EP2881516B2 - Bodenverdichtungsmaschine - Google Patents

Bodenverdichtungsmaschine Download PDF

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Publication number
EP2881516B2
EP2881516B2 EP14004040.3A EP14004040A EP2881516B2 EP 2881516 B2 EP2881516 B2 EP 2881516B2 EP 14004040 A EP14004040 A EP 14004040A EP 2881516 B2 EP2881516 B2 EP 2881516B2
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EP
European Patent Office
Prior art keywords
imbalance
unbalanced
shaft
mass
auxiliary
Prior art date
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Active
Application number
EP14004040.3A
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German (de)
English (en)
French (fr)
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EP2881516A1 (de
EP2881516B1 (de
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
Original Assignee
Bomag GmbH and Co OHG
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Application filed by Bomag GmbH and Co OHG filed Critical 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 compacting machine, in particular a vibration compactor, which comprises a vibration exciter with two parallel unbalanced shafts lying next to one another and with a drive device for the unbalanced shafts.
  • soil compaction machines are used wherever an increase in the density of the subsoil is desired. This applies in particular to the compaction of asphalt, soil, gravel, sand etc. This is regularly the case, for example, in road, path and route construction, although this list is in no way to be understood as limiting.
  • soil compaction machines often have a vibration means, via which load impulses that compact the subsurface can be introduced into the surface of the subsurface.
  • a vibration means usually comprises a vibration exciter and a ground contact device.
  • vibration compressors include, in particular, vibrating plates with a plate as the bottom contact device and vibrating rollers with a hollow cylindrical bandage as the bottom contact device, which are particularly preferred developments of the present invention.
  • Such vibratory rollers can be self-propelled or hand-held. Specifically, it can be, for example, so-called single drum rollers or tandem rollers.
  • the vibration exciters used here have been specially developed for this "compaction of the subsoil" application and are optimally matched to the structural conditions and the intended use of construction machinery for soil compaction. This applies in particular to the design of the vibration exciters that can be used here with regard to their operating variables, such as vibration frequency, vibration amplitude, etc.
  • the vibration exciters used in such soil compaction machines are used to generate alternating load impulses for compacting a subsoil, which are introduced into the subsoil via the respective soil contact device.
  • a vibratory roller is known, in the drum of which a vibration exciter is installed, which has two parallel, counter-rotating unbalanced shafts. These are arranged opposite one another in the bandage with respect to the center axis of the bandage and are connected to one another via a mechanical coupling in the form of a gear transmission.
  • the two unbalanced shafts are driven by a motor that acts on one of the unbalanced shafts, while the other unbalanced shaft is set in rotation by the gear mechanism.
  • a vibrating plate and a hand-held soil compaction roller are, for example, from the EP 2 743 402 A2 known.
  • the WO 2013/113819 A1 discloses a compressor roller with an oscillating mass arrangement and a vibrating mass arrangement, each with its own drive motor.
  • the CN 1407179 discloses a vibration exciter with a drive, two unbalanced shafts, each with an unbalanced mass and an unbalanced mass adjustable relative thereto, the phase position being adjusted with the aid of a planetary gear.
  • the parallel arrangement of the two unbalanced shafts makes it possible to generate directional vibrations by changing the phase position of the two unbalanced shafts relative to one another by means of an adjusting device.
  • the phase position is changed by adjusting the angular position of one unbalanced shaft in relation to the other unbalanced shaft.
  • axially displaceable adjusting helix is available, with which an axial control movement is converted into a rotary movement.
  • the invention has for its object to provide a soil compaction machine of the type mentioned, in which the vibration exciter enables a large number of excitation functions with relatively simple technical means.
  • the invention has the advantage that there is no mechanical or hydraulic coupling between the two unbalanced shafts, and instead each unbalanced shaft can be controlled independently via the associated motor. Both the rotational speed and the phase position of each unbalanced shaft can thus be set independently. The speed of rotation and the phase position of each unbalanced shaft can be changed individually. In addition to setting a positive or negative phase shift, the directions of rotation of the two unbalanced shafts can also be changed independently of one another. It is also possible to stop one of the two unbalanced shafts while the other unbalanced shaft is rotating. This enables a large number of excitation functions.
  • Electric or hydraulic motors are particularly suitable as motors for the vibration exciter.
  • the vibration exciter of the soil compaction machine according to the invention enables a large number of different operating modes with regard to vibration amplitude, vibration direction and type of vibration.
  • the following operating modes can be carried out with the vibration exciter of the soil compaction machine according to the invention:
  • Operating mode 1 In operating mode 1, the first unbalanced shaft runs at a constant speed, while the second unbalanced shaft stands still or at maximum half the speed of the first unbalanced shaft. The result is a centrifugal force amplitude that circles the exciter in a circle. Due to the considerably lower speed of the second unbalanced shaft, its centrifugal force is so low that it has no noticeable influence on the movement behavior and in particular the excitation vibration of the entire vibration exciter.
  • the centrifugal force initiated by the second unbalanced shaft or by the unbalanced mass arranged thereon only corresponds to a maximum of a quarter of the centrifugal force of the first unbalanced shaft.
  • the slow rotation of the second unbalanced 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 by the vibration of the first unbalanced shaft when stationary.
  • Operating mode 2 In operating mode 2, the first unbalanced shaft runs at a constant speed, while the second unbalanced shaft follows in phase synchronization and at an essentially identical speed in the same direction of rotation, ie with the same sign Rotation speed. This creates a centrifugal force amplitude that rotates in a circle. The resulting amplitude is twice as high as in operating mode 1.
  • Operating mode 3 In operating mode 3, the first unbalanced shaft runs at a constant speed, while the second unbalanced shaft follows in synchronism with the first unbalanced shaft in the same direction of rotation, i.e. 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. There is no vibration movement. If the two unbalanced shafts are not arranged coaxially, but offset parallel to each other, an alternating oscillation moment arises. This oscillation moment causes a torsional vibration of the vibration exciter.
  • Operating mode 4 In operating mode 4, the first unbalanced shaft runs at a constant speed, the second unbalanced shaft runs in phase synchronization with the speed of the first unbalanced shaft, but in the opposite direction. A vibration (perpendicular to the plane of extension of the unbalanced shafts) is created with the same maximum amplitude as in operating mode 2.
  • Operating mode 5 In operating mode 5, the first unbalanced shaft runs at a constant speed, while the second unbalanced shaft runs synchronously with the first unbalanced shaft, but in the opposite direction of rotation and with a phase rotated by 180 °. The result is a directional vibration with the same maximum amplitude as in operating mode 4, but the resulting direction of vibration and in particular the vibration vector are rotated by 90 °.
  • the drive device of the vibration exciter is designed in such a way that it is in operative connection with the two unbalanced shafts that the rotational speed of the first unbalanced shaft and / or the rotational speed of the second unbalanced shaft can be changed between a positive and a negative rotational speed.
  • This switching between a positive and a negative rotational speed whereby it is of course also possible to set a rotational speed with the value equal to zero, therefore allows the respective unbalanced shaft to be reversed in rotation, so that two unbalanced shafts can be set to run in unison, but also in opposite directions.
  • any intermediate position between the operating modes 4 and 5 can be set.
  • a vibration directed vertically to the ground enables a maximum compaction effect, this compaction effect being successively reduced when the direction of oscillation is turned horizontally.
  • phase position can also be set between the previously described operating modes. This means that the effective compaction performance can be adapted to the requirements.
  • the resulting vibration is a combination of circular (so-called undirected vibration) and oscillation.
  • the first and the second motor of the vibration exciter each have a first and a second drive shaft, each of which is operatively connected to the first and the second unbalanced shaft via a gear, in particular a gear transmission.
  • a gear in particular a gear transmission.
  • the first and the second drive shaft are preferably arranged coaxially to one another.
  • the two motors are also aligned on a common axis, wherein they are preferably in particular arranged to the side of the two parallel unbalanced shafts.
  • the drive shafts therefore lie on a common axis of symmetry, to which the first and second unbalanced shafts are arranged, offset relative to the left and right in one plane. In this way, the power transmission from the drive shaft to the associated unbalanced shaft can be realized very simply by means of a pair of gearwheels or the like gear, these gearwheels being arranged on the drive shaft and the respective unbalanced shaft and meshing with one another.
  • the first and the second unbalanced shaft are preferably arranged relative to one another in the direction of their axes of rotation such that the centrifugal force results of the two unbalanced shafts lie at least approximately in a common plane. 'At least approximately in one plane' should be understood here so that the two planes deviate from each other by less than 100 mm or a maximum of 5% of the total width, in particular of the bandage. In this way, the loads acting on the vibration exciter can be removed very easily, in particular in a vibration exciter housing.
  • the vibration 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 unbalanced shaft.
  • a direct conclusion about the prevailing unbalance loads and, in particular, their direction can be drawn from the angular position, the sensor data preferably being transmitted to the actuating means, which can initiate appropriate steps for setting the respective operating modes and in particular can specifically control the respective motor.
  • the phase position can be deduced very simply and, if necessary, the phase can be adjusted. It is also possible to provide corresponding speed sensors which detect the speed of the unbalanced shafts either directly or via the angular position and their change and thus allow conclusions to be drawn about the respective operating modes.
  • At least one first additional unbalanced mass rotatable about its axis of rotation and / or on the second unbalanced shaft at least one second additional unbalanced mass rotatable about its rotational axis are arranged on the first unbalanced shaft of the vibration exciter, the first additional unbalanced mass being at least a first coupling element is rotationally coupled to the second unbalanced shaft or the second additional unbalanced mass is rotationally coupled to the first unbalanced shaft via at least one second coupling element.
  • the second additional unbalanced mass arranged on the second unbalanced shaft also rotates as a function of the first unbalanced shaft, even if the second unbalanced shaft is stationary.
  • the first additional unbalanced mass arranged on the first unbalanced shaft rotates depending on the rotation of the second unbalanced shaft.
  • the drive device assigned to the respective first and second unbalanced shafts and in particular the respective first and second motors drive Suitable additional coupling elements each arranged on the parallel shafts on additional additional unbalance masses.
  • the direction of vibration can be set in a simple manner.
  • At least one unbalanced shaft and the additional unbalanced mass arranged thereon are preferably designed such that the unbalance formed by at least one unbalanced element of the unbalanced shaft and the additional unbalanced mass formed by the additional unbalanced mass are of the same size.
  • driving this one unbalanced shaft is sufficient to generate a directional vibration. In this way, a directional vibration can be generated using a single unbalanced shaft.
  • the first and the second additional unbalance masses are preferably of identical design such that the additional unbalances formed by them on the respective unbalance shafts are of the same size.
  • unbalance shafts which are also identical or provided with identical unbalances, this results in a vibration exciter with a very wide range of setting and operating mode.
  • the first coupling element has at least one gear element, with at least two gearwheels that are in operative connection, in particular meshing gears, namely a first drive gearwheel that is operatively connected to the first unbalanced shaft and at least one second output gearwheel that is connected to the second additional unbalanced mass in There is an operative connection, and / or the second coupling element has at least one gear element, with at least two gearwheels which are in operative connection and in particular meshing, namely a second drive gearwheel which is operatively connected to the second unbalanced shaft, and at least a first output gearwheel which is connected to the the first additional unbalanced mass is in operative connection.
  • a very simple and space-saving arrangement can be achieved.
  • the first and / or the second additional unbalance mass have at least one hollow cylinder shell which is arranged on the associated unbalanced shaft in such a way that it at least partially surrounds an unbalance element arranged thereon.
  • the hollow cylinder shell can be supported on the unbalanced shaft with its two U-legs, so that it rotates around the unbalanced element of the unbalanced shaft during rotation.
  • the first and / or the second additional unbalanced mass can of course be designed differently in a correspondingly geometrical manner, wherein it is preferably always designed such that it surrounds the unbalance element arranged on the respective unbalanced shaft or is arranged on the unbalanced shaft in such a way that it rotates around this unbalance element.
  • Fig. 1a shows a side view of a machine designed as a self-propelled vibratory roller for soil compaction.
  • the vibratory roller 1 has a front carriage 8 with a driver's cab 42 and a rear carriage 3 with a diesel engine, which are connected via an articulated joint 41.
  • a bandage 4 (ground contact device) is arranged on the front carriage 8 and on the rear carriage 3 via a bandage support 2. At least one of the bandages 4 is provided with a travel drive.
  • each bandage 4 is provided with a vibration exciter 6 ( Fig. 2 , 3rd , 8th ) are provided, with which the bandages 4 are set into vibrations, which are emitted to the substrate for vibration compaction.
  • Fig. 2 , 3rd , 8th are provided, with which the bandages 4 are set into vibrations, which are emitted to the substrate for vibration compaction.
  • FIG. 1b illustrates an example of the basic structure of a soil compacting machine of the vibrating plate type.
  • Essential elements here are a drive motor, a compression plate 50 (ground contact device) with a vibration exciter (not visible) and a guide bracket 51.
  • Fig. 1c finally shows the basic structure of a soil compacting machine of the type hand-held vibratory roller, which in the present exemplary embodiment comprises two bandages 4 with vibration exciters (not visible).
  • FIG. 2 A first embodiment of a vibration exciter 6, not according to the invention, as it is according to the invention in particular for one of the in the Figures 1a to 1c is provided as an example is shown in Fig. 2 shown.
  • the vibration exciter 6 is specifically for use in a generic soil compaction machine, in particular one according to the Figures 1a to 1c , educated.
  • the bandage 4 has a hollow cylinder 5 and a round plate 7 on each end face, with which the bandage 4 is rotatably supported by means of bearings 33 on two stub axles 9, 9 '.
  • the stub axles 9, 9 ' are mounted on opposite drum supports 2 (not shown).
  • the vibration exciter 6 On the stub axles 9, 9 ', a housing 32 of the vibration exciter 6 is also arranged in the cavity of the bandage 4.
  • 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 second eccentric devices 13, 13 'can also be controlled and operated independently of one another.
  • 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 or second motor 12, 12 ', and a first or second unbalanced shaft 10, 10' with a first or second unbalanced mass 11, 11 ', which run parallel to each other and to the axis of rotation A RW of the drum 4.
  • the two unbalanced shafts 10, 10 ' lie opposite each other with respect to the axis of rotation A RW of the bandage 4 and at the same distance from it.
  • the first drive shaft 14 is connected to the first motor 12, is arranged outside the cavity of the bandage 4 on the first end face of the bandage and is attached to one of the bandage supports 2. Within the first axle stub 9, the first drive shaft 14 is rotatably mounted coaxially to the latter and is guided into the interior of the housing 32 from the outside.
  • the first drive shaft 14 is connected to the first unbalanced shaft 10 via a first gear from a first gear pair 34, 36 and is mounted on the housing 32 via bearings 15.
  • the first unbalanced shaft 10 can be set in rotation about its axis of rotation A R1 by the first motor 12.
  • 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 drum 4 on the associated drum support 2 (not shown).
  • the second drive shaft 14' is rotatably mounted coaxially with the latter and is guided into the interior of the housing 32 from the outside.
  • the second drive shaft 14 ' is connected to the second unbalanced shaft 10' via a second gear from a second pair of gearwheels 34 ', 36' and is mounted on the housing 32 via bearings 15 '.
  • the second unbalanced shaft 10 ' can be rotated about its axis of rotation A R2 by the second motor 12'.
  • the unbalanced masses 11, 11 'of the unbalanced shafts 10, 10' are equal, so that the forces acting at an identical rotational speed Fliehkraftresultierenden F 1 and F 2 are also equal.
  • the two unbalanced shafts 10, 10 ' are arranged with respect to one another along their axes of rotation A R1 and A R2 in such a way that the centrifugal forces resulting F 1 and F 2 act at least approximately in a plane E which extends along the axis in FIG Fig. 2 line shown extends.
  • first unbalanced shaft 10 can be actively driven via the first motor 12 or only the second unbalanced shaft 10 'can be actively driven via the second motor 12' while the other unbalanced shaft is stopped.
  • first motor 12 is controlled so that the first unbalanced shaft 10 runs at a constant speed, while the second motor 12 'is stationary or only rotates at the maximum half the speed of the first motor 12, resulting from the centrifugal force resulting F 1 proportional to the first unbalanced mass 11 and their rotational speed a rotating excitation amplitude.
  • the operating mode described here corresponds to operating mode 1 described in the introduction.
  • FIG Fig. 3 The size and direction of the resulting unbalance force of the vibration exciter 6 and the resulting torques according to operating mode 1 are shown in FIG Fig. 3 illustrated.
  • the direction of the unbalance force resulting in each phase position is indicated by arrow 22 and the different sizes of the unbalance forces on the first and second unbalance shafts 10 and 10 'are designated by points 23 and 23'.
  • both motors 12, 12 ' are operated at the same speed and in phase synchronization, so that a synchronous rotation of the unbalanced shafts 10, 10' results with the same rotation speed and in particular with a rotation speed with the same sign.
  • an excitation oscillation arises in a circular manner, the amplitude of which is twice as large as in the previously described operating mode 1.
  • the centrifugal forces resulting F 1 and F 2 add up here.
  • Operating mode 2 is in Fig. 4 illustrated, the same reference numerals being used for the same sizes.
  • the first motor 12 is operated at a constant speed, while the second motor 12 'is operated in phase synchronization and at a rotational speed such that the unbalanced shafts 10, 10' rotate in opposite directions.
  • the embodiment shown here creates a vertical one directional vibration with the same maximum amplitude as it has already occurred in operating mode 2.
  • Fig. 6 illustrates operating mode 4.
  • both a vector adjustment and an amplitude adjustment of the excitation oscillation can thus 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 section as shown in FIG Fig. 1 is shown.
  • the vibration exciter 6 'shown here is in comparison with the first embodiment Fig. 2 expanded by some components and setting options.
  • the same parts are provided with the same reference numerals. To this extent, the description is based on Fig. 2 referred.
  • additional unbalanced masses 16, 16 ' namely a first additional unbalanced mass 16 and a second additional unbalanced mass 16', are arranged on the unbalanced shafts 10, 10 '.
  • These additional unbalanced masses 16, 16 ' are designed here as hollow bodies in the form of sectors of hollow cylindrical shells, which are rotatably supported by legs 38 on the respective unbalanced shaft 10, 10'.
  • the additional unbalanced masses 16, 16 ' are shaped and arranged in such a way that they can rotate around the first and second unbalanced masses 11, 11' without impeding rotation of the first and second unbalanced masses 11, 11 '.
  • the additional unbalanced masses 16, 16 ' are cross-coupled with the unbalanced shafts 10', 10 in a rotary manner.
  • the second additional unbalanced mass 16 'mounted on the second unbalanced shaft 10' is connected to the first unbalanced shaft 10.
  • the first imbalance shaft 10 rotates
  • the second additional imbalance mass 16 ' rotates in addition to the first imbalance element 11.
  • the first additional unbalanced mass 16 rotates together with the second unbalanced 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 unbalanced shaft 10 to the second additional unbalanced mass 16 'and the second coupling element 18' connects the second unbalanced shaft 10 'to the first additional unbalanced 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 mesh with each other.
  • the unbalanced shafts 10, 10 'driven by the motors 12, 12' drive the additional unbalanced masses 16, 16 'arranged on the other unbalanced shaft 10, 10' via the additional coupling elements 18, 18 '.
  • the unbalanced masses 11, 11 'and additional unbalanced masses 16, 16' arranged on each unbalanced shaft 10, 10 ' are of the same size in this embodiment, so that the total unbalances resulting from them are of the same size on each unbalanced shaft 10, 10'.
  • the unbalanced mass 11 on the first unbalanced shaft 10 causes (in terms of amount) the same unbalance U 1 as the first additional unbalanced mass 16 (unbalance U Z1 ).
  • driving a single motor 12, 12 'or an unbalanced shaft 10, 10' is sufficient to generate a directional vibration.
  • the total unbalance can be changed. For particularly high speeds, e.g. the total unbalance can be reduced in order to reduce loads on the vibration bearings.
  • Fig. 8 the first unbalanced mass 11 and the first additional unbalanced mass 16 are driven by the first motor 12.
  • the second unbalanced mass 11 'and the second additional unbalanced mass 16' are driven by the second motor 12 '. If both motors 12, 12 'are operated at the same speed, depending on the phase position of the unbalance, a directional vibration with a larger or smaller amplitude can be achieved.
  • the greatest amplitude is defined as follows: U 1 + U Z. 1 + U 2nd + U Z. 2nd , the smallest amplitude by the ratio: U 1 - U Z. 1 + U 2nd - U Z. 2nd .
  • Another operating mode is also possible with the second exemplary embodiment of the vibration exciter 6 '.
  • the motors 12, 12 ' are driven in such a way that the unbalanced shafts 10, 10' rotate in the same direction of rotation and with the same sign of the respective rotational speed.
  • the first unbalanced mass 11 rotates in the opposite direction to the first additional unbalanced mass 16 and the second unbalanced mass 11 'rotates in the opposite direction to the second additional unbalanced mass 16'.
  • a directional vibration with a constant vibration amplitude is generated.
  • a third and fourth unbalanced shaft 39 and 39 ' are arranged parallel to the first and second unbalanced shaft 10, 10'.
  • the first and the third unbalanced shaft (10, 39) are coupled via a mechanical gear in the form of a gear 40 which meshes with the gear 36 on the first unbalanced shaft 10.
  • the second unbalanced shaft 10 ' is connected to the fourth unbalanced shaft 39' via a gear 40 'which meshes with the gear 36' on the second unbalanced shaft 10 '.
  • the first embodiment according to Fig. 1 instead of two independent unbalanced shafts there are two independent pairs of unbalanced shafts, each of which is driven by its own motor 12, 12 '.
  • the unbalanced shafts 10, 39 and 10 ', 39', respectively, of each pair of unbalanced shafts Fig. 9 are aligned in such a way that the unbalanced shafts of a pair rotate in phase.
  • the third and fourth unbalanced shafts 39, 39 ' are arranged 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.
  • the planes spanned by the axes of rotation of each pair of unbalanced shafts run parallel to one another.
  • the axis of rotation A R1 of the first unbalanced shaft 10 and the axis of rotation A R3 of the third unbalanced shaft span a first plane that runs parallel to the plane that is from the axis of rotation A R2 of the second unbalanced shaft 10 ′ and the axis of rotation A R4 of the fourth unbalanced shaft 39 'is stretched.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Architecture (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Soil Sciences (AREA)
  • Agronomy & Crop Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (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)
EP14004040.3A 2013-12-03 2014-12-01 Bodenverdichtungsmaschine Active EP2881516B2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013020690.1A DE102013020690A1 (de) 2013-12-03 2013-12-03 Schwingungserreger für einen Vibrationsverdichter sowie Baumaschine mit einem solchen Schwingungserreger

Publications (3)

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EP2881516A1 EP2881516A1 (de) 2015-06-10
EP2881516B1 EP2881516B1 (de) 2016-08-31
EP2881516B2 true EP2881516B2 (de) 2020-03-25

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EP14004040.3A Active EP2881516B2 (de) 2013-12-03 2014-12-01 Bodenverdichtungsmaschine

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US (1) US9334613B2 (ja)
EP (1) EP2881516B2 (ja)
JP (1) JP6487684B2 (ja)
CN (1) CN104695310B (ja)
DE (1) DE102013020690A1 (ja)

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DE102016109888A1 (de) * 2016-05-30 2017-11-30 Hamm Ag Bodenverdichter und Verfahren zum Betreiben eines Bodenverdichters
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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
US20220010506A1 (en) * 2020-07-07 2022-01-13 Milwaukee Electric Tool Corporation Plate compactor
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RU2752916C1 (ru) * 2020-12-21 2021-08-11 Федеральное государственное бюджетное образовательное учреждение высшего образования "Тихоокеанский государственный университет" Вибрационный валец дорожного катка
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JP6487684B2 (ja) 2019-03-20
CN104695310B (zh) 2019-11-15
JP2015110898A (ja) 2015-06-18
CN104695310A (zh) 2015-06-10
EP2881516A1 (de) 2015-06-10
DE102013020690A1 (de) 2015-06-03
US20150152606A1 (en) 2015-06-04
EP2881516B1 (de) 2016-08-31
US9334613B2 (en) 2016-05-10

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