EP0239561A2 - Appareillage pour produire des vibrations - Google Patents

Appareillage pour produire des vibrations Download PDF

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Publication number
EP0239561A2
EP0239561A2 EP87890045A EP87890045A EP0239561A2 EP 0239561 A2 EP0239561 A2 EP 0239561A2 EP 87890045 A EP87890045 A EP 87890045A EP 87890045 A EP87890045 A EP 87890045A EP 0239561 A2 EP0239561 A2 EP 0239561A2
Authority
EP
European Patent Office
Prior art keywords
group
unbalanced masses
unbalanced
masses
shaft
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.)
Granted
Application number
EP87890045A
Other languages
German (de)
English (en)
Other versions
EP0239561A3 (en
EP0239561B1 (fr
Inventor
Ferdinand Hirn
Michael Schmölzer
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.)
MASCHINENFABRIK LIEZEN GESELLSCHAFT M.B.H.
Original Assignee
Maschinenfabrik Liezen GmbH
Voestalpine AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Maschinenfabrik Liezen GmbH, Voestalpine AG filed Critical Maschinenfabrik Liezen GmbH
Publication of EP0239561A2 publication Critical patent/EP0239561A2/fr
Publication of EP0239561A3 publication Critical patent/EP0239561A3/de
Application granted granted Critical
Publication of EP0239561B1 publication Critical patent/EP0239561B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/162—Making use of masses with adjustable amount of eccentricity
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll

Definitions

  • the invention relates to a device for generating vibrations, in particular for soil compaction machines, such as road rollers, with unbalanced masses rotatably mounted about a common axis and drivable for rotation about the common axis, which are rotatable relative to one another.
  • the object of the invention is to simplify and facilitate the adaptation of the amplitudes of the vibrations to the respective work task. This is particularly true for adapting the effectiveness of a road roller to different soil conditions.
  • the invention essentially consists in the fact that two groups of unbalanced masses are provided, of which a first group has two unbalanced masses, which can be rotated relative to one another in two end positions determined by stops and can be fixed by hand in these end positions are, and a second group in the area of both axial ends of the unbalanced masses of the first group each has an unbalanced mass, which can be rotated in the same direction relative to the unbalanced masses of the first group in two end positions determined by stops, the unbalanced masses of the second group being the same and oriented in the same direction Have eccentricities and equal masses.
  • the invention enables the vibrator to be set to four different levels. Due to the unbalanced masses of the first group, two basic settings can be selected. These basic settings are made manually before the device is started up. Because the two basic settings are determined by stops, the setting in these two basic settings can be carried out easily and without specialist knowledge. Because the unbalance masses of the first group are rotated by 180 ° between the stops, this basic setting has the greatest effect. If the eccentricities of the two unbalanced masses of the first group are aligned, the greatest effect of these unbalanced masses of the first group is given. If the eccentricities of these two unbalanced masses are opposite, the smallest unbalance effect results, which can even be reduced to zero.
  • the two stages selected by manual adjustment of the unbalanced masses of the first group can again be divided into two stages, so that the vibrator can be adjusted in four stages. Since the positions of the unbalanced masses of the second group also end attacks, this setting is easy to choose and requires no specialist knowledge.
  • the two unbalanced masses of the first group can expediently be latched in their end positions offset by 180 °, which simplifies operation and eliminates the possibility of errors.
  • the unbalanced masses of the first group are formed in a manner known per se from a hollow cylinder arranged eccentrically to the axis of rotation and a shaft with an unbalanced mass mounted centrally within the same to the axis of rotation, the shaft in the front ends of the hollow cylinder in the axis of rotation of the same is rotatable and axially displaceable counter to a spring force and has a radial projection which alternatively engages in two detents of 180 ° offset from one end.
  • the unbalanced masses of the second group can be used to double the levels of vibrator effect achieved by adjusting the unbalanced masses of the first group alone.
  • the decisive factor for the amplitudes resulting in the respective positions of the unbalanced masses of the second group relative to the unbalanced masses of the first group is the eccentricity of the total center of gravity of all unbalanced masses.
  • the eccentricity of this overall center of gravity is increased or decreased.
  • the unbalanced masses of the second group are therefore expedient in the angular range between the two twist end positions the unbalanced masses of the first group can be rotated by less than 180 °.
  • the unbalanced masses of the second group are expediently adjustable in their end positions determined by stops, so that an interruption in operation is not necessary for the purpose of changing the vibration effect given by the preselected setting of the unbalanced masses of the first group.
  • each unbalanced mass of the second group has two stop surfaces which, when these unbalanced masses are rotated, interact with a stop block connected to the rotating shaft, the unbalanced masses being rotated from one end position to the other by reversing the direction of rotation the wave occurs. The operator can thus change the amplitudes of the vibrations or the vibration effect by simply switching the direction of rotation.
  • one of the stop surfaces on the unbalanced masses of the second group itself and one of the stop surfaces on the unbalanced masses opposite and connected to them are formed.
  • the angular distance between these two stop surfaces determines the angle by which the unbalanced masses of the second group are adjusted when the direction of rotation is switched.
  • the arrangement can be made in accordance with the invention such that the arms having the stop surfaces are diametrically opposite the unbalanced masses.
  • These arms, which have the stop surfaces also have a mass and therefore also represent a, albeit small, unbalanced mass which must be subtracted from the large unbalanced mass. Because these arms are diametrically opposite the unbalanced masses, the direction of the eccentricity of the resulting unbalanced masses remains unchanged.
  • the vibrator shaft can be driven by a hydraulic motor via an elastic claw coupling, which is the simplest type of drive for road rollers, for example.
  • the vibrator shaft and the unbalanced masses of the first and second groups can be sealed in a pipe connected to the bearing body according to the invention.
  • the encapsulation of the vibrator offers the advantages that the hollow roller can be filled with water to increase the weight and the lubrication of the vibrating device can be carried out very easily and effectively.
  • the rotating shaft 1 of the vibrator is driven by a hydraulic motor 2 via an elastic claw coupling 3.
  • the shaft is supported in bearings 4 and 5.
  • the unbalanced masses of the first group are formed by a hollow cylinder 6 and a shaft 7 arranged inside the hollow cylinder 6.
  • the hollow cylinder 6 is arranged eccentrically to the axis 8 and screwed to the shaft ends 1a and 1b. This hollow cylinder 6 therefore forms an unbalanced mass.
  • the shaft 7 is arranged coaxially with the axis 8, but is removed on the side 9. This wave therefore has a semicircular cross-section, whereby this shaft 7 also acts as an unbalanced mass.
  • the shaft 1 is divided into two shaft ends 1a and 1b, which are connected to one another by the hollow cylinder 6.
  • the shaft ends 1a and 1b form end walls of the hollow cylinder 6.
  • the shaft 7 is rotatably supported in these two end walls or shaft ends 1a and 1b.
  • a pin 10 is inserted, which protrudes into a semicircular groove 11 of the shaft 7.
  • Axially directed recesses 12 are provided at the two ends of this groove opposite each other by 180 °.
  • the shaft 7 is axially displaceably supported and pressed in the direction to the left by a helical spring 13. In the position shown in the drawing, the pin 10 engages in one of the two recesses 12.
  • the operator presses the shaft 7 to the right against the pressure of the spring 13 and rotates it by 180 ° by attaching a wrench to a hexagon 14.
  • the eccentricities of the hollow cylinder 6 and the shaft 7 are directed in the same direction.
  • the unbalanced masses of the hollow cylinder 6 and the shaft 7 therefore add up in this position. If the shaft 7 is rotated 180 ° relative to the hollow cylinder 6, the eccentricities of the hollow cylinder 6 and shaft 7 are directed in opposite directions and the unbalanced mass of the shaft 7 must therefore be subtracted from the unbalanced mass of the hollow cylinder 6.
  • the unbalance masses 15 are the unbalance masses of the second group. These unbalanced masses 15 of the second group are freely rotatably supported on the shaft ends 1a and 1b.
  • the unbalanced masses 15 are connected to arms 16.
  • the unbalanced masses 15 have stop surfaces 17 and the arms 16 have stop surfaces 18.
  • 19 are stop blocks, which with the rotating shaft 1, etc. are rigidly connected to the shaft ends 1a and 1b. In the direction of rotation of the arrow 20, the stop block 19 takes up a stop against the stop Area 18 of the arm 16 with the unbalanced masses 15. The position shown in FIG. 2 thus results.
  • 22 is a tube that seals the vibrator. This can be of advantage in road rollers where it is possible to fill the hollow roller with water to increase its weight.
  • the unbalanced masses can now be rotated relative to one another in different positions shown in FIGS. 3 to 6, which results in different unbalance effects.
  • the axis of rotation is again designated 8 in FIGS. 3 to 6.
  • S1 the center of gravity of the unbalanced mass of the hollow cylinder 6
  • S3 the center of gravity of the unbalanced mass formed by the shaft 7
  • S2 the common focus of the two unbalanced masses 15 minus the unbalanced masses of the two arms 16.
  • 3a to 6a is analogously the mass of the hollow cylinder 6 with m1, the mass of the shaft 7 with m3 and the common mass of the two unbalanced masses 15 minus the two arms 16 with m2.
  • the eccentricities of the focal points S1, S3 and S2 are denoted by e1, e3 and e2.
  • FIG. 3 shows the position of the unbalanced masses 15 when rotating in the direction of the arrow 21 according to FIG. 2, the stop surface 17 abutting the stop blocks 19.
  • Hiebei has the focus S1 an eccentricity e1 and Focus S3 an eccentricity e3 on. These two eccentricities are therefore directed in the same direction.
  • the focus S2 of the two unbalanced masses 15 minus the unbalanced masses of the two arms 16 has an eccentricity e2.
  • This focus S2 is now shifted approximately towards the focus S1 and S3. Since the eccentricities e 1 and e 3 are directed in the same direction and the center of gravity S 2 is shifted approximately in the direction of the centers S 1 and S 3, the largest resulting mass moment for the vibrations results. These mass moments are shown in the diagram in FIG.
  • Fig. 4 the priorities S1, S3 and S2 are shown relative to the axis of rotation 8 again.
  • the unbalanced masses 6, 7 of the first group are set again so that the eccentricities e 1 and e 3 of the centers of gravity S 1 and S 3 are directed in the same direction.
  • the manual adjustment of the two unbalanced masses 6 and 7 of the first group thus remains unchanged.
  • the direction of rotation is now reversed in the direction of arrow 20 in FIG. 2.
  • the common focus S2 of the two unbalanced masses 15 minus the unbalanced masses of the two arms 16 of the second group is therefore adjusted in the other direction.
  • the eccentricity e2 of the focus S2 is now directed against the eccentricities e1 and e3. This results in a diagram according to FIG.
  • the unbalanced masses 6 and 7 of the first group are now changed by manually rotating the shaft 7 with respect to the hollow cylinder 6 by 180 ° from the position shown in the drawing.
  • the eccentricity e3 of the center of gravity S3 is now directed against the eccentricity e1 of the center of gravity S1.
  • the unbalanced masses 6 and 7 therefore act in the opposite direction and are to be subtracted from one another.
  • the eccentricity e2 of the center of gravity S2 is directed approximately in the direction of the center of gravity S1.
  • This center of gravity S1 is the center of gravity of the hollow cylinder 6, the mass of which is greater than the mass of the shaft 7.
  • m. E mass moment
  • the unbalanced masses 15 are adjusted by rotation in the direction of the arrow 20 according to FIG. 2 so that the stop surface 18 bears against the stop block 19.
  • the eccentricity e2 of the center of gravity S2 of the unbalanced masses 15 of the second group is now adjusted against the eccentricity e1 of the unbalanced mass of the hollow cylinder 6.
  • the resultant mass moment (m. E) res is smaller than in the setting according to FIG. 5.
  • such a position of the unbalanced masses in asphalt construction is selected if smaller mass moments or amplitudes appear necessary.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Road Paving Machines (AREA)
EP19870890045 1986-03-27 1987-03-10 Appareillage pour produire des vibrations Expired - Lifetime EP0239561B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT833/86 1986-03-27
AT0083386A AT389723B (de) 1986-03-27 1986-03-27 Einrichtung zur erzeugung von vibrationen

Publications (3)

Publication Number Publication Date
EP0239561A2 true EP0239561A2 (fr) 1987-09-30
EP0239561A3 EP0239561A3 (en) 1988-06-15
EP0239561B1 EP0239561B1 (fr) 1992-07-29

Family

ID=3500831

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870890045 Expired - Lifetime EP0239561B1 (fr) 1986-03-27 1987-03-10 Appareillage pour produire des vibrations

Country Status (5)

Country Link
EP (1) EP0239561B1 (fr)
CN (1) CN87102358A (fr)
AT (1) AT389723B (fr)
DE (1) DE3780666D1 (fr)
TR (1) TR23201A (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0411349A1 (fr) * 1989-08-03 1991-02-06 Ammann Verdichtung AG Dispositif pour compacter le sol
WO1999034935A1 (fr) * 1997-12-31 1999-07-15 Nordberg-Lokomo Oy Ensemble vibratoire
DE102010021961A1 (de) * 2010-05-28 2012-04-19 Bomag Gmbh Schwingungserreger für ein Bodenverdichtungsgerät und Bodenverdichtungsgerät
CN106192688A (zh) * 2016-08-31 2016-12-07 广西恒日科技股份有限公司 一种偏心振动机构
CN107891506A (zh) * 2017-12-31 2018-04-10 高唐县鼎力建筑机械有限公司 一种多级卧式底置混凝土高频振动器

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3799022B2 (ja) * 2003-02-24 2006-07-19 酒井重工業株式会社 振動機構及び振動ローラ
DE102009055950A1 (de) * 2009-11-27 2011-06-01 Hamm Ag Verdichtungsgerät, sowie Verfahren zum Verdichten von Böden
CN102510165B (zh) * 2011-11-02 2013-10-23 无锡富岛精工有限公司 可换向振动马达
CN104653592B (zh) * 2013-11-15 2019-01-22 迪纳帕克压紧设备股份公司 具有固定的和可动的偏心质量块的偏心轴
CN105980762A (zh) * 2014-02-10 2016-09-28 沃尔沃建造设备有限公司 具有增强润滑的结构简单的偏心组件
WO2017114546A1 (fr) * 2015-12-28 2017-07-06 Volvo Construction Equipment Ab Ensemble excentrique pour machine de compactage par vibration

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1111107B (de) * 1955-03-14 1961-07-13 Dingler Werke Ag Vibrationswalze zur Verdichtung von Boeden und sonstigen Schuettmassen
FR2006576A1 (fr) * 1968-04-19 1969-12-26 Abg Werke Gmbh
GB1374517A (en) * 1972-03-23 1974-11-20 Simonacco Ltd Vibrating devices
US3909147A (en) * 1974-11-07 1975-09-30 Raygo Inc Variable amplitude vibration generator

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT203196B (de) * 1956-11-10 1959-05-11 Byggmekanisering Ab Abreibemaschine
AT220651B (de) * 1959-03-09 1962-04-10 Schenkir Dipl Ing Ludwig Bodenverdichter mit rotierenden Unwuchten
AT250423B (de) * 1963-10-17 1966-11-10 Buckau Wolf Maschf R Selbstbewegliche Verdichtungsmaschine
DE1634257A1 (de) * 1965-12-24 1971-09-30 Bopparder Maschb Gmbh Vibrationswalze
DE1558848A1 (de) * 1967-03-11 1970-06-18 Losenhausen Maschb Ag Als Richtschwinger mit veraenderbarer Schwingungsrichtung ausgebildeter Schwingungserzeuger
DE1558869A1 (de) * 1967-05-19 1970-05-06 Wissenschaftlich Tech Zentrum Vibrationsgeraet zur Verdichtung von fein- und grobkoernigen Materialien
AT274032B (de) * 1967-09-30 1969-09-10 Losenhausen Maschinenbau Ag Unwucht-Schwingungserzeuger
DE1758131A1 (de) * 1968-04-06 1970-12-23 Frisch Geb Kg Eisenwerk Ruettler
DE1758226A1 (de) * 1968-04-26 1971-01-14 Losenhausen Maschb Ag Unwuchtruettler
DE1758996A1 (de) * 1968-09-13 1971-04-08 Eberhard Borsutzki Mehrwellen-Kreisschwinger mit planetar angeordneten,stufenlos und gerichtet verstellbaren Unwuchten zur Groessen- oder Richtungsveraenderung der Zentrifugalkraft
DE2231338C3 (de) * 1972-06-27 1979-07-12 Maschinenbau Ulm Gmbh, 7900 Ulm Rotationsvibrator

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1111107B (de) * 1955-03-14 1961-07-13 Dingler Werke Ag Vibrationswalze zur Verdichtung von Boeden und sonstigen Schuettmassen
FR2006576A1 (fr) * 1968-04-19 1969-12-26 Abg Werke Gmbh
GB1374517A (en) * 1972-03-23 1974-11-20 Simonacco Ltd Vibrating devices
US3909147A (en) * 1974-11-07 1975-09-30 Raygo Inc Variable amplitude vibration generator

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0411349A1 (fr) * 1989-08-03 1991-02-06 Ammann Verdichtung AG Dispositif pour compacter le sol
WO1999034935A1 (fr) * 1997-12-31 1999-07-15 Nordberg-Lokomo Oy Ensemble vibratoire
DE102010021961A1 (de) * 2010-05-28 2012-04-19 Bomag Gmbh Schwingungserreger für ein Bodenverdichtungsgerät und Bodenverdichtungsgerät
US8590408B2 (en) 2010-05-28 2013-11-26 Bomag Gmbh Vibration exciter for a ground compactor and ground compactor
CN106192688A (zh) * 2016-08-31 2016-12-07 广西恒日科技股份有限公司 一种偏心振动机构
CN107891506A (zh) * 2017-12-31 2018-04-10 高唐县鼎力建筑机械有限公司 一种多级卧式底置混凝土高频振动器
CN107891506B (zh) * 2017-12-31 2024-03-19 高唐县鼎力建筑机械有限公司 一种多级卧式底置混凝土高频振动器

Also Published As

Publication number Publication date
EP0239561A3 (en) 1988-06-15
DE3780666D1 (de) 1992-09-03
TR23201A (tr) 1989-06-15
AT389723B (de) 1990-01-25
CN87102358A (zh) 1988-01-06
ATA83386A (de) 1989-06-15
EP0239561B1 (fr) 1992-07-29

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