WO2016102433A1 - 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
WO2016102433A1
WO2016102433A1 PCT/EP2015/080735 EP2015080735W WO2016102433A1 WO 2016102433 A1 WO2016102433 A1 WO 2016102433A1 EP 2015080735 W EP2015080735 W EP 2015080735W WO 2016102433 A1 WO2016102433 A1 WO 2016102433A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration damper
fastening element
radial projection
radially
coupling
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.)
Ceased
Application number
PCT/EP2015/080735
Other languages
German (de)
English (en)
Inventor
Albert Schneider
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.)
Rsm Grundbau and Willi Meyer Bauunternehmen GmbH In GbR GmbH
Original Assignee
Rsm Grundbau and Willi Meyer Bauunternehmen GmbH In GbR GmbH
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 Rsm Grundbau and Willi Meyer Bauunternehmen GmbH In GbR GmbH filed Critical Rsm Grundbau and Willi Meyer Bauunternehmen GmbH In GbR GmbH
Priority to EP15823601.8A priority Critical patent/EP3237687B1/fr
Publication of WO2016102433A1 publication Critical patent/WO2016102433A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
  • a deep vibrator is a horizontally vibration generating device for soil stabilization of unsustainable soil. Deep vibrators are used to carry out various
  • Vibration method used to improve the subsoil if this for the proposed project does not have sufficient capacity.
  • 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 (Rütteldruck compost).
  • the deep vibrator is doing by air flushing in
  • 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, by means of this with a suspension on an excavator or a leader guided
  • Supporting device can be suspended or attached.
  • 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 clutch) connects the striking mechanism with the drive or the
  • the coupling serves to connect the percussion mechanism and the coupling punch such that the percussion mechanism is guided safely in the direction of the longitudinal axis, i. can be pressed and pulled, and at the same time his
  • This part of the deep vibrator can also be referred to as a coupling joint.
  • the coupling joint is designed to be elastic to the pendulum movement of
  • the coupling joint is usually provided by one or more vibration dampers, e.g. one
  • Swing metal can 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 oscillating metal in the direction of the longitudinal axis may be about the coupling punch and the lower part of the longitudinal axis in the direction of the longitudinal axis
  • Swing metal may be mounted in the coupling housing. Also, 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 disadvantage here is that a self-aligning bearing has no elastic effect and thus can not absorb vibrations. Thus, this coupling joint no train and
  • An object of the present invention is to provide a vibration damper for a
  • 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 an at least partially radially arranged 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 comparatively short and compact in this way in the direction of the longitudinal axis. Furthermore, by this arrangement
  • Spring element can be pressed at least partially in the direction of the longitudinal axis.
  • 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.
  • 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 Projection or by tensile forces away from the radial projection, the spring element can be pressed against this surface of the radial projection and pulled away from it. As a result, 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.
  • Damping effects can be achieved as a single projection.
  • Fastening element on a radial projection which is spaced in the direction of the longitudinal axis to the ends of the second fastening element, preferably approximately centrally disposed. 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 partially in the direction of the longitudinal axis
  • the radial projections partially overlap radially.
  • the projections extend in the radial direction so that they overlap when 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.
  • 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 at least
  • 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 the first radial projection of the first
  • Fastening element substantially parallel extending formed and or or the radial projection of the second fastening element is formed substantially parallel to the second radial projection of the first fastening element.
  • 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. In this way, the previously described characteristics and advantages of the
  • vibration damper according to the invention are 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.
  • 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.
  • Vibration damper 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 fastening element, a second fastening element and at least partially arranged radially between the first fastening element and the second fastening element
  • Vibration damper is arranged opposite the second vibration damper in the direction of the longitudinal axis.
  • the third vibration damper which is preferably constructed identical to the second vibration damper, the inclusion of
  • Torsions further improved and the first vibration are further relieved of this task. 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.
  • Vibration dampers are integrally formed.
  • the fastening elements may be integrally formed.
  • the spring bodies are in one piece
  • 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 is a schematic representation of a deep vibrator
  • Fig. 2 is a schematic representation of a coupling according to the invention a
  • Fig. 3 is a schematic representation of a coupling according to the invention a
  • FIG. 4 shows a schematic detail view of a vibration damper according to the invention in a first embodiment
  • FIG. 5 shows a schematic detail view of a vibration damper according to the invention in a second embodiment
  • FIG. 6 is a schematic detail view of a vibration damper according to the invention in a third embodiment.
  • 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 the radial direction R or the radius R extends perpendicularly.
  • the deep vibrator 1 has in the lower region of the illustration of FIG. 1, the vibrator housing 10 and housing 10, which has a cylindrical housing part 11 and the
  • the deep vibrator 1 has in the upper part of the illustration of FIG. 1, the coupling ram 8 and the linkage 8, which is connected via a coupling 4 and a Trottler coupling 4 with the striking mechanism 3 and its striking mechanism housing 11.
  • FIG. 2 shows a schematic representation of a coupling 4 according to the invention of a deep vibrator 1 in a first embodiment.
  • FIG. 3 shows a schematic representation of a coupling 4 according to the invention of 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 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.
  • radially between the fastener pairs 51, 52, 61, 62, 71, 72 is a
  • 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.
  • Vibration damper 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 are connected to the
  • Clutch joint 42 can be joined together.
  • the three vibration dampers 5, 6, 7 are made in one piece, wherein the metal elements 51, 52, 61, 62, 71, 72 throughout, the elastic rubber body 53, 63, 73, however are executed in several parts.
  • 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 oscillating metal 5 of FIG. 2, which is arranged 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 to the 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 Rl.
  • 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 Rl 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 with an approximately constant thickness between the
  • Metal elements 51, 52 are formed so that the spring body 53 can produce a comparable resilient effect in all directions. Also, 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 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.
  • Vibration damper 5 second, radially inner fastening element or metal element of the first vibration damper 5

Landscapes

  • 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)

Abstract

L'invention concerne un amortisseur de vibrations (5) pour une articulation d'accouplement (42) d'un dispositif de vibration en profondeur (1) destiné à compacter un sol. L'articulation d'accouplement (42) est conçue pour pouvoir être disposée radialement entre une extrémité inférieure (80) radialement côté intérieur d'un vérin d'accouplement (8) du dispositif de vibration en profondeur (1) et un carter d'accouplement (40) radialement côté extérieur du dispositif de vibration en profondeur (1). Ledit amortisseur comprend un premier élément de fixation (51), un deuxième élément de fixation (52) et un élément ressort (53) agencé au moins en partie radialement entre le premier élément de fixation (51) et le deuxième élément de fixation (52). L'amortisseur de vibrations (5) est caractérisé en ce qu'au moins un élément de fixation (51, 52) comprend 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).
PCT/EP2015/080735 2014-12-23 2015-12-21 Amortisseur de vibrations pour articulation d'accouplement d'un dispositif de vibration en profondeur Ceased WO2016102433A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15823601.8A EP3237687B1 (fr) 2014-12-23 2015-12-21 Amortisseur de vibrations pour articulation d'accouplement d'un dispositif de vibration en profondeur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014019138.9 2014-12-23
DE102014019138.9A DE102014019138A1 (de) 2014-12-23 2014-12-23 Schwingungsdämpfer für ein Kupplungsgelenk eines Tiefenrüttlers

Publications (1)

Publication Number Publication Date
WO2016102433A1 true WO2016102433A1 (fr) 2016-06-30

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PCT/EP2015/080735 Ceased WO2016102433A1 (fr) 2014-12-23 2015-12-21 Amortisseur de vibrations pour articulation d'accouplement d'un dispositif de vibration en profondeur

Country Status (3)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117403622A (zh) * 2023-11-30 2024-01-16 北京振冲工程机械有限公司 超深振冲施工用振冲器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202019105307U1 (de) 2019-09-25 2019-10-21 Albert Schneider Tiefenrüttler zum Verdichten eines Bodens

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1016759A1 (fr) * 1998-12-29 2000-07-05 KELLER GRUNDBAU GmbH Méthode et dispositif d'amélioration du sol de fondation avec détermination du degré de compaction
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
WO2010086537A1 (fr) * 2009-01-30 2010-08-05 Soletanche Freyssinet Dispositif vibreur a motorisation hydraulique pour machine de vibrocompactage

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10115107A1 (de) * 2001-03-27 2002-10-31 Wilhelm Degen Tiefenrüttler
ATE465348T1 (de) * 2004-06-23 2010-05-15 Bertin Technologies Sa Vorrichtung zur schaftführung bei oszillationsbewegungen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1016759A1 (fr) * 1998-12-29 2000-07-05 KELLER GRUNDBAU GmbH Méthode et dispositif d'amélioration du sol de fondation avec détermination du degré de compaction
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
WO2010086537A1 (fr) * 2009-01-30 2010-08-05 Soletanche Freyssinet Dispositif vibreur a motorisation hydraulique pour machine de vibrocompactage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117403622A (zh) * 2023-11-30 2024-01-16 北京振冲工程机械有限公司 超深振冲施工用振冲器

Also Published As

Publication number Publication date
EP3237687A1 (fr) 2017-11-01
DE102014019138A1 (de) 2016-06-23
EP3237687B1 (fr) 2019-09-11

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