EP0975839B1 - Compacteur destine au compactage du sol - Google Patents

Compacteur destine au compactage du sol Download PDF

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Publication number
EP0975839B1
EP0975839B1 EP98909445A EP98909445A EP0975839B1 EP 0975839 B1 EP0975839 B1 EP 0975839B1 EP 98909445 A EP98909445 A EP 98909445A EP 98909445 A EP98909445 A EP 98909445A EP 0975839 B1 EP0975839 B1 EP 0975839B1
Authority
EP
European Patent Office
Prior art keywords
stamping device
mass
crank
crank drive
movement
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.)
Expired - Lifetime
Application number
EP98909445A
Other languages
German (de)
English (en)
Other versions
EP0975839A1 (fr
Inventor
Martin Greppmair
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.)
Wacker Construction Equipment AG
Original Assignee
Wacker Construction Equipment AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wacker Construction Equipment AG filed Critical Wacker Construction Equipment AG
Publication of EP0975839A1 publication Critical patent/EP0975839A1/fr
Application granted granted Critical
Publication of EP0975839B1 publication Critical patent/EP0975839B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • E01C19/30—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
    • E01C19/36—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 direct-acting explosion chambers
    • 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
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • 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
    • E02D3/061—Tampers with directly acting explosion chambers

Definitions

  • the invention relates to a ramming device for soil compaction according to the preamble of claim 1.
  • Such devices which are supported on the ground solely by the pest foot, be by an operator through direct transfer of executives by means of a guide bracket or about a drawbar during the Swinging movement of the padfoot in the desired direction out. at switched off drive, the device is difficult to transport, it must be worn or with a suitable device, such as a cart.
  • JP-A-04312603 a ramming device for soil compaction is described, with a ramming tool in which a working mass via a crank mechanism linear reciprocating drivable.
  • the ramming tool is over a chassis additionally supported against the ground. Between the crank mechanism and the working mass is arranged a spring set.
  • the ramming tool can be pivoted relative to the chassis using a worm gear.
  • the invention is based on the object, a ramming device of the type described above To design a way such that generated by the rammer Vibrations as low as possible on the chassis or an operator of the Ramming device can be transmitted.
  • the object is achieved by a ramming device according to claim 1 solved.
  • a very advantageous embodiment provides that the additional Suspension carries the combustion engine.
  • Another very advantageous embodiment is to provide the landing gear with a self-propelled, preferably for generating the ramming movement and the chassis drive a common power source is provided.
  • a self-propelled chassis can be advantageous as a hydraulic drive be formed or done via a drive chain.
  • the suspension drive between front and Reverse switchable can be advantageous as a hydraulic drive be formed or done via a drive chain.
  • the suspension can be beneficial by an additional support wheel on the of the drivable Axis facing away from the padfoot as a three-point landing gear be educated.
  • Known, hand-guided rammers are designed to that the upper mass is about two-thirds and the beating work- or lower mass one third of the total rammer mass while that of the upper mass and the working mass each path traveled in inverse proportion to each other stand.
  • the upper mass moves in the order of magnitude from 25 to 30 mm.
  • the output power of the ramming system is largely of the Upper mass dependent because too much work mass or too high speed of the working mass the upper mass oversized moves and amplifies the problems described above.
  • Embodiment of the device according to the invention in that it is in Area of the upper mass with one together with the working mass, but in the opposite direction to the movement of the working mass of Motor driven countermass is provided.
  • the upper mass is from one himself to his case supporting crank drive pushed in the moment up, in which the crank drive via its connecting rod, a guide piston and a spring set the working mass and thus the padfoot pushes down.
  • the Federsatz has the consequence that at the Downward movement of the guide piston initially under these springs Energy intake are curious, what they do with one conditional delay then the stored Return energy to the downward movement of the pest foot. This delay must be taken into account when the movement the counterweight matched to the movement of the working mass becomes. When the working mass through the crank pin of the crank mechanism is pulled up again, the upper mass moved down.
  • An advantageous embodiment is that the Drive the counterweight is derived from the crank mechanism and the Movement of the connected to the crank mechanism end of the spring set and the movement of the counterweight relative to the crank angle by 180 ° minus one of the design parameters the spring set derived phase shift against each other are offset.
  • the counterweight is on the upper mass parallel to the direction of movement of the working mass is guided.
  • the counterweight of a Aus Dissexzenter on the crank mechanism is driven, for example via a Connecting rod.
  • the connection between the countermass and the Balancing eccentric be designed as a crank loop.
  • the counterweight exists of two each on one side or the other of the crank mechanism at about the same height with respect to the axis of rotation of Crankshaft arranged sub-masses and each sub-mass is from an eccentric on an associated, with the Crank drive rotatably coupled eccentric disc, the connection between the eccentric pin and the associated Part mass is executed in each case as a crank loop.
  • a further advantageous variant is that the counterweight from at the upper mass around mutually parallel axes rotatably mounted, driven in opposite directions by the crank mechanism driven Imbalance exists whose momentum and mutual momentum Phase are set up so that they are one of the Work mass counteracting directed vibration, wherein a further embodiment is that the counterweight from two symmetrical to the direction of movement of the working mass next to each other at about the same height in this direction arranged, in opposite directions rotatably coupled directly to each other, consists of crank mechanism driven flyweights.
  • the renewal trained ramming device is in a first, in particular with 100a designated embodiment in the Figs. 1 and 2 and in a second, generally designated 100b Embodiment shown in Figs. 3 and 4, wherein usually by hand on a guide bracket or a Drawbar guided ramming tool referred to as 110a and 110b is.
  • the ramming tool 110a is about parallel links 112 and 114 connected to a single-axle chassis 116a, the two wheels 118 and 120, whose track is the width of the padfoot 12th of the ramming tool 110a does not exceed.
  • the ramming tool 110b is approximately rigidly connected to the chassis 116b, i. it Only a slight relative movement by elastic attenuators 124 and 126 between the ramming tool 110b and the chassis 116b allows the transmission of vibrations to counteract the chassis 116b.
  • Another, striking difference is that the suspension 116b by a third jockey wheel 128 to a three-point suspension is added to the stability, especially at off ramming tool 110b to improve.
  • This third jockey wheel 128 is supported by a crankcase 14 of the Tamping tool 110b mounted arm 130 is worn.
  • Stampffußes 12 serves in the crankcase 14 of the ramming tool 110a and 110b arranged crank drive, which will be explained in more detail with reference to FIGS. 5 to 13.
  • crank mechanism rammed 100a or 100b provided with an internal combustion engine by the chassis 116a and 116b is supported and arranged in the area 134 is.
  • FIGS. 1 and 2 is a Oscillation between the ramming tool 110a and the chassis 116a possible with a relatively large angular deflection.
  • This device 100a is therefore equipped with a hydraulic drive, the one with the engine, not shown in the area 134 connected hydraulic pressure source includes.
  • On the crankcase 14 is a hydraulic motor 136 for operating the crank mechanism attached, via supply lines 138 to the pressure source connected is.
  • Supply lines 140 lead in the area of the chassis 116a to a hydraulic drive 142 of the Landing wheels.
  • At the relatively low movement between the ramming tool 110b and the chassis 116b may be a direct drive connection between the arranged in the region 134 internal combustion engine and arranged in the crankcase 14 crank mechanism be provided, with only a small compensation of the axial offset is required, the expert no difficulties prepares. It can therefore rely on a hydraulic drive waived and provided to drive the wheels a chain drive 144 become.
  • the ramming tool 110a or 110b is dynamic from one associated with the padfoot 12 Working mass over one of a bellows fairing section 18 hidden spring set with a crank mechanism is connected, which is stored in the so-called.
  • Upper mass represented by the crankcase 14 in FIGS becomes.
  • the crank mechanism is a vibration between Built up and working mass.
  • the upper mass are kept as small as possible. Serve this purpose the measures described below with reference to FIGS. 5 to 13.
  • FIG. 5 shows the crank mechanism via an engine output shaft 22 supplied with drive energy, with a Pinion 24 is provided with a crank 26 in Intervention is.
  • the crank pulley 26 carries two by about 180 ° offset crankpins 28 and 30 (Figure 6).
  • the crank pin 28 is about a bow-shaped, the output shaft 22 encompassing Connecting rod 32 connected to a guide piston 34 which in a connected to the crankcase 14 piston guide 36 in the direction the axis 16 is arranged to be movable and - in Fig. 5th obscured by the bellows-like section 18 - over the Federsatz with the padfoot 12 is connected.
  • the crankpin 30 is connected via a connecting rod 38, a piston 40 which also in the direction of the axis 16 movable in a piston guide 42 is arranged and together with the connecting rod 38 a Countermass to working mass forms.
  • Fig. 6 is between the crank pin 28 and 30 an angle kelabstand of 180 ° shown. This would the piston or the Counter mass 40 reach the top dead center when the with the Not shown spring set associated guide piston 34 its bottom dead center reached.
  • the piston 40 is dependent on design features of the spring set the top dead center delayed reach, which is why the angular distance by a certain phase shift angle less than 180 ° must be selected. In In practice, this phase shift angle can be 50-70 °.
  • crank disk 26 1 When in Figs. 7 and 8 variant illustrated with the pinion gear 24 1 to the output shaft 22 1 engaged crank disk 26 1 is provided with a for forming the crankpin 28 1 and 30 1 cranked crank 29, wherein the free end the crank 29 forming crank pin 28 1 engages in a sliding block 31 which is slidably disposed in a guide slot 33 which is formed in a piston serving as counterweight 40 1 .
  • the piston 40 1 is movably guided parallel to the movement axis 16 in a guide 42 1 formed on the crankcase 14 1 .
  • the connecting rod 32 1 On the crank pin 28 1 , the connecting rod 32 1 is mounted for connection to the guide piston, not shown, the movement transmission to the spring set serving.
  • the operation of this Varriante largely corresponds to the construction of FIGS. 5 and 6, but allows because of the drive of the counterweight by a crank grinding a shortened in the direction of the movement axis 16 construction.
  • a variant which also provides a crank grinding for the counterweight, the arrangement allows a further reduction.
  • the provided with the crank pin 28 2 for the connecting rod 32 2 for transmitting motion on the spring set crank 26 2 is rotatably connected to a coaxially arranged gear 35, with both sides of the movement axis 16 and with respect to this at the same height two toothed on the circumference Eccentric discs 37 and 39 are engaged.
  • the eccentric discs each carry an eccentric pin 30a 2 and 30b 2 , the guide slots 33a 2 and 33b 2 of two identically formed pistons 40a 2 and 40b 2 which together form the counterweight and the associated ones in them, on the crankcase 14 2 trained guides 42a 2 and 42b 2 are slidably mounted parallel to the axis of movement.
  • a toothed wheel 35 3 is non-rotatably connected to the crank disk 26 3 for the actuation of the connecting rod 32 3 and coaxial with it.
  • On both sides of the movement axis 16 and with the same distance from this and at the same height in relation to these two intermeshing toothed disks 37 3 and 39 3 of the same size and number of teeth are arranged, which are each provided with a flyweight 41 and 43 respectively.
  • the toothed disc 37 3 is rotatably and coaxially connected to a gear 45 which is in engagement with the gear 35 3 of the same number of teeth, so that the two flyweights 41 and 43 in a predetermined phase position for movement of the connecting rod 32 3 move in opposite directions.
  • the centrifugal weights 41 and 43 are arranged such that their respective positions are mirror images of the movement axis 16. As a result, both side forces are avoided, as they are caused in the embodiments of FIGS. 5 and 6 by the inclined connecting rod 38, as well as friction losses in the guides 33, 33a 2 and 33b 2 shown in FIGS. 7 to 9 avoided.
  • the variant according to FIG. 11 shows an unbalance acting on the crank mechanism in only one direction and two counterbalancing imbalances which create a mass balance and thus also prevent any lateral movement.
  • the imbalance on the crank mechanism is represented by the flyweight 47 on the crank disk 26 4 .
  • Two in diameter with the crank disc 26 4 matching, provided with centrifugal weights 41 4 and 43 4 discs 37 4 and 39 4 are arranged symmetrically to the movement axis.
  • the three disks 26 4, 37 4 and 39 4 are connected by a slip-free transmission connection, for example a chain 51 to move together such that the two discs 37 4 and 39 4, but move in the same direction of rotation opposite to the crank disk 26. 4

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Civil Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Environmental & Geological Engineering (AREA)
  • Soil Sciences (AREA)
  • Architecture (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Agronomy & Crop Science (AREA)
  • Mechanical Engineering (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Soil Working Implements (AREA)
  • Transmission Devices (AREA)
  • Road Paving Machines (AREA)

Claims (24)

  1. Engin de damage (100a, 100b) pouvant être guidé à la main au moyen d'un arceau de guidage ou similaire pour le compactage du sol, comportant un outil de damage (110a, 110b) dans lequel une masse de travail (12) peut être entraínée linéairement dans un sens et dans l'autre par un moteur à combustion interne, par l'intermédiaire d'une transmission à manivelle (26, 28, 30), dans lequel
    l'outil de damage (110a, 110b) est soutenu en outre par rapport au sol par un châssis (116a, 116b) à au moins un essieu,
    un jeu de ressorts est disposé entre la transmission à manivelle (26, 28, 30) et la masse de travail (12),
    l'outil de damage (110a, 110b) est relié au châssis (116a, 116b) déplaçable dans une mesure limitée par des éléments de liaison élastiques (124, 126), ou est relié déplaçable par des bras oscillants parallèles (112, 114) ; et dans lequel
    l'outil de damage (110a, 110b) est déplaçable, par rapport au châssis (116a, 116b), pendant le fonctionnement de l'engin de damage (100a, 100b), pour contrer la transmission des oscillations.
  2. Engin de damage selon la revendication 1, caractérisé en ce que le châssis supplémentaire porte le moteur à combustion interne.
  3. Engin de damage selon la revendication 1 ou 2, caractérisé en ce que le châssis (116a, 116b) est pourvu de son propre dispositif d'entraínement (142, 144).
  4. Engin de damage selon la revendication 3, caractérisé en ce que le dispositif d'entraínement (142, 144) du châssis peut commuter entre la marche avant et la marche arrière.
  5. Engin de damage selon l'une des revendications 3 ou 4, caractérisé en ce que pour produire le mouvement de damage et pour l'entraínement autonome il est prévu une source d'énergie commune.
  6. Engin de damage selon la revendication 5, caractérisé en ce qu'il est prévu une transmission hydraulique des forces (136, 138) au moins pour l'entraínement de la transmission à manivelle.
  7. Engin de damage selon l'une des revendications 3 à 6, caractérisé en ce que la transmission des forces au châssis s'effectue par une transmission à chaíne (144).
  8. Engin de damage selon l'une des revendications précédentes, caractérisé en ce qu'une masse supérieure, portant la transmission à manivelle, est reliée de manière approximativement rigide au châssis (116b).
  9. Engin de damage selon la revendication 8, caractérisé en ce que la masse supérieure est reliée au châssis, de manière déplaçable dans une mesure limitée, par des éléments de liaison (124, 126) élastiques.
  10. Engin de damage selon l'une des revendications 8 ou 9, caractérisé en ce que le châssis (116b) est complété en un châssis à trois points par une roue d'appui (128) supplémentaire sur le côté du pied (12) de la dame opposé à l'essieu moteur.
  11. Engin de damage selon la revendication 6 ou selon les revendications 6 et 7, caractérisé en ce qu'une masse supérieure, portant la transmission à manivelle, est reliée au châssis (116a), de manière déplaçable, par un système d'articulation (112, 114).
  12. Engin de damage selon la revendication 11, caractérisé en ce que le système d'articulation est constitué de bras oscillants parallèles (112, 114).
  13. Engin de damage selon l'une des revendications précédentes, caractérisé par une contre-masse (40 : 401 : 40a2, 40b2 ; 41, 43 ; 414, 434. 47 ; 59, 61) qui peut être entraínée par le moteur au moins sur une grande partie de la distance de déplacement de la masse de travail, dans le sens opposé à son déplacement.
  14. Engin de damage selon la revendication 13, caractérisé en ce que l'entraínement de la contre-masse (40 : 401 : 40a2, 40b2 ; 41, 43 ; 414, 434. 47 ; 59, 61) est dérivé de la transmission à manivelle.
  15. Engin de damage selon l'une des revendications 13 ou 14, caractérisé en ce que le déplacement de l'extrémité (34), reliée à la transmission à manivelle, du jeu de ressorts et le déplacement de la contre-masse (40 : 401 : 40a2, 40b2 ; 41, 43 ; 414, 434. 47 ; 59, 61) sont décalés l'un par rapport à l'autre et par rapport à l'angle de manivelle, de 180° moins un déphasage dérivé des paramètres de construction du jeu de ressorts.
  16. Engin de damage selon l'une des revendications 13 à 15, caractérisé en ce que la contre-masse (40 : 401 : 40a2, 40b2) est guidée sur la masse supérieure parallèlement à la direction de déplacement de la masse de travail.
  17. Engin de damage selon la revendication 16, caractérisé en ce que la contre-masse est entraínée par un excentrique de compensation (30 ; 301 ; 30a2, 30b2) sur la transmission à manivelle.
  18. Engin de damage selon la revendication 17, caractérisé en ce que l'excentrique de compensation (30) entraíne la contre-masse (40) par une bielle (38).
  19. Engin de damage selon la revendication 17, caractérisé en ce que la liaison entre la contre-masse (401 : 40a2, 40b2) et l'excentrique de compensation (301 ; 30a2, 30b2) est réalisé comme mécanisme à manivelle.
  20. Engin de damage selon l'une des revendications 14 ou 15, caractérisé en ce que la contre-masse est constituée de deux masses partielles (40a2, 40b2) disposées chacune sur l'un ou l'autre côté de la transmission à manivelle, approximativement à même hauteur par rapport à l'axe de rotation de la transmission à manivelle, et chaque masse partielle est entraínée par un axe d'excentrique (30a2, 30b2) sur un disque d'excentrique (37, 39) qui lui est associé et couplé tournant avec la transmission à manivelle, la liaison entre l'axe d'excentrique et la masse partielle correspondante étant réalisée respectivement comme un mécanisme à manivelle.
  21. Engin de damage selon l'une des revendications 14 ou 15, caractérisé en ce que la contre-masse est constituée de balourds (41, 43 ; 414, 434. 47 ; 59, 61) montés tournants sur la masse supérieure autour d'axes parallèles les uns aux autres, et entraínés en rotation en sens contraire par la transmission à manivelle, balourds dont le moment d'inertie et les relations opposées des phases sont tels qu'ils produisent une oscillation dirigée dans le sens opposé à la masse de travail.
  22. Engin de damage selon la revendication 21, caractérisé en ce que la contre-masse est constituée de deux masselotes (41, 43) disposées symétriquement à la direction de déplacement de la masse de travail, côte à côte, à peu près à même hauteur dans cette direction et couplées directement entre elles de manière à tourner en sens contraire, et entraínées par la transmission à manivelle.
  23. Engin de damage selon la revendication 21, caractérisé en ce que la contre-masse est constituée d'une première masselote (47) calée directement sur l'arbre de la transmission à manivelle, et de deux deuxièmes masselotes (414, 434) disposées côte à côte symétriquement par rapport à la direction de déplacement de la masse de travail, à peu près à même hauteur dans cette direction, et dont les moments d'inertie sont égaux, lesquelles deuxièmes masselotes sont entraínées en rotation par la transmission à manivelle dans le sens contraire à la première masselote (47) et dont le moment d'inertie est environ la moitié du moment d'inertie de la première masselote (47).
  24. Engin de damage selon la revendication 21, caractérisé en ce que la contre-masse est constituée d'une première masselote (61) calée directement sur l'axe de rotation de la transmission à manivelle et d'une deuxième masselote (59) disposée derrière la première, qui présente approximativement le même moment d'inertie que la première masselote (61) et est entraínée dans le sens contraire à la première masselote (61), autour d'un axe de rotation légèrement décalé par rapport à l'axe de rotation de la transmission à manivelle, parallèlement à la direction de déplacement de la masse de travail.
EP98909445A 1997-04-18 1998-02-11 Compacteur destine au compactage du sol Expired - Lifetime EP0975839B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE29707017U DE29707017U1 (de) 1997-04-18 1997-04-18 Stampfgerät zur Bodenverdichtung
DE29707017U 1997-04-18
PCT/EP1998/000768 WO1998048119A1 (fr) 1997-04-18 1998-02-11 Compacteur destine au compactage du sol

Publications (2)

Publication Number Publication Date
EP0975839A1 EP0975839A1 (fr) 2000-02-02
EP0975839B1 true EP0975839B1 (fr) 2005-10-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP98909445A Expired - Lifetime EP0975839B1 (fr) 1997-04-18 1998-02-11 Compacteur destine au compactage du sol

Country Status (5)

Country Link
US (1) US6293729B1 (fr)
EP (1) EP0975839B1 (fr)
JP (1) JP3776131B2 (fr)
DE (2) DE29707017U1 (fr)
WO (1) WO1998048119A1 (fr)

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* Cited by examiner, † Cited by third party
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DE19714555C2 (de) * 1997-04-09 2001-06-21 Wacker Werke Kg Arbeitsgerät, insbesondere Stampfgerät zur Bodenverdichtung oder Hammer
DE19840453C2 (de) * 1998-09-04 2000-09-21 Wacker Werke Kg Bodenverdichtungsvorrichtung mit ausfahrbarem Fahrwerk
DE20105768U1 (de) 2001-03-30 2001-06-21 BOMAG GmbH & Co. oHG, 56154 Boppard Vibrationsstampfer
DE10226920B4 (de) * 2002-06-17 2007-08-23 Wacker Construction Equipment Ag Bodenverdichtungsvorrichtung mit Fahrwerk
US6742960B2 (en) 2002-07-09 2004-06-01 Caterpillar Inc. Vibratory compactor and method of using same
US20060165488A1 (en) * 2005-01-27 2006-07-27 Keith Morris Hand held tamping device
CA2507397A1 (fr) * 2005-02-07 2006-08-07 3980367 Canada Inc. Ensemble de transport a roues pour vibrofonceur
US7354221B2 (en) * 2005-02-28 2008-04-08 Caterpillar Inc. Self-propelled plate compactor having linear excitation
US7144195B1 (en) * 2005-05-20 2006-12-05 Mccoskey William D Asphalt compaction device
US20060285924A1 (en) * 2005-05-20 2006-12-21 Mccoskey William D Asphalt compaction device with pneumatic wheels
DE102005058485A1 (de) * 2005-12-07 2007-06-14 Wacker Construction Equipment Ag Vibrationsplatte mit Stabilisationseinrichtung
DE202006013718U1 (de) 2006-09-07 2007-03-08 Bomag Gmbh Transportvorrichtung für einen Vibrationsstampfer
EP2245229A1 (fr) * 2008-01-24 2010-11-03 Lord Corporation Compacteur motorisé de sol de construction et procédé de fabrication
DE502008001334D1 (de) * 2008-07-01 2010-10-28 Anlagentech Baumasch Ind Schwingungserzeuger
DE102008045557B4 (de) * 2008-09-03 2012-04-12 Bomag Gmbh Transportanbau einer Vibrationsplatte
DE102011115008A1 (de) * 2011-10-06 2013-04-11 Wacker Neuson Produktion GmbH & Co. KG Elektrowerkzeug mit Schutzhaube
US20160340849A1 (en) 2015-05-18 2016-11-24 M-B-W, Inc. Vibration isolator for a pneumatic pole or backfill tamper
JP6839110B2 (ja) * 2018-01-29 2021-03-03 酒井重工業株式会社 締固め機
CN109898493B (zh) * 2019-04-02 2020-08-28 高超 一种水利施工振动碾压装置
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DE29707017U1 (de) 1997-07-10
JP2001521593A (ja) 2001-11-06
DE59813124D1 (de) 2006-03-02
JP3776131B2 (ja) 2006-05-17
WO1998048119A1 (fr) 1998-10-29
EP0975839A1 (fr) 2000-02-02
US6293729B1 (en) 2001-09-25

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