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EP1711660A1 - Appareil vitratoire pour pieux, pourvu de paliers pour des masses non equilibrees rotatives - Google Patents

Appareil vitratoire pour pieux, pourvu de paliers pour des masses non equilibrees rotatives

Info

Publication number
EP1711660A1
EP1711660A1 EP05706713A EP05706713A EP1711660A1 EP 1711660 A1 EP1711660 A1 EP 1711660A1 EP 05706713 A EP05706713 A EP 05706713A EP 05706713 A EP05706713 A EP 05706713A EP 1711660 A1 EP1711660 A1 EP 1711660A1
Authority
EP
European Patent Office
Prior art keywords
bearing
bearing bush
groove
ramming
bearings
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.)
Withdrawn
Application number
EP05706713A
Other languages
German (de)
English (en)
Inventor
Christian Heichel
Albrecht Kleibl
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.)
ABI GmbH
Original Assignee
ABI 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 ABI GmbH filed Critical ABI GmbH
Publication of EP1711660A1 publication Critical patent/EP1711660A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D13/00—Accessories for placing or removing piles or bulkheads, e.g. noise attenuating chambers
    • E02D13/02—Accessories for placing or removing piles or bulkheads, e.g. noise attenuating chambers specially adapted for placing or removing bulkheads
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D11/00—Methods or apparatus specially adapted for both placing and removing sheet pile bulkheads, piles, or mould-pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid

Definitions

  • It relates to a vibration device for ramming and pulling rammed material with bearings for rotating unbalanced masses, the unbalanced masses being arranged in a bearing flange by means of a bearing journal and a bearing bush, or with bearings for shafts to which the unbalanced masses are attached.
  • Rotating unbalanced masses are used in vibration devices for mechanical ramming and pulling of rammed material to generate vibrations which are transferred to the ramming material and thereby facilitate its penetration into the ground.
  • the pile can be e.g. consist of sheet piles, beams or steel pipes.
  • the technology is mainly used in the construction of port facilities and to protect deep construction pits against slipping earth material. With the increased use of technology, the pile material used became heavier and larger. The speed and static moment of the unbalanced masses were increased accordingly.
  • the rolling bearings used to support the unbalanced masses are only suitable for high speeds to a limited extent because their load capacity decreases with increasing speed, so that rolling bearings can only be used to a limited extent for the development and manufacture of larger and more powerful machines.
  • the invention is based on the object of designing a bearing for the unbalanced masses installed in vibration devices, which allows the generation and transmission of unbalanced forces to the pile at high speeds and also has a high load-bearing capacity.
  • bearings which are characterized in that - the bearings are liquid-lubricated plain bearings,
  • each bearing bush has at least two channels (bearing bush channels) running in the radial direction
  • each bearing bush has groove-shaped depressions on at least one end face which run in the radial direction or such nu LN th are attached in the axial contact surfaces of the unbalances or the shafts mounted in the plain bearings in the bearing bush,
  • the surface of the bearing journal or the shaft surrounded by the bearing bush has one or more groove-shaped depressions.
  • the bearing according to the invention is a liquid-lubricated plain bearing consisting of a bearing journal and bearing bush.
  • the bearing bush has two or more channels running in the radial direction. The channels are used to pass lubricant through to the bearing journal, which rests on the inside of the bearing bush and on the surface of which there are one or more groove-shaped depressions.
  • each bearing bush has at least one groove-shaped recesses on at least one end face, which run in the radial direction and allow the lubricant to be drained off with as little resistance as possible.
  • the core concept of the invention is that hydrodynamic plain bearings are installed for the transmission of the centrifugal forces, the bearing bushes of the liquid-lubricated plain bearings have more than just one channel in the radial direction, lubrication grooves on the surface of the journal support the even distribution of the lubricant and channels on the end faces derive the lubricant quickly from the bearing bushes. Due to the supply pressure and the rotational speed between the bearing journal surrounded by the bearing bush and the inside of the bearing bush, a thin film of liquid, which greatly reduces the frictional resistance between the bearing journal and the bearing bush. Lubrication grooves on the surface of the bearing journal promote the even distribution of the lubricant in the bearing.
  • the channels provided on the end faces of the bearing bushes are dimensioned so that the lubricant can be drained off with as little resistance as possible. This enables a high lubricant throughput and good heat dissipation.
  • Vibration devices are due to the increased load capacity of the bearings at high speeds. Due to the elimination of the rolling element cage, the dead weight and moment of inertia of the plain bearing according to the invention are significantly lower compared to a rolling bearing with a corresponding load-bearing capacity. The lower mass moment of inertia is particularly advantageous in the case of so-called directional shaking, because it causes constantly changing angular acceleration. In addition, the use of hydrodynamically lubricated plain bearings reduces the noise generated when operating the vibration device and favors their use in residential areas.
  • the bearing bush has eight channels running in the radial direction, and also a circumferential one on the outside of the unbalance flange
  • the channels leading radially inwards start from this groove.
  • the annular groove ensures that the lubricant supplied through the channel in the unbalance flange is evenly distributed over the entire outer circumference of the bearing bush and can flow quickly into the channels of the bearing bush.
  • at least one of the end faces in each bearing bush is designed as a contact surface.
  • these contact surfaces have groove-shaped depressions in the radial direction. These depressions should slide the lubricant as freely as possible so that new lubricant can flow in quickly.
  • the grooves are accommodated with an equally advantageous effect instead of in the contact surface in the axial contact surfaces of the unbalances or the shafts mounted in the slide bearings.
  • the surface of the bearing journal surrounded by the bearing bush has at least one groove-shaped depression in the azimuthal direction and / or in the axial direction.
  • This design of the trunnion surface supports the fast and even distribution of the lubricant over the entire load range of the trunnion.
  • the length of the groove in the azimuthal direction is dimensioned such that it extends over the openings of at least two adjacent bearing bushing channels.
  • the grooves running in the axial direction end blind and thereby prevent the lubricant from flowing away without pressure.
  • a bearing clearance between the journal and the bearing bush of 1-3 / 1000 of the journal diameter is considered to be particularly favorable.
  • copper-aluminum alloys i.e. Copper-aluminum casting alloys (DIN 1714) or copper-aluminum wrought alloys (DIN 17665) are used.
  • the cast alloys are heterogeneous and have good casting properties, while the wrought alloys are homogeneous and have ductile properties. Both are characterized by high wear resistance.
  • Figure 1a shows the unbalance flange 1 with the bearing bush 3 used from the top.
  • Figure 1b shows the two components in cross section.
  • the oil supply bore 2 running in the radial direction can be seen.
  • the bearing bush 3 shows five of the eight bores 4a-4e running in the radial direction.
  • the bores 4a-4e each start from an annular groove 5 on the outside of the bearing bush 3 and end on the inside of the bearing bush 3, so that connections between the oil feed bore for the lubricant
  • the unbalanced mass 11 connected to the journal 10 is shown in FIG. 1 c after the unbalanced flange 1 has been installed.
  • the unbalanced mass 11 is connected via the bearing pin 10 to the unbalanced mass 12, which is located on the opposite side of the unbalanced flange 1. In the example shown, screws are used to make this connection.
  • the bearing bush 3 can be seen in cross section in FIG. 2a.
  • FIG. 2b shows the contact surface 7 of the bearing bush 3.
  • the contact surface 7 is characterized by four grooves 6a running in the radial direction.
  • FIG. 2c shows the eight bearing bush channels 4a-4h running in the radial direction.
  • the bearing bushing channels 4–4h are connected via the groove on the outside of the bearing bushing. len-shaped recess 5 evenly supplied with lubricant liquid during the rotation of the bearing journal.
  • Figure 3 shows the ring 8, which serves to enlarge the second end face of the bearing bush 3 shown in Figure 2c.
  • the ring 8 shown in plan view in FIG. 3b shows the four groove-shaped depressions 9a-9d running in the radial direction.
  • the ring 8 is attached to the bearing bush after installation of the bearing bush 3 in the unbalance flange 1. Just like the groove-shaped depressions 6a-6d on the opposite end face of the bearing bush 3, the depressions 9a-9d serve for the resistance-free discharge of the lubricant.
  • the unbalanced mass 11 connected to the bearing journal 10 is shown in FIGS. 4a-4c. 4c, the lubrication grooves 13, 14 can be seen on the running surface of the journal 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne un appareil vibratoire pour le battage et l'extraction de pieux, pourvu de paliers pour des masses non équilibrées rotatives (11, 12), lesdites masses non équilibrées étant placées dans une bride de palier (1) au moyen d'un tourillon (10) et d'un coussinet, ou de paliers pour des arbres sur lesquels ces masses non équilibrées sont fixées. Selon la présente invention, ces paliers sont des paliers lisses sur couche de fluide ; chaque coussinet comporte au moins deux canaux s'étendant dans le sens radial (canaux de coussinet) ; chaque coussinet présente sur au moins une face des évidements en rainures s'étendant dans le sens radial ou des gorges de ce type sont formées dans les surfaces d'arrêt axiales, adjacentes au coussinet, des masses non équilibrées ou des arbres montés dans les paliers lisses et la surface du tourillon ou de l'arbre, entourée par le coussinet, présente un ou plusieurs évidements en rainures.
EP05706713A 2004-02-04 2005-01-27 Appareil vitratoire pour pieux, pourvu de paliers pour des masses non equilibrees rotatives Withdrawn EP1711660A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004005443A DE102004005443A1 (de) 2004-02-04 2004-02-04 Vibrationsgerät für Rammgut mit Lagern für rotierende Unwuchtmassen
PCT/DE2005/000121 WO2005075749A1 (fr) 2004-02-04 2005-01-27 Appareil vitratoire pour pieux, pourvu de paliers pour des masses non equilibrees rotatives

Publications (1)

Publication Number Publication Date
EP1711660A1 true EP1711660A1 (fr) 2006-10-18

Family

ID=34801547

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05706713A Withdrawn EP1711660A1 (fr) 2004-02-04 2005-01-27 Appareil vitratoire pour pieux, pourvu de paliers pour des masses non equilibrees rotatives

Country Status (4)

Country Link
US (1) US20070053751A1 (fr)
EP (1) EP1711660A1 (fr)
DE (2) DE102004005443A1 (fr)
WO (1) WO2005075749A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007018794A1 (de) 2007-04-20 2008-10-23 Abi Anlagentechnik-Baumaschinen- Industriebedarf Maschinenfabrik Und Vertriebsgesellschaft Mbh Ausgleich umlaufender Wellenschrägstellung
DE102007018793A1 (de) 2007-04-20 2008-10-23 Abi Anlagentechnik-Baumaschinen- Industriebedarf Maschinenfabrik Und Vertriebsgesellschaft Mbh Vorrichtung zur Fluidförderung
DE102007018795B4 (de) 2007-04-20 2012-06-14 Abi Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik Und Vertriebsgesellschaft Mbh Ausgleich umlaufender Wellenschrägstellung
DE102007018796B4 (de) * 2007-04-20 2012-06-21 Abi Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik Und Vertriebsgesellschaft Mbh Ausgleich umlaufender Wellenschrägstellung
DE102011100881B4 (de) * 2011-05-07 2014-11-13 Abi Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik Und Vertriebsgesellschaft Mbh Schwingungserzeuger
DE102016215943A1 (de) * 2016-08-25 2018-03-01 Zf Friedrichshafen Ag Verformungsoptimiertes Gleitlager
US11624406B2 (en) * 2020-03-09 2023-04-11 American Piledriving Equipment, Inc. Bearing cooling systems and methods for vibratory pile drivers

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH273491A (de) * 1948-10-14 1951-02-15 Studer Ag Fritz Lagereinrichtung.
US2937908A (en) * 1957-06-14 1960-05-24 Golten Sigurd Bearings
GB904309A (en) * 1959-12-18 1962-08-29 Simonacco Ltd Improvements relating to vibrators
US3343893A (en) * 1965-01-27 1967-09-26 Ingersoll Rand Co Floating bearing of split-shell construction
GB1435499A (en) * 1972-06-23 1976-05-12 Secretary Industry Brit Vibratory impact generators
US5602945A (en) * 1996-03-21 1997-02-11 Nordberg, Incorporated Thrust bearing for use in a conical crusher
DE10159949C1 (de) * 2001-12-06 2003-05-22 Wieland Werke Ag Verwendung einer Kupfer-Aluminium-Legierung mit definierten Deckschichten als Lagerwerkstoff zur Herstellung von verschleißfesten Gleitlagern
US6929402B1 (en) * 2002-04-11 2005-08-16 Morgan Construction Company Journal bearing and thrust pad assembly

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005075749A1 *

Also Published As

Publication number Publication date
DE112005000793D2 (en) 2006-12-21
DE102004005443A1 (de) 2005-08-25
WO2005075749A1 (fr) 2005-08-18
US20070053751A1 (en) 2007-03-08

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Inventor name: HEICHEL, CHRISTIAN

Inventor name: KLEIBL, ALBRECHT

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