/or the co-rotating adjusting gear, so to speak fulfills a double function, an adjusting force, possibly acting from the outside, can arise the adjusting drive and/or the adjusting gear for turning the eccentric bushing can be significantly reduced. As a result, the components used for adjusting the tamper stroke can also be structurally reduced, with the result that manufacturing costs can be reduced.

Das während des Einbaubetriebs vorzugsweise von der Exzenterwelle kontinuierlich abgegriffene Drehmoment ist im abgezweigten Kraftfluss anhand des darin angeordneten, mitrotierenden Verstellantriebs und/oder des mitrotierenden Verstellgetriebes derart manipulierbar, dass damit ohne großen zusätzlichen Krafteintrag eine Verstellbewegung der Exzenterbuchse auf der mittels der Antriebsdrehzahl rotierenden Exzenterwelle problemlos möglich ist. Ein Verstellmoment zum Variieren des Tamperhubs, sprich zum Ändern einer vektoriellen Summe der Einzelexzentrizitäten der Exzenterbuchse und der Exzenterwelle, resultiert aus der mittels des Verstellantriebs und/oder des Verstellgetriebes ansteuerbaren Phasenverstellung. Während der Durchführung der Phasenverstellung wird die Exzenterbuchse relativ zur Drehbewegung der Exzenterwelle in oder entgegen einer Drehrichtung der Exzenterwelle gedreht, bis die Exzenterbuchse eine gegenüber ihrer Ausgangsposition verstellte gewünschte Winkellage auf der Exzenterwelle einnimmt.The torque, which is preferably continuously tapped off from the eccentric shaft during paving operation, can be manipulated in the branched-off power flow using the co-rotating adjustment drive and/or the co-rotating adjusting gear arranged therein in such a way that an adjustment movement of the eccentric bushing on the eccentric shaft rotating by means of the drive speed is possible without any problems and without a large additional force input is. An adjusting torque for varying the tamper stroke, ie for changing a vectorial sum of the individual eccentricities of the eccentric bushing and the eccentric shaft, results from the phase adjustment that can be controlled by means of the adjusting drive and/or the adjusting gear. During the implementation of the phase adjustment, the eccentric bushing is rotated relative to the rotational movement of the eccentric shaft in or counter to a direction of rotation of the eccentric shaft until the eccentric bushing assumes a desired angular position on the eccentric shaft that is shifted from its starting position.

Vorzugsweise ist der mitrotierende Verstellantrieb und/oder das mitrotierende Verstellgetriebe dazu ansteuerbar, einen Drehwinkel eines auf der Exzenterwelle verdrehbar gelagerten Maschinenelements zu verstellen. Das Maschinenelement ermöglicht eine konstruktiv einfach herstellbare Kopplung des Verstellantriebs und/oder des Verstellgetriebes mit der auf der Exzenterwelle gelagerten Exzenterbuchse. Das Maschinenelement kann beispielsweise in Form eines Zahnrads oder einer Riemenscheibe für einen Synchronriemen vorliegen.The co-rotating adjusting drive and/or the co-rotating adjusting gear can preferably be controlled to adjust a rotation angle of a machine element rotatably mounted on the eccentric shaft. The machine element enables the adjustment drive and/or the adjustment gear to be coupled in a structurally simple manner to the eccentric shaft mounted eccentric bush. The machine element can for example be in the form of a toothed wheel or a pulley for a synchronous belt.

Eine Ausführungsform sieht vor, dass das Maschinenelement selbst die Exzenterbuchse ausbildet oder mittels einer formschlüssigen Kupplung, beispielsweise mittels einer Klauenkupplung, mit der Exzenterbuchse verbunden ist. Die erstgenannte Alternative ergibt einen Aufbau mit einer reduzierten Teileanzahl. Die zweite Alternative kann für Service- und/oder Instandsetzungsmaßnahmen vorteilhaft sein.One embodiment provides that the machine element itself forms the eccentric bushing or is connected to the eccentric bushing by means of a positive coupling, for example by means of a claw coupling. The former alternative results in an assembly with a reduced part count. The second alternative can be advantageous for service and/or repair measures.

Für einen standardisierten Aufbau ist es von Vorteil, wenn mindestens ein weiteres Maschinenelement vorgesehen ist, das zum Übertragen einer Drehbewegung der Exzenterwelle auf den Verstellantrieb und/oder das Verstellgetriebe ausgebildet ist. Das weitere Maschinenelement ist vorzugsweise drehfest auf der Exzenterwelle montiert. Es handelt sich dabei vorzugsweise um ein Zahnrad oder eine Riemenscheibe für einen Synchronriemen. Für das weitere Maschinenelement kann am Verstellantrieb und/oder am Verstellgetriebe, beispielsweise auf einem Getriebegehäuse des Verstellgetriebes oder auf einem Gehäuse des Verstellantriebs, ein komplementäres Koppelglied, beispielsweise in Form eines Zahnrads oder einer Riemenscheibe für den Synchronriemen, drehfest montiert sein.For a standardized structure, it is advantageous if at least one additional machine element is provided, which is designed to transmit a rotary motion of the eccentric shaft to the adjusting drive and/or the adjusting gear. The further machine element is preferably mounted in a rotationally fixed manner on the eccentric shaft. This is preferably a toothed wheel or a pulley for a synchronous belt. For the other machine element, a complementary coupling element, for example in the form of a gear wheel or a belt pulley for the synchronous belt, can be mounted non-rotatably on the adjustment drive and/or on the adjustment gear, for example on a gear housing of the adjustment gear or on a housing of the adjustment drive.

Mittels des weiteren Maschinenelements kann die Bewegungs- bzw. Kräfteübertragung von der Exzenterwelle auf den Verstellmechanismus durchgeführt werden. Eine dazu gesonderte, beispielsweise hydraulische oder elektromechanische Ansteuerung des in Rotation gesetzten Verstellmechanismus, insbesondere des mitrotierenden Verstellantriebs und/oder des mitrotierenden Verstellgetriebes, bewirkt, dass das an dessen Abtriebsseite gekoppelte, auf der Exzenterwelle verdrehbar angeordnete erste Maschineelement - und somit auch die Exzenterbuchse - phasenverstellt wird. Sobald das erste Maschinenelement die gewünschte Winkelposition eingenommen hat, d.h. der Soll-Tamperhub eingestellt ist, wird die vorangehend genannte gesonderte Ansteuerung des drehangetriebenen Verstellmechanismus abgebrochen. Ein am Verdichtungsaggregat dadurch eingestellter Ist-Drehwinkel zwischen der Exzenterbuchse und der Exzenterwelle ist dann mittels geeigneter Sensorik gut erfassbar. Der kontinuierlich während des Betriebs des Verdichtungsaggregats mitrotierende Verstellmechanismus kann für eine anschließend gewünschte Phasenverstellung erneut angesteuert werden, sodass es an seiner mit der Exzenterbuchse gekoppelten Abtriebsseite gegenüber seiner Antriebsseite zu einem erneuten Schaltmoment kommt.The motion or forces can be transmitted from the eccentric shaft to the adjustment mechanism by means of the additional machine element. A separate, for example hydraulic or electromechanical control of the adjusting mechanism set in rotation, in particular the co-rotating adjusting drive and/or the co-rotating adjusting gear, causes the first machine element, which is coupled to its output side and is rotatably arranged on the eccentric shaft - and thus also the eccentric bushing - to be phase-adjusted becomes. As soon as the first machine element has assumed the desired angular position, ie the target tamper stroke has been set, the aforementioned separate activation of the rotary-driven adjustment mechanism is terminated. An actual angle of rotation between the eccentric bushing and the eccentric shaft that is thus set on the compression unit can then be easily detected by means of suitable sensors. The adjustment mechanism, which rotates continuously during the operation of the compression unit, can be controlled again for a subsequently desired phase adjustment, so that a new switching moment occurs on its output side coupled to the eccentric bushing compared to its drive side.

Die zuvor beschriebenen Maschinenelemente zum Koppeln der Exzenterwelle mit dem Verstellmechanismus sowie zum Koppeln desselben mit der Exzenterbuchse können als Zahnrad, Riemenscheibe und/oder Kettenrad vorliegen und bilden somit standardisierte, vor allem kostengünstige Maschinebauteile aus.The machine elements described above for coupling the eccentric shaft to the adjusting mechanism and for coupling the same to the eccentric bushing can be in the form of gearwheels, belt pulleys and/or sprockets and thus form standardized, primarily cost-effective machine components.

Es bietet sich an, obwohl dies nicht zwingend nötig ist, dass während eines Betriebs des Verdichtungsaggregats der Verstellantrieb und/oder das Verstellgetriebe mit derselben Drehzahl wie die Exzenterwelle drehangetrieben ist. Beispielsweise werden hierfür gleichdimensionierte Zahn-/Kettenräder oder Riemenscheiben im Antriebsstrang zwischen der Exzenterwelle und dem damit drehangetriebenen Verstellmechanismus eingesetzt. Insbesondere kann während eines Betriebs des Verdichtungsaggregats der Verstellantrieb und/oder das Verstellgetriebe eine andere Drehzahl als die Exzenterwelle haben. Ein gewünschter Tamperhub kann dadurch erreicht werden, dass zwischen der Exzenterwelle und dem Verstellgetriebe und zwischen dem Verstellgetriebe und der Exzenterbuchse die gleiche Übersetzung vorliegt. Mit anderen Worten können die Exzenterwelle und die Verstellwelle, auf welcher das Verstellgetriebe gelagert ist, unterschiedliche Drehzahlen aufweisen; die Exzenterwelle und die Exzenterbuchse nicht.Although this is not absolutely necessary, it makes sense for the adjusting drive and/or the adjusting gear to be driven in rotation at the same speed as the eccentric shaft during operation of the compression unit. For example, gear wheels/chain wheels or belt pulleys of the same dimensions are used for this purpose in the drive train between the eccentric shaft and the adjustment mechanism that is driven in rotation with it. In particular, during operation of the compression unit, the adjusting drive and/or the adjusting gear can have a different speed than the eccentric shaft. A desired tamper stroke can be achieved in that there is the same translation between the eccentric shaft and the adjusting gear and between the adjusting gear and the eccentric bushing. In other words, the eccentric shaft and the adjusting shaft on which the adjusting gear is mounted can have different speeds; the eccentric shaft and the eccentric bushing do not.

Es ist vorteilhaft, wenn der Verstellantrieb und/oder das Verstellgetriebe hydraulisch, elektrisch und/oder mechanisch betätigbar ist. Mittels eines hydraulischen Verstellantriebs und/oder Verstellgetriebes könnten vor allen Dingen große Verstellkräfte erzeugt werden. Ein elektrischer oder elektromechanischer Verstellmechanismus würde in kürzeren Reaktionszeiten, sprich unabhängig von einer Hydrauliktemperatur, die Tamperhubverstellung ermöglichen.It is advantageous if the adjusting drive and/or the adjusting gear can be actuated hydraulically, electrically and/or mechanically. Above all, large adjusting forces could be generated by means of a hydraulic adjusting drive and/or adjusting gear. An electrical or electromechanical adjustment mechanism would allow the tamper stroke to be adjusted with shorter reaction times, i.e. independently of a hydraulic temperature.

Bevorzugt ist das Verstellgetriebe ein stufenlos verstellbares mechanisches, hydrostatisches oder elektrisches Getriebe. Vorzugsweise ist das Verstellgetriebe zum Einstellen eines gewünschten Übersetzungsverhältnisses mittels eines an der Einbaubohle ohnehin vorliegenden mechanischen, hydraulischen oder elektrischen Antriebs ansteuerbar, d.h. mittels eines Antriebs, der ferner zum Betrieb einer anderen Arbeitskomponente der Einbaubohle eingesetzt wird. Dies trägt weiter zu einer Reduzierung der eingesetzten Bauteile bzw. Baugruppen bei.The adjusting gear is preferably a continuously adjustable mechanical, hydrostatic or electric gear. The adjusting gear can preferably be controlled to set a desired transmission ratio by means of a mechanical, hydraulic or electric drive that is already present on the screed, i.e. by means of a drive that is also used to operate another working component of the screed. This further contributes to a reduction in the number of components or assemblies used.

Eine Variante sieht vor, dass der Verstellantrieb einen ansteuerbaren Servomotor aufweist und/oder für das Verstellgetriebe ein Servomotor vorgesehen ist. Der Servomotor kann zusammen mit dem Verstellgetriebe eine zur Exzenterwelle mitrotierende Funktionseinheit ausbilden, wobei der Servomotor für eine gewünschte Phasenverstellung derart ansteuerbar ist, dass er durch das mit ihm verbundene Verstellgetriebe den auf die Exzenterbuchse über den mitrotierenden Verstellmechanismus übertragenen Kraftfluss ändert. In Reaktion darauf verdreht sich die Exzenterbuchse auf der Exzenterwelle in die gewünschte Winkelposition.A variant provides that the adjusting drive has a controllable servo motor and/or a servo motor is provided for the adjusting gear. The servomotor together with the adjusting gear can form a functional unit rotating with the eccentric shaft, the servomotor being controllable for a desired phase adjustment in such a way that it changes the power flow transmitted to the eccentric bushing via the adjusting mechanism rotating with it through the adjusting gear connected to it. In response, the eccentric bushing rotates on the eccentric shaft to the desired angular position.

Vorzugsweise ist das Verstellgetriebe als Kurvengetriebe ausgebildet und/oder weist ein Paar rotierender Umlenkrollen auf. Damit kann das Verstellgetriebe besonders robust ausgebildet sein. Vorstellbar ist es, dass das Kurvengetriebe zwei zueinander verstellbar gelagerte Kurvenscheiben aufweist, die linear und/oder rotatorisch zueinander verlagerbar sind. Eine Bewegung der Kurvenscheiben zueinander kann bewirken, dass die daran gelagerten Umlenkrollen entlang daran ausgebildeter Kurvenbahnen verstellt werden, wodurch eine Phasenverstellung resultiert.The adjusting mechanism is preferably designed as a cam mechanism and/or has a pair of rotating deflection rollers. In this way, the adjustment gear can be designed to be particularly robust. It is conceivable for the cam mechanism to have two cam disks which are mounted so as to be adjustable in relation to one another and can be displaced linearly and/or rotationally in relation to one another. A movement of the cam discs relative to each other can cause the deflection rollers mounted thereon to be adjusted along curved paths formed thereon, which results in a phase adjustment.

Gemäß einer Ausführungsform der Erfindung sieht das Verstellgetriebe zum Verschieben der daran gelagerten, im Kraftfluss mitrotierenden Umlenkrollen mindestens eine ortsfest gelagerte Kurvenscheibe und mindestens eine daran beweglich gelagerte Kurvenscheibe vor. Diese ist für eine translatorische und/oder eine rotatorische Verlagerung an der ortsfesten Kurvenscheibe montiert, um dadurch für eine Phasenverstellung eine Verschiebung der Drehachsen der mitrotierenden Umlenkrollen einzustellen.According to one embodiment of the invention, the adjustment mechanism provides at least one stationary cam and at least one movably mounted cam for shifting the deflection rollers mounted thereon and rotating in the power flow. This is mounted on the stationary cam disk for translational and/or rotational displacement, in order thereby to set a displacement of the axes of rotation of the deflection rollers that rotate along for a phase adjustment.

Gemäß einer Ausführungsform ist das Paar rotierender Umlenkrollen zum Verdrehen der Exzenterbuchse auf der Exzenterwelle quer zur Exzenterwelle, d.h. quer zu dessen Drehachse, verschiebbar gelagert. Die mitrotierenden Umlenkrollen können an einem Zahnriemen oder an einer Antriebskette anliegend gelagert sein, der oder die mit dem auf der Exzenterwelle verdrehbar gelagerten Maschinenelement verbunden ist. Mittels einer Verlagerung der Umlenkrollen ändert sich zugleich ein Längenverhältnis der gegenüber geführten Riemen- oder Kettenabschnitte, sodass sich in Reaktion darauf das Maschinenelement auf der Exzenterwelle verdreht, sprich die Exzenterbuchse zur Exzenterwelle phasenverstellt wird.According to one embodiment, the pair of rotating deflection rollers for rotating the eccentric bushing is mounted on the eccentric shaft so as to be displaceable transversely to the eccentric shaft, i.e. transversely to its axis of rotation. The co-rotating deflection rollers can be mounted adjacent to a toothed belt or a drive chain, which is connected to the machine element mounted rotatably on the eccentric shaft. By shifting the deflection rollers, the length ratio of the belt or chain sections guided opposite one another changes at the same time, so that the machine element on the eccentric shaft rotates in response to this, i.e. the eccentric bushing is phase-shifted in relation to the eccentric shaft.

Die beiden mitrotierenden Umlenkrollen können hinsichtlich zueinander beabstandeten, parallel gelagerten Drehachsen drehbar gelagert sein. Anhand einer Änderung der Positionierung der mitrotierenden Umlenkrollen, insbesondere bei einer Änderung des Abstands zwischen den Drehachsen, kann auf den Phasenverstellwinkel Einfluss genommen werden, anhand dessen die Exzenterbuchse auf der Exzenterwelle liegt.The two co-rotating deflection rollers can be rotatably mounted with respect to mutually spaced, parallel mounted axes of rotation. A change in the positioning of the co-rotating deflection rollers, in particular a change in the distance between the axes of rotation, can be used to influence the phase adjustment angle, based on which the eccentric bushing lies on the eccentric shaft.

Vorzugsweise führt eine translatorische Verschiebung der mitrotierenden Umlenkrollen quer zur Drehachse der Exzenterwelle auf einer Seite des um die Umlenkrollen gelenkten Synchronriemens oder der Antriebskette zu einer Bahnverlängerung, was gleichzeitig durch eine Bahnverkürzung auf der gegenüberliegenden Seite des Synchronriemens oder der Antriebskette kompensiert wird. Dadurch kann unter geringem Kraftaufwand eine Verdrehung der Exzenterbuchse auf der Exzenterwelle erfolgen, sodass die Exzenterbuchse zum Einstellen des Tamperhubs einen gewünschten Drehwinkel auf der Exzenterwelle einnimmt.Preferably, a translational displacement of the deflection rollers that rotate along transversely to the axis of rotation of the eccentric shaft on one side of the synchronous belt guided around the deflection rollers or of the drive chain leads to a lengthening of the track, which is simultaneously compensated for by a shortening of the track on the opposite side of the synchronous belt or the drive chain. As a result, the eccentric bushing can be rotated on the eccentric shaft with little effort, so that the eccentric bushing assumes a desired angle of rotation on the eccentric shaft for setting the tamper stroke.

Eine vorteilhafte Variante sieht vor, dass der Verstellantrieb und/oder das Verstellgetriebe zum synchronen Verstellen mehrerer entlang der Exzenterwelle verdrehbar gelagerter Exzenterbuchsen ausgebildet ist (Gesamthubverstellung) oder der Verstellmechanismus mehrere Verstellantriebe und/oder Verstellgetriebe zum separaten Verstellen mehrerer entlang der Exzenterwelle verdrehbar gelagerter Exzenterbuchsen umfasst (Einzelhubverstellung). Die entlang mehrerer Aggregatabschnitte installierten Exzenterbuchsen können bei diesen Varianten gemeinsam, also synchron miteinander, oder unabhängig voneinander, d.h. einzeln, verstellt werden. Anhand von unabhängig voneinander ansteuerbaren Exzenterbuchsen ließen sich während einer Einbaufahrt über die mittels der Einbaubohle herstellbare Einbaubreite verschiedene Tamperhübe einstellen.An advantageous variant provides that the adjusting drive and/or the adjusting gear is designed for the synchronous adjustment of several eccentric bushings that are rotatably mounted along the eccentric shaft (overall stroke adjustment) or the adjusting mechanism includes several adjusting drives and/or adjusting gears for the separate adjustment of several eccentric bushings that are rotatably mounted along the eccentric shaft ( single stroke adjustment). With these variants, the eccentric bushings installed along several unit sections can be adjusted together, i.e. synchronously with one another, or independently of one another, i.e. individually. Using eccentric bushings that can be controlled independently of one another, different tamper strokes can be set during one paving journey over the paving width that can be created using the screed.

Für ein synchrones Verstellen der Exzenterbuchsen kann der Verstellmechanismus an seiner Abtriebsseite mit einer Verstellwelle gekoppelt sein. Die Verstellwelle kann eine zentral mittels des Verstellmechanismus eingestellte Phasenverstellung synchron an mehrere Aggregatabschnitte des Verdichtungsaggregats, d.h. an daran gelagerte Exzenterbuchsen, weitergeben. Alternativ dazu kann für jeden Aggregatabschnitt des Verdichtungsaggregats ein eigenständig ansteuerbarer, mitrotierender Verstellmechanismus vorliegen. Diese können auf einer gemeinsamen Welle gelagert sein, über die sie jeweils eine Drehbewegung der Exzenterwelle aufnehmen. An deren Ausgangseite lassen sich jedoch verschiedene Phasenverstellungen einstellen. Vorzugsweise ist die Verstellwelle bzw. die Welle parallel zur Exzenterwelle gelagert.For synchronous adjustment of the eccentric bushes, the adjustment mechanism can be coupled to an adjustment shaft on its output side. The adjustment shaft can transmit a phase adjustment set centrally by means of the adjustment mechanism synchronously to a number of unit sections of the compression unit, i.e. to eccentric bushings mounted thereon. As an alternative to this, there can be an independently controllable, co-rotating adjusting mechanism for each unit section of the compression unit. These can be mounted on a common shaft, via which they each record a rotational movement of the eccentric shaft. However, different phase adjustments can be set on the output side. The adjusting shaft or the shaft is preferably mounted parallel to the eccentric shaft.

Gemäß einer Ausführungsform ist der Verstellantrieb und/oder das Verstellgetriebe zum Einstellen des gewünschten Drehwinkels der Exzenterbuchse mittels einer Steuereinrichtung ansteuerbar. Die Steuereinrichtung, unabhängig davon, ob sie für eine Gesamthubverstellung oder eine Einzelhubverstellung eingesetzt wird, kann als integraler Bestandteil des Verstellmechanismus vorliegen. Die Steuereinrichtung kann über ein CAN-Bussystem mit einer Fahrzeugsteuerung des Straßenfertigers verbunden sein, von welcher aus der Soll-Tamperhub bzw. die jeweiligen Soll-Tamperhübe vorhaltbar sind.According to one embodiment, the adjusting drive and/or the adjusting gear can be controlled by means of a control device in order to set the desired angle of rotation of the eccentric bushing. The control device, regardless of whether it is used for a total stroke adjustment or an individual stroke adjustment, can be present as an integral part of the adjustment mechanism. The control device can be connected via a CAN bus system to a vehicle controller of the road finisher, from which the setpoint tamper stroke or the respective setpoint tamper strokes can be maintained.

Eine besonders bevorzugte Variante sieht vor, dass die Steuereinrichtung zur dynamischen Drehwinkelanpassung der Exzenterbuchse zumindest einen auf mindestens einen während des Betriebs des Straßenfertigers erfassbaren Prozessparameter ansprechenden Regelkreis aufweist. Anhand des Regelkreises kann beispielsweise auf einen gemessenen materialspezifischen Wert des zu verbauenden Einbauguts, beispielsweise auf eine gemessene Temperatur des aus dem Gutbunker des Straßenfertigers zur Einbaubohle transportierten Einbaumaterials, und/oder der hergestellten Einbauschicht, beispielsweise auf eine gemessene Temperatur der Einbauschicht, entsprechend mit einer Anpassung des Drehwinkels zwischen der Exzenterbuchse und der Exzenterwelle reagiert werden, um ein optimales Einbauergebnis herzustellen.A particularly preferred variant provides that the control device for the dynamic adjustment of the angle of rotation of the eccentric bushing has at least one control loop that responds to at least one process parameter that can be detected during operation of the road finisher. On the basis of the control circuit, for example, a measured material-specific value of the paving material to be paved, for example a measured temperature of the paving material transported from the goods bunker of the road finisher to the paving screed, and/or the paving layer produced, for example a measured temperature of the paving layer, be reacted accordingly with an adjustment of the angle of rotation between the eccentric bushing and the eccentric shaft in order to produce an optimal installation result.

Eine bevorzugte Ausführungsform der Erfindung sieht vor, dass der Regelkreis dazu in der Lage ist, in Reaktion auf eine Störgröße, beispielsweise eine Umgebungstemperatur, eine dynamische Drehwinkelverstellung zwischen der Exzenterbuchse und der Exzenterwelle zum kontinuierlichen Anpassen des Tamperhubs zu steuern.A preferred embodiment of the invention provides that the control circuit is able to control a dynamic angle of rotation adjustment between the eccentric bushing and the eccentric shaft in response to a disturbance variable, for example an ambient temperature, for the continuous adjustment of the tamper stroke.

Vorstellbar ist es, dass beim Einregeln der Tamperhubeinstellung ein eingestellter Anstellwinkel der Einbaubohle, eine gefahrene Einbaugeschwindigkeit des Straßenfertigers, eine eingestellte Antriebsdrehzahl der Exzenterwelle, eine Temperatur von Verdichterplatten der Einbaubohle und/oder Messwerte eines gesonderten Baustellenfahrzeugs, beispielsweise Messwerte bezüglich der hergestellten Einbauschicht, die anhand eines dem Straßenfertiger hinterherfahrenden Verdichterfahrzeugs erfasst werden, berücksichtigt werden.It is conceivable that when adjusting the tamper stroke setting, a set angle of attack of the screed, a paving speed driven by the road finisher, a set drive speed of the eccentric shaft, a temperature of the compactor plates of the screed and/or measured values from a separate construction site vehicle, for example measured values regarding the paving layer produced, which are based on of a compactor vehicle driving behind the road finisher can be taken into account.

Vorzugsweise umfasst der Verstellmechanismus mindestens eine Sensoreinheit, die zum Erfassen eines eingestellten Phasenwinkels zwischen der Exzenterbuchse und der sie tragenden Exzenterwelle und/oder zum Erfassen eines Hubs der Tamperleiste ausgebildet ist. Vorstellbar ist es, dass der Verstellantrieb, vor allem dann, wenn er als Servomotor vorliegt, mindestens eine dafür zweckmäßige Sensoreinheit, beispielsweise einen oder mehrere Winkelsensoren, aufweist. Damit ließe sich auf Basis der erfassten Winkelposition der Motorwelle des Servomotors die Phasenverstellung zwischen der Exzenterbuchse und der Exzenterwelle herleiten. Anhand der erfassten Phaseneinstellung kann die Steuereinrichtung den Ist-Tamperhub berechnen. Vorstellbar ist es, dass die Steuereinrichtung basierend auf der gemessenen Phaseneinstellung, beispielsweise mittels Phasen-Kennlinien, den dementsprechenden Ist-Tamperhub herleitet. Eine mittels der Sensoreinheit erfasste bzw. variierende Phaseneinstellung kann zeitecht an die Steuereinheit übermittelt werden, sodass diese basierend auf einem Soll-Ist-Tamperhubvergleich ggf. ein dementsprechendes Steuersignal an den Verstellantrieb, insbesondere den Servomotor, ausgibt, um reaktionsschnell eine Verdrehung der Exzenterbuchse für eine Tamperhubanpassung anzusteuern.The adjustment mechanism preferably includes at least one sensor unit, which is designed to detect a set phase angle between the eccentric bushing and the eccentric shaft that carries it and/or to detect a stroke of the tamper strip. It is conceivable that the adjustment drive, especially when it is in the form of a servo motor, has at least one sensor unit suitable for this purpose, for example one or more angle sensors. This would allow the phase shift between the eccentric bushing and the eccentric shaft to be derived on the basis of the detected angular position of the motor shaft of the servomotor. The control device can calculate the actual tamper stroke based on the detected phase setting. It is conceivable that the control device derives the corresponding actual tamper stroke based on the measured phase setting, for example by means of phase characteristics. A phase setting detected or varying by means of the sensor unit can be transmitted to the control unit in a timely manner, so that based on a target/actual tamper stroke comparison, it may output a corresponding control signal to the adjustment drive, in particular the servo motor, in order to quickly rotate the eccentric bushing for a to control tamper stroke adjustment.

Die Sensoreinheit könnte gemäß einer Ausführungsform mindestens einen Abstandssensor aufweisen, der dazu ausgebildet ist, direkt einen eingestellten Ist-Tamperhub der Tamperleiste zu messen.According to one embodiment, the sensor unit could have at least one distance sensor, which is designed to directly measure a set actual tamper stroke of the tamper strip.

Eine praktische Variante sieht vor, dass der Verstellmechanismus manuell verstellbar ausgebildet ist. Dies kann vor allen Dingen für eine Kalibrierung der Tamperleiste zu Beginn der Einbaufahrt hilfreich sein. Ein automatisierter Betrieb des Verstellmechanismus lässt sich dagegen hervorragend während der Einbaufahrt einsetzten.A practical variant provides that the adjustment mechanism is designed to be manually adjustable. Above all, this can be used to calibrate the tamper strip at the beginning of the paving journey be helpful. Automated operation of the adjustment mechanism, on the other hand, can be used excellently during the paving journey.

Die Erfindung bezieht sich auch auf ein Verfahren zur stufenlosen Tamperhubverstellung an einem Verdichtungsaggregat eines Straßenfertigers, wobei zum Verstellen des Taperhubs mindestens eine Exzenterbuchse auf einer sie lagernden Exzenterwelle verdreht wird. Erfindungsgemäß wird zum Verdrehen der Exzenterbuchse auf der Exzenterwelle ein zur Exzenterwelle beabstandet gelagerter, zumindest teilweise mit einer Drehbewegung der Exzenterwelle mitrotierender Verstellmechanismus angesteuert.The invention also relates to a method for stepless adjustment of the tamper stroke on a compacting unit of a road finisher, with at least one eccentric bush being rotated on an eccentric shaft supporting it in order to adjust the taper stroke. According to the invention, in order to rotate the eccentric bushing on the eccentric shaft, an adjusting mechanism is controlled which is mounted at a distance from the eccentric shaft and rotates at least partially with a rotational movement of the eccentric shaft.

Vorzugsweise kommt die relative Verdrehung zwischen der Exzenterbuchse und der Exzenterwelle dadurch zustande, dass ein von der Exzenterwelle abgeleiteter, den Verstellmechanismus oder zumindest Teile davon in eine Rotationsbewegung versetzender Kraftfluss anhand des Verstellmechanismus zumindest kurzzeitig derart unter- oder übersetzt wird, dass sich dadurch der Drehwinkel zwischen der Exzenterbuchse und der Exzenterwelle verändert. Hier wird also das Drehmoment von der Exzenterwelle abgeleitet und als Antriebsdrehmoment auf den Verstellmechanismus übertragen. Insbesondere ein daran angeschlossenes, ebenfalls mitrotierendes Verstellgetriebe kann für eine Drehmomentenanpassung mittels eines Verstellantriebs angesteuert werden. Bei dieser Ausführungsform dreht die Exzenterbuchse, ohne eine zusätzliche Ansteuerung des Verstellantriebs, auf der Exzenterwelle gleichförmig, d.h. mit gleicher Drehzahl, mit. Anhand einer gesonderten Ansteuerung des Verstellantriebs kann über das mit ihm gekoppelte Verstellgetriebe zwischen der Exzenterbuchse und der sie lagernden Exzenterwelle eine Differenzgeschwindigkeit erzeugt werden, wodurch sich die Exzenterbuchse auf der Exzenterwelle in eine neue Winkelposition verdreht. Dadurch wird der Tamperhub verstellt. Damit kommt das Verdichtungsaggregat insgesamt mit einer reduzierten Anzahl an mechanischen, elektrischen und/oder hydraulischen Komponenten auskommt, um den Tamperhub zu variieren. Dadurch entsteht eine praktische, kostengünstig herstellbare und im Wesentlichen autonom arbeitende Verstelleinrichtung zum Variieren des Tamperhubs am Straßenfertiger.Preferably, the relative rotation between the eccentric bushing and the eccentric shaft is brought about by the fact that a flow of force derived from the eccentric shaft, which causes the adjustment mechanism or at least parts of it to rotate, is at least briefly reduced or increased by means of the adjustment mechanism in such a way that the angle of rotation between the eccentric bushing and the eccentric shaft changed. Here, the torque is derived from the eccentric shaft and transmitted to the adjustment mechanism as drive torque. In particular, an adjustment gear that is connected to it and also rotates along with it can be controlled for torque adjustment by means of an adjustment drive. In this embodiment, the eccentric bush rotates uniformly on the eccentric shaft, i.e. at the same speed, without additional control of the adjustment drive. Using a separate control of the adjusting drive, a differential speed can be generated via the adjusting gear coupled to it between the eccentric bushing and the eccentric shaft supporting it, as a result of which the eccentric bushing rotates into a new angular position on the eccentric shaft. This adjusts the tamper stroke. This means that the compression unit can manage overall with a reduced number of mechanical, electrical and/or hydraulic components in order to vary the tamper stroke. This results in a practical adjustment device that can be produced inexpensively and works essentially autonomously for varying the tamper stroke on the road finisher.

Vorteilhafte Ausführungsformen der Erfindung werden anhand der folgenden Figuren genauer erläutert. Es zeigen:

Figur 1
eine schematische Seitenansicht eines Straßenfertigers,
Figur 2
ein Verdichtungsaggregat für eine Einbaubohle eines Straßenfertigers gemäß einer ersten Ausführungsform,
Figur 2A
ein erster Betriebszustand des in Figur 2 gezeigten Verdichtungsaggregats,
Figur 2B
ein zweiter Betriebszustand des in Figur 2 gezeigten Verdichtungsaggregats,
Figur 2C
eine Variante der in Figur 2 gezeigten ersten Ausführungsform für eine Gesamthubverstellung,
Figur 2D
eine Variante der in Figur 2 gezeigten Ausführungsform für eine Einzelhubverstellung,
Figur 3
ein Verdichtungsaggregat für eine Einbaubohle eines Straßenfertigers gemäß einer zweiten Ausführungsform,
Figur 3A
eine Schnittdarstellung des Verstellmechanismus der in Figur 3 gezeigten zweiten Ausführungsform,
Figur 3B
eine gesonderte Darstellung des Verstellmechanismus der in Figur 3 gezeigten Ausführungsform,
Figur 3C
eine Variante der in Figur 3 gezeigten zweiten Ausführungsform für eine Gesamthubverstellung, und
Figur 3D
eine schematische Darstellung der zweiten Ausführungsform aus Figur 3 für eine Einzelhubverstellung.
Advantageous embodiments of the invention are explained in more detail with reference to the following figures. Show it:
figure 1
a schematic side view of a road finisher,
figure 2
a compaction unit for a screed of a road finisher according to a first embodiment,
Figure 2A
a first operating state of the in figure 2 compression unit shown,
Figure 2B
a second operating state of the in figure 2 compression unit shown,
Figure 2C
a variant of the in figure 2 shown first embodiment for a total stroke adjustment,
Figure 2D
a variant of the in figure 2 shown embodiment for a single stroke adjustment,
figure 3
a compaction unit for a screed of a road finisher according to a second embodiment,
Figure 3A
a sectional view of the adjustment mechanism in figure 3 shown second embodiment,
Figure 3B
a separate representation of the adjustment mechanism in figure 3 shown embodiment,
Figure 3C
a variant of the in figure 3 shown second embodiment for a total stroke adjustment, and
Figure 3D
a schematic representation of the second embodiment figure 3 for a single stroke adjustment.

Gleiche Komponenten sind in den Figuren durchgängig mit den gleichen Bezugszeichen versehen.Identical components are provided with the same reference symbols throughout the figures.

Figur 1 zeigt einen Straßenfertiger 1 mit einer Einbaubohle 2 zum Herstellen einer Einbauschicht 3 in Einbaufahrtrichtung R. Die Einbaubohle 2 verfügt über mindestens ein Verdichtungsaggregat 4 zum Vorverdichten eines der Einbaubohle 2 zugeführten Einbaumaterials 5. Das Verdichtungsaggregat 4 weist eine Tamperleiste 6 auf, die mit einem variierbaren Tamperhub H und/oder einer variierbaren Frequenz F zum Vorverdichten des der Einbaubohle 2 zugeführten Einbaumaterials 5 antreibbar ist. figure 1 shows a road finisher 1 with a screed 2 for producing a paving layer 3 in the paving direction of travel R. The screed 2 has at least one compacting unit 4 for pre-compacting paving material 5 fed to the screed 2. The compacting unit 4 has a tamper strip 6, which has a variable tamper stroke H and/or a variable frequency F for pre-compacting the paving material 5 fed to the screed 2.

Figur 2 zeigt das Verdichtungsaggregat 4 gesondert in vergrößerter Perspektivdarstellung. Das Verdichtungsaggregat 4 verfügt über einen am Bohlenkörper befestigten Lagerbock 7 und eine daran drehbar gelagerte Exzenterwelle 8. Die Exzenterwelle 8 treibt ein Pleuel 9 an, woran die Tamperleiste 6 befestigt ist. figure 2 shows the compression unit 4 separately in an enlarged perspective view. The compression unit 4 has a bearing block 7 fastened to the screed body and an eccentric shaft 8 rotatably mounted thereon. The eccentric shaft 8 drives a connecting rod 9 to which the tamper bar 6 is fastened.

Figur 2 zeigt ferner einen Verstellmechanismus 10, der mittels der Exzenterwelle 8 drehangetrieben ist. Der Verstellmechanismus 10 kann dazu angesteuert werden, einen für die Tamperleiste 6 variierbaren Soll-Tamperhub 11 einzustellen. Dafür umfasst der mitrotierende Verstellmechanismus 10 einen Verstellantrieb 12 und/oder ein Verstellgetriebe 13. Gemäß Figur 2 sind der Verstellantrieb 12 und das Verstellgetriebe 13 als eine Funktionseinheit ausgebildet. Diese Funktionseinheit ist an eine Drehbewegung der Exzenterwelle 8 mittels eines Synchronriemens 14 gekoppelt. figure 2 also shows an adjusting mechanism 10 which is driven in rotation by means of the eccentric shaft 8 . The adjusting mechanism 10 can be controlled to set a target tamper stroke 11 that can be varied for the tamper strip 6 . For this purpose, the co-rotating adjustment mechanism 10 includes an adjustment drive 12 and/or an adjustment gear 13. According to FIG figure 2 the adjusting drive 12 and the adjusting gear 13 are designed as a functional unit. This functional unit is coupled to a rotary motion of the eccentric shaft 8 by means of a timing belt 14 .

Der Verstellmechanismus 10 kann, ohne zusätzlich angesteuert zu werden, das mittels des Synchronriemens 14 an seiner Eingangsseite antreibende, ihn in Rotation versetzende Drehmoment mittels eines an seiner Ausgangsseite vorgesehenen, weiteren Synchronriemens 15 auf ein auf der Exzenterwelle 8 verdrehbar gelagertes Maschinenelement 16 zurückführen. Durch eine zusätzliche Ansteuerung des Verstellmechanismus 10 kann ein Phasenwinkel des auf der Exzenterwelle 8 gelagerten Maschinenelements 16 verändert werden. Anhand dieser Phasenverstellung lässt sich eine innerhalb des Pleuels 9 auf der Exzenterwelle 8 verdrehbar gelagerte, an das Maschinenelement 16 gekoppelte Exzenterbuchse 17 (siehe Figur 2C) verstellen. Gemäß Figur 2 ist somit zum Verdrehen der Exzenterbuchse 17 auf der Exzenterwelle 8 der zur Exzenterwelle 8 beabstandet gelagerte, mit der Drehbewegung der Exzenterwelle 8 mitrotierende Verstellmechanismus 10 ansteuerbar.The adjustment mechanism 10 can, without being additionally controlled, return the torque driving it by means of the synchronous belt 14 on its input side and setting it into rotation to a machine element 16 rotatably mounted on the eccentric shaft 8 by means of a further synchronous belt 15 provided on its output side. A phase angle of the machine element 16 mounted on the eccentric shaft 8 can be changed by an additional activation of the adjustment mechanism 10 . On the basis of this phase adjustment, an eccentric bushing 17 (see Fig Figure 2C ) adjust. According to figure 2 is thus for rotating the eccentric bushing 17 on the eccentric shaft 8 of the eccentric shaft 8 mounted spaced, with the rotational movement of the eccentric shaft 8 co-rotating adjustment mechanism 10 can be controlled.

Anhand der Figuren 2A und 2B wird schematisch das Durchführen einer Phasenverstellung mittels des Verstellmechanismus 10 gezeigt, um den Tamperhub 11 zu verstellen.Based on Figures 2A and 2B the implementation of a phase adjustment by means of the adjustment mechanism 10 is shown schematically in order to adjust the tamper stroke 11 .

In Figur 2A überträgt der Synchronriemen 14, der über eine drehfest auf der Exzenterwelle 8 montierte Riemenscheibe 18 geführt ist, die Drehbewegung der Exzenterwelle 8 auf ein Gehäuse 19 des Verstellmechanismus 10. Das Gehäuse 19 kann mit einem Durchmesser wie die Riemenscheibe 18 ausgebildet sein. Damit ist zwischen der Exzenterwelle 8 und dem Verstellmechanismus 10 ein Riemenantrieb hergestellt, der dafür sorgt, dass der Verstellmechanismus 10 mit der Drehzahl der Exzenterwelle 8 rotiert.In Figure 2A the synchronous belt 14, which is guided over a pulley 18 mounted in a torque-proof manner on the eccentric shaft 8, transmits the rotational movement of the eccentric shaft 8 to a housing 19 of the adjusting mechanism 10. The housing 19 can be designed with a diameter like the pulley 18. A belt drive is thus produced between the eccentric shaft 8 and the adjustment mechanism 10 which ensures that the adjustment mechanism 10 rotates at the speed of the eccentric shaft 8 .

In Figur 2A wird der mitrotierende Verstellmechanismus 10 nicht zusätzlich angesteuert, so dass ein an seinem Gehäuse 19, an seiner Eingangsseite anliegendes Drehmoment über den an seiner Ausgangsseite befestigten weiteren Synchronriemen 15 an das Maschinenelement 16 weitergegeben wird. Dies hat gemäß Figur 2A zur Folge, dass die innerhalb des Pleuels 9 gelagerte Exzenterbuchse 17 mit der Drehzahl der Exzenterwelle 8 rotiert, sprich ihre Winkelposition zur Exzenterwelle 8 beibehält. Figur 2A zeigt diese Situation schematisch anhand der beiden gleichläufigen Markierungen A, B.In Figure 2A the co-rotating adjusting mechanism 10 is not additionally controlled, so that a torque applied to its housing 19 on its input side is passed on to the machine element 16 via the further synchronous belt 15 fastened on its output side. This has according to Figure 2A As a result, the eccentric bushing 17 mounted within the connecting rod 9 rotates at the speed of the eccentric shaft 8, ie it maintains its angular position relative to the eccentric shaft 8. Figure 2A shows this situation schematically using the two markings A, B running in the same direction.

In Figur 2B hat der Verstellmechanismus 10 gegenüber Figur 2A eine Phasenverstellung 26 durchgeführt. Dies wird anhand der beiden nun verschoben zueinander dargestellten Markierungen A, B gezeigt. In Reaktion darauf hat sich das Maschinenelement 16 gegenüber der in Figur 2A gezeigten Position auf der Exzenterwelle 8 entsprechend der Phasenverstellung 26 verdreht. Dieses bewirkt, dass die an das Maschinenelement 16 gekoppelte Exzenterbuchse 17 ebenfalls eine um die Phasenverstellung 26 geänderte Winkelposition auf der Exzenterwelle 8 einnimmt, sodass sich daraus in Summe mit der Exzentrizität der Exzenterwelle 8 ein neuer Soll-Tamperhub 11 ergibt.In Figure 2B has the adjustment mechanism 10 opposite Figure 2A a phase adjustment 26 performed. This is shown on the basis of the two markings A, B that are now shown shifted relative to one another. In response to this, the machine element 16 has moved in relation to the Figure 2A shown position on the eccentric shaft 8 according to the phase adjustment 26 rotated. This has the effect that the eccentric bushing 17 coupled to the machine element 16 also assumes an angular position on the eccentric shaft 8 that has been changed by the phase adjustment 26 , so that the sum of the eccentricity of the eccentric shaft 8 results in a new target tamper stroke 11 .

Figur 2C zeigt eine erste Variante der in Figur 2 gezeigten Ausführungsform für eine Gesamthubverstellung am Verdichtungsaggregat 4. Damit ist gemeint, dass mehrere entlang der Exzenterwelle 8 positionierte Exzenterbuchsen 17 synchron mittels des Verstellmechanismus 10 verdrehbar sind. Figure 2C shows a first variant of the in figure 2 embodiment shown for a total stroke adjustment on the compression unit 4. This means that a plurality of eccentric bushings 17 positioned along the eccentric shaft 8 can be rotated synchronously by means of the adjustment mechanism 10.

In Figur 2C wird die Exzenterwelle 8 von einem Motor 20 angetrieben. Die in der Figur 2 dargestellten Riemenantriebe zum Koppeln der Exzenterwelle 8 mit dem Verstellmechanismus 10 und zum Koppeln des Verstellmechanismus 10 mit dem Maschinenelement 16 werden in den Figuren 2C und 2D durch Antriebsräder 21, 22 und Verstellräder 23, 24 ersetzt. Das Antriebsrad 21 ist drehfest auf der Exzenterwelle 8 gelagert. Das Antriebsrad 22 sitzt drehfest auf dem Gehäuse 19 des Verstellmechanismus 10. Der Verstellmechanismus 10 ist drehfest auf einer Welle 25 gelagert. Der Verstellmechanismus 10 ist dazu konfiguriert, zwischen dem auf seinem Gehäuse 19 montierten Antriebsrad 22 und dem an seiner Abriebseite gelagerten Verstellrad 23 die Phasenverstellung 26 durchzuführen. Die mittels des Verstellmechanismus 10 durchgeführte Phasenverstellung 26 wird vom Verstellrad 23 auf das Verstellrad 24 sowie das Maschinenelement 16 übertragen. Gemäß Figur 2C sind das Verstellrad 24 und das Maschinenelement 16 einteilig ausgebildet. Anhand einer Verdrehung des Maschinenelements 16 wird die in Figur 2C mittels einer Klauenkopplung 27 daran angeschlossene Exzenterbuchse 17 auf der Exzenterwelle 18 verdreht. Dadurch kommt eine Änderung des (Soll-)Tamperhubs 11 der Tamperleiste 6 zustande.In Figure 2C the eccentric shaft 8 is driven by a motor 20. The one in the figure 2 Belt drives shown for coupling the eccentric shaft 8 to the adjustment mechanism 10 and for coupling the adjustment mechanism 10 to the machine element 16 are in the Figures 2C and 2D replaced by drive wheels 21, 22 and adjusting wheels 23, 24. The drive wheel 21 is mounted on the eccentric shaft 8 in a torque-proof manner. The drive wheel 22 is seated on the housing 19 of the adjustment mechanism 10 in a rotationally fixed manner. The adjustment mechanism 10 is mounted on a shaft 25 in a rotationally fixed manner. The adjustment mechanism 10 is configured to carry out the phase adjustment 26 between the drive wheel 22 mounted on its housing 19 and the adjustment wheel 23 mounted on its wear side. The phase adjustment 26 carried out by means of the adjustment mechanism 10 is transmitted from the adjustment wheel 23 to the adjustment wheel 24 and the machine element 16 . According to Figure 2C the adjustment wheel 24 and the machine element 16 are formed in one piece. By twisting the machine element 16, the in Figure 2C twisted by means of a claw coupling 27 connected thereto eccentric bushing 17 on the eccentric shaft 18 . This results in a change in the (desired) tamper stroke 11 of the tamper bar 6 .

In Figur 2C verfügt der Verstellmechanismus 10 eine Sensoreinheit 28, die dazu konfiguriert ist, die Phasenverstellung 26 und somit auch die Winkelposition der Exzenterbuchse 17 auf der Exzenterwelle 8 zu erfassen. Die Sensoreinheit 28 übermittelt ihre Messergebnisse fortlaufend an eine mit ihr verbundene Steuereinrichtung 29. Der Steuereinrichtung 29 ist der Soll-Tamperhub 11 vorhaltbar, wobei die Steuereinrichtung 29 dazu konfiguriert ist, aus der gemessenen Phasenverstellung 26 einen Ist-Tamperhub zu berechnen und diesen mit dem vorgehaltenen Soll-Tamperhub 11 zu vergleichen, worauf basierend die Steuereinrichtung 29 ein Steuersignal 30 an den Verstellantrieb 12 des Verstellmechanismus 10 aussendet. Der Verstellantrieb 12, beispielsweise ein mitrotierender Synchronmotor M, kann dann basierend auf dem Steuersignal 20 die Phasenverstellung 26 anpassen.In Figure 2C the adjustment mechanism 10 has a sensor unit 28 which is configured to detect the phase adjustment 26 and thus also the angular position of the eccentric bushing 17 on the eccentric shaft 8 . The sensor unit 28 continuously transmits its measurement results to a control device 29 connected to it. The control device 29 can be provided with the setpoint tamper stroke 11, with the control device 29 being configured to calculate an actual tamper stroke from the measured phase adjustment 26 and to compare this with the provided To compare target tamper stroke 11, based on which the control device 29 sends a control signal 30 to the Adjustment drive 12 of the adjustment mechanism 10 emits. The adjustment drive 12, for example a co-rotating synchronous motor M, can then adjust the phase adjustment 26 based on the control signal 20.

Die Steuereinrichtung 29 kann einen Regelkreis RK aufweisen, der auf einen während des Betriebs des Straßenfertigers 1 gemessenen Prozessparameter P anspricht, worauf basierend eine dynamische Drehwinkelanpassung, sprich eine dynamische Phasenverstellung 26 zum Variieren des Tamperhubs 11 möglich ist. Das Funktionsprinzip der Steuereinrichtung 29 und/oder des Regelkreises RK ist in Zusammenhang mit allen folgenden Ausführungsformen ebenfalls anwendbar.The control device 29 can have a control circuit RK, which responds to a process parameter P measured during operation of the road finisher 1, on the basis of which a dynamic angle of rotation adjustment, ie a dynamic phase adjustment 26 for varying the tamper stroke 11, is possible. The functional principle of the control device 29 and/or the control circuit RK can also be used in connection with all of the following embodiments.

Figur 2C zeigt weiter, dass der Verstellmechanismus 10 an seiner Abtriebsseite eine Verstellwelle 31 aufweist. Gemäß Figur 2C ist das Verstellrad 23 drehfest auf der Verstellwelle 31 gelagert. Dadurch ist es möglich, die in Figur 2C mittels des Verstellmechanismus 10 eingestellte Phasenverstellung 26 über die Verstellwelle 31 synchron an einen anderen Aggregatsabschnitt 32 zu übertragen. Dort wird mittels weiterer Verstellräder 33, 34 eine am Aggregatsabschnitt 32 nicht gezeigte Exzenterbuchse in analoger Weise synchron zur Exzenterbuchse 17 verdreht. Figure 2C FIG. 12 further shows that the adjustment mechanism 10 has an adjustment shaft 31 on its output side. According to Figure 2C the adjustment wheel 23 is mounted on the adjustment shaft 31 in a rotationally fixed manner. This makes it possible to Figure 2C to transmit the phase adjustment 26 set by means of the adjustment mechanism 10 synchronously to another unit section 32 via the adjustment shaft 31 . There, by means of further adjustment wheels 33, 34, an eccentric bushing, which is not shown on the unit section 32, is rotated synchronously with the eccentric bushing 17 in an analogous manner.

Figur 2C zeigt somit, dass der Verstellmechanismus 10 über die Verstellwelle 31 zum synchronen Verstellen mehrerer entlang der Exzenterwelle 8 verdrehbar gelagerter Exzenterbuchsen 17 ausgebildet ist. Figure 2C thus shows that the adjustment mechanism 10 is designed via the adjustment shaft 31 for the synchronous adjustment of a plurality of eccentric bushings 17 that are rotatably mounted along the eccentric shaft 8 .

Figur 2D zeigt eine Vorrichtung, die zum separaten Verstellen mehrerer entlang der Exzenterwelle 8 verdrehbar gelagerter Exzenterbuchsen 17 ausgebildet ist. Mittels dieser Vorrichtung ist somit eine Einzelhubverstellung möglich. Figure 2D 12 shows a device which is designed for the separate adjustment of a plurality of eccentric bushings 17 which are rotatably mounted along the eccentric shaft 8 . A single stroke adjustment is thus possible by means of this device.

Gemäß Figur 2D umfasst das Verdichtungsaggregat 4 den Verstellmechanismus 10 zum Variieren des Soll-Tamperhubs 11 der Tamperleiste 6 und ferner einen zusätzlichen Verstellmechanismus 10' für den weiteren Aggregatsabschnitt 32. Der Verstellmechanismus 10' wird über die Welle 25 angetrieben und verfügt über eine Sensoreinheit 28', mittels welcher sich eine am Aggregatsabschnitt 32 eingestellte Phasenverstellung 26' messen lässt, auf Basis welcher die am Aggregatsabschnitt 32 gelagerte Exzenterbuchse 17' auf der Exzenterwelle 8 verdreht ist. Für eine unabhängige Betätigung der beiden Verstellräder 23, 33 sind diese drehbar auf der Welle 25 gelagert. Damit ist es möglich, an den jeweiligen Aggregatsabschnitten des Verdichtungsaggregats 4 unabhängig zueinander den Soll-Tamperhub 11, 11' für die jeweiligen Tamperleisten 6, 6' einzustellen.According to Figure 2D the compression unit 4 includes the adjustment mechanism 10 for varying the target tamper stroke 11 of the tamper strip 6 and also an additional adjustment mechanism 10' for the further unit section 32. The adjustment mechanism 10' is driven via the shaft 25 and has a sensor unit 28', by means of which a phase adjustment 26' set on the unit section 32 can be measured, on the basis of which the eccentric bushing 17' mounted on the unit section 32 is rotated on the eccentric shaft 8. For independent actuation of the two adjusting wheels 23, 33, they are rotatably mounted on the shaft 25. This makes it possible to set the desired tamper stroke 11, 11' for the respective tamper strips 6, 6' on the respective unit sections of the compression unit 4 independently of one another.

Figur 3 zeigt eine zweite Ausführungsform des Verdichtungsaggregats 4. Das Verdichtungsaggregat 4 verfügt über einen Verstellmechanismus 35. Der Verstellmechanismus 35 kann dazu angesteuert werden, das verdrehbar auf der Exzenterwelle 8 gelagerte Maschinenelement 16 derart zu verdrehen, dass sich der Soll-Tamperhub 11 an der Tamperleiste 6 einstellen lässt. figure 3 shows a second embodiment of the compression unit 4. The compression unit 4 has an adjustment mechanism 35. The adjustment mechanism 35 can be controlled to rotate the machine element 16, which is rotatably mounted on the eccentric shaft 8, in such a way that the target tamper stroke 11 is set on the tamper bar 6 leaves.

Der Verstellmechanismus 35 aus Figur 3 verfügt über ein Paar mitrotierender Umlenkrollen 36a, 36b. Die beiden Umlenkrollen 36a, 36b sind quer zur Exzenterwelle 8 hin und her verschiebbar gelagert, das zeigen die Doppelpfeile v1, v2. Der Verstellmechanismus 35 ist mittels drehfest gelagerter Antriebsscheiben 37, 38, 39 mittels daran geführter Synchronriemen 40, 41 mit der Drehbewegung der Exzenterwelle 8 verbunden. Die in Figur 3 separat dargestellten Antriebsscheiben 38, 39 könnten auch als ein Bauteil ausgeführt sein. Eine Verlagerung der beiden Umlenkrollen 36a, 36b quer zur Exzenterwelle 8 bewirkt, dass sich das über den Synchronriemen 41 mit dem Verstellmechanismus 35 verbundene Maschinenelement 16 auf der Exzenterwelle 8 verdreht. Die daran befestigte Exzenterbuchse 17 ändert dadurch ebenfalls ihre Winkelposition auf der Exzenterwelle 8, sodass der (Soll-)Tamperhub 11 verstellt wird.The adjustment mechanism 35 off figure 3 has a pair of co-rotating deflection rollers 36a, 36b. The two deflection rollers 36a, 36b are mounted so as to be displaceable back and forth transversely to the eccentric shaft 8, as shown by the double arrows v1, v2. The adjustment mechanism 35 is connected to the rotational movement of the eccentric shaft 8 by means of drive pulleys 37, 38, 39 mounted in a rotationally fixed manner by means of synchronous belts 40, 41 guided thereon. In the figure 3 Drive pulleys 38, 39 shown separately could also be designed as one component. A displacement of the two deflection rollers 36a, 36b transversely to the eccentric shaft 8 causes the machine element 16, which is connected to the adjustment mechanism 35 via the synchronous belt 41, to rotate on the eccentric shaft 8. The eccentric bushing 17 attached thereto also changes its angular position on the eccentric shaft 8 as a result, so that the (set) tamper stroke 11 is adjusted.

Das Funktionsprinzip der Phasenverstellung anhand des Verstellmechanismus 35 ist in der Figur 3A genauer dargestellt. In der linken Bildhälfte der Figur 3A sind die Antriebsscheibe 39 und das Maschinenelement 16 beide im Drehwinkel ϕ gelagert. Dafür nimmt der Verstellmechanismus 35 eine dementsprechende Position gemäß Figur 3A ein. Diese Positionierung der beiden mitrotierenden Umlenkrollen 36a, 36b resultiert in einem minimalen Tamperhub 11 für die Tamperleiste 6.The functional principle of the phase adjustment using the adjustment mechanism 35 is in Figure 3A shown in more detail. In the left half of the picture Figure 3A the drive pulley 39 and the machine element 16 are both mounted at the angle of rotation φ. For this, the adjusting mechanism 35 assumes a corresponding position according to FIG Figure 3A a. This positioning of the two co-rotating deflection rollers 36a, 36b results in a minimal tamper lift 11 for the tamper bar 6.

In der rechten Bildhälfte der Figur 3A wird die Einstellung des Verstellmechanismus 35 für einen maximalen Tamperhub 11 der Tamperleiste 6 gezeigt. In Reaktion auf eine Verlagerung R1,R1' , R2,R2' der beiden Umlenkrollen 36a, 36b hat sich für das Maschinenelement 16 ein neuer Drehwinkel ϕ' ergeben. Die Verlagerung der beiden mitrotierenden Umlenkrollen 36a, 36b quer zur sie antreibenden Exzenterwelle 8 bewirkt damit die Phasenverstellung 26 des Maschinenelements 16, wodurch sich die Exzenterbuchse 17 auf der Exzenterwelle 8 verdreht.In the right half of the picture Figure 3A the setting of the adjusting mechanism 35 for a maximum tamper stroke 11 of the tamper strip 6 is shown. In response to a shift R1 , R1 ' , R2 , R2 ' of the two deflection rollers 36a, 36b, a new angle of rotation φ′ has resulted for the machine element 16 . The displacement of the two co-rotating deflection rollers 36a, 36b transversely to the eccentric shaft 8 driving them thus causes the phase adjustment 26 of the machine element 16, as a result of which the eccentric bushing 17 on the eccentric shaft 8 rotates.

Figur 3B zeigt einen potentiellen Aufbau für den Verstellmechanismus 35. Der Verstellmechanismus 35 weist eine verstellbar gelagerte Kurvenscheibe 42 mit einer ersten Kurvenbahn 43 für die Umlenkrolle 36a und mit einer zweiten Kurvenbahn 44 für die Umlenkrolle 36b auf. Ferner verfügt der Verstellmechanismus 35 über eine stationär gelagerte Kurvenscheibe 45 mit einer Führungsbahn 46 für die Umlenkrollen 36a, 36b. Mittels einer Verlagerung der Kurvenscheibe 42 in Richtung E werden die beiden Umlenkrollen 36a, 36b in der Führungsbahn 46 gemeinsam in Richtung F verschoben. Durch das Verlagern der beiden Umlenkrollen 36a, 36b findet die Phasenverstellung 26 am Maschinenelement 16 statt, wodurch sich die Exzenterbuchse 17 auf der Exzenterwelle 8 verdreht. Figure 3B shows a potential structure for the adjustment mechanism 35. The adjustment mechanism 35 has an adjustably mounted cam 42 with a first cam track 43 for the deflection roller 36a and with a second cam track 44 for the deflection roller 36b. Furthermore, the adjustment mechanism 35 has a stationary cam 45 with a guide track 46 for the deflection rollers 36a, 36b. The two deflection rollers 36a, 36b in the guide track 46 are moved together in the direction F by means of a displacement of the cam disk 42 in direction E. By shifting the two deflection rollers 36a, 36b, the phase adjustment 26 takes place on the machine element 16, as a result of which the eccentric bushing 17 rotates on the eccentric shaft 8.

Weiter zeigt Figur 3B in ihrer rechten Bildhälfte ein Schnitt A-A. Die Umlenkrolle 36a ist auf einem Bolzen 47 gelagert. Zum Reduzieren eines Reibungswiderstands ist die Umlenkrolle 36a mittels eines Wälzlagers 48 auf dem Bolzen 47 befestigt.Next shows Figure 3B in the right half of the picture a section AA. The deflection roller 36a is mounted on a bolt 47 . To reduce frictional resistance, the deflection roller 36a is attached to the bolt 47 by means of a roller bearing 48 .

Die Figuren 3C und 3D zeigen Varianten des Verstellmechanismus 35, wobei die in Figur 3C gezeigte Variante zum synchronen Verstellen mehrerer entlang der Exzenterwelle 8 drehbar gelagerte Exzenterbuchsen 17 (Gesamthubverstellung) und wobei die in Figur 3D dargestellte Variante für eine Einzelhubverstellung an jeweiligen benachbarten Aggregatsabschnitten des Verdichtungsaggregats 4 konfiguriert sind.the Figures 3C and 3D show variants of the adjustment mechanism 35, with the in Figure 3C Variant shown for the synchronous adjustment of a plurality of eccentric bushings 17 rotatably mounted along the eccentric shaft 8 (overall stroke adjustment) and wherein the in Figure 3D shown variant are configured for a single stroke adjustment on respective adjacent unit sections of the compression unit 4.

In Figur 3C ist der Verstellmechanismus 35 zwischen dem Antriebsrad 37 und einem Verstellrad 50 gelagert. Eine mittels des Verstellmechanismus 35 in Figur 3C eingestellte Phasenverstellung 26 wirkt über den Synchronriemen 40 auf das Verstellrad 50, wobei die das Verstellrad 50 tragende Verstellwelle 31' das Drehmoment auf weitere Aggregatsabschnitte des Verdichtungsaggregats 4 synchron übertragen kann, um dort gelagerte Exzenterbuchsen entsprechend der Exzenterbuchse 17 aus Figur 3C einzustellen.In Figure 3C the adjustment mechanism 35 is mounted between the drive wheel 37 and an adjustment wheel 50 . A using the adjustment mechanism 35 in Figure 3C set phase adjustment 26 acts via the timing belt 40 on the adjusting wheel 50, wherein the adjusting wheel 50 carrying the adjusting shaft 31 'can transmit the torque synchronously to other unit sections of the compression unit 4 to eccentric bushings stored there corresponding to the eccentric bushing 17 Figure 3C set.

In Figur 3C wird die mittels des Verstellmechanismus 35 eingestellte Phasenverstellung 26 über die beiden Verstellräder 50, 51 und den Synchronriemen 41 auf das Maschinenelement 16 übertragen, welches auf der Exzenterwelle 8 einen dementsprechenden Drehwinkel ϕ einnimmt. Das Maschinenelement 16 ist über die Klauenkupplung 27 mit der Exzenterbuchse 17 verbunden. Die am Maschinenelement 16 eingestellte Phasenverstellung 26 wird damit auf die Exzenterbuchse 17 übertragen, worauf basierend der Soll-Tamperhub 11 einstellbar ist.In Figure 3C the phase adjustment 26 set by means of the adjustment mechanism 35 is transmitted via the two adjustment wheels 50, 51 and the timing belt 41 to the machine element 16, which occupies a corresponding angle of rotation φ on the eccentric shaft 8. The machine element 16 is connected to the eccentric bushing 17 via the claw coupling 27 . The phase adjustment 26 set on the machine element 16 is thus transmitted to the eccentric bushing 17, on the basis of which the target tamper stroke 11 can be set.

Die schematische Darstellung aus Figur 3D zeigt, dass der Verstellmechanismus 35 gemäß Figur 3 angeordnet ist, also zwischen dem Antriebsrad 39 und dem Maschinenelement 16 die Phasenverstellung 26 erzeugen kann. Gemäß Figur 3D kann für jeden Aggregatsabschnitt des Verdichtungsaggregats 4 ein separater Verstellmechanismus 35 angeordnet sein, sodass sich die jeweiligen Tamperhübe 11 der Aggregatsabschnitte unabhängig voneinander ansteuern lassen.The schematic diagram Figure 3D shows that the adjustment mechanism 35 according to figure 3 is arranged, so between the drive wheel 39 and the machine element 16, the phase adjustment 26 can generate. According to Figure 3D a separate adjustment mechanism 35 can be arranged for each unit section of the compression unit 4, so that the respective tamper strokes 11 of the unit sections can be controlled independently of one another.

Claims (15)

Straßenfertiger (1) mit einer Einbaubohle (2) zum Herstellen einer Einbauschicht (3), wobei die Einbaubohle (2) mindestens ein Verdichtungsaggregat (4) zum Vorverdichten eines der Einbaubohle (2) zugeführten Einbaumaterials (5) aufweist, wobei das Verdichtungsaggregat (4) mindestens eine Exzenterbuchse (17) aufweist, die auf einer sie tragenden Exzenterwelle (8) in einen gewünschten Drehwinkel verdrehbar gelagert ist, um dadurch stufenlos einen Soll-Tamperhub einer Tamperleiste (6) des Verdichtungsaggregats (4) einzustellen, dadurch gekennzeichnet, dass zum Verdrehen der Exzenterbuchse (17) auf der Exzenterwelle (8) ein zur Exzenterwelle (8) beabstandet gelagerter, zumindest teilweise mit einer Drehbewegung der Exzenterwelle (8) mitrotierender Verstellmechanismus (10, 35) ansteuerbar ist.Road finisher (1) with a screed (2) for producing a paving layer (3), the screed (2) having at least one compacting unit (4) for pre-compacting a paving material (5) fed to the screed (2), the compacting unit (4 ) has at least one eccentric bushing (17), which is mounted on an eccentric shaft (8) that carries it so that it can be rotated into a desired angle of rotation, in order to continuously adjust a target tamper stroke of a tamper bar (6) of the compression unit (4), characterized in that rotation of the eccentric bushing (17) on the eccentric shaft (8), an adjusting mechanism (10, 35) mounted at a distance from the eccentric shaft (8) and rotating at least partially with a rotary movement of the eccentric shaft (8) can be controlled. Straßenfertiger nach Anspruch 1, dadurch gekennzeichnet, dass der Verstellmechanismus (10, 35) mindestens einen mittels der Drehbewegung der Exzenterwelle (8) als solchen drehangetriebenen, zum Verdrehen der Exzenterbuchse (17) ansteuerbaren Verstellantrieb (12) und/oder mindestens ein mittels der Drehbewegung der Exzenterwelle (8) drehangetriebenes, zum Verdrehen der Exzenterbuchse (17) ansteuerbares Verstellgetriebe (13) umfasst.Road finisher according to Claim 1, characterized in that the adjustment mechanism (10, 35) has at least one adjustment drive (12) driven in rotation by the rotary movement of the eccentric shaft (8) as such and controllable for turning the eccentric bushing (17) and/or at least one by means of the rotary movement the eccentric shaft (8) includes rotary-driven, for rotating the eccentric bushing (17) controllable adjusting gear (13). Straßenfertiger nach Anspruch 2, dadurch gekennzeichnet, dass der mitrotierende Verstellantrieb (12) und/oder das mitrotierende Verstellgetriebe (13) dazu ansteuerbar ist, einen Drehwinkel (ϕ) eines auf der Exzenterwelle (8) verdrehbar gelagerten Maschinenelements (16) zu verstellen.Road finisher according to Claim 2, characterized in that the co-rotating adjusting drive (12) and/or the co-rotating adjusting gear (13) can be controlled to adjust a rotation angle (ϕ) of a machine element (16) rotatably mounted on the eccentric shaft (8). Straßenfertiger nach Anspruch 3, dadurch gekennzeichnet, dass das Maschinenelement (16) selbst die Exzenterbuchse (17) ausbildet oder mittels einer formschlüssigen Kupplung (27) mit der Exzenterbuchse (17) verbunden ist.Road finisher according to Claim 3, characterized in that the machine element (16) itself forms the eccentric bushing (17) or is connected to the eccentric bushing (17) by means of a positive coupling (27). Straßenfertiger nach einem der Ansprüche 3 oder 4, dadurch gekennzeichnet, dass mindestens ein weiteres Maschinenelement vorgesehen ist, das zum Übertragen einer Drehbewegung der Exzenterwelle (8) auf den Verstellantrieb (12) und/oder das Verstellgetriebe (13) ausgebildet ist.Road finisher according to one of Claims 3 or 4, characterized in that at least one further machine element is provided which is designed to transmit a rotational movement of the eccentric shaft (8) to the adjusting drive (12) and/or the adjusting gear (13). Straßenfertiger nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, dass während eines Betriebs des Verdichtungsaggregats (4) der Verstellantrieb (12) und/oder das Verstellgetriebe (13) mit derselben Drehzahl oder einer anderen Drehzahl wie die Exzenterwelle (8) drehangetrieben ist.Road finisher according to one of Claims 2 to 5, characterized in that during operation of the compaction unit (4) the adjusting drive (12) and/or the Adjusting gear (13) is driven in rotation at the same speed or at a different speed than the eccentric shaft (8). Straßenfertiger nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, dass der Verstellantrieb (12) und/oder das Verstellgetriebe (13) hydraulisch, elektrisch und/oder mechanisch betätigbar ist.Road finisher according to one of Claims 2 to 6, characterized in that the adjusting drive (12) and/or the adjusting gear (13) can be actuated hydraulically, electrically and/or mechanically. Straßenfertiger nach einem der Ansprüche 2 bis 7, dadurch gekennzeichnet, dass der Verstellantrieb (12) einen ansteuerbaren Servomotor (M) aufweist und/oder für das Verstellgetriebe (13) ein Servomotor (M) vorgesehen ist.Road finisher according to one of Claims 2 to 7, characterized in that the adjusting drive (12) has a controllable servo motor (M) and/or a servo motor (M) is provided for the adjusting gear (13). Straßenfertiger nach einem der Ansprüche 2 bis 8, dadurch gekennzeichnet, dass das Verstellgetriebe (13) als Kurvengetriebe ausgebildet ist und/oder ein Paar rotierender Umlenkrollen (36a, 36b) aufweist.Road finisher according to one of Claims 2 to 8, characterized in that the adjusting mechanism (13) is designed as a cam mechanism and/or has a pair of rotating deflection rollers (36a, 36b). Straßenfertiger nach Anspruch 9, dadurch gekennzeichnet, dass das Paar rotierender Umlenkrollen (36a, 36b) zum Verdrehen der Exzenterbuchse (17) auf der Exzenterwelle (8) quer zur Exzenterwelle (8) verschiebbar gelagert ist.Road finisher according to Claim 9, characterized in that the pair of rotating deflection rollers (36a, 36b) for rotating the eccentric bushing (17) is mounted on the eccentric shaft (8) so that it can be displaced transversely to the eccentric shaft (8). Straßenfertiger nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, dass der Verstellmechanismus (10, 35) zum synchronen Verstellen mehrerer entlang der Exzenterwelle (8) verdrehbar gelagerter Exzenterbuchsen (17) ausgebildet ist oder der Verstellmechanismus (10, 35) mehrere Verstellantriebe (12) und/oder Verstellgetriebe (13) zum separaten Verstellen mehrerer entlang der Exzenterwelle (8) verdrehbar gelagerter Exzenterbuchsen (17) umfasst.Road finisher according to one of Claims 2 to 10, characterized in that the adjustment mechanism (10, 35) is designed for the synchronous adjustment of a plurality of eccentric bushes (17) which are rotatably mounted along the eccentric shaft (8), or the adjustment mechanism (10, 35) has a plurality of adjustment drives (12 ) and/or adjusting gear (13) for separately adjusting a plurality of eccentric bushings (17) rotatably mounted along the eccentric shaft (8). Straßenfertiger nach einem der Ansprüche 2 bis 11, dadurch gekennzeichnet, dass der Verstellantrieb (12) und/oder das Verstellgetriebe (13) zum Einstellen des gewünschten Drehwinkels (ϕ) der Exzenterbuchse (17) mittels einer Steuereinrichtung (29) ansteuerbar ist.Road finisher according to one of Claims 2 to 11, characterized in that the adjusting drive (12) and/or the adjusting gear (13) can be controlled by means of a control device (29) to set the desired angle of rotation (ϕ) of the eccentric bushing (17). Straßenfertiger nach Anspruch 12, dadurch gekennzeichnet, dass die Steuereinrichtung (29) zur dynamischen Drehwinkelanpassung der Exzenterbuchse (17) mindestens einen auf mindestens einen während des Betriebs des Straßenfertigers (1) erfassbaren Prozessparameter (P) ansprechenden Regelkreis (RK) aufweist.Road finisher according to Claim 12, characterized in that the control device (29) for dynamic angle of rotation adjustment of the eccentric bushing (17) has at least one control circuit (RK) which responds to at least one process parameter (P) which can be detected during operation of the road finisher (1). Straßenfertiger nach einem der Ansprüche 2 bis 13, dadurch gekennzeichnet, dass der Verstellmechanismus (10, 35) mindestens eine Sensoreinheit (28) umfasst, die zum Erfassen eines eingestellten Drehwinkels (ϕ) der Exzenterbuchse (17) auf der sie tragenden Exzenterwelle (8) und/oder zum Erfassen eines Tamperhubs (11) der Tamperleiste (6) ausgebildet ist.Road finisher according to one of Claims 2 to 13, characterized in that the adjustment mechanism (10, 35) comprises at least one sensor unit (28) which, for detecting a set angle of rotation (ϕ) of the eccentric bushing (17) on the eccentric shaft (8) carrying it and/or is designed to detect a tamper stroke (11) of the tamper strip (6). Verfahren zur stufenlosen Tamperhubverstellung an einem Verdichtungsaggregat (4) eines Straßenfertigers (1), wobei zum Verstellen des Tamperhubs (11) mindestens eine Exzenterbuchse (17) auf einer sie lagernden Exzenterwelle (8) verdreht wird, dadurch gekennzeichnet, dass zum Verdrehen der Exzenterbuchse (17) auf der Exzenterwelle (8) ein zur Exzenterwelle (8) beabstandet gelagerter, zumindest teilweise mit einer Drehbewegung der Exzenterwelle (8) mitrotierender Verstellmechanismus (10, 35) angesteuert wird.Method for steplessly adjusting the tamper stroke on a compaction unit (4) of a road finisher (1), in which at least one eccentric bushing (17) on an eccentric shaft (8) supporting it is rotated in order to adjust the tamper stroke (11), characterized in that for rotating the eccentric bushing ( 17) on the eccentric shaft (8) an adjusting mechanism (10, 35) mounted at a distance from the eccentric shaft (8) and rotating at least partially with a rotational movement of the eccentric shaft (8) is controlled.
EP21151610.9A 2021-01-14 2021-01-14 Tamper stroke adjustment Active EP4029991B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
PL21151610.9T PL4029991T3 (en) 2021-01-14 2021-01-14 Tamper stroke adjustment
EP21151610.9A EP4029991B1 (en) 2021-01-14 2021-01-14 Tamper stroke adjustment
JP2022000936A JP7361808B2 (en) 2021-01-14 2022-01-06 Tamper stroke adjustment
BR102022000675-0A BR102022000675A2 (en) 2021-01-14 2022-01-13 ROAD FINISHING MACHINE WITH PAVEMENT COURSE ADJUSTMENT AND METHOD FOR A PAVEMENT COURSE ADJUSTMENT
CN202220107328.3U CN217266804U (en) 2021-01-14 2022-01-14 Road finishing machine
US17/575,687 US20220220675A1 (en) 2021-01-14 2022-01-14 Tamper stroke adjustment
CN202210056305.9A CN114763691A (en) 2021-01-14 2022-01-14 Adjustment of the tamping stroke

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21151610.9A EP4029991B1 (en) 2021-01-14 2021-01-14 Tamper stroke adjustment

Publications (2)

Publication Number Publication Date
EP4029991A1 true EP4029991A1 (en) 2022-07-20
EP4029991B1 EP4029991B1 (en) 2023-05-10

Family

ID=74184474

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21151610.9A Active EP4029991B1 (en) 2021-01-14 2021-01-14 Tamper stroke adjustment

Country Status (6)

Country Link
US (1) US20220220675A1 (en)
EP (1) EP4029991B1 (en)
JP (1) JP7361808B2 (en)
CN (2) CN114763691A (en)
BR (1) BR102022000675A2 (en)
PL (1) PL4029991T3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4029991B1 (en) 2021-01-14 2023-05-10 Joseph Vögele AG Tamper stroke adjustment

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1905899A2 (en) 2006-09-28 2008-04-02 Dynapac GmbH Tamping beam for a road finisher
CN101906750B (en) * 2010-08-05 2012-01-25 三一重工股份有限公司 Screed vibrator and paver
US8371770B1 (en) 2012-04-09 2013-02-12 Caterpillar Inc. Apparatus for tamping paving material
EP2599918A1 (en) 2011-12-01 2013-06-05 BOMAG GmbH Method and apparatus for amplitude adjustment of a stamping bar of a road finisher
EP2599919A1 (en) 2011-12-01 2013-06-05 BOMAG GmbH Device for the displacement of a tamping bar of a road finisher
WO2015179988A1 (en) * 2014-05-26 2015-12-03 Ammann Schweiz Ag Method for converting a rotary movement into a translatory movement, use of same and device for carrying same out
EP3249101A1 (en) * 2016-05-23 2017-11-29 Caterpillar Paving Products Inc. Tamper device of a paver screed
EP3138961B1 (en) 2009-11-20 2018-08-22 Joseph Vögele AG Paving screed

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB659423A (en) * 1949-02-02 1951-10-24 Albert Godenir Improvements in or relating to tamping machines
JPS4810985Y1 (en) * 1969-10-29 1973-03-24
SE420112B (en) * 1980-03-06 1981-09-14 Dynapac Maskin Ab VIBRATOR PLATOR MANOVERDON
US4427358A (en) 1982-01-15 1984-01-24 Stilwell Leo J Sectional concrete screed machine
DE3300092A1 (en) 1983-01-04 1984-07-12 Abg-Werke Gmbh, 3250 Hameln SCREED FOR A PAVER
US4828428A (en) * 1987-10-23 1989-05-09 Pav-Saver Manufacturing Company Double tamping bar vibratory screed
JPH02240306A (en) * 1989-03-13 1990-09-25 Nippon Hodo Co Ltd Bent surface finishing device
JP2865896B2 (en) * 1991-05-02 1999-03-08 株式会社建調神戸 Vibration generator
DE4307535A1 (en) * 1993-03-10 1994-09-15 Mueller Weingarten Maschf Stroke adjustment device for an eccentric drive, in particular for an eccentric press
JPH07116897A (en) 1993-10-26 1995-05-09 Sankyo Seisakusho:Kk Mechanical press
US5423628A (en) 1994-06-28 1995-06-13 M-B-W Inc. Winch construction for a vibratory concrete screed
DE19810406A1 (en) 1998-03-11 1999-09-16 Schuler Pressen Gmbh & Co Eccentric press with variable slide movement
US6551018B2 (en) * 2001-03-29 2003-04-22 Blaw-Knox Construction Equipment Corporation Apparatus for tamping paving material
US20020168226A1 (en) * 2001-05-14 2002-11-14 Feucht Timothy A. Automatic tamping mechanism control
CA2515660A1 (en) * 2004-08-11 2006-02-11 Dirk Heims Vibratory paving screed for a paver
JP4700481B2 (en) * 2005-11-22 2011-06-15 共栄テクニカ株式会社 Stroke variable device
PL2325391T3 (en) 2009-11-20 2013-08-30 Voegele Ag J Tamper with variable stroke
DE102009055950A1 (en) * 2009-11-27 2011-06-01 Hamm Ag Compactor for compacting grounds, has movable drum rotatable around drum axle, where drum part of drum comprises vibration generator that is supported at distance from drum axle in drum
PL2366831T3 (en) * 2010-03-18 2015-07-31 Voegele Ag J Method for controlling the process of applying a layer of road paving material and paver
EP2366832B1 (en) * 2010-03-18 2015-09-23 Joseph Vögele AG Method and paver for producing a compacted paved surface
CN102107180B (en) * 2010-11-22 2012-10-31 唐忠盛 Vibrating mechanism with stepless adjustable eccentric moment
CN102535314B (en) * 2012-01-18 2014-01-08 中铁三局集团有限公司 Power dynamic compaction tool
DE102013021494B4 (en) * 2012-12-28 2023-11-30 Bomag Gmbh Vibration plate with a vibration exciter
PL2905378T3 (en) * 2014-02-07 2017-05-31 Joseph Vögele AG Tamping device
DE102015016777A1 (en) * 2015-12-23 2017-06-29 Bomag Gmbh Ramming bar device of a screed, screed, paver and method for changing the stroke of a tamper strip device
US10246834B1 (en) * 2017-11-20 2019-04-02 Caterpillar Paving Products Inc. Tamper bar and wear plate for screed assembly of paving machine
DE102018128524B4 (en) * 2018-11-14 2022-09-22 Bayerische Motoren Werke Aktiengesellschaft Compression ratio changing device, reciprocating internal combustion engine and working device
CN110158422A (en) * 2019-06-27 2019-08-23 安徽劲帆建设有限公司 A kind of road asphalt paves head and its installation apparatus
EP4097300B1 (en) 2020-01-27 2024-05-01 Volvo Construction Equipment AB A tamper device for a screed of a working machine and a method for adjusting a stroke of a tamper device for a screed of a working machine
PL4029991T3 (en) 2021-01-14 2023-09-18 Joseph Vögele AG Tamper stroke adjustment

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1905899A2 (en) 2006-09-28 2008-04-02 Dynapac GmbH Tamping beam for a road finisher
EP3138961B1 (en) 2009-11-20 2018-08-22 Joseph Vögele AG Paving screed
CN101906750B (en) * 2010-08-05 2012-01-25 三一重工股份有限公司 Screed vibrator and paver
EP2599918A1 (en) 2011-12-01 2013-06-05 BOMAG GmbH Method and apparatus for amplitude adjustment of a stamping bar of a road finisher
EP2599919A1 (en) 2011-12-01 2013-06-05 BOMAG GmbH Device for the displacement of a tamping bar of a road finisher
US8371770B1 (en) 2012-04-09 2013-02-12 Caterpillar Inc. Apparatus for tamping paving material
WO2015179988A1 (en) * 2014-05-26 2015-12-03 Ammann Schweiz Ag Method for converting a rotary movement into a translatory movement, use of same and device for carrying same out
EP3249101A1 (en) * 2016-05-23 2017-11-29 Caterpillar Paving Products Inc. Tamper device of a paver screed

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4029991B1 (en) 2021-01-14 2023-05-10 Joseph Vögele AG Tamper stroke adjustment

Also Published As

Publication number Publication date
BR102022000675A2 (en) 2022-07-26
JP7361808B2 (en) 2023-10-16
PL4029991T3 (en) 2023-09-18
EP4029991B1 (en) 2023-05-10
JP2022109228A (en) 2022-07-27
CN114763691A (en) 2022-07-19
US20220220675A1 (en) 2022-07-14
CN217266804U (en) 2022-08-23

Similar Documents

Publication Publication Date Title
DE4103160C2 (en) Folding apparatus with an adjustable element, in particular folding jaws or arcuate segments, having a folding mechanism cylinder
DE3838314A1 (en) FOLDING VALVE CYLINDER FOR A ROLL ROTARY PRINTING MACHINE
EP2325391A1 (en) Tamper with variable stroke
EP0844976B1 (en) Device for pivoting a roller for a moving web
EP0453868B1 (en) Device to adjust the folding flaps of a folding flap cylinder
EP4029991B1 (en) Tamper stroke adjustment
WO2014063841A1 (en) Drive apparatus
EP1870617B1 (en) Actuating device for the transmission of a vehicle
EP2008800A1 (en) Drive device for a press, die cutter or moulding machine
DE1752276C3 (en) Device for the partial feeding of strip material or the like
EP2895869B1 (en) Combined block- and individual-drive device, in particular for pipetting channels
EP4029992B1 (en) Road finisher and method for tamper stroke adjustment
EP1981792B1 (en) Apparatus for treating a material web
EP0133287B1 (en) Apparatus for controlling the movements in a film processing machine
DE2545386C3 (en) Device for the oscillating driving of a continuous casting mold
DE3001596C2 (en) Crank gear
DE202007009064U1 (en) Drive device for an automatic press, punching machine or forming machine comprises a drive motor and a control gear that has two controller notches for driving an eccentric shaft and is switchable only when the machine is switched off
DE3925485C1 (en) Metal forming press system - incorporates feed stroke adjuster system with motor drive
DE2317759C3 (en) Control device for a continuously variable transmission for vehicles
EP1179408A1 (en) Driving mechanism for the movable platen of an injection moulding machine
DE2137743A1 (en) DEVICE FOR THE STEP-BY-STEP FEEDING OF A MATERIAL TAPE IN PRE-DETERMINABLE LENGTH INTO A MACHINE
DE2328376C3 (en) Bag making machine
DE2706351A1 (en) FEED DEVICE FOR THE MATERIAL INFEED FOR MACHINERY OR DEVICES
WO1992021601A1 (en) Plaiting machine
DE102004011690A1 (en) Oscillating drive for depositing mineral fibers on conveyor involves a stationary gear ring with an inner gear of half the diameter running round within it

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20210622

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20221207

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1566791

Country of ref document: AT

Kind code of ref document: T

Effective date: 20230515

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502021000649

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230524

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20230510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230911

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230810

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230910

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230811

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 502021000649

Country of ref document: DE

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

26 Opposition filed

Opponent name: VOLVO CONSTRUCTION EQUIPMENT ABG ALLGEMEINE BAUMA SCHINEN-GESELLSCHAFT MBH/VOLVO CONSTRUCTION EQUIP MENT AB/ABG ALLGEMEINE BAUMASCHINEN-GESELL

Effective date: 20240212

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

R26 Opposition filed (corrected)

Opponent name: VOLVO CONSTRUCTION EQUIPMENT ABG ALLGEMEINE BAUMA SCHINEN-GMBH/VOLVO CONSTRUCTION EQUIP MENT AB/ABG ALLGEMEINE BAUMASCHINEN-GMBH

Effective date: 20240212

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240124

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230510

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: PL

Payment date: 20240104

Year of fee payment: 4

Ref country code: IT

Payment date: 20240131

Year of fee payment: 4

Ref country code: FR

Payment date: 20240124

Year of fee payment: 4