EP2881516B1 - Compacteur routier - Google Patents

Compacteur routier Download PDF

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Publication number
EP2881516B1
EP2881516B1 EP14004040.3A EP14004040A EP2881516B1 EP 2881516 B1 EP2881516 B1 EP 2881516B1 EP 14004040 A EP14004040 A EP 14004040A EP 2881516 B1 EP2881516 B1 EP 2881516B1
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EP
European Patent Office
Prior art keywords
imbalance
shaft
mass
auxiliary
shafts
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.)
Active
Application number
EP14004040.3A
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German (de)
English (en)
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EP2881516A1 (fr
EP2881516B2 (fr
Inventor
Peter Erdmann
Niels Laugwitz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bomag GmbH and Co OHG
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Bomag GmbH and Co OHG
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/282—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows self-propelled, e.g. with an own traction-unit
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/282—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows self-propelled, e.g. with an own traction-unit
    • E01C19/283—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows self-propelled, e.g. with an own traction-unit pedestrian-controlled, e.g. with safety arrangements for operator
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/30—Tamping or vibrating apparatus other than rollers ; Devices for ramming individual paving elements
    • E01C19/34—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight
    • E01C19/35—Hand-held or hand-guided tools
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/30—Tamping or vibrating apparatus other than rollers ; Devices for ramming individual paving elements
    • E01C19/34—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight
    • E01C19/38—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight with means specifically for generating vibrations, e.g. vibrating plate compactors, immersion vibrators
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/026—Improving by compacting by rolling with rollers usable only for or specially adapted for soil compaction, e.g. sheepsfoot rollers

Definitions

  • the invention relates to a soil compaction machine, in particular a vibratory compactor comprising a vibration exciter with two juxtaposed parallel imbalance shafts and with a drive device for the imbalance shafts.
  • Construction machinery for soil compaction or soil compacting machines are used wherever an increase in the density of the substrate is desired. This applies in particular to the compaction of asphalt, earth, gravel, sand, etc. This is the case, for example, regularly in road, path and track construction, and this list is by no means to be understood as limiting.
  • ground compaction machines have a vibration means, via which the ground can be introduced compacting load pulses into the surface of the ground.
  • a vibration means usually comprises a vibration exciter and a ground contact device.
  • vibratory compactors vibrating plates, with a plate as ground contact device, and vibrating rollers, with a hollow-cylindrical drum as ground contact device, are particularly to be mentioned, which are particularly preferred developments of the present invention.
  • Such vibratory rollers can be self-propelled or hand-guided. Specifically, it may in particular be, for example, so-called compactors or tandem rollers.
  • the vibration exciters used are specially developed for this application "compaction of the ground surface" and optimally adapted to the structural conditions and the intended use of construction machinery for soil compaction. This concerns in particular the interpretation of the Here usable vibration exciter with regard to their operating variables, such as vibration frequency, vibration amplitude, etc.
  • a vibratory roller is known in the bandage, a vibration generator is installed, which has two parallel counter-rotating unbalanced shafts. These are arranged opposite each other with respect to the center axis of the bandage in the bandage and connected to each other via a mechanical coupling in the form of a gear transmission.
  • the drive of the two imbalance shafts via a motor which acts on one of the imbalance shafts, while the other imbalance shaft is rotated via the gear transmission in rotation.
  • a vibratory plate and a hand-guided soil compaction roller are for example from EP 2 743 402 A2 known.
  • phase position of the two imbalance shafts is changed by means of an adjusting device to each other.
  • the change of the phase position is effected by an adjustment of the angular position of an imbalance shaft with respect to the other imbalance shaft.
  • a hydraulically axially displaceable adjusting spiral is present at the respective imbalance shaft, with which an axial control movement is converted into a rotational movement.
  • the invention has for its object to provide a soil compaction machine of the type mentioned, in which the vibration exciter with relatively simple technical means allows a large number of excitation functions.
  • the drive means of the vibration exciter comprises two motors, of which a first motor with the first imbalance shaft and a second motor with the second imbalance shaft are in operative connection.
  • the invention has the advantage that no mechanical or hydraulic coupling between the two unbalanced shafts is present, and that instead each unbalanced shaft can be controlled independently via the associated motor.
  • both the rotational speed and the phase angle of each unbalanced shaft can be adjusted independently.
  • the rotational speed and the phase angle of each imbalance shaft can be changed individually.
  • the directions of rotation of the two imbalance shafts can be changed independently of each other. It is also possible to stop one of the two imbalance shafts while the other imbalance shaft is rotating. In this way, a large number of excitation functions is made possible.
  • Operating mode 1 In operating mode 1, the first imbalance shaft runs at a constant speed, while the second imbalance shaft is stationary or runs at a maximum of half the speed of the first imbalance shaft. The result is a centrifugal force amplitude, which circulates the vibration exciter in a circle. Due to the significantly lower rotational speed of the second imbalance shaft, its centrifugal force is so low that it has no noticeable influence on the movement behavior and in particular the exciter vibration of the entire vibration exciter. Since the centrifugal force is proportional to the square of the rotational speed, the centrifugal force initiated by the second imbalance shaft or by the imbalance mass arranged thereon only corresponds to a maximum of one quarter of the centrifugal force of the first imbalance shaft.
  • the slow rotation of the second imbalance shaft has the advantage that vibration bearings, in which the unbalanced shafts are usually stored, can build up a lubricating film and are not damaged in the state by the vibration of the first imbalance shaft.
  • Operating mode 2 In operating mode 2, the first imbalance shaft is running at constant speed, while the second imbalance shaft is phase synchronous and substantially identical Speed follows in the same direction of rotation, ie with the same sign of the rotational speed. This results in a centrifugal force amplitude, which circulates in a circle. The resulting amplitude is twice as high as in operating mode 1.
  • Operating mode 3 In operating mode 3, the first imbalance shaft runs at constant speed, while the second imbalance shaft follows the same imbalance in synchronism with the first imbalance shaft, ie with the same rotational speed sign, but offset by a phase angle of 180 °. The centrifugal forces of the two unbalanced shafts are exactly opposite during the entire operating time. It thus creates no vibration movement. If the two imbalance shafts are not arranged coaxially but offset parallel to one another, however, a changing oscillation moment arises. This oscillation torque causes a torsional vibration of the vibration exciter.
  • Operating mode 4 In operating mode 4, the first imbalance shaft runs at constant speed, the second imbalance shaft runs in phase with the speed of the first imbalance shaft, but in the opposite direction. The result is a (perpendicular to the plane of extension of the imbalance waves) directed vibration with the same maximum amplitude as in operation mode. 2
  • Operating mode 5 In operating mode 5, the first imbalance shaft runs at a constant speed, while the second imbalance shaft runs synchronously with the first imbalance shaft, but in the opposite direction of rotation and with a phase rotated by 180 °. This produces a directional oscillation with the same maximum amplitude as in operating mode 4, but the resulting oscillation direction and in particular the oscillation vector are rotated by 90 °.
  • the drive means of the vibration exciter is designed such that it is in operative connection with the two imbalance shafts that the rotational speed of the first imbalance shaft and / or the rotational speed of the second imbalance shaft between a positive and a negative rotational speed is variable.
  • This switching between a positive and a negative rotational speed which of course also the setting of a rotational speed with the value zero is possible, thus allowing a rotation reversal of the respective imbalance shaft, so that at two unbalanced shafts a synchronization, but also a counter run of the unbalanced shafts can be adjusted.
  • any intermediate position between the operating modes 4 and 5 can be set.
  • a vertically directed to the ground vibration allows a maximum compression effect, wherein upon rotation of the oscillation direction in the horizontal compression effect is successively reduced.
  • any other phase position can also be set between the operating modes described above.
  • the effective compaction performance can be adapted to the requirements.
  • the resulting vibration is a combination of circular (so-called undirected oscillation) and oscillation.
  • the first and the second motor of the vibration exciter each have a first and a second drive shaft, which are respectively operatively connected via a transmission, in particular a gear transmission, with the first and the second unbalanced shaft.
  • a transmission in particular a gear transmission
  • the first and the second drive shaft are arranged coaxially with each other.
  • the two motors are aligned on a common axis, wherein they are preferably arranged in particular each side of the two parallel unbalanced shafts.
  • the drive shafts are thus located on a common axis of symmetry, to which, offset relative to the left and right in a plane, the first and the second imbalance shaft are arranged. In this way, the power transmission from the drive shaft to the respective unbalanced shaft is very easily realized by a pair of gears or the like gear, said gears are arranged on the drive shaft and the respective imbalance shaft and mesh with each other.
  • the first and the second imbalance shaft are preferably arranged relative to one another in the direction of their axes of rotation such that the centrifugal force resultant of the two imbalance shafts lie at least approximately in a common plane. 'At least approximately in one plane' should in this case be understood to mean that the two levels are less than 100 mm or a maximum of 5% of the total width of the bandage in particular differ. In this way, the loads acting on the vibration exciter are very easy, especially in a vibration exciter housing, ablatable.
  • the oscillation exciter of the soil compaction machine preferably comprises at least one sensor device which is designed to detect the angular position of the first and / or the second imbalance shaft.
  • the sensor data are preferably transmitted to the actuating means, which initiate corresponding steps for setting the respective operating modes and in particular can selectively control the respective motor.
  • the actuating means which initiate corresponding steps for setting the respective operating modes and in particular can selectively control the respective motor.
  • At least one first additional imbalance mass rotatable about its axis of rotation and / or on the second imbalance shaft at least one second additional imbalance mass rotatable about its axis of rotation are arranged on the first imbalance shaft of the vibration generator, wherein the first additional imbalance mass is over at least a first coupling element is rotatably coupled to the second imbalance shaft or the second additional imbalance mass is rotationally coupled via at least one second coupling element with the first imbalance shaft.
  • the respective first and second unbalanced shafts associated drive means and in particular the respective first and second motors drive via suitable coupling elements respectively arranged on the parallel shafts further additional imbalance masses at.
  • the vibration direction can be adjusted in a simple manner.
  • At least one imbalance shaft and the additional imbalance mass arranged thereon are designed such that the imbalance formed by at least one imbalance element of the imbalance shaft and the additional imbalance formed by the additional imbalance mass are equal.
  • driving this one imbalance shaft is sufficient to already generate a directional vibration. In this way, a directional vibration can be generated by means of a single unbalance shaft.
  • the first and the second additional imbalance mass are formed identically so that the additional imbalances formed by them on the respective unbalanced shafts are equal.
  • the first coupling element has at least one transmission element, with at least two actively meshed, in particular meshing gears, namely a first drive gear, which is operatively connected to the first imbalance shaft, and at least one second output gear, with the second additional imbalance mass in Is active compound, and / or the second coupling element at least one transmission element, with at least two interacting with each other and in particular meshing gears, namely a second drive gear, which is in operative connection with the second imbalance shaft, and at least one first output gear, with the first additional imbalance mass is in operative connection.
  • a very simple and space-saving arrangement can be achieved.
  • the first and / or the second additional imbalance mass have at least one hollow cylindrical shell which is arranged on the associated imbalance shaft such that it at least partially encloses an imbalance element arranged thereon.
  • the hollow cylindrical shell for example, be stored with its two U-legs on the imbalance shaft so that it rotates upon rotation about the imbalance element of the imbalance shaft.
  • the first and / or the second additional unbalanced mass may be formed differently geometrically, preferably always designed so that it surrounds the unbalance element arranged on the respective unbalanced shaft or is arranged on the imbalance shaft, that they rotates around this imbalance element.
  • Fig. 1a shows a side view of running as a self-propelled vibratory roller 1 machine for soil compaction.
  • the vibratory roller 1 has a front end 8 with a cab 42 and a rear end 3 with a diesel engine, which are connected via an articulation 41.
  • a bandage 4 ground contact device
  • a bandage support 2 is arranged at the front of the car 8 and the rear 3 .
  • At least one of the bandages 4 is provided with a travel drive.
  • each bandage 4 is inside with a vibration exciter 6 ( Fig. 2 . 3 . 8th ) provided with which the bandages 4 are vibrated, which are delivered to the vibratory compaction to the ground.
  • Fig. 1a shows a side view of running as a self-propelled vibratory roller 1 machine for soil compaction.
  • the vibratory roller 1 has a front end 8 with a cab 42 and a rear end 3 with a diesel engine, which are connected via an articulation 41.
  • FIG. 1b exemplifies the basic structure of a soil compacting machine type vibrating plate.
  • Essential elements here are a drive motor, a compression plate 50 (ground contact device) with a vibration exciter (not visible) and a guide bracket 51st
  • Fig. 1 c finally shows the basic structure of a soil compaction machine of the type hand-guided vibratory roller, which in the present embodiment comprises two bandages 4 with vibration exciters (not visible).
  • a drive motor and a guide bracket 51 is also present here, with which an operator can direct the hand-held vibratory roller in the working mode.
  • FIG. 2 A first embodiment of a vibration generator 6, as he in particular according to the invention for one of the in the FIGS. 1a to 1c is provided as shown in FIG Fig. 2 shown.
  • the vibration exciter 6 is in terms of its structural design and the possible operating parameters with him specifically for use in a generic soil compaction machine, in particular one according to the FIGS. 1a to 1c , educated.
  • the bandage 4 has a hollow cylinder 5 and on each end face a Ronde 7, with which the bandage 4 by means of bearings 33 on two stub axles 9, 9 'are rotatably mounted.
  • the vibration exciter 6 has two identically constructed eccentric devices 13, 13 'and a drive device, which consists of a first and a second motor 12, 12' for the first eccentric device 13 and the second eccentric device 13 '.
  • the first and second motors 12, 12 ' are independent so that they can be operated and controlled separately. In this way, the first and the second eccentric device 13, 13 'can be independently controlled and operated.
  • the first and second motors 12, 12 ' are designed as hydraulic motors.
  • Each of the two eccentric devices 13, 13 ' has a first or second drive shaft 14, 14', which is driven by the first and second motor 12, 12 ', and a first and second unbalanced shaft 10, 10' with a first and second second imbalance mass 11, 11 ', which run parallel to each other and to the axis of rotation A RW of the bandage 4.
  • the two unbalanced shafts 10, 10 ' are located with respect to the axis of rotation A RW of the bandage 4 and at the same distance from this.
  • the first eccentric device 13 will first be described below.
  • the first drive shaft 14 is connected to the first motor 12, arranged outside the cavity of the bandage 4 at the first end face of the bandage and attached to one of the bandage supports 2.
  • the first drive shaft 14 is mounted rotatably coaxially therewith and guided from the outside into the interior of the housing 32.
  • the first drive shaft 14 is connected via a first gear from a first gear pair 34, 36 with the first imbalance shaft 10 and mounted on the housing 32 via bearings 15.
  • the first unbalanced shaft 10 can be set in rotary motion about its axis of rotation A R1 .
  • the second motor 12 'of the second eccentric device 13' is connected to the second drive shaft 14 'and arranged in mirror image to the first motor 12 in front of the second end face of the bandage 4 on the associated bandage support 2 (not shown).
  • the second drive shaft 14' is rotatably mounted coaxially therewith and guided from the outside into the interior of the housing 32.
  • the second drive shaft 14 ' is connected via a second gear from a second gear pair 34', 36 'to the second imbalance shaft 10' and mounted on the housing 32 via bearings 15 '.
  • the second imbalance shaft 10' can be set in rotary motion about its axis of rotation A R2 .
  • the first and the second motor 12, 12 allow both the rotational speeds of the respective associated imbalance shaft 10, 10' as well as their direction of rotation and adjust the phase position.
  • the imbalance masses 11, 11 'of the imbalance shafts 10, 10' are the same size, so that the centrifugal force F 1 and F 2 acting at an identical rotational speed are also equal.
  • the two unbalanced shafts 10, 10 ' are arranged relative to each other along their axes of rotation A R1 and A R2 such that the centrifugal force-resultant F 1 and F 2 act at least approximately in a plane E extending along the in Fig.2 extends shown line.
  • first imbalance shaft 10 can be actively driven via the first motor 12, or only the second imbalance shaft 10 'can be actively driven via the second motor 12', while the respective other imbalance shafts is stopped.
  • first motor 12 is controlled so that the first imbalance shaft 10 runs at a constant speed, while the second motor 12 'is stationary or only rotates at the maximum half speed of the first motor 12, F 1 is proportional to the first due to the centrifugal force-resultant F 1 Imbalance mass 11 and the rotational speed of a circulating pathogen amplitude. Since the rotational speed of the unbalanced shafts 10, 10 'has an exponential influence on the exciter amplitude, in such an operating mode, the slow rotation of the second imbalance shaft 10' is negligible. However, this slow rotation causes lubrication of the bearing 33, which significantly increases the service life of the vibration generator 6.
  • the operating mode described here corresponds to the operating mode 1 described in the introduction.
  • Fig. 3 The magnitude and direction of the resulting unbalance force of the vibrator 6 and the resulting torques according to operating mode 1 are in Fig. 3 illustrated.
  • the direction of the imbalance force resulting in each phase position is indicated by arrow 22 and the different magnitudes of the imbalance forces on the first and second imbalance shafts 10 and 10 'are designated by points 23 and 23', respectively.
  • both motors 12, 12 ' are operated at the same speed and phase-synchronously, so that a synchronous rotation of the unbalanced shafts 10, 10' results with the same rotational speed and in particular with a rotational speed with the same sign.
  • an exciter oscillation which circulates in a circle, wherein the amplitude is twice as large as in the previously described operating mode 1.
  • the centrifugal force resulting F 1 and F 2 are added here.
  • the operating mode 2 is in Fig. 4 illustrated, wherein like reference numerals are used for equal sizes.
  • Fig. 6 illustrates the operating mode 4.
  • both a vector adjustment and an amplitude adjustment of the excitation oscillation can be carried out by a targeted control of the two motors 12, 12 '.
  • Fig. 8 shows a second embodiment of a vibration exciter 6 'in a cutting guide as shown in Fig. 1 is shown.
  • the vibration exciter 6 'shown here is according to the first embodiment according to Fig. 2 extended by some components and adjustment options. Identical parts are provided with the same reference numerals. To the description is so far on Fig. 2 directed.
  • additional imbalance masses 16, 16' namely a first additional imbalance mass 16 and a second additional imbalance mass 16 'are arranged.
  • These additional imbalance masses 16, 16 'are here designed as hollow bodies in the form of sectors of hollow cylindrical shells, which are rotatably supported by legs 38 on the respective imbalance shaft 10, 10'.
  • the additional imbalance masses 16, 16 'are formed and arranged such that they can rotate around the first or second imbalance mass 11, 11' without obstructing rotation of the first or second imbalance mass 11, 11 '.
  • the additional imbalance masses 16, 16 ' are rotationally coupled in a crosswise manner to the imbalance shafts 10', 10. This means that the first additional imbalance mass 16 arranged on the first imbalance shaft 10 is connected to the second imbalance shaft 10 '.
  • the second additional imbalance mass 16 'mounted on the second imbalance shaft 10' is connected to the first imbalance shaft 10.
  • the second additional imbalance mass 16 ' also rotates.
  • the first additional imbalance mass 16 rotates together with the second imbalance mass 11'.
  • first or second mechanical coupling elements 18, 18 ' are present, which transmit the respective rotational forces.
  • first coupling element 18 couples the first imbalance shaft 10 with the second additional imbalance mass 16 'and the second coupling element 18' couples the second imbalance shaft 10 'with the first additional imbalance mass 16.
  • the respective coupling elements 18, 18' are also here again as one Combination of drive gears 17, 17 'and driven gears 19, 19' formed, which are in Kämm together.
  • the first imbalance mass 11 and the first additional imbalance mass 16 are driven via the first motor 12.
  • the second imbalance mass 11 'and the second additional imbalance mass 16' are driven by the second motor 12 '. If both motors 12, 12 'operated at the same speed, depending on the phase position of the unbalance directional vibration with greater or smaller amplitude can be achieved.
  • the largest amplitude is defined by the following ratio: U 1 + U Z 1 + U 2 + U Z 2 .
  • each unbalanced shaft 10, 10 'so there are two imbalances 11, 16 and 11', 16 ', whose relative positions can be changed to each other.
  • the unbalance can be continuously adjusted from the maximum value to zero.
  • the bearings of the unbalanced shafts 10, 10 ' are relieved, whereby higher rotational speeds of the unbalanced shafts 10, 10' are possible.
  • the storage of additional imbalance masses 16, 16 'on the unbalanced shafts 10 and 10' is not critical, since only the adjustment movements are transmitted here. It occur regardless of the vibration speed only low relative velocities during a change in the phase position.
  • the vibration exciter 6 ' a further mode of operation is possible.
  • the motors 12, 12 ' are driven in such a way that the imbalance shafts 10, 10' rotate in the same direction of rotation and with the same sign of the respective rotational speed.
  • the first imbalance mass 11 rotates in opposite directions to the first additional imbalance mass 16 and the second imbalance mass 11 'in opposite directions to the second additional imbalance mass 16'.
  • a directional vibration is generated with a constant oscillation amplitude.
  • the unbalanced shafts 10, 39 and 10 ', 39' of each pair of unbalanced shafts according to Fig. 9 are aligned so that the imbalance waves of a pair circulate in phase.
  • the third and the fourth imbalance shaft 39, 39 'at the same distance from the axis of rotation A RW of the bandage 4 and diametrically to the axis of rotation A RW of the bandage 4 are arranged.
  • the planes spanned by the axes of rotation of each pair of unbalanced shafts are parallel to each other.
  • the rotational axis A R1 of the first imbalance shaft 10 and the rotational axis A R3 of the third imbalance shaft clamp a first plane parallel to the plane passing from the rotational axis A R2 of the second imbalance shaft 10 'and the rotational axis A R4 of the fourth imbalance shaft 39 'is spanned.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Architecture (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Soil Sciences (AREA)
  • Agronomy & Crop Science (AREA)
  • Environmental & Geological Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • General Engineering & Computer Science (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Road Paving Machines (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)

Claims (9)

  1. Engin de compactage du sol, en particulier compacteur vibrant, comprenant un générateur de vibrations destiné à générer différents types de vibrations, comprenant deux arbres parallèles à balourd (10, 10') situés adjacents entre eux et un dispositif d'entraînement pour les arbres à balourd (10, 10'),
    caractérisé en ce que
    le dispositif d'entraînement comprend deux moteurs (12, 12'), un premier moteur (12) qui est opérationnellement relié au premier arbre à balourd (10) et un second moteur (12') qui est opérationnellement relié au second arbre à balourd (10').
  2. Engin de compactage du sol selon la revendication 1,
    caractérisé en ce que
    le premier et le second moteurs (12, 12') comprennent chacun un premier et un second arbres d'entraînement (14, 14'), qui sont chacun opérationnellement reliés, au moyen d'un élément d'engrenage (30, 30'), et en particulier en s'engrenant, avec le premier et le second arbres à balourd (10, 10'), respectivement.
  3. Engin de compactage du sol selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le premier et le second arbres d'entraînement (14, 14') sont disposés coaxialement l'un par rapport à l'autre.
  4. Engin de compactage du sol selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le premier et le second arbres à balourd (10, 10') sont disposés l'un par rapport à l'autre dans la direction de leurs axes de rotation (AR1 , AR2) de telle sorte les forces centrifuges résultantes (F1, F2) des deux arbres à balourd (10, 10') se trouvent, au moins approximativement, dans un plan commun (E).
  5. Engin de compactage du sol selon l'une quelconque des revendications précédentes,
    caractérisé enceque
    au moins une première masse de balourd auxiliaire (16) pouvant tourner sur son axe de rotation (AR1,) est disposée sur le premier arbre à balourd (10) et/ou au moins une seconde masse de balourd auxiliaire (16') pouvant tourner sur son axe de rotation (AR2) est disposée sur le second arbre à balourd (10'), la première masse de balourd auxiliaire (16) étant couplée rotativement, au moyen d'au moins un premier élément de couplage (18), au second arbre à balourd (10'), et la seconde masse de balourd auxiliaire (16') étant couplée rotativement, au moyen d'au moins un second élément de couplage (18'), au premier arbre à balourd (10), respectivement.
  6. Engin de compactage du sol selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    au moins un arbre à balourd (10, 10') et la masse de balourd auxiliaire (16, 16') disposée sur celui-ci, sont mis en oeuvre de telle sorte que le balourd (U1, U2) formé par au moins une masse de balourd (11, 11') de l'arbre à balourd (10, 10') et le balourd auxiliaire (Uz1,, Uz2) formé par la masse de balourd auxiliaire soient de taille égale.
  7. Engin de compactage du sol selon l'une quelconque des revendications précédentes,
    caractérisé enceque
    la première et la seconde masses de balourd auxiliaires (16, 16') sont mises en oeuvre de manière identique de telle sorte que les balourds auxiliaires ((Uz1, Uz2) formés par elles sur les arbres de balourd respectifs (10, 10') soient de taille égale.
  8. Engin de compactage du sol selon l'une quelconque des revendications précédentes,
    caractérisé enceque
    le premier élément de couplage (18) possède au moins un élément d'engrenage ayant au moins deux roues dentées (17, 19), qui sont opérationnellement reliées l'une à l'autre, en particulier en s'engrenant, à savoir une première roue dentée menante (17), qui est opérationnellement reliée au premier arbre à balourd (10), et au moins une seconde roue dentée menée (19), qui est opérationnellement reliée à la seconde masse de balourd auxiliaire (16'), et/ou
    le second élément de couplage (18') possède au moins un élément d'engrenage ayant au moins deux roues dentées (17', 19'), qui sont opérationnellement reliées l'une à l'autre, et en particulier en s'engrenant, à savoir une seconde roue dentée menante (17'), qui est opérationnellement reliée au second arbre à balourd (10'), et au moins une première roue dentée menée (19'), qui est opérationnellement reliée à la première masse de balourd auxiliaire (16).
  9. Engin de compactage du sol selon l'une quelconque des revendications précédentes,
    caractérisé enceque
    la première et/ou la seconde masse de balourd auxiliaire (16, 16') comprend/ comprennent au moins une coque de cylindre creux, qui est disposée sur l'arbre à balourd associé (10, 10') de telle façon qu'elle entoure, au moins partiellement, une masse de balourd (11, 11') qui y est placée.
EP14004040.3A 2013-12-03 2014-12-01 Compacteur routier Active EP2881516B2 (fr)

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DE102013020690.1A DE102013020690A1 (de) 2013-12-03 2013-12-03 Schwingungserreger für einen Vibrationsverdichter sowie Baumaschine mit einem solchen Schwingungserreger

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DE102020132973A1 (de) 2020-12-10 2022-06-15 Hamm Ag Verdichterwalze für einen Bodenverdichter

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DE102016109888A1 (de) * 2016-05-30 2017-11-30 Hamm Ag Bodenverdichter und Verfahren zum Betreiben eines Bodenverdichters
CN107130498B (zh) * 2017-06-22 2022-11-04 合肥永安绿地工程机械有限公司 一种振动状态可调的压路机激振器
EA039914B1 (ru) 2018-02-19 2022-03-28 Деррик Корпорейшн Эксцентриковая вибрационная система и способ
EP3765672B1 (fr) * 2018-03-14 2022-02-09 Generator.Technik.Systeme GmbH & Co. Kg Système de dispositif compacteur et procédé de commande d'un système de dispositif compacteur
DE102018006441A1 (de) * 2018-08-14 2020-02-20 Bomag Gmbh Bodenverdichtungsmaschine sowie verfahren zum betrieb einer oszillationsbandage einer bodenverdichtungsmaschine
US10889944B2 (en) * 2018-08-28 2021-01-12 Caterpillar Paving Products Inc. Control system for controlling operation of compaction systems of a paving machine
DE102019113947A1 (de) * 2019-05-08 2020-11-12 Liebherr-Components Biberach Gmbh Schwingungserzeuger sowie Baumaschine mit einem solchen Schwingungserzeuger
US10851942B1 (en) * 2019-05-30 2020-12-01 Caterpillar Paving Products Inc. Vibratory system lubrication remaining useful life
RU2734533C1 (ru) * 2020-02-26 2020-10-20 Федеральное государственное бюджетное образовательное учреждение высшего образования "Тихоокеанский государственный университет" Вибрационный валец дорожного катка
WO2022010999A1 (fr) * 2020-07-07 2022-01-13 Milwaukee Electric Tool Corporation Compacteur à plaque
WO2022011008A1 (fr) * 2020-07-07 2022-01-13 Milwaukee Electric Tool Corporation Compacteur à plaque
RU2752916C1 (ru) * 2020-12-21 2021-08-11 Федеральное государственное бюджетное образовательное учреждение высшего образования "Тихоокеанский государственный университет" Вибрационный валец дорожного катка
RU205972U1 (ru) * 2021-02-11 2021-08-12 Федеральное государственное бюджетное образовательное учреждение высшего образования "Тихоокеанский государственный университет" Вибрационный валец дорожного катка
EP4380037A1 (fr) * 2023-08-08 2024-06-05 Volvo Construction Equipment AB Système informatique pour détecter et contrôler une position relative de deux arbres excentriques rotatifs, véhicule comprenant un tel système informatique, methode et moyen de stockage de programme informatique correspondant
CN117419882B (zh) * 2023-10-24 2024-06-25 青岛连山铸造有限公司 一种桥梁支座抗震性能测试平台及测试方法

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EP0092014A1 (fr) 1982-04-21 1983-10-26 Losenhausen Maschinenbau AG& Co Kommanditgesellschaft Dispositif de réglage pour générateur de vibrations à masses non équilibrées
EP0704575B1 (fr) 1994-09-29 1998-07-22 BOMAG GmbH Méthode et dispositif pour le compactage dynamique du sol
EP0980292B1 (fr) 1997-05-05 2002-10-30 Wacker-Werke Gmbh & Co. Kg Generateur de vibrations orientees
EP0951949A1 (fr) 1998-04-22 1999-10-27 International Construction Equipment B.V. Procedé et dispositif pour entraíner un objet
CN1407179A (zh) 2001-09-07 2003-04-02 孙祖望 振幅无级可调的复合作用振动压路机
EP1481739A1 (fr) 2003-05-30 2004-12-01 Kandt Special Crane Equipment B.V. Un vibrateur avec deux paires de deux poids excentrés
DE102005029434A1 (de) 2005-06-24 2006-12-28 Wacker Construction Equipment Ag Vibrationsplatte mit individuell einstellbaren Schwingungserregern
WO2008000535A1 (fr) 2006-06-26 2008-01-03 Gebr. Bellmer Gmbh Maschinenfabrik Dispositif pour générer des vibrations
CN101864772B (zh) 2010-06-24 2012-11-21 河海大学常州校区 一种自动调节偏心力矩和打击频率的振动打桩头
WO2013113819A1 (fr) 2012-02-01 2013-08-08 Hamm Ag Cylindre compacteur pour engin de compactage de sol
CN102605706A (zh) 2012-03-23 2012-07-25 徐工集团工程机械股份有限公司科技分公司 一种压路机、其压实装置及压实控制方法
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Publication number Priority date Publication date Assignee Title
DE102017122371A1 (de) * 2017-09-27 2019-03-28 Hamm Ag Verdichterwalze
DE102020132973A1 (de) 2020-12-10 2022-06-15 Hamm Ag Verdichterwalze für einen Bodenverdichter

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US20150152606A1 (en) 2015-06-04
EP2881516A1 (fr) 2015-06-10
US9334613B2 (en) 2016-05-10
JP2015110898A (ja) 2015-06-18
CN104695310A (zh) 2015-06-10
DE102013020690A1 (de) 2015-06-03
EP2881516B2 (fr) 2020-03-25
JP6487684B2 (ja) 2019-03-20
CN104695310B (zh) 2019-11-15

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