EP2198091A1 - Vorrichtung zur erzeugung von schwingungen - Google Patents
Vorrichtung zur erzeugung von schwingungenInfo
- Publication number
- EP2198091A1 EP2198091A1 EP08801235A EP08801235A EP2198091A1 EP 2198091 A1 EP2198091 A1 EP 2198091A1 EP 08801235 A EP08801235 A EP 08801235A EP 08801235 A EP08801235 A EP 08801235A EP 2198091 A1 EP2198091 A1 EP 2198091A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- masses
- imbalance masses
- imbalance
- bearing
- arms
- 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- Withdrawn
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
- E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses
-
- 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
- B06B1/167—Orbital vibrators having masses being driven by planetary gearings, rotating cranks or the like
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
- E02D7/18—Placing by vibrating
Definitions
- the invention relates to a device for generating vibrations, in particular for attachment to RammMechn that are rammed or pulled by these vibrations in a soil, with at least two counter-synchronized rotating unbalanced masses, which roll on a track and are driven by separate shafts.
- vibration devices are used, which are also called vibration bear or shaker.
- Such vibratory bears or vibrators can be fixed non-positively by means of a clamping pliers on a sheet pile wall or the other piling. If the vibrating bear is set into vibration, the body to be driven in is driven into the ground even at low load or even by its own weight, or its removal is facilitated.
- two eccentric masses are arranged on at least two separate shafts. The shafts are connected via gears so that the imbalance masses rotate in pairs in opposite directions.
- An embodiment of the prior art provides for this two pairs unbalanced shafts whose unbalance via a control device, for. B. an adjusting motor on another shaft are adjustable relative to each other.
- a control device for. B. an adjusting motor on another shaft are adjustable relative to each other.
- the centrifugal forces cancel each other in each angular position.
- the centrifugal forces of the imbalances add up in one plane.
- the amplitude of a vibration unit is determined by the so-called static moment divided by the weight of the oscillating mass.
- the static moment is calculated from the masses of the rotating imbalances multiplied by the distance of the center of gravity of the individual imbalance masses to the axis of rotation. It follows that for a high amplitude a high static torque and / or a small oscillating total mass is needed.
- the amplitude as a parameter of a vibration bear is independent of the speed or the oscillation frequency of the vibration bear.
- High-frequency vibrators require large bearings to support the high centrifugal forces per shaft, which increases the dynamic weight of the vibrating mass and thus reduces the amplitude.
- the adjusting means increase the dynamic weight of the vibrating bear, so that an additional reduction of the amplitude takes place.
- An increase in the static torque for larger and heavier pile material is technically possible only by increasing the number of unbalanced shafts, which is associated with a proportional increase in the installation space of the vibrator. The associated increase in weight results in no improvement in the amplitude.
- a special embodiment of devices for generating vibrations is the so-called upright vibrator.
- This is a version with a small width of the device in order to be able to set a third pile between two ramming goods not yet rammed.
- the small width is achieved by placing the individual unbalanced shafts vertically one above the other. According to the prior art, this four waves are arranged one above the other to eliminate horizontal force-related torsional moments.
- a reduction in the amplitude up to the value zero is achieved in that two imbalances on a shaft are rotatable relative to each other.
- the preferred arrangement of the adjustment is in this case according to an executed prior art, an adjusting on an axis between two shaft pairs.
- a high-amplitude vibrator which has a housing with two spaced-apart bores, in each of which two imbalance masses are mounted on the walls of the bores to roll off.
- the imbalance masses are arranged on one arm, wherein the angular position between the arms and thus between the imbalance masses via a mechanism is adjustable, so that different unbalance moments are adjustable.
- neither the complicated adjusting mechanism nor the simple guidance of the rollers in grooves is suitable for fulfilling the task described above, to realize a compact vibration unit with high amplitude at high oscillation frequency.
- Object of the present invention is to provide a device of the initially to create said type, which achieves a significantly higher amplitude of high-frequency vibration bear in a smaller space than is possible according to the prior art and allows in an expanded version an adjustability of the vibration amplitude.
- a device is also known from DE 41 39 798 A1, in the housing of which two spaced and parallel shafts are provided.
- Each of the shafts is associated with a single variable hydraulic motor that drives the shafts.
- Each shaft has an imbalance mass in the form of a piston which is displaceable longitudinally displaceable and relatively smooth in each case a hollow body in the direction of the longitudinal axis.
- the hollow body is in each case integrally connected to the associated shaft.
- the longitudinal axes of the different hollow bodies on different shafts are arranged parallel to each other and orthogonal to a center line, on which the centers of the shafts are at a distance from each other.
- unbalance masses are arranged longitudinally displaceable.
- the waves are accelerated in idle up to the desired speed, wherein the imbalance masses are arranged in a neutral position. Only after reaching the desired speed unbalance masses are moved to an eccentric position.
- both the imbalance masses and the raceways are made of a hardened material, in a preferred embodiment in a bearing steel, and a hardness of HRC> 50 and has a suitable lubrication in the contact area of Wälzpartner.
- a resilient bias in the radial direction is essential.
- Suitable materials for the races and rollers are through hardened steels and case hardened steels.
- lubrication must be provided.
- an oil lubrication is provided, which can be realized as immersion bath lubrication.
- a pressure circulation lubrication can also be provided.
- the bearing ring is replaceable. This offers the advantage that it can be easily replaced when wear of the track.
- the device according to the invention is characterized in that one or more cylindrical unbalanced masses roll on the inner jacket of two stationary bearing shells, the axis of rotation of which is connected via an arm to a driving shaft, so that the static moments which can be generated increase considerably.
- the particular advantage of this device is that the static moments that can be generated can be increased considerably if hardened steels are used as the material of the bearing shells and of the unbalanced masses.
- the centrifugal forces generated during the rotation without the otherwise usual significant bending loads of the drive shaft, can be collected.
- 2 imbalance masses are arranged in each bearing shell, which are rigidly interconnected, so that their mutual distance does not change. These masses act kinematically like a single mass, which is rotated on a circular arc, which is determined by the bearing shell.
- two imbalance masses by means of arms rotatably and rotatably disposed in the bearing shell, wherein the angular distance of the arms is changeable.
- the rotatable imbalance masses at an angular distance of z. B. 180 °, so that - with the same mass of imbalances and the same radial distance from the drive shaft - the unbalance resulting from each imbalance mass is compensated (provided that the centrifugal forces of the arms and the other connecting means are negligible).
- the angular distance of the arms is adjustable with an adjusting gear which is arranged in a rotating manner on the respective drive shaft. After adjustment no further friction losses occur due to the movement of additional waves.
- a particularly compact design is achieved by pushing two counter-rotating shafts in an axis, whereby the width of the vibrating device is halved.
- a particularly compact design for the so-called vertical vibrators is achieved. Reversing the direction of rotation on one axis can be achieved with simple means by means of a bevel gearbox, in this case a bevel gearbox. This design allows a significant increase in the useful length of a leader led vibrator win while increasing the performance of the vibrator.
- the adjustable angular distance of the arms is limited to a minimum value by a spacer, which is formed according to a further embodiment of the invention by respective free legs of an angle arm which abut each other at a minimum distance. Through this spacer it is ensured that the rotating cylindrical or spherical imbalance masses can rotate freely in the bearing shell.
- the sum of the diameter of the imbalance mass plus the radius of the drive shaft is the same size as the radius of the bearing shell in which the imbalance masses are rotatably arranged.
- a raceway guard in front of and / or behind the imbalance masses, which is preferably a scraper which scraps foreign matter from the imbalance masses. The wear of both the imbalance masses and the bearing ring is thereby reduced, whereby the durability of the components is significantly improved.
- An advantageous embodiment provides that the imbalance masses are pressed against the race, in particular at low frequencies by a compression spring with a minimum pressure. As a result, when starting the device, ie at low frequencies, a sliding of the imbalance masses is avoided on the bearing ring. This also minimizes signs of wear that always occur when sliding between two solids.
- the imbalance masses in different bearing shells rotate synchronously in opposite directions.
- the synchronization can - as in principle in the known prior art constructions - by means of a gear drive or z. B. be realized by means of a belt drive.
- FIG. 1 is a schematic diagram of two bearing respectively with two imbalance masses bearing shells of a vibration device in different angular positions of the imbalance masses
- Fig. 2, 3 and 4 schematic diagrams with a preferred embodiment of
- Fig. 5 shows another embodiment of the invention with a
- Fig. 1 two bearing shells 13, 14 are shown, each with a pair of cylindrical imbalance masses 4, 5, wherein the imbalance masses of a pair are each rigidly coupled together via links 3, so that each pair kinetically acts as a single constant imbalance mass, each can roll in the bearing shell in the illustrated arrow direction.
- the drive takes place in each case via a shaft 1, 2.
- the imbalance masses 4, 5 as well as the bearings consisting of raceways made of a hardened material such.
- the vibration device 10 has two bearing shells 13, 14 which are arranged about axes of rotation 11 and 12 and into which a respective bearing ring 32 is embedded.
- On the running surfaces of the bearing rings 32 are each two (or more) imbalance masses 15 and 16, which are cylindrical, unrolled.
- the running surface of the bearing rings 32 and / or the imbalance masses 15, 16 are lubricated, to which preferably an oil immersion lubrication 31 is used.
- the respective unwinding direction is shown by arrows 17 and 18, which indicate that the unbalanced body in the two hollow shafts roll in opposite directions.
- two scrapers 33 are provided.
- a biasing device which presses the imbalance masses 15, 16 against the bearing rings 32.
- a synchronous opposite movement of the imbalance masses is ensured for example by the pinion, belt or the like.
- Each cylindrical imbalance mass 15, 16 is fastened with its axis of rotation 19 to an angle arm 21, 22.
- Each angle arm is fastened on the one hand with its first end on a rotary shaft 23.
- the free ends 24, 25 are angled so that they abut each other in the position in which the two cylindrical imbalance masses 15 and 16 have the least possible distance from each other.
- an unillustrated electrical, hydraulic or pneumatic control it is possible to change the angular distance of the angle arms 21 and 22 continuously up to 180 °.
- the cylindrical imbalance masses 15 and 16 are arranged diametrically opposite in the hollow shaft, so that cancel their static torques.
- the vibration device can be raised to the desired operating frequency vibration-free.
- the oscillation amplitude can be adjusted steplessly by adjusting the angles of the imbalance masses.
- an unillustrated scraper is arranged in front of or behind the imbalance masses, which strips off dirt and dust particles from the imbalance masses.
- FIG. 2 shows a schematic representation of an adjusting member 26 which engages the arms 27, 28. By a linear displacement of the actuator 29, any angular positions can be adjusted continuously.
- a minimum angle of about 70 ° and in Fig. 3 is set an angle of almost 180 °, in which the imbalance masses 15, 16 and the associated parts, which rotate with the imbalance masses are in static equilibrium.
- FIG. 2 shows a lubricant spray device 30, in FIG. 3 a dip bath 31 and in FIG. 4 a pressure spray device 34 as alternative lubrication.
Landscapes
- Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Civil Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Paleontology (AREA)
- General Life Sciences & Earth Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Agronomy & Crop Science (AREA)
- Environmental & Geological Engineering (AREA)
- Soil Sciences (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007049435A DE102007049435A1 (de) | 2007-10-16 | 2007-10-16 | Vorrichtung zur Erzeugung von Schwingungen |
PCT/DE2008/001416 WO2009049576A1 (de) | 2007-10-16 | 2008-08-26 | Vorrichtung zur erzeugung von schwingungen |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2198091A1 true EP2198091A1 (de) | 2010-06-23 |
Family
ID=40206389
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08801235A Withdrawn EP2198091A1 (de) | 2007-10-16 | 2008-08-26 | Vorrichtung zur erzeugung von schwingungen |
Country Status (5)
Country | Link |
---|---|
US (1) | US8226329B2 (de) |
EP (1) | EP2198091A1 (de) |
DE (1) | DE102007049435A1 (de) |
RU (1) | RU2487212C2 (de) |
WO (1) | WO2009049576A1 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ATE550494T1 (de) * | 2009-05-16 | 2012-04-15 | Anlagentech Baumasch Ind | Vorrichtung und verfahren zum einbringen von rohren in den boden |
DE102011112316B4 (de) * | 2011-09-02 | 2020-06-10 | Bomag Gmbh | Schwingungserreger zur Erzeugung einer gerichteten Erregerschwingung |
CN104005384B (zh) * | 2014-06-19 | 2016-03-09 | 中国水利水电第十六工程局有限公司 | 平板夯实机及碾压混凝土重力坝夯实混凝土的施工工艺 |
DE202015003475U1 (de) | 2015-02-11 | 2016-05-12 | Liebherr-Components Biberach Gmbh | Rüttler |
CN106628459B (zh) * | 2016-12-31 | 2018-10-30 | 博众精工科技股份有限公司 | 一种振动机构 |
CN108118679A (zh) * | 2017-10-09 | 2018-06-05 | 广西南宁东能建筑工程技术有限公司 | 一种斜坡专用夯实装置 |
CN108104100A (zh) * | 2017-10-09 | 2018-06-01 | 广西南宁东能建筑工程技术有限公司 | 一种斜坡路面专用夯实装置 |
CN108118678A (zh) * | 2017-10-09 | 2018-06-05 | 广西南宁东能建筑工程技术有限公司 | 一种道路斜坡面专用夯实装置 |
WO2024013638A1 (en) * | 2022-07-11 | 2024-01-18 | Valsavio Holding S.R.L. | Vibration device for soil compaction |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2127317A (en) * | 1937-07-07 | 1938-08-16 | Ajax Flexible Coupling Company | Vibratory motion producing apparatus |
GB619775A (en) * | 1942-01-08 | 1949-03-15 | Pierre Charles Marie Rebut | Improvements in high-power, high-frequency vibrators |
US2778230A (en) | 1952-08-09 | 1957-01-22 | Edwin F Peterson | Positive drive vibratory mechanism |
DE1165505B (de) * | 1953-01-30 | 1964-03-12 | Vibro Verken Ab | Mechanischer Schwingungserzeuger fuer eine Ruettelwalze |
US2831353A (en) | 1955-09-06 | 1958-04-22 | Int Research & Dev Co Ltd | Force producing apparatus |
US3195659A (en) | 1962-01-17 | 1965-07-20 | Bodine Albert G | Sonic pile driver |
DD61653A1 (de) * | 1967-07-24 | 1968-05-05 | Schwingantrieb | |
US3750228A (en) * | 1970-06-18 | 1973-08-07 | Essco Inc Green Bay | Oscillating doctor-blade mechanism |
DE2127433B2 (de) * | 1971-06-03 | 1973-05-30 | Grimmer, Klaus Jürgen, Dr Ing , 4720 Beckum | Unwuchterreger zum antrieb einer schwingrinne oder eines schwingsiebes |
US3868859A (en) * | 1973-07-16 | 1975-03-04 | Bell Telephone Labor Inc | Positive drive vibratory mechanism |
DE2706667A1 (de) * | 1977-02-17 | 1979-01-11 | Bosch Gmbh Robert | Vibrationsgeraet zur bodenverdichtung |
US4306300A (en) | 1979-12-31 | 1981-12-15 | International Business Machines Corporation | Multi-level charge-coupled device memory system including analog-to-digital and trigger comparator circuits |
JPS5826118A (ja) * | 1981-08-07 | 1983-02-16 | Takahashi Eng:Kk | 振動杭打機 |
US4856358A (en) * | 1983-08-01 | 1989-08-15 | Montalbano Paul J | Conversion of rotational output to linear force |
JPS61233123A (ja) | 1985-04-10 | 1986-10-17 | Nippon Steel Corp | 高周波起振機 |
DE4139798C2 (de) | 1991-12-03 | 1995-08-17 | Tuenkers Maschinenbau Gmbh | Vibrationsbär |
US5355964A (en) * | 1993-07-12 | 1994-10-18 | White John L | Pile driving and/or pile pulling vibratory assembly with counterweights |
RU2098557C1 (ru) * | 1995-12-27 | 1997-12-10 | Фирма "Транстехновация" - Товарищество с ограниченной ответственностью | Вибропогружатель |
DE19631991B4 (de) | 1996-08-08 | 2005-02-24 | Abi Maschinenfabrik Und Vertriebsgesellschaft Mbh | Vibrator, insbesondere für einen Vibrationsbären |
US6669026B2 (en) * | 2000-11-01 | 2003-12-30 | Ohio Central Steel Company | Portable screening plant with displaceable eccentric |
RU2274499C1 (ru) * | 2004-08-23 | 2006-04-20 | ГОУ ВПО "Дальневосточный государственный университет путей сообщения МПС России" (ДВГУПС) | Вибровозбудитель направленного действия |
US7434890B2 (en) * | 2005-03-23 | 2008-10-14 | Boart Longyear Inc. | Vibratory milling machine having linear reciprocating motion |
-
2007
- 2007-10-16 DE DE102007049435A patent/DE102007049435A1/de not_active Withdrawn
-
2008
- 2008-08-26 RU RU2010118086/03A patent/RU2487212C2/ru not_active IP Right Cessation
- 2008-08-26 EP EP08801235A patent/EP2198091A1/de not_active Withdrawn
- 2008-08-26 WO PCT/DE2008/001416 patent/WO2009049576A1/de active Application Filing
- 2008-08-26 US US12/672,559 patent/US8226329B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2009049576A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102007049435A1 (de) | 2009-04-30 |
RU2010118086A (ru) | 2011-11-27 |
US8226329B2 (en) | 2012-07-24 |
RU2487212C2 (ru) | 2013-07-10 |
US20110013990A1 (en) | 2011-01-20 |
WO2009049576A1 (de) | 2009-04-23 |
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Legal Events
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