Classifications

• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
  • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
  • E02D3/02—Improving by compacting
  • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
  • E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses
• • 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

Definitions

• the invention relates to a vibration plate according to the preamble of claim 1.
• Vibratory plates for soil compaction are well known. They basically consist of a ground contact plate acted upon by a vibration exciter and a drive that drives the vibration exciter.
• the drive is assigned to an upper mass, while the vibration exciter and the ground contact plate are considered to belong to a lower mass.
• the upper mass and the lower mass are movably connected to one another via a spring device. This is intended to achieve a vibration decoupling of the upper mass in order to protect the drive and the operator guiding the vibration plate on the upper mass.
• the operator When repairing road surfaces, the operator must ensure that the transition between the existing asphalt layer and the newly applied asphalt layer that is now to be compacted is as smooth as possible. To do this, the operator tries to achieve particularly strong compaction of the fresh asphalt in the transition area. For this purpose, it has been found in practice to tilt the vibrating plate, i. H. to place it on an edge of the ground contact plate. Often this work is supported by a second operator.
• the spring device described above, connecting the upper mass to the lower mass is usually implemented in the form of rubber buffers which are arranged between the upper mass and the lower mass. Such rubber buffers allow a relative movement between the upper mass and the lower mass in any spatial direction.
• the ground contact plate is tilted, i. H. the lower mass, in relation to the upper mass. This tilting movement is not prevented by the rubber buffers and is only limited in its extent by the spring action of the rubber buffers.
• V-belt drive ie from a V-belt pulley arranged on the drive via a V-belt to a V-belt pulley provided on the vibration exciter. If a canting or transverse displacement occurs between the upper mass and the lower mass, the V-belt pulleys of the drive and vibration exciter no longer align, which leads to considerable stress on the V-belt running between them and thus to a shortened service life. The result is more frequent interruptions in vibration work and the associated costs.
• the invention has for its object to provide a vibration plate in which misalignment between the V-belt pulleys of the upper and lower mass due to tilt or transverse offset positions between the upper and lower mass can be avoided or reduced.
• a vibration plate according to the invention is characterized in that, in addition to the spring device connecting the upper mass to the lower mass, a stabilizing device is provided for guiding the lower mass as it moves relative to the upper mass.
• the stabilization device thus ensures that the upper mass and the lower mass can only assume predefined relative positions specified by the stabilization device.
• the stabilization device is to be designed in such a way that it only permits relative positions in which the required alignment of the V-belt pulleys and the resulting orientation between the upper and lower mass is guaranteed.
• the stabilization device is designed as a parallel guide, in such a way that it only displaces the upper mass and
• an advantageous embodiment of the invention is particularly interesting in practice, in which the stabilization device does not allow the upper mass to tilt relative to the lower mass. While the spring device connecting the upper and lower mass in the form of z. B. rubber buffers, depending on the spring constant, allows almost any tilt positions between the upper and lower mass, the stabilization device prevents tilting or significantly reduces the tilt angle. Of course, due to the high forces acting and the tolerances tolerated in such construction machines, it cannot be ruled out that tilting between the upper and lower mass can nevertheless occur. However, the tilt angle permitted by the stabilization device is considerably smaller than without the stabilization device.
• the stabilization device does not allow the upper mass to tilt relative to the lower mass about an axis directed in a main direction of travel. This prevents transverse tilting, which occurs in particular when the vibrating plate is placed on a side edge of the ground contact plate. Tilting about an axis transverse to the main direction of travel remains possible in order to allow a principle-related pitching movement between the upper and lower mass and thereby to avoid an increased load on the stabilization device.
• connection between the upper and lower mass is to be designed in such a way that the horizontal and vertical relative movement is permitted.
• the stabilization device is designed such that it does not permit a transverse offset or a transverse displacement of the upper mass relative to the lower mass transversely to the main direction of travel. On in this way, an alignment error between the V-belt pulleys of the upper and lower mass can also be prevented or reduced.
• the stabilization device preferably has at least one dimensionally stable connecting element which connects the upper mass to the lower mass, the connecting element preferably being articulated to the upper and lower mass.
• the connecting element represents a guiding or steering device and ensures that only relative positions between the upper and lower mass can be assumed that are permitted by the connecting element.
• the connecting element is a transverse stabilizer.
• the transverse stabilizer can have a substantially horizontally arranged U-shaped element, which is attached to the upper mass and to the lower mass via pivot bearings.
• Transverse stabilizers are known in principle from vehicle technology and ensure that tilting between the upper mass and the lower mass is reduced or prevented.
• the U-shaped element is advantageously fastened to the upper mass and / or to the lower mass via at least one vertical lever, the vertical lever being articulated to the upper or lower mass and to the U-shaped element.
• the linkage is preferably carried out via two vertical levers in order to ensure the required stability.
• the open ends of the U-shaped element are articulated either on the upper or lower mass, while a central part of the U-shaped element enclosed by the open ends is articulated accordingly on the opposite lower or upper mass.
• the middle part can preferably be substantially perpendicular to the open ends of the U-shaped element enclosing it.
• the anti-roll bar can be produced in a simple manner at low manufacturing costs.
• the open ends of the U-shaped element are oriented essentially in the main direction of travel, and that pivot axes predetermined by the pivot bearings are directed transversely to the main direction of travel of the vibration plate. This arrangement ensures that the transverse stabilizer prevents the upper mass from tilting relative to the lower mass about an axis directed in the main direction of travel.
• the open ends of the U-shaped element can also be directed essentially in a direction transverse to the main direction of travel. Accordingly, the pivot axes predetermined by the pivot bearings are aligned in the main direction of travel of the vibration plate. Then a pitching movement between the upper and lower mass explained above can be prevented, which occurs due to the principle of vibration exciters, in which at least two unbalanced shafts are arranged parallel to each other and driven in rotation. Since the unbalanced masses carried by the unbalanced shafts are not arranged in the overall center of gravity of the lower mass, they each cause a rotational moment about the transverse center of gravity axis of the lower mass, which is expressed in a pitching movement of the ground contact plate.
• the U-shaped element can be designed in such a way that its transverse rigidity is low and the U-shaped element accordingly behaves smoothly in the transverse direction.
• two U-shaped elements or transverse stabilizers are provided, which are arranged essentially at right angles to one another. In this way, tilting between the upper and lower mass can be avoided and a pitching movement suppressed.
• the connecting element is in particular by a connecting rod formed a panard stick.
• a Panard rod is also known from automotive engineering and ensures guidance between the elements to which it is attached.
• the Panard rod can be articulated at its ends to the upper mass and the lower mass.
• the connecting rod is preferably arranged essentially transversely to the main direction of travel, in order in this way to avoid a transverse displacement between the upper and lower mass.
• the connecting rod has a sufficiently long length, the fact that the vertical movement between the upper and lower mass is small means that the horizontal movement (transverse displacement, transverse displacement) can also be kept small.
• the connecting rod is preferably arranged essentially horizontally in order to avoid unnecessary overall height. Of course, however, it can also have a slight inclination with respect to the horizontal plane. So that the connecting rod can achieve the desired effect, it is advantageous if the pivot axes predetermined by the pivot bearings are directed in the main direction of travel.
• the pivot bearings can preferably be implemented in the form of ball joint bearings in order to achieve a corresponding angular mobility.
• the connecting rod should be as long as possible, but this must be adapted to the available space.
• two connecting rods are provided which are arranged essentially parallel to one another. In this way, e.g. B. a connecting rod in front and a connecting rod behind the vibration exciter of the lower mass.
• the connecting element ie the transverse stabilizer or the connecting rod
• the connecting element should be dimensionally stable. That means preferably that the connecting element is essentially dimensionally stable. to achieve the desired leadership effect.
• spring devices can be provided at the ends of the connecting element, that is to say at the connecting points with the upper or lower mass, via which the connecting element is held.
• the pivot bearings can be designed such that they have spring properties.
• the stiffness should apply in particular with regard to an imaginary connecting line that runs between the articulation points of the connecting element on the upper mass and on the lower mass.
• the connecting element is resilient transversely to the imaginary connecting line between the articulation points. That means that it still has to be dimensionally stable. However, due to its elastic properties, it can allow certain deformations. Since the spring action generates spring forces in the manner chosen by the arrangement of the connecting element, a reduction in the tilt angle or the transverse offset between the upper and lower mass is also achieved.
• FIG. 1 shows a first embodiment of a vibration plate according to the invention in top view (a) and side view (b);
• Fig. 2 shows a second embodiment of the vibration plate in plan view (a) and side view (b).
• FIG. 1 shows a first embodiment of a vibration plate according to the invention, FIG. 1a) showing a top view and FIG. 1b) showing a side view.
• a vibration exciter 2 which is only shown schematically, is arranged on a ground contact plate 1 which runs over the ground during the compaction work.
• the vibration exciter 2 can have a single unbalanced shaft (drag oscillator), which is driven in rotation by a drive (internal combustion engine, electric motor) that is not shown in an upper mass 3. It is also possible for the vibration exciter 2 to comprise two or more unbalanced shafts which are driven parallel to one another.
• the rotation of the unbalanced shafts must be coordinated with respect to their speed and their phase position in such a way that a desired resulting force results which can be used for soil compaction and for propelling the vibration plate.
• the unbalanced shafts are coupled to one another in a form-locking manner so they can rotate in opposite directions.
• At least one of the unbalanced shafts in the vibration exciter 2 is driven in a rotating manner via the drive in the upper mass 3, a V-belt drive usually being used to transmit the rotary movement, but this is not shown in FIG. 1, but only in the figure described later . 2.
• the ground contact plate 1 and the vibration exciter 2 form essential elements of a lower mass 4.
• the lower mass 4 is connected to the upper mass 3 via rubber buffers 5 serving as spring devices. Due to the spring properties of the rubber buffers 5, the upper mass 3 and the lower mass 4 can be moved relative to one another in almost any spatial direction. The mobility is limited only by the spring constant of the rubber buffer 5 and the effective deflection force.
• the rubber buffers 5 have the task of decoupling the intentionally strong vibrations acting on the lower mass 4 from the upper mass 3 in order to protect the drive accommodated there and also the operator guiding the vibration plate on the upper mass 3.
• the operator exerts an asymmetrical compressive force on the upper mass 3, directed towards the floor, to achieve an increased edge pressure of the ground contact plate 1 in this way.
• pressing the upper mass 3 down on one side tilts the upper mass 3 in relation to the lower mass 4.
• V-belt pulleys which are provided on the drive of the upper mass 3 and on the vibration exciter 2 of the lower mass 4, in order to form the V-belt drive, no longer swear.
• the V-belt rotating between the V-belt pulleys is tilted, which considerably reduces its service life.
• a transverse stabilizer 6 is provided, which is designed as a U-shaped element.
• Open ends 7 of the U-shaped element are pivoted 8 with the sub-mass 4, z.
• B. a housing or a carrier of the drive are attached.
• a vertical lever 11 can be provided on the lower mass 4 or the upper mass 3. If necessary, a plurality of vertical levers 11 can also be arranged in order to enable stable guidance of the transverse stabilizer 6.
• the one or more vertical levers 1 1 are pivotally connected to the upper mass 3 via pivot bearings 12.
• the vertical lever 1 1 should be short in relation to the cross stabilizer 6 in order to avoid greater leverage.
• the transverse stabilizer 6 is designed as a dimensionally stable connecting element, thereby preventing the upper mass 3 from tilting relative to the lower mass 4 in order to avoid an axis directed in a main direction of travel X of the vibration plate. Accordingly, if the operator tries to place the vibrating plate with its bottom contact plate 1 on a lateral edge, the entire vibrating plate behaves stiffly, so that, in particular, tilting of the upper mass 3 relative to the lower mass 4 is prevented.
• FIG. 2 shows a second embodiment of the vibration plate according to the invention, which in principle has a similar structure to the vibration plate described in connection with FIG. 1.
• the lower mass 4 is essentially formed by the base contact plate 1 and the vibration exciter 2, while the drive (not shown) is accommodated in the upper mass 3.
• the lower mass 4 is decoupled in terms of vibration from the upper mass 3 via the rubber buffers 5.
• 2a) and 2b) also show a V-belt pulley 15 which is connected to one of the unbalanced shafts of the vibration exciter 2.
• a V-belt 16 can be seen in FIG. 2b), which transmits the drive energy in a known manner from a V-belt pulley present under the cover of the upper mass 3 and belonging to the drive, to the V-belt pulley 15 of the vibration exciter 2.
• Panard rods 17 and 18 (connecting rods) articulated.
• pivot bearings 19 are provided on the lower mass and 3 pivot bearings 20 on the upper mass.
• the Panard rods 17, 18 should be as long as possible, so that when there are changes in the distance between the upper mass 3 and the lower mass 4, only slight horizontal displacements (with respect to the ground contact plate 1 in the horizontal position) result from changes in angle.
• the Panard rods 17, 18 are arranged essentially horizontally, as shown in FIGS. 2a) and 2b). A slight inclination to the horizontal is permitted.
• the Panard rods 17, 18 are arranged transversely to the main direction of travel X, as can be seen in particular from FIG. 2a).
• the Panard rods 17, 18 stabilize the relative position between the upper mass 3 and lower mass 4 in such a way that a lateral offset can be avoided or reduced, in particular when transverse forces are applied, so that the V-belt pulleys remain essentially in one plane.
• the Panard rods 17, 18 should be as rigid as possible in order to fulfill their guiding effect.
• the articulation of the Panard rods 17, 18 on the pivot bearings 19, 20 can also be done via bending elements, such as. B. springs or rubber vibrating metals.
• the relative movement between the upper mass 3 and the lower mass 4 lies in an area which can easily be absorbed by rubber springs.
• the entire panard rod 17, 18 can also be designed as a spring element, in which case it does not necessarily have to be attached to the upper and lower mass via pivot bearings. Rather, the ends of the Panard rod can also be firmly articulated to the upper and lower mass. If the spring-elastic Panard rod is dimensioned sufficiently strong, it is able to absorb vertically directed transverse forces by elastic deformation and thereby allow vertical movement of the ground contact plate 1 relative to the upper mass 3, while transverse forces, which are directed horizontally, are axially introduced into the Panard rod 17, 18 are, so that they cause no significant deformation due to the axial rigidity of the Panard rod 17, 18. Instead of the two Panard rods 17, 18 shown in FIG.
• the wishbone 6 with one or more Panard rods 17, 18.
• the possible variations are determined by the designer's wish to enable or prevent or reduce certain relative movements between the upper and lower mass.
• the stabilization device which has at least one connecting element in the form of the transverse stabilizer 6 or the Panard rod 17, 18, it is possible to avoid or reduce unwanted relative movements between the upper and lower mass (roll movement, tilting, transverse offset) without the vibration isolation of the To affect upper mass 3 from lower dimension 4.

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• Engineering & Computer Science (AREA)
• Structural Engineering (AREA)
• Civil Engineering (AREA)
• Life Sciences & Earth Sciences (AREA)
• Environmental & Geological Engineering (AREA)
• Soil Sciences (AREA)
• General Life Sciences & Earth Sciences (AREA)
• Mining & Mineral Resources (AREA)
• Paleontology (AREA)
• Agronomy & Crop Science (AREA)
• General Engineering & Computer Science (AREA)
• Architecture (AREA)
• Road Paving Machines (AREA)
• Vibration Prevention Devices (AREA)
• Apparatuses For Generation Of Mechanical Vibrations (AREA)

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• 2005
  • 2005-12-07 DE DE102005058485A patent/DE102005058485A1/de not_active Withdrawn
• 2006
  • 2006-12-01 US US12/096,289 patent/US20080298893A1/en not_active Abandoned
  • 2006-12-01 CN CN2006800453950A patent/CN101341299B/zh not_active Expired - Fee Related
  • 2006-12-01 WO PCT/EP2006/011554 patent/WO2007065604A1/de active Application Filing
  • 2006-12-01 EP EP06818950A patent/EP1957715A1/de not_active Withdrawn
  • 2006-12-01 JP JP2008543706A patent/JP2009518171A/ja active Pending

Non-Patent Citations (1)

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