EP3237687B1 - Amortisseur de vibrations pour articulation d'accouplement d'un dispositif de vibration en profondeur - Google Patents

Amortisseur de vibrations pour articulation d'accouplement d'un dispositif de vibration en profondeur Download PDF

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Publication number
EP3237687B1
EP3237687B1 EP15823601.8A EP15823601A EP3237687B1 EP 3237687 B1 EP3237687 B1 EP 3237687B1 EP 15823601 A EP15823601 A EP 15823601A EP 3237687 B1 EP3237687 B1 EP 3237687B1
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EP
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Prior art keywords
vibration damper
fastening element
coupling
radial projection
radially
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EP15823601.8A
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German (de)
English (en)
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EP3237687A1 (fr
Inventor
Albert Schneider
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Rsm Ingenieure and Willi Meyer Bauunternehmen GmbH In GbR GmbH
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Rsm Ingenieure and Willi Meyer Bauunternehmen GmbH In GbR GmbH
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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
    • E02D3/054—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil involving penetration of the soil, e.g. vibroflotation

Definitions

  • the invention relates to a vibration damper for a coupling joint of a deep vibrator according to the preamble of claim 1, a coupling joint of a deep vibrator with such a vibration damper according to claim 10 and a deep vibrator with such a coupling joint according to claim 14.
  • a deep vibrator is a horizontal vibration generating device for soil stabilization of unsustainable soil. Deep vibrators are used to perform various vibratory methods to improve the structure of the subsoil if it does not have sufficient bearing capacity for the proposed project. For this purpose vibrations are introduced into the soil by the deep vibrator.
  • Coarse-grained and mobile soils such as e.g. Sand or gravel can be consolidated by these vibrations, i. are compacted by being brought into a denser storage (Rütteldruckmaschine).
  • the deep vibrator is introduced by air flushing in the dry process or by water flushing in the wet process in the ground and made the consolidation when pulling the Tiefenrüttlers from the ground.
  • the deep vibrator can also be designed as a lock vibrator in order to be able to introduce the addition material through a lock via a transport tube to the vibrator tip and there into the cavity created by lifting and lowering the deep vibrator.
  • Deep vibrators have a cylindrical metal tube as a housing or Trottlergephase, the lower end of the housing tip or Trottlerspitze represents, with which they can penetrate into the ground.
  • the striking mechanism is arranged within the housing and above the housing tip.
  • a in general. arranged electrical drive which is connected to the percussion and this can drive, with a hydraulic drive is possible.
  • This entire area of the housing with drive and percussion can be referred to as percussion gear housing.
  • the housing is connectable at its upper end via a Rüttler coupling with an extension tube in order to be suspended or fastened by means of this with a suspension to an excavator or a leader-guided carrying device.
  • the striking mechanism has an imbalance weight which can rotate about the longitudinal axis of the deep vibrator within the striking mechanism housing by means of the drive.
  • the rotating imbalance weight can put the striking mechanism housing together with the housing tip in a swinging, tumbling rotational movement about the longitudinal axis, so that the surrounding liquefied soil material displaced radially and / or can be rearranged.
  • the clutch (Rüttler coupling) connects the percussion mechanism including the drive or the striking mechanism housing vibration-damping with the coupling punch, which in turn is rigidly connected to the extension tube.
  • the coupling is used to connect the percussion mechanism and the coupling punch so that the hammer mechanism can be safely guided in the direction of the longitudinal axis, ie pressed and pulled, and at the same time can perform its pendulum motion about the longitudinal axis.
  • This part of the deep vibrator can also be referred to as a coupling joint.
  • the coupling joint is designed to be elastic to allow the pendulum movement of the striking mechanism about the longitudinal axis. At the same time, the elasticity of the coupling joint is used to absorb bouncing impacts, which can be introduced by the shaking of the soil in the hammer mechanism to keep them away from the coupling punch and thus from the carrier or excavator. Also, this is to avoid the transmission of the vibrations of the vibrating on support or excavator.
  • the coupling joint is usually provided by one or more vibration dampers, e.g. realized a vibrating metal, which represents the actual coupling joint.
  • the vibration metal may also be referred to as a vibration damper bush or shock absorber.
  • the vibrating metal is a rubber-metal compound in which an elastic rubber body is vulcanized between two metal parts and can act elastically damping between them.
  • the upper part of the rocker metal in the direction of the longitudinal axis can be fastened to the coupling punch and the lower part of the rocker metal in the direction of the longitudinal axis can be fastened in the coupling housing.
  • radially inner part of the oscillating metal can be fastened to the coupling punch and the radially outer part of the oscillating metal to the coupling housing.
  • the concrete designs of the coupling joint are individual construction of the individual production companies of deep vibrators.
  • the coupling can be designed differently and is generally an individual design of the manufacturers of deep vibrators.
  • couplings are known which are fully elastic, i. have only vibration metals, as well as clutches, in addition to vibration metals and pendulum bearings or the like, which may be a self-aligning ball bearing or a spherical roller bearing. These are structured differently and can have a different transmission behavior.
  • a self-aligning bearing can withstand axial and radial loads and is well suited to compensate for misalignments.
  • Self-aligning bearings are suitable for the heaviest loads, ie they have high load capacities.
  • the EP 1 016 759 A1 describes a depth vibration device which is lowered vertically into the ground.
  • an imbalance weight is rotated about the longitudinal axis of the device, so that the device follows a rotation path in a horizontal plane.
  • the angle between the deflection of the device in the rotation path plane and the imbalance weight within the device is determined and used to calculate the degree of compaction, which in turn is used to control the compaction performance of the device.
  • the DE 102 32 314 describes a vibratory drilling tool with a shaped drill having a radial vibrator that includes a rotating mass to drive the shaped drill into the ground.
  • An additional vibrator in the head of the drill bit generates axial vibrations for faster penetration of hard soil layers.
  • a vibration damping insert is positioned between the vibrators while a conventional damping insert is positioned between the drill bit and the carrier.
  • the axial vibrator works as a hydraulic / pneumatic hammer.
  • the vibrators are driven by electric, hydraulic or pneumatic motors.
  • the drill bit has an integral supply of ballast material to refill the hole as the drill bit is withdrawn.
  • the EP 1759 125 B1 describes a device for guiding a shaft in an oscillatory motion about a pivot point located on the axis of the shaft, the device having a spherical ball bearing mounted on the shaft within two ball bearings arranged one above the other and in a fixed support are mounted.
  • the WO 02 077 371 A1 describes a depth vibrator with a vibrator tube and an eccentric plate, which is disposed within the vibrator tube and around a Eccentric shaft rotates, and a motor that drives the eccentric shaft and which is located outside of the vibrator tube.
  • An object of the present invention is to provide a vibration damper for a coupling joint of a deep vibrator, which is compact and at the same time can absorb both torsional forces and tensile / compressive forces.
  • the present invention relates to a vibration damper for a coupling joint of a deep vibrator for compacting a soil.
  • the coupling joint is designed to be able to be arranged radially between a radially inwardly lower end of a coupling ram of the deep vibrator and a radially outer side coupling housing of the deep vibrator.
  • the coupling joint has a first fastening element, a second fastening element and a spring element arranged at least in sections radially between the first fastening element and the second fastening element.
  • the fastening elements may be metal elements and the spring element may be a rubber body, so that the vibration damper may also be referred to as a vibration metal.
  • the rubber body may be vulcanized to the two metal elements, whereby a firm connection between these elements can be created.
  • vibration damper can be constructed relatively short and compact in this way in the direction of the longitudinal axis. Further, by this arrangement, vibrations from the upper coupling rubber, which elastically connects the outer edges of the coupling housing and the coupling punch together and the Termination of the clutch joint against the environment serves to be kept away because they can be excluded by the radially formed vibration damper. Vibrations can lead to a breakage of the upper coupling rubber, which can then cause soil between the coupling punch and the clutch housing, which can lead to a stiffening or to a breakage of the clutch. This risk can thus be reduced.
  • the vibration damper according to the invention is characterized in that at least one fastening element has at least one radial projection which extends at least partially radially to the other fastening element and against which the spring element can be pressed at least partially in the direction of the longitudinal axis, wherein the radial projections partially radially overlap.
  • the radial projection narrows the radial distance between the two fasteners, wherein the remaining regions of the fastening elements have a greater distance from each other and in other words, the projections extend in the radial direction so that they overlap viewed from the longitudinal axis.
  • the spring body is arranged at least partially completely in the direction of the longitudinal axis between the projections, so that the damping of tensile or compressive forces can be further improved.
  • a surface of the radial projection is created, which is at least partially aligned in the direction of the longitudinal axis and can also be referred to as a collar or plate.
  • the spring element can be pressed against this surface of the radial projection or pulled away from it.
  • the tensile or compressive forces can be damped, which can occur in particular during retraction into the soil and during the drawing process during soil compaction.
  • the spring element torsional forces and bounce can continue to be recorded and a pendulum motion allows.
  • Such loads can not be absorbed by a pendulum bearing.
  • a vibration metal is cheaper than a self-aligning bearing.
  • the first fastening element has a first radial projection and a second radial projection, which are arranged spaced from one another in the direction of the longitudinal axis.
  • tensile or compressive forces can be damped in both directions of the longitudinal axis, which is the damping Effect improved.
  • the damping Effect improved can be achieved by the arrangement of mutually offset two projections of the first fastener with intermediate spring body that pulls at a load in the direction of the longitudinal axis of the spring body on the one projection and presses on the other projection. If the direction of the load reverses, the spring body pushes on the one projection and pulls on the other projection. In this way, with identical design of the projections equal damping effects can be achieved in both directions. If the projections are configured differently, better damping effects than with only one projection can be achieved.
  • the second fastening element has a radial projection, which is spaced apart in the direction of the longitudinal axis to the ends of the second fastening element, preferably approximately centrally. This also makes it possible to achieve a damping of tensile or compressive forces, in which arrangement the spring element can press on the one projection from both sides in the direction of the longitudinal axis or can pull on this.
  • the radial projection of the second fastening element is arranged in the direction of the longitudinal axis between the first radial projection and the second radial projection of the first fastening element. This arrangement further improves the damping of tensile or compressive forces, because the spring body is fastened in the direction of the longitudinal axis to partially opposite surfaces and in each case can pull or press against them.
  • At least one radial projection is at least partially obliquely formed.
  • An oblique course is understood to mean that this oblique surface of the projection extends partially in the radial direction and at the same time partially in the direction of the longitudinal axis. In this way it can be achieved that the spring body over all its areas can absorb radial forces, torsional forces and tensile and compressive forces.
  • the first radial projection and the second radial projection of the first fastening element are formed at least partially opposite to each other obliquely.
  • the opposite projection of the second fastener include between them and the spring element can simultaneously absorb radial forces, torsional forces and tensile and compressive forces.
  • the radial projection of the second fastening element is formed at least in sections on one side, preferably on both sides, obliquely. In this way, this projection can also help that the spring body can absorb both radial forces and tensile and compressive forces.
  • the radial projection of the second fastening element is designed to extend substantially parallel to the first radial projection of the first fastening element and / or the radial projection of the second fastening element is formed to extend substantially parallel to the second radial projection of the first fastening element.
  • the first fastening element is arranged radially on the outside and the second fastening element is arranged radially on the inside.
  • the present invention also relates to a coupling joint for a deep vibrator for compacting a floor with a first vibration damper as described above.
  • a coupling joint for a deep vibrator for compacting a floor with a first vibration damper as described above.
  • the properties and advantages of the vibration damper according to the invention described above can be used in a coupling joint of a deep vibrator.
  • the coupling joint further comprises a second vibration damper having a first fastening element, a second fastening element and a spring element arranged at least partially radially between the first fastening element and the second fastening element, wherein the second vibration damper in the direction of the longitudinal axis below or above the first vibration damper is arranged.
  • the second vibration damper is provided for receiving torsional forces about the longitudinal axis, which represent the essential loads in a deep vibrator. In this way, this task can be supported by the second vibration damper, so that the first vibration damper can be formed and used in addition to the damping of tensile and compressive forces, without the coupling joint could not absorb torsional forces sufficient.
  • the coupling joint further comprises a third vibration damper with a first fastener, a second fastener and at least partially radially disposed between the first fastener and the second fastener spring element, wherein the third vibration damper relative to the first vibration damper the second vibration damper is arranged opposite in the direction of the longitudinal axis.
  • the third vibration damper which is preferably constructed identically to the second vibration damper, the uptake of torsional forces can be further improved and the first vibration damper relieved of this task even further. Due to the two-sided arrangement of the second and third vibration damper in the direction of the longitudinal axis about the first vibration damper around the substantially torsional forces receiving elements can be evenly distributed distributed in the coupling joint.
  • the first vibration damper and the second vibration damper and / or the third vibration damper are integrally formed.
  • the fastening elements may be integrally formed.
  • the spring body are further integrally formed. This simplifies the manufacture and assembly of the vibration damper and improves the positioning of the individual vibration damper to each other.
  • the present invention also relates to a deep vibrator for compacting a floor with a coupling joint as described above, wherein the coupling joint is radially inwardly connected to the lower end of a coupling ram of the deep vibrator and radially outside with a coupling housing of the deep vibrator.
  • the coupling joint is radially inwardly connected to the lower end of a coupling ram of the deep vibrator and radially outside with a coupling housing of the deep vibrator.
  • Fig. 1 shows a schematic representation of a deep vibrator 1.
  • the deep vibrator 1 extends substantially cylindrically in the direction of its longitudinal axis L, to which extends perpendicular to the radial direction R and the radius R.
  • the deep vibrator 1 has in the lower part of the representation of Fig. 1 the vibrator housing 10 and housing 10, which has a cylindrical housing part 11 and the striking mechanism housing 11, from which further down the housing tip 12 and Jottlerspitze 12 extends, with the deep vibrator 1 can retract into the ground.
  • the striking mechanism 3 is arranged, which has an electric drive 2, which can put an imbalance weight 31 in the unbalance generating rotational movement about the longitudinal axis L via an imbalance weight shaft 30.
  • the deep vibrator 1 has in the upper part of the representation of Fig. 1 the coupling ram 8 and the linkage 8, which is connected via a coupling 4 and a croquttler coupling 4 with the percussion mechanism 3 and its striking mechanism housing 11.
  • Fig. 2 shows a schematic representation of a coupling 4 according to the invention a deep vibrator 1 in a first embodiment.
  • Fig. 3 shows a schematic representation of a coupling 4 according to the invention a deep vibrator 1 in a second embodiment.
  • the clutch 4 has a radially outer cylindrical clutch housing 40 which is connected in the direction of the longitudinal axis L via a cylindrical annular coupling housing elastic closure 41, which may also be referred to as a coupling rubber 41, with the cylindrical outer wall or outside of the clutch ram 8.
  • the coupling rubber 41 serves the elastic completion of the clutch 4 out to the surrounding soil.
  • the clutch 4 is connected via a coupling joint 42 with the lower end 80 of the coupling punch 8.
  • the coupling joint 42 has a first vibration damper 5, which is arranged centrally in the direction of the longitudinal axis L between a second, upper vibration damper 6 and a third, lower vibration damper 7.
  • Each vibration damper 5, 6, 7 has radially outboard a first fastening element 51, 61, 71, which is connected to the coupling housing 40, and a radially inner fastening element 52, 62, 72, which is connected to the lower end 80 of the coupling punch 8, on.
  • a spring element 53, 63, 73 is arranged.
  • the fastening elements 51, 52, 61, 62, 71, 72 are formed as metal elements 51, 52, 61, 62, 71, 72 and the spring elements 53, 63, 73 as elastic rubber body 53, 63, 73 and vulcanized to each other.
  • the vibration dampers 5, 6, 7 can therefore also be referred to as vibration metals 5, 6, 7.
  • the three vibration dampers 5, 6, 7 are formed as separate elements, which can be joined together to form the coupling joint 42.
  • the two embodiment of a coupling 4 according to the invention according to the Fig. 3 are the three vibration damper 5, 6, 7 made in one piece, wherein the metal elements 51, 52, 61, 62, 71, 72 are continuous, the elastic rubber body 53, 63, 73, however, are made in several parts.
  • the coupling joint 42 can absorb torsional forces, which is essentially taken over by the second, upper oscillating metal 6 and the third, lower oscillating metal 7.
  • the first, central oscillating metal 5 can absorb not only torsional forces but also tensile and compressive forces at the same time, as will be described in more detail below with reference to three embodiments of the vibrating metal 5 according to the invention.
  • Fig. 4 shows a schematic detail view of a vibration damper 5 or vibration metal 5 according to the invention in a first embodiment. Shown is the part of the vibrating metal 5 of Fig. 2 , which is disposed on the left between the lower end 80 of the coupling punch 8 and the clutch housing 40, so that the radial direction R in the illustration of Fig. 4 extends to the left and thus the longitudinal axis L is right of the illustration (not shown).
  • the first, radially outer metal element 51 has spaced apart in the direction of the longitudinal axis L and arranged at its upper or lower edge in the direction of the longitudinal axis L each have a radial projection 54, 55 which are equally radially inwardly to the second, radially inner metal element 52nd extend to a radius R1.
  • a radial projection 56 on the second, radially inner metal member 52 is disposed radially outwardly to the first, radially outer metal member 51 through extends to a radius R2.
  • the radius R1 is less than the radius R2, so that the projections 54, 55, 56 overlap in this area viewed from the longitudinal axis L. This overlap ensures that, at least in this area, forces FL in the direction of the longitudinal axis L can be transmitted via the elastic rubber body 53 between the metal elements 51, 52.
  • forces FL in the direction of the longitudinal axis L can be transmitted via the elastic rubber body 53 between the metal elements 51, 52.
  • the projections 54, 55, 56 are aligned obliquely and parallel to each other.
  • the spring body 53 can be formed with an approximately constant thickness between the metal elements 51, 52, so that the spring body 53 can produce a comparable resilient effect in all directions.
  • the oscillations of the percussion mechanism 3 with respect to the coupling ram 8 can be carried out or transmitted uniformly in this way.
  • the vibration metal 5 according to the invention, the projections 54, 55 of the first, radially outer metal element 51 are formed round or arcuate. As a result, even more even oscillations of the hammer mechanism 3 can be achieved with respect to the coupling punch 8.
  • the projections 54, 55, 56 are angular, so that they each have edges purely in the radial direction or purely in the direction of the longitudinal axis L. This may be the production of the Metal elements 51, 52 simplify and improve the transmission of tensile and compressive forces, however, limit the possibilities of the pendulum movements of the percussion mechanism 3 relative to the coupling ram 8 or make them less uniform.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Soil Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Agronomy & Crop Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Springs (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (14)

  1. Amortisseur de vibrations (5) destiné à une articulation d'accouplement (42) d'un dispositif de vibration en profondeur (1) servant à compacter un sol, l'articulation d'accouplement (42) étant conçue pour être agencé radialement entre une extrémité inférieure (80) radialement intérieure d'un vérin d'accouplement (8) du dispositif de vibration en profondeur (1) et un carter d'accouplement (40) radialement extérieur au dispositif de vibration en profondeur (1), ledit amortisseur de vibrations comprenant un premier élément de fixation (51), un second élément de fixation (52) et un élément ressort (53) agencé au moins en partie radialement entre le premier élément de fixation (51) et le second élément de fixation (52), caractérisé en ce qu'au moins un élément de fixation (51, 52) présente au moins une saillie radiale (54, 55, 56) qui s'étend au moins en partie radialement en direction de l'autre élément de fixation (51, 52) et contre lequel l'élément ressort (53) peut être pressé au moins en partie en direction de l'axe longitudinal (L), les saillies radiales (54, 55, 56) se chevauchant en partie radialement.
  2. Amortisseur de vibrations (5) selon la revendication 1, dans lequel le premier élément de fixation (51) présente une première saillie radiale (54) et une seconde saillie radiale (55) espacées l'une de l'autre en direction de l'axe longitudinal (L).
  3. Amortisseur de vibrations (5) selon la revendication 1 ou 2, dans lequel le second élément de fixation (52) présente une saillie radiale (56) espacée des extrémités du second élément de fixation (52) en direction de l'axe longitudinal (L), et de préférence équidistante de celles-ci.
  4. Amortisseur de vibrations (5) selon la revendication 2 ou 3, dans lequel la saillie radiale (56) du second élément de fixation (52) est disposée en direction de l'axe longitudinal (L) entre la première saillie radiale (54) et la seconde saillie radiale (55) du premier élément de fixation (51).
  5. Amortisseur de vibrations (5) selon l'une des revendications précédentes, dans lequel au moins une saillie radiale (54, 55, 56) est conçue pour s'étendre obliquement au moins en partie.
  6. Amortisseur de vibrations (5) selon l'une des revendications 2 à 5, dans lequel la première saillie radiale (54) et la seconde saillie radiale (55) du premier élément de fixation (51) sont conçues pour s'étendre au moins en partie obliquement de façon mutuellement opposée.
  7. Amortisseur de vibrations (5) selon l'une des revendications 3 à 6, dans lequel la saillie radiale (56) du second élément de fixation (52) est conçue pour s'étendre au moins en partie obliquement sur un côté, de préférence sur les deux côtés.
  8. Amortisseur de vibrations (5) selon l'une des revendications 3 à 7, dans lequel la saillie radiale (56) du second élément de fixation (52) est conçue pour s'étendre sensiblement parallèlement à la première saillie radiale (54) du premier élément de fixation (51), et/ou dans lequel la saillie radiale (56) du second élément de fixation (52) est conçue pour s'étendre sensiblement parallèlement à la seconde saillie radiale (55) du premier élément de fixation (51).
  9. Amortisseur de vibrations (5) selon l'une des revendications précédentes, dans lequel le premier élément de fixation (51) est disposé radialement à l'extérieur et le second élément de fixation (52) est disposé radialement à l'intérieur.
  10. Articulation d'accouplement (42) destinée à un dispositif de vibration en profondeur (1) servant à compacter un sol, comportant un premier amortisseur de vibrations (5) selon l'une des revendications précédentes.
  11. Articulation d'accouplement (42) selon la revendication 10, comportant en outre un deuxième amortisseur de vibrations (6), un premier élément de fixation (61), un second élément de fixation (62) et un élément ressort (63) disposé au moins en partie radialement entre le premier élément de fixation (61) et le second élément de fixation (62), le deuxième amortisseur de vibrations (6) étant disposé en dessous ou au-dessus du premier amortisseur de vibrations (5) en direction de l'axe longitudinal (L).
  12. Articulation d'accouplement (42) selon la revendication 11, comportant en outre un troisième amortisseur de vibrations (7), un premier élément de fixation (71), un second élément de fixation (72) et un élément ressort (73) disposé au moins en partie radialement entre le premier élément de fixation (71) et le second élément de fixation (72), le troisième amortisseur de vibrations (7) étant disposé, par rapport au premier amortisseur de vibrations (5), en face du deuxième amortisseur de vibrations (6) en direction de l'axe longitudinal (L).
  13. Articulation d'accouplement (42) selon la revendication 11 ou 12, dans lequel le premier amortisseur de vibrations (5) et le deuxième amortisseur de vibrations (6) et/ou le troisième amortisseur de vibrations (7) sont conçus d'un seul tenant.
  14. Dispositif de vibration en profondeur (1) servant à compacter un sol, comportant une articulation d'accouplement (42) selon l'une des revendications 10 à 13, l'articulation d'accouplement (42) étant reliée radialement à l'intérieur à l'extrémité inférieure (80) d'un vérin d'accouplement (8) du dispositif de vibration en profondeur (1) et radialement à l'extérieur à un carter d'accouplement (40) du dispositif de vibration en profondeur (1).
EP15823601.8A 2014-12-23 2015-12-21 Amortisseur de vibrations pour articulation d'accouplement d'un dispositif de vibration en profondeur Active EP3237687B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014019138.9A DE102014019138A1 (de) 2014-12-23 2014-12-23 Schwingungsdämpfer für ein Kupplungsgelenk eines Tiefenrüttlers
PCT/EP2015/080735 WO2016102433A1 (fr) 2014-12-23 2015-12-21 Amortisseur de vibrations pour articulation d'accouplement d'un dispositif de vibration en profondeur

Publications (2)

Publication Number Publication Date
EP3237687A1 EP3237687A1 (fr) 2017-11-01
EP3237687B1 true EP3237687B1 (fr) 2019-09-11

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EP (1) EP3237687B1 (fr)
DE (1) DE102014019138A1 (fr)
WO (1) WO2016102433A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE202019105307U1 (de) 2019-09-25 2019-10-21 Albert Schneider Tiefenrüttler zum Verdichten eines Bodens

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DE19859962C2 (de) * 1998-12-29 2001-07-12 Keller Grundbau Gmbh Verfahren und Vorrichtung zur Verbesserung eines Baugrundes unter Ermittlung des Verdichtungsgrades
DE10115107A1 (de) * 2001-03-27 2002-10-31 Wilhelm Degen Tiefenrüttler
DE10232314A1 (de) * 2002-07-17 2004-02-05 Bauer Spezialtiefbau Gmbh Vorrichtung und Verfahren zum Verdichten von Böden und zur Herstellung von säulenförmigen Körpern im Boden mit Hilfe von Tiefenrüttlern
CA2570791C (fr) * 2004-06-23 2013-12-17 Bertin Technologies Dispositif de guidage d'un arbre en mouvement oscillant
FR2941714B1 (fr) * 2009-01-30 2015-01-02 Cie Du Sol Dispositif vibreur a motorisation hydraulique pour machine de vibrocompactage.

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WO2016102433A1 (fr) 2016-06-30
DE102014019138A1 (de) 2016-06-23

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