EP1131491B1 - Drehbare Nockenvorrichtung - Google Patents

Drehbare Nockenvorrichtung Download PDF

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Publication number
EP1131491B1
EP1131491B1 EP99939636A EP99939636A EP1131491B1 EP 1131491 B1 EP1131491 B1 EP 1131491B1 EP 99939636 A EP99939636 A EP 99939636A EP 99939636 A EP99939636 A EP 99939636A EP 1131491 B1 EP1131491 B1 EP 1131491B1
Authority
EP
European Patent Office
Prior art keywords
eccentric
arrangement
amplitude
roll
rotatable
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.)
Expired - Lifetime
Application number
EP99939636A
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English (en)
French (fr)
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EP1131491A1 (de
Inventor
Rune Sturesson
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Individual
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Individual
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Publication of EP1131491A1 publication Critical patent/EP1131491A1/de
Application granted granted Critical
Publication of EP1131491B1 publication Critical patent/EP1131491B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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 present invention relates to a rotatable eccentric element for continuous adjustment of the vibration amplitude in the roll in vibrating rollers.
  • the invention relates to a rotatable eccentric arrangement adapted for stepless adjustment of the vibration amplitude, comprising a rotatable shaft with an eccentric weight arranged in a fixed manner thereon and a movable weight which is pivotable relative to the fixed weight between a position with maximum amplitude and a position with minimum amplitude for changing the vibration amplitude of the arrangement, means for converting an axial movement into said pivoting in a radial plane, and also a piston arrangement for providing said axial movement.
  • the eccentric In most cases, the eccentric is driven by a hydraulic motor on one side of the roll. On the other side, in the roll centre, there is in most cases a slow-running hydraulic motor with high torque or a planetary gear with a fast-running hydraulic motor for propulsion of the roller. Parts of these are connected to the roll via rubber elements and rotate with the roll. This makes it difficult and impractical to carry out any regulation inside the roll from this side, and constructions in which this is done are often complicated and have poor durability. On the other side, as already mentioned, the drive motor for the rotation of the eccentric is usually located on one side of the roll.
  • the rolls should not vibrate when the roller is at a standstill or changing its direction of travel.
  • the rollers on the market stop the rotation of the eccentric element before the roller stops or changes the direction of travel. If the eccentric element is started and stopped when the amplitude is great, the result is a resonant frequency with undesirable vibrations as a consequence. It is therefore desirable to be able to start the rotation of the eccentric element essentially without amplitude and to be able to provide the amplitude at the desired frequency, that is to say the desired speed of rotation. It is also desirable to be able to adjust to zero amplitude even with full frequency.
  • the invention comprises a rotatable eccentric arrangement with steplessly adjustable imbalance.
  • a preferred embodiment of the invention as shown in Figs 1-3 , comprises a shaft 1 which is rotatably mounted in two rotary bearings 3. On the shaft 1, there is a tube 4 with a movable eccentric weight 5 which is pivotable in relation to the shaft 1 and fixed weights 2 arranged thereon, so as to make adjustment of the vibration amplitude possible.
  • This pivoting of the movable weight is obtained by displacing a pin 6 in an axial slot in the shaft 1 and at the same time by means of the ends in a helical slot in the tube 4. In this way, an axial displacement of the pin 6 will be converted into a rotation of the movable weight in a radial plane relative to the shaft 1.
  • the weights interact with or counteract one another and increase or, as the case may be, decrease the imbalance depending on the direction in which the rotation takes.place.
  • the displacement of the pin 6 is brought about by one, two or even more axially displaceable rods 7 which run in a corresponding number of holes adapted for this purpose in the shaft 1.
  • the rods are preferably arranged symmetrically around the centre line of the shaft 1 and, in this embodiment, two such rods are arranged on opposite sides of the centre line of the shaft 1.
  • the rods are arranged between means for bringing about a pivoting of the movable weight 5, that is to say in this case the pin 6, and means for bringing about an axial displacement.
  • the rods are not loaded by the torque which is used to rotate the eccentric. In this way, the frictional forces which arise if the displacement is instead brought about by the rotary shaft 14 are avoided.
  • the rods are preferably connected to one of the sides of a rotary bearing 8 and, in this embodiment, are connected to the inner ring of the rotary bearing 8. However, it is nevertheless possible of course to connect the rods to the outer ring of the bearing.
  • the other side of the bearing that is to say the outer ring in this case, is connected to the displacement means, in this case a hydraulic cylinder 9, which is arranged on the same side as the drive means 15 for the rotation of the eccentric, and opposite the side with the planetary gear 25 for propulsion of the roller.
  • the piston runs in the interspace inside an outer tube 12 and outside an inner tube 13 arranged therein.
  • the shaft 14 which connects the drive means 15 and the eccentric shaft 1 rotates inside the tube 13.
  • the non-rotating piston 9 can be caused to be displaced, the force being transmitted to the rotating pin 6 which in turn causes the various eccentric weights to rotate in relation to one another by means of the axial or, as the case may be, the helical slot.
  • the piston 9 can be drawn back with the force which is required in order to rotate the weights 5.
  • the restoring force can be supplemented or replaced by a spring 11.
  • the spring ensures that the imbalance (the amplitude) can be reduced to zero and retains the tube 4 with the weights 5 in this position when the shaft is at a standstill. This means that the rotation of the shaft can be started without amplitude, that is to say with the movable weight in the position for minimum amplitude, as shown in Fig. 3 .
  • a spring-loaded catch 26 can retain the weight in the zero position. The catch is thrown out and released by the centrifugal force at a given threshold frequency, after which the desired regulation can take place.
  • other retaining means which are released at a given force or a given frequency are also possible.
  • the pressure from the rods 7 can be transmitted via a yoke 17 to the centre of the pin 6.
  • the yoke 19 can also be designed as a plate spring and can then be screwed firmly to the pin 6. The yoke prevents the pin 6 from rotating about its axis and also holds it in the centre of the shaft 1.
  • a second exemplary embodiment of the invention as shown in Fig. 4 , the displacement of the pin 6 is brought about by virtue of a second pin 21 being arranged inside the inner ring 22 of the rotary bearing 8.
  • This pin 21 is displaceable in an axial slot in the drive shaft 20 and is furthermore connected to a rod 23 extending in the centre of the drive shaft 1 as far as the pin 6.
  • this embodiment corresponds to that described previously.
  • the displacement means is an electric actuating device instead of a hydraulic piston.
  • This electric actuating device functions as a worm gear screw which, by interacting with an external thread of an inner displaceable tube, exerts a displacing force against the bearing 8.
  • Displacement means other than those indicated above are of course also possible.
  • Fig. 5 shows a third exemplary embodiment of the invention.
  • the single-acting cylinder and the spring have been replaced by a double-acting cylinder which consequently has twin chambers and can impart axial displacement forces in both directions.
  • the direction of rotation of the shaft 1 is then optional.
  • the single-acting cylinder may be designed so that the tube 24 is a part of the piston.
  • Figs 6 and 7 show a third embodiment according to the invention, in which the pivoting axis of the movable weight 5 has been displaced from the centre of rotation of the shaft 1 towards the centre of gravity of the fixed weights 2. If the weight 5 has a common centre of rotation with the shaft, it will adopt a position which produces minimum amplitude. By displacing the centre of rotation of the weight 5 towards the centre of gravity of the fixed weights, this force is reduced, and if it is displaced even further, the force will instead be directed in the opposite direction. Without pressure to the piston, the weight will then adopt the position with maximum amplitude, as shown in Fig. 6 .
  • the weights will be rotated in relation to one another and be rotated towards the position with minimum amplitude, as shown in Fig. 7 .
  • the eccentric element can be started and stopped with minimum amplitude or without amplitude. Impact originating from the weight 5 can then be avoided.
  • Control of the weights in a suitable manner in order to obtain the correct amplitude and/or frequency can advantageously be effected automatically by means of an electronic or digital control unit which can be fed an input signal from a packing meter or the like.

Landscapes

  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Road Paving Machines (AREA)
  • Massaging Devices (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (7)

  1. Drehbare Exzenteranordnung angeordnet in einer Valze zu einer Vibrationsrolle mit einer Antriebsvorrichtung (15) für den Exzenter angeordnet an einem Ende der Walze, die Exzenteranordnung angepaßt für stufenlose Umstellung der Vibrationsamplitude und umfaßt eine im Zentrum der Walze sich ausdehnende drehbare Welle (1,14) mit mindestens einem darauf fest angeordneten Exzentergewicht (2) und mindestens einem beweglichen Gewicht (5), welches schwenkbar ist, im Verhältnis zum festen Gewicht zwischen einer Position mit maximaler Amplitude und einer Position mit minimaler Amplitude für Veränderung der Vibrationsamplitude dieser Anordnung, Vorrichtung um eine axiale Bewegung zur genannten Schwingung in einem Radialplan zu überführen, sowie eine auf derselben Seite der Walze wie die Antriebsvorrichtung (15) angeordnete Verschiebungsanordnung zur Verfügung für obengenannte axiale Bewegung, gekennzeichnet davon dass die Verschiebungsanordnung und die Vorrichtung zur Ueberführung einer axialen Bewegung in eine Schwingung sich auf Abstand von einander befinden und durch mindestens eine, parallel mit der drehbaren Welle (1,14), axial verschiebbare Stange (7,23) angeschlossen sind, so dass die Verschiebungsanordnung an der Seite der drehbaren Welle (14) angeordnet ist und wirkt gegen eine Seite eines Rotationslagers (8) und die verschiebbare Stange ist mit der anderen Seite desselben Lagers angeschlossen, so dass die Stange nicht mit dem Drehmoment belastet wird, das für die Rotation des Exzenters verwendet wird.
  2. Die drehbare Exzenteranordnung nach einem der obenstehenden Patentansprüche dadurch gekennzeichnet dass das fest angeordnete und das bewegliche Gewicht diegleiche Exzentermasse haben und dass das bewegliche Gewicht zu einer Position geführt werden kann, wo die Gewichte im wesentlichen sich balancieren so dass die Amplitude im wesentlichen Null wird.
  3. Die drehbare Exzenteranordnung nach einem der obenstehenden Patentansprüche dadurch gekennzeichnet dass eine Feder (11) angeordnet ist, so dass sie dafür wirkt das bewegliche Gewicht (5) zu führen, so dass die Amplitude verringert wird, und um zu versichern , dass die Anordnung eine minimale Amplitude hat wenn die Rotation gestartet wird.
  4. Die drehbare Exzenteranordnung nach einem der obenstehenden Patentansprüche dadurch gekennzeichnet, dass die Verschiebungsanordnung eine Kolbenanordnung umfaßt, und vorzugsweise einen hydraulichen Kolben.
  5. Die drehbare Exzenteranordnung nach einem der obenstehenden Patentansprüche dadurch gekennzeichnet, dass sie eine Lenkanordnung hat, angepaßt die Amplitude nach der Frequenz, d.h. der Umdrehungszahl zu lenken oder umgekehrt, so dass die Lagerbelastung im wesentlichen konstant bleibt.
  6. Die drehbare Exzenteranordnung nach einem der obenstehenden Patentansprüche dadurch gekennzeichnet, dass das Rotationszentrum für das bewegliche Gewicht (5) versetzt ist gegen den Schwerpunkt des festen Gewichtes (2).
  7. Die drehbare Exzenteranordnung nach einem der obenstehenden Patentansprüche, weiter eine Sperrvorrichtung (26) umfassend, angeordnet um das bewegliche Gewicht in der Position mit minimaler Amplitude festzuhalten, eine Sperrvorrichtung die eingerichtet ist von der Zentrifugalkraft bei einer gewissen Schwellenfrequenz ausgelöst zu werden.
EP99939636A 1998-07-13 1999-07-12 Drehbare Nockenvorrichtung Expired - Lifetime EP1131491B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE9802523 1998-07-13
SE9802523A SE514877E5 (sv) 1998-07-13 1998-07-13 Roterbar excenteranordning avpassad för steglös omställning av vibrationsamplituden
PCT/SE1999/001257 WO2000005455A1 (en) 1998-07-13 1999-07-12 Rotatable eccentric device

Publications (2)

Publication Number Publication Date
EP1131491A1 EP1131491A1 (de) 2001-09-12
EP1131491B1 true EP1131491B1 (de) 2008-03-12

Family

ID=20412070

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99939636A Expired - Lifetime EP1131491B1 (de) 1998-07-13 1999-07-12 Drehbare Nockenvorrichtung

Country Status (7)

Country Link
EP (1) EP1131491B1 (de)
AT (1) ATE389067T1 (de)
AU (1) AU5389299A (de)
DE (1) DE69938358D1 (de)
GB (1) GB0807840D0 (de)
SE (1) SE514877E5 (de)
WO (1) WO2000005455A1 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE525020C2 (sv) 2003-03-21 2004-11-09 Metso Dynapac Ab Ställdon för reglering av en vältvals excenteraxels excentermoment
CN1325729C (zh) * 2003-09-28 2007-07-11 徐州工程机械科技股份有限公司徐工研究院 振动压实机械振动轮无级调幅装置
DE102005014014B4 (de) * 2005-03-26 2008-04-03 Schenck Process Gmbh Schwingungsantrieb, insbesondere Exzenterantrieb für Schwingmaschinen
CN102787544B (zh) * 2011-05-16 2017-08-25 池州腾虎机械科技有限公司 压路机的一种定向振动轮
CN102747670B (zh) * 2012-07-09 2014-12-10 池州腾虎机械科技有限公司 一种可连续调整偏心矩的振动压路机的激振器振动机构
EP3325181B1 (de) * 2015-07-17 2023-08-09 Movax Oy Vibratorvorrichtung
CN111250379A (zh) * 2019-08-09 2020-06-09 济南豪特创新管理咨询合伙企业(有限合伙) 一种回转件组合装置
CN111229581A (zh) * 2019-08-09 2020-06-05 济南豪特创新管理咨询合伙企业(有限合伙) 回转件组合装置
CN111250381A (zh) * 2019-08-09 2020-06-09 济南豪特创新管理咨询合伙企业(有限合伙) 一种回转件组合装置的连接轴

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT375845B (de) * 1982-08-23 1984-09-10 Voest Alpine Ag Einrichtung zur erzeugung von vibrationen

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
US3896677A (en) * 1974-01-18 1975-07-29 Raygo Inc Dual amplitude vibration generator
SE416145B (sv) * 1974-07-31 1980-12-01 Dynapac Maskin Ab Excenterelement for alstring av cirkulera vibrationer
IT1073972B (it) * 1975-07-29 1985-04-17 Komatsu Mfg Co Ltd Vibratore a forza variabile
SE443591B (sv) * 1981-10-28 1986-03-03 Dynapac Ab Anordning for kontinuerlig omstellning av vibrationsamplituden hos ett roterbart excenterelement
DE3418268A1 (de) * 1984-05-17 1985-11-21 Benno 5205 St Augustin Kaltenegger Vibrationsvorrichtung, insbesondere fuer bodenverdichtungsgeraete
US4568218A (en) * 1984-07-16 1986-02-04 Wacker Corporation Adjustably controllable centrifugal vibratory exciter
SE453000B (sv) * 1986-06-27 1988-01-04 Dynapac Ab Vibrationsplatta

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT375845B (de) * 1982-08-23 1984-09-10 Voest Alpine Ag Einrichtung zur erzeugung von vibrationen

Also Published As

Publication number Publication date
SE9802523D0 (sv) 1998-07-13
GB0807840D0 (en) 2008-06-04
AU5389299A (en) 2000-02-14
SE514877C2 (sv) 2001-05-07
SE9802523L (sv) 2000-01-14
DE69938358D1 (de) 2008-04-24
EP1131491A1 (de) 2001-09-12
SE514877E5 (sv) 2011-06-14
ATE389067T1 (de) 2008-03-15
WO2000005455A1 (en) 2000-02-03

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