WO2009089899A1 - Plaque vibrante dotée d'une transmission par courroie à renvoi multiple - Google Patents

Plaque vibrante dotée d'une transmission par courroie à renvoi multiple Download PDF

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Publication number
WO2009089899A1
WO2009089899A1 PCT/EP2008/011073 EP2008011073W WO2009089899A1 WO 2009089899 A1 WO2009089899 A1 WO 2009089899A1 EP 2008011073 W EP2008011073 W EP 2008011073W WO 2009089899 A1 WO2009089899 A1 WO 2009089899A1
Authority
WO
WIPO (PCT)
Prior art keywords
belt
plate according
drive
mass
vibration plate
Prior art date
Application number
PCT/EP2008/011073
Other languages
German (de)
English (en)
Inventor
Otto W. Stenzel
Original Assignee
Wacker Neuson Se
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wacker Neuson Se filed Critical Wacker Neuson Se
Priority to EP08870704A priority Critical patent/EP2245231A1/fr
Priority to US12/810,046 priority patent/US20100278590A1/en
Priority to CN2008801218247A priority patent/CN101903597A/zh
Publication of WO2009089899A1 publication Critical patent/WO2009089899A1/fr

Links

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
    • E01C19/30—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
    • E02D3/046—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

Definitions

  • the invention relates to a vibrating plate for soil compaction according to the preamble of patent claim 1.
  • Vibratory plates for soil compaction have an upper mass enclosing the drive and a relatively movable lower mass with a ground contact plate and a vibration exciter.
  • the power transmission from the drive motor to the vibration exciter takes place predominantly with the help of a V-belt.
  • the V-belt directly connects the V-belt pulley on the motor shaft with the V-belt pulley of the unbalance exciter.
  • vibrating plates which have a tensioning pulley which is frequently provided on the drive and in which the two wedge disk pulley plates are axially compressed by means of a spring or an eccentric so that the pitch circle diameter of the belt pulley is increased at a low belt tension while the pitch diameter decreases when the belt is tight. It is also known to press a tension roller from the inside against the V-belt on the empty belt side in order to maintain the necessary tension on the empty belt side.
  • the distance between the upper mass and the lower mass changes with the exciter frequency.
  • the upper mass is excited to vibrate in several forms of motion (eigenmodes).
  • the operator practices in operation while guiding the vibrating plate Help a tiller forces out to the upper mass. He presses the upper mass sideways or down. It is also possible that it tugs laterally on the upper mass in order to achieve a higher compression on one side. This creates additional changes in the distance between the upper mass and the lower mass.
  • there are misalignment between the pulleys on the input and the output side and vertical and horizontal angle errors The changes in the distance, as well as the misalignment and angle errors, mean that the V-belt can not circulate between the pulleys as intended. Rather, his movement is significantly disturbed.
  • V-belt Due to the numerous disturbances of the V-belt is sometimes insufficient and in the next moment again excessively tense. This is superimposed by high forces resulting from the non-uniform rotational movement of the mutually interfering rotational speed changes of the drive motor and vibration exciter.
  • the V-belt can slip through at one time and be torn into a stiction the next moment. Due to these untypical stresses of the V-belt, the intended life is usually not reached.
  • the belt drive between upper and lower mass is usually provided only on one side of the vibrating plate. Thus load the V-belt tension and the tensile force of the load strand, the one provided on one side between the upper mass and the lower mass spring elements.
  • the resulting unbalanced bias of the spring elements and the resulting unbalanced spring stiffness can cause the vibrating plate, if not guided by the operator, to make a turn.
  • the operator must therefore constantly act in a corrective manner in order to achieve a bicycle ride.
  • FIG. Ia shows a schematic side view of a known vibration plate.
  • FIG. 1 b shows a simplified mechanical substitute image.
  • An upper mass 1 has a drive 2, e.g. a one- or two-cylinder internal combustion engine.
  • a drawbar 3 is provided for guiding the vibrating plate by the operator.
  • the upper mass 1 is coupled via spring devices, not shown, spring / damper devices with a lower mass 4 in a known manner.
  • the lower mass 4 has a ground contact plate 5 and a vibration exciter 6 arranged thereon.
  • On the drive 2 a drive pulley 7 is provided, while the vibration exciter 6 has a driven pulley 8.
  • the drive pulley 7 is e.g. mounted directly on the crankshaft of the drive 2, while the driven pulley 8 is fastened on an extension of an imbalance shaft of the vibration exciter 6.
  • the drive energy is transmitted from the drive pulley 7 via a belt 9 to the driven pulley 8 and thus the vibration exciter 6.
  • the structure of this vibrating plate is known, so that can be dispensed with a further description.
  • the object of the invention is to improve a belt drive for a vibration plate in such a way that changes in the distance between the upper and lower mass, angular errors and rotational speed fluctuations can affect the service life of the belt to a lesser extent.
  • a vibration plate with a belt drive which has a drive disk provided on a drive, an output disk provided on a vibration generator and a belt rotating between the drive disk and the output disk, is characterized in that at least two further deflection rollers are provided for guiding the belt.
  • the deflection rollers can be mounted on the same side from an imaginary connecting line between a rotation axis of the drive plate. be arranged and a rotation axis of the driven pulley. As a result, the belt is deflected several times and thus has a greater length, which can better compensate for the interference.
  • Those parts or sections of the belt which extend between elements of the upper mass and lower mass elements and thus couple the respective elements may extend substantially horizontally or at an angle of less than 30 ° to the horizontal.
  • changes in distance between the upper mass and lower mass only have a minor effect.
  • the belt part running around the deflection rollers or disks only changes its position by a few angular degrees so that its length barely changes due to the cosine effect.
  • both deflection rollers are mounted on the upper mass or that a deflection roller is mounted on the upper mass and a deflection roller on the lower mass. It is possible to store the pulleys on a lever generated by intermediate shore. It is also possible to arrange both pulleys on the lower mass, but this may be disadvantageous in view of the fact that there are considerably stronger vibrations at the lower mass.
  • the vibrating plate is designed as a towed oscillating plate.
  • Towing armature plates often have only a single unbalance shaft, which is usually arranged in the front region on the lower mass.
  • reversible vibrating plates which has a vibration generator for generating directed vibrations.
  • two or more oppositely positively coupled rotatable unbalanced shafts are usually arranged centrally on the lower mass.
  • the vibrating plate is a sling plate and has an imbalance shaft in its front portion, the deflecting rollers may be disposed in a rear portion of the vibrating plate. As a result, a very long horizontal course of the belt can be achieved.
  • a deflection roller by two (or more) usually smaller pulleys with lower angles of wrap.
  • a pulley which has a wrap angle of 180 °, be replaced by two pulleys with a wrap angle of 90 °.
  • any other wrap angles are possible.
  • the distance between a pulley of a bank and the over the course of the belt associated and thus coupled to the pulley drive pulley or driven pulley on the other shore should be as large as possible. As a result, changes in distance or angle errors can be effectively compensated. the distance should be at least 20 percent of in
  • the deflection rollers can be arranged such that a wrap angle on the drive pulley and / or on the driven pulley is greater than 180 °. This allows for efficient transmission of power between the discs and the belt.
  • At least one of the deflection rollers can be displaceably or cardanically mounted along its axis of rotation.
  • a deflection roller on the upper mass and a deflection roller mounted on the lower mass wherein those parts of the belt which extend between the upper mass and the lower mass, extend substantially parallel to each other. With a relative movement between the upper mass and the lower mass, this compensates for the belt length changes.
  • a compensating roller for clamping can be provided as the load end of the belt.
  • the compensating roller can be held by a spring device in a normal position.
  • the bias of the spring device be dimensioned such that the compensating roller is movable when exceeding a predetermined belt force in which the compensating roller with a certain angle encircling Lasttrum from the normal position against the action of the spring device in a relief position, so that the compensating role of the belt force yields and the belt force acting in the load strand is reduced.
  • the preload force is not exceeded, so that the compensating roller acts like a rigidly mounted roller.
  • the allowable belt force is exceeded, and the biasing force of the spring device is exceeded.
  • the compensation roller is moved out of the normal position, thereby freeing belt length, so that the belt is relieved in the area of the load strand.
  • the liberated belt length should then be tensioned by a tension roller in the slack side, in order to maintain the sufficient return tension for a slip operation.
  • the axes of rotation of the pulleys may vary with respect to the horizon- talen be inclined. This can be particularly useful if the pulleys are to be arranged as close as possible next to each other or even partially axially next to each other.
  • a towed swinging plate e.g. It may be appropriate to arrange the two arranged in the rear area pulleys next to each other to extend horizontally extending between the upper and lower mass belt length. If the pulleys are inclined with respect to the horizontal, they can be arranged close to each other. As a result, the belt is easily twisted, but this is not a problem.
  • the outer contour of the pulleys can be performed slightly spherical to support the twisting. Furthermore, it may be expedient if the drive pulley and the driven pulley are slightly offset relative to one another.
  • the belt may also be used to drive an accessory such as e.g. a fan blower, an auxiliary hydraulics or a generator is used.
  • an accessory such as e.g. a fan blower, an auxiliary hydraulics or a generator is used.
  • deflection rollers may be provided, depending on the embodiment, two deflection rollers in a front region of the vibrating plate and two deflection rollers are arranged in a rear region of the vibrating plate or a deflection roller in the front region and three deflection rollers in the rear region or three deflection rollers are arranged in the front region and a deflection roller in the rear region.
  • the axes of rotation of the pulleys do not necessarily have to be parallel. Rather, inclinations of the axes of rotation are allowed because a twisting of the belt because of the complex movement behavior is possible and also useful.
  • one of the pulleys on the O-pulp and one of the pulleys on the lower mass is arranged, wherein the belt is guided such that it rotates the drive pulley with its one side and the driven pulley rotates with its other side.
  • a belt must be provided, which provides profiling on both sides, such as a V-ribbed belt or a toothed belt. This results in a reversal of the direction of rotation between the drive and the vibration exciter.
  • the two deflection rollers are arranged on different sides of the imaginary connecting line between the axis of rotation of the drive pulley and the axis of rotation of the drive pulley.
  • the parts of the belt that run between elements of the upper mass and the lower mass should be parallel to each other. This applies at least to the load area.
  • At least one of the deflection rollers is mounted both on the upper mass and on the lower mass.
  • the storage must be designed such that it can compensate for the relative movement between the upper mass and lower mass.
  • the respective deflection roller may be mounted on two lever elements, one of which is pivotally mounted on the upper mass and one is mounted pivotably on the lower mass.
  • the lever elements run predominantly parallel to the respective belt sections which run away from the respective deflection roller.
  • the storage of the lever elements on the upper or lower mass can be formed in the form of joints. Because of the non-parallel movement of the upper and lower mass, they can be hung cardanically. Likewise, elastic members can be used here alternatively.
  • the intermediate banks where the pulleys between upper and lower mass are attached, can also be attached via parallelogram lever systems at least on a bank.
  • Figure 1 is a schematic representation of a side view (a) of a known vibration plate without the belt drive according to the invention, as well as a mechanical replacement image (b).
  • Fig. 4 is a rear view of Fig. 3;
  • Fig. 8 in turn another variant of the belt drive.
  • Fig. 2 shows a schematic side view of a much simplified vibration plate with a belt drive.
  • the vibrating plate is similar to the vibrating plate described above with reference to FIG. Therefore, the same reference numerals are used for the same components.
  • the belt 9 is not only around the drive disc 7 (motor M) and the driven pulley 8 (exciter E), but also to two mounted on the upper mass 1 pulleys 10 and guided around a mounted on the lower mass 4 pulley 1 1.
  • Der Umlenkrolle 1 ist mit dem Umlenkrolle 1sky.
  • the two mounted on the upper mass 1 pulleys 10 can also be formed by a single pulley whose wrap is then correspondingly larger.
  • the guide rollers 10, 1 1 are arranged with respect to an imaginary connecting line 12 between the axes of rotation of the drive pulley 7 and the driven pulley 8 on the same side (in Fig. 2 of the left side).
  • the pulleys 10, 11 are placed with respect to the pulleys 7, 8 such that pulley segments 9a that couple elements on different shafts are substantially horizontal.
  • a belt segment 9a is defined between the drive pulley 7 provided on the upper mass and the deflection roller 11 mounted on the lower mass, while the other belt segment 9a extends between the driven pulley 8 provided on the lower mass and one of the pulleys 10 mounted on the upper mass.
  • FIG. 2 is particularly suitable for a rever- sierbare vibration plate, in which the driven of the driven pulley 8 vibration exciter 6 has two or more coupled with each other, in opposite directions rotating unbalanced shafts, which are usually arranged centrally on the lower mass 4.
  • Fig. 3 shows an embodiment, especially for a
  • two deflection rollers are provided, namely a deflection roller 10 mounted on the upper pulley 1 and one on the lower mass 4 mounted pulley 1 1.
  • the belt segments 9a extend between respective guide rollers 10, 1 1 and discs 7, 8 different banks 1, 4 substantially horizontally.
  • the distance between a guide roller 10, 1 1 and the respective associated disc 7, 8 of the other bank 1, 4 is as large as possible.
  • angle errors between the upper and lower mass or an offset can be well tolerated.
  • a large belt length ensures greater elasticity to mitigate the belt force peaks from the rotational speed fluctuations.
  • the guide rollers 10, 1 1 gimbal and / or are mounted longitudinally displaceable on its axis of rotation, so that the offset and the tilting on the belt 9 averages before and behind the respective roller 10, 1 1.
  • FIG. 4 shows a variant of FIG. 3 in a rear view from the right.
  • Fig. 4 shows that the axes of rotation of the guide rollers 10, 1 1 are inclined with respect to the horizontal and the pulleys 10, 1 1 thereby almost side by side or at least close to each other can arrange.
  • the belt lengths of the horizontal belt segments 9a can be extended somewhat.
  • the belt 9 must be slightly twisted, but this does not pose a problem over the length.
  • the contour of the deflecting rollers 10, 1 1 should be slightly convex.
  • the drive pulley 7 and the driven pulley 8 should be arranged slightly offset, as shown in FIG. 4.
  • FIG. 5 shows a variant with four deflecting rollers, with three deflecting rollers 10 mounted on the upper mass 1 and a deflecting roller 11 on the lower mass 4.
  • the belt segments 9a the elements of different banks 1, 4 connect, arranged horizontally.
  • Fig. 6 shows a variant in which instead of a V-belt, a V-ribbed belt or a toothed belt with profilings on both sides can be used. In this case, belt segments 9b are provided, which run substantially parallel to one another.
  • FIG. 7 shows an arrangement in which deflection rollers 13 are mounted on the upper mass 1 and on the lower mass 4.
  • each guide roller 13 is coupled via a lever element 14 with the upper mass 1 and a lever member 15 with the lower mass 4.
  • the lever elements 14, 15 extend predominantly parallel to the respective belt sections, i. to the sections of the belt 9, which extend between the respective guide roller 13 and the associated disc 7, 8.
  • Fig. 8 shows a similar variant as Fig. 7, in which the deflection rollers 13 press the belt 9 inwards and thereby achieve a larger wrap angle of the discs 7, 8.
  • a particular advantage of the arrangements shown in Figs. 7 and 8 is that the biasing forces of the belt 9 are completely compensated.
  • the belt tension thus does not pull together the upper mass 1 and the lower mass 4 on one side.
  • Fig. 7 shown embodiment allows an extension of the belt 9 in the load strand, as indicated by the direction of rotation arrows.
  • lever elements 14, 15 are suspended on the upper mass 1 and the lower mass 4 via joints gimbal.
  • elastic members for supporting the lever elements 14, 15 may be used.

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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)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Road Paving Machines (AREA)

Abstract

La présente invention concerne une plaque vibrante comprenant une masse supérieure (1) dotée d'un entraînement (2) ainsi qu'une masse inférieure (4) logée de façon élastiquement mobile par rapport à la masse supérieure (1) et dotée d'un générateur de vibrations (6) et d'une plaque de contact de fond (5). L'entraînement (2) est couplé au générateur de vibrations (6) par une transmission par courroie (9). La transmission par courroie (9) comprend un disque menant (7) disposé sur l'entraînement (2), un disque mené (8) disposé sur le générateur de vibrations (6) et une courroie (9) circulant entre le disque menant (7) et le disque mené (8). L'invention prévoit au moins deux autres poulies de renvoi (10, 11) destinées à guider la courroie (9).
PCT/EP2008/011073 2008-01-18 2008-12-23 Plaque vibrante dotée d'une transmission par courroie à renvoi multiple WO2009089899A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP08870704A EP2245231A1 (fr) 2008-01-18 2008-12-23 Plaque vibrante dotée d'une transmission par courroie à renvoi multiple
US12/810,046 US20100278590A1 (en) 2008-01-18 2008-12-23 Vibration plate having belt drive having multiple deflection
CN2008801218247A CN101903597A (zh) 2008-01-18 2008-12-23 具有多重偏转的带式驱动装置的振动板

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008005066A DE102008005066A1 (de) 2008-01-18 2008-01-18 Vibrationsplatte mit Riementrieb mit Mehrfachumlenkung
DE102008005066.0 2008-01-18

Publications (1)

Publication Number Publication Date
WO2009089899A1 true WO2009089899A1 (fr) 2009-07-23

Family

ID=40419052

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/011073 WO2009089899A1 (fr) 2008-01-18 2008-12-23 Plaque vibrante dotée d'une transmission par courroie à renvoi multiple

Country Status (5)

Country Link
US (1) US20100278590A1 (fr)
EP (1) EP2245231A1 (fr)
CN (1) CN101903597A (fr)
DE (1) DE102008005066A1 (fr)
WO (1) WO2009089899A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011157344A1 (fr) * 2010-06-18 2011-12-22 Wacker Neuson Produktion GmbH & Co. KG Plaque vibrante avec stabilisateur de courroie trapézoïdale
WO2012159716A1 (fr) * 2011-05-26 2012-11-29 Wacker Neuson Produktion GmbH & Co. KG Appareil de travail à producteur de courant adaptatif et procédé associé
CN104975554A (zh) * 2014-04-04 2015-10-14 维特根有限公司 自动推进的建筑机械和控制自动推进的建筑机械的方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011077538A1 (de) * 2011-06-15 2012-12-20 Schaeffler Technologies AG & Co. KG Aktuator zur Verstellung zweier relativ zueinander bewegbarer Bauteile
DE102018007825A1 (de) * 2018-10-04 2020-04-09 Bomag Gmbh Verfahren zur Steuerung einer Bodenverdichtungsmaschine und Bodenverdichtungsmaschine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221567A (en) * 1962-04-09 1965-12-07 Jr Richard W Brandt Belt drive for shaking device
DE9202880U1 (fr) * 1991-04-03 1992-05-07 Cron, Josef, 5420 Lahnstein, De
US5209331A (en) * 1991-03-13 1993-05-11 M-B-W Inc. Clutch construction
EP0582872A1 (fr) * 1992-08-12 1994-02-16 RILCO GmbH Transmission à courroie

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
US2792769A (en) * 1953-09-01 1957-05-21 Russell P Harshberger Earth working machine or the like
US3283677A (en) * 1964-09-01 1966-11-08 Wacker Hermann Manually guided motor driven tamping device for earth, concrete and other materials
US3491662A (en) * 1965-09-14 1970-01-27 Bernhard Beierlein Tamping device
DE3709112C1 (de) * 1986-08-27 1988-01-28 Knauer Maschf Gmbh Ruettelvorrichtung fuer eine Betonsteinformmaschine
US5149225A (en) * 1991-03-13 1992-09-22 M-B-W Inc. Reversible drive for a vibratory compactor
DE4210507C2 (de) * 1991-04-03 2002-11-07 Josef Cron Vorrichtung zur Einstellung von wenigstens zwei auf Unwuchtwellen umlaufenden Unwuchten in ihrer Unwuchtlage zueinander
FR2676664B1 (fr) * 1991-05-22 1995-01-27 Vaillant Materiels Vincent Dispositif autorisant le controle et l'action d'effets vibratoires sur des machines destinees notamment a la fabrication de produits destines a etre vibres et compactes.
US5439314A (en) * 1994-01-03 1995-08-08 Wadensten; Theodore S. Reversible self-propelled plate compactor
JP3134050B2 (ja) * 1996-06-28 2001-02-13 茂 小林 コンクリート型枠加振装置
US5672027A (en) * 1996-08-01 1997-09-30 Wadensten; Theodore S. Reversible plate compactor having an improved drive and directional control
US6837648B1 (en) * 2004-05-27 2005-01-04 Theodore S. Wadensten Portable roller-type compactor apparatus having a combined means for the vibrating and the reversible propelling thereof

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221567A (en) * 1962-04-09 1965-12-07 Jr Richard W Brandt Belt drive for shaking device
US5209331A (en) * 1991-03-13 1993-05-11 M-B-W Inc. Clutch construction
DE9202880U1 (fr) * 1991-04-03 1992-05-07 Cron, Josef, 5420 Lahnstein, De
EP0582872A1 (fr) * 1992-08-12 1994-02-16 RILCO GmbH Transmission à courroie

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011157344A1 (fr) * 2010-06-18 2011-12-22 Wacker Neuson Produktion GmbH & Co. KG Plaque vibrante avec stabilisateur de courroie trapézoïdale
WO2012159716A1 (fr) * 2011-05-26 2012-11-29 Wacker Neuson Produktion GmbH & Co. KG Appareil de travail à producteur de courant adaptatif et procédé associé
CN104975554A (zh) * 2014-04-04 2015-10-14 维特根有限公司 自动推进的建筑机械和控制自动推进的建筑机械的方法

Also Published As

Publication number Publication date
DE102008005066A1 (de) 2009-07-30
EP2245231A1 (fr) 2010-11-03
CN101903597A (zh) 2010-12-01
US20100278590A1 (en) 2010-11-04

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