EP0088071B1 - Dispositif à balourd pour la génération de vibrations - Google Patents

Dispositif à balourd pour la génération de vibrations Download PDF

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Publication number
EP0088071B1
EP0088071B1 EP19830890022 EP83890022A EP0088071B1 EP 0088071 B1 EP0088071 B1 EP 0088071B1 EP 19830890022 EP19830890022 EP 19830890022 EP 83890022 A EP83890022 A EP 83890022A EP 0088071 B1 EP0088071 B1 EP 0088071B1
Authority
EP
European Patent Office
Prior art keywords
shaft
wedges
flyweight
mass device
rigidly connected
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
Application number
EP19830890022
Other languages
German (de)
English (en)
Other versions
EP0088071A3 (en
EP0088071A2 (fr
Inventor
Ferdinand Ing. Hirn
Manfred Edlinger
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.)
Voestalpine AG
Original Assignee
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 Voestalpine AG filed Critical Voestalpine AG
Publication of EP0088071A2 publication Critical patent/EP0088071A2/fr
Publication of EP0088071A3 publication Critical patent/EP0088071A3/de
Application granted granted Critical
Publication of EP0088071B1 publication Critical patent/EP0088071B1/fr
Expired 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
    • 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
    • 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
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid

Definitions

  • the invention relates to an unbalance arrangement for generating vibrations, in particular for road rollers, with a rotatably drivable shaft to which at least one unbalanced mass is connected in a rotationally secure manner, with a counter-holder arranged on the opposite side of the shaft being rigidly connected to the unbalanced mass, and wherein the The eccentricity of the overall center of gravity of the rotating masses can be changed continuously during the rotation by an actuating element arranged outside the roller body and the unbalanced mass is guided axially immovably and radially displaceably on the shaft.
  • Imbalance arrangements are used to generate vibrations, which are caused by an unbalanced mass being connected eccentrically to a rapidly rotating shaft. Such unbalance arrangements are used, for example, in road rollers to compact the soil.
  • the vibrations improve the compaction effect and it is therefore possible to keep the weight of the rollers lower.
  • the amplitude of the vibrations depends on the extent of the eccentricity of the overall center of gravity of the masses. In the case of road rollers, the most favorable amplitude of the vibrations now depends on the state of compaction and the nature of the soil. If the degree of compaction of the soil is low at high dumping heights, large vibration amplitudes are generally advantageous for a favorable efficiency. However, as the compression progresses, the amplitudes of the vibrations should be reduced.
  • DE-A-2131 853 has already disclosed an embodiment of an unbalance arrangement in which the unbalance is formed by a chamber which can be filled with a liquid and the weight of this unbalance is changed by changing the liquid filling. Furthermore, it is known, for example from DE-A-1 634474, to change the effect of the unbalance by rotating several unbalanced masses relative to one another. Finally, from DE-B-926308 an unbalance arrangement of the type mentioned at the outset has become known, in which the eccentricity of the unbalance can be changed. In this known device eccentric rings are adjusted by a piston. The connection of the eccentric rings to the shaft only takes place via the pistons and it is therefore relatively unstable and susceptible to faults.
  • the invention now aims to achieve the adaptation of the amplitude of the vibrations to the particular task in a particularly simple, robust and reliable design.
  • the invention consists in that on the shaft two interacting with the unbalanced mass, axially spaced wedges, which are rigidly connected to one another, preferably by bolts running in the axial direction, are axially displaceable, the wedge surface of each Wedge is formed from the base of a recess formed on the circumference of a disc, the edges of which engage around the counter-holder, and wherein the counter-holder has the counter-wedge surfaces.
  • These wedges which are spaced apart from one another, ensure stable guidance of the unbalanced mass even with a large axial extension thereof.
  • Through the rigid connection of the two wedges to each other enables precise adjustment of the two wedges in the same direction. Because the wedge surfaces are formed by the base of a recess formed on the circumference of a disk, the edges of these recesses can be used as an axial guide for the unbalanced mass. The unbalance mass is pushed outwards by the centrifugal force and the counterholder pulls the unbalance mass inwards.
  • the counter-wedge surfaces are formed on the counter-holder enables a simple construction in which the wedges which are displaceable on the axis push the counter-holder outwards, as a result of which the unbalanced mass is pulled inwards against the centrifugal force and a constant positive engagement of the wedges on the counter-wedge surfaces the counterhold is guaranteed. This results in a simple construction and good guidance of the unbalanced mass by means of the counter holder.
  • the mass of the counter-holder is less than the unbalanced mass. Because the mass of the counter-holder is less than the unbalanced mass connected to this counter-holder, the centrifugal force of the unbalanced mass pushes this counter-holder centrally inwards, and since the unbalanced mass has the counter-wedge surfaces for the wedges, these wedges are constantly subjected to pressure and it the imbalance mass can be pulled centrally inwards by the advance of the wedges, thereby reducing the eccentricity of the overall center of gravity and thus the vibration amplitude.
  • the counter-holder can be connected to the unbalanced mass by bolts which are passed through transverse bores of the shaft.
  • the arrangement is such that a hydraulically actuated piston is axially displaceably guided in a central bore of the shaft, which has a cross bolt in the region of its end facing away from its acted end face, which passes through at least one axial slot of the shaft protrudes through and engages the wedges, the wedges being loaded by at least one spring supported against a part rigidly connected to the shaft against the pressure of the hydraulic medium acting on the piston.
  • a single-acting hydraulic piston can be used. Only one connection for the pressure medium to the rotating unbalanced shaft is required.
  • the force exerted on the piston by the hydraulic medium is expediently directed in the direction of the tip angle of the wedge. In this way, the wedge is driven by the hydraulic force and the spring only has to be dimensioned for the restoring force, so that it can be found with a weaker spring.
  • the disk having the wedge surface preferably has a recess encompassing the unbalanced mass on the side opposite the wedge surface.
  • the edges of this recess thus support the rigid unit of the unbalanced mass and counter-holder and the wedges in the direction of rotation.
  • a disk is preferably rigidly connected to the shaft, which has recesses on its circumference, the edges of which encompass the unbalanced mass and the counter-holder and form a radial guide thereof.
  • the rigid unit of the unbalanced mass and the counter-holder is guided radially and is supported in the direction of rotation, so that the unbalanced mass is carried along with the rotation of the unbalanced shaft, and the wedges are again supported in the direction of rotation via the unbalanced mass and the counter-holder .
  • the arrangement is such that the disk rigidly connected to the shaft forms the support for the springs which load the wedges against the pressure of the hydraulic medium acting on the piston and that the bolts connecting the wedges penetrate the disk.
  • FIG. 1 shows the overall arrangement of a road roller.
  • 2 to 8 show the unbalance arrangement accommodated in the roller body.
  • 2 shows an axial section when the unbalanced mass is set to the greatest eccentricity
  • FIG. 3 shows a section along line 111-111 of FIG. 2
  • FIG. 4 shows a section along line IV-IV of FIG. 2
  • FIG. 5 shows a section
  • FIG. 6 shows an axial section along line VV of FIG. 2 when the unbalance mass is set to the smallest eccentricity
  • FIG. 7 shows a section along line VII-VII of FIGS. 6 and 8.
  • FIG. 1 shows a road roller in which two roller bodies 2 are mounted in fork-shaped carriers 3 on the frame 1.
  • the fork-shaped carrier 3 are rotatably mounted about pin 4 to to enable the steering of the road roller.
  • the roller bodies 2 are elastically supported in the fork-shaped carriers, for example with the interposition of rubber buffers, so that the vibrations caused by the unbalance arrangement are not transmitted to the fork-shaped carriers 3 and to the frame 1.
  • the roller body 2 are hollow and the unbalance arrangement shown in FIGS. 2 to 8 is provided within this roller body 2.
  • This unbalance arrangement has a shaft 5, which is mounted in two bearings 6 and 7 in the hollow roller body.
  • the bearings 6 and 7 are rigid and connected to the roller body without the interposition of rubber buffers or the like, so that the vibrations emanating from the shaft 5 are transmitted directly to the roller body 2.
  • the roller body 2 is suitably made of sheet metal.
  • the shaft 5 is driven at high speed by a motor, not shown, for example a hydraulic motor.
  • the unbalanced mass 8 is an unbalanced mass which is connected to a counter holder 9 by means of screw bolts 10.
  • the bolts 10 are passed through bores 11 of the shaft 5.
  • a disk 12 is rigidly connected to the shaft 5 by means of a screw 13.
  • This disc 12 has recesses 14 and 15 on its circumference.
  • the unbalanced mass 8 is guided radially in the recess 14 or on the side edges of this recess and the counter-holder 9 is guided radially in the recess 15 or on the side edges thereof.
  • the unbalanced mass 8 and the counter-holder 9 are thus taken along by the shaft 5 when the same rotates.
  • the counter holder 9 has two counter wedge surfaces 16 and 17, with which wedges 18 and 19 cooperate.
  • the unbalanced mass 8 is larger than the counter-holder 9 and, during rotation, the unbalanced mass 8 therefore tends to deflect outwards and pulls the counter-holder 9 inwards.
  • the counter wedge surfaces 16 and 17 are therefore constantly in contact with the wedges 18 and 19 during rotation. When the wedges 18 and 19 are pushed to the left, the counter support 9 is pressed outwards and the unbalanced mass 8 is pulled inwards.
  • the wedges 18, 19 are on the right and the unbalanced mass 8 has its greatest eccentricity. 6, the wedges are in the outermost left position 18 ', 19' and in this position the unbalanced mass 8 is pulled into its innermost position 8 'and therefore has its smallest eccentricity.
  • the eccentricity of the unbalanced mass 8 can be changed continuously as desired between the positions according to FIGS. 2 and 6.
  • the wedges 18 and 19 are formed on disks 20 and 21. These disks 20 and 21 have recesses 22 and 23 on their circumference.
  • the recesses 22 encompass the unbalanced mass 8 and the recesses 23 encompass the counter holder 9. In this way, the disks 20 and 21 are coupled with the unbalanced mass 8 and the counter holder 9 in the direction of rotation.
  • the base of the recesses 23 forms the wedge surfaces 24 and 25 of the wedges 18 and 19.
  • the two disks 20 and 21 are rigidly connected to one another by bolts 26 which pass through bores 27 of the disk 12. These bolts and bores also couple the disks 20 and 21 to the disk 12 and therefore to the shaft 5 in the direction of rotation.
  • a hydraulic piston 29 is guided axially displaceably in a central bore 28 of the shaft 5.
  • the working space 30 of this piston is connected via a central bore 31 to a hydraulic pressure source via a connection, not shown.
  • the piston 29 has a transverse pin 33 which passes through axial slots 34 in the shaft 5 and connects the disk 20 to the piston.
  • the piston 29 pushes the disks 20 and 21 or the wedges 18 and 19 to the left, as a result of which the eccentricity of the unbalanced mass 8 is reduced.
  • the disks 20 and 21 and the piston 29 are reset by compression springs 35 which surround the bolts 26 and are supported against the disk 12. In this way, the eccentricity of the unbalanced mass 8 is reduced.
  • the eccentricity of the unbalanced mass 8 and thus the vibration amplitude can thus be changed continuously.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (7)

1. Dispositif de balourd destiné à la production de vibrations, en particulier pour rouleaux compresseurs, comprenant un arbre (5) pouvant être entraîné en rotation, auquel au moins une masse de balourd (8) est reliée solidairement en rotation, dans lequel un organe de retenue (9) disposé sur le côté opposé de l'arbre (5) est relié rigidement à la masse de balourd (8) et où l'excentricité du centre de gravité d'ensemble des masses tournantes peut être modifiée par variation continue pendant la rotation par un organe d'actionnement disposé à l'extérieur du corps (2) du cylindre, la masse de balourd (8) étant montée sur l'arbre (5) de façon à être immobilisée dans la direction axiale et mobile dans la direction radiale, caractérisé en ce que, sur l'arbre (5) sont montés mobiles en translation axiale deux coins (18, 19) disposés à un certain écartement axial mutuel, qui coopèrent avec la masse de balourd (8) et qui sont reliés rigidement l'un à l'autre, de préférence par des broches (26) qui s'étendent dans la direction axiale, le plan incliné (24, 25) de chaque coin (18, 19) étant formé par la surface de fond d'un évidement (23) formé sur la circonférence d'un disque (20, 21) et dont les bords encadrent l'organe de retenue (9), cet organe de retenue présentant les plans inclinés conjugués (16, 17).
2. Dispositif de balourd selon la revendication 1, caractérisé en ce que la masse de l'organe de retenue (9) est plus petite que la masse de balourd (8).
3. Dispositif de balourd selon la revendication 1 ou la revendication 2, caractérisé en ce que, dans un perçage central (28) de l'arbre (5), est guidé mobile en translation axiale un piston (29) pouvant être chargé hydrauliquement, qui présente, dans la région de son extrémité qui est à l'opposé de la surface frontale chargée, une broche transversale (33) qui traverse au moins une fente axiale (34) de l'arbre (5) et qui attaque les coins (18, 19), les coins (18, 19) étant chargés par au moins un ressort (35) qui prend appui contre un élément (12) relié rigidement à l'arbre (5), en antagonisme par rapport à la pression du fluide hydraulique agissant sur le piston (29).
4. Dispositif de balourd selon l'une des revendications 1, 2 et 3, caractérisé en ce que les disques (20, 21) qui présentent les plans inclinés (24, 25) des coins présentent, sur le côté qui est à l'opposé des plans inclinés, un évidement (22) qui encadre la masse de balourd (8).
5. Dispositif de balourd selon l'une des revendications 1 à 4, caractérisé en ce qu'à l'arbre (5) est fixé rigidement un disque (12) qui présente, sur sa circonférence, des évidements (14, 15) dont les bords encadrent la masse de balourd (8) et l'organe de retenue (9), et forment un guidage radial pour ces éléments.
6. Dispositif de balourd selon la revendication 5, caractérisé en ce que le disque (12) qui est relié rigidement à l'arbre (5) forme l'appui pour les ressorts (35) qui chargent les coins (18, 19) en antagonisme par rapport à la pression du fluide hydraulique agissant sur le piston (29), et en ce que les broches (26) qui relient les coins (18, 19) traversent le disque (12).
7. Dispositif de balourd selon l'une des revendications 3 à 6, caractérisé en ce que la force qui est exercée sur le piston (29) par le fluide hydraulique, est dirigée vers l'angle de sommet des coins (18,19).
EP19830890022 1982-02-17 1983-02-17 Dispositif à balourd pour la génération de vibrations Expired EP0088071B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT61182A AT376728B (de) 1982-02-17 1982-02-17 Unwuchtanordnung zur erzeugung von vibrationen
AT611/82 1982-02-17

Publications (3)

Publication Number Publication Date
EP0088071A2 EP0088071A2 (fr) 1983-09-07
EP0088071A3 EP0088071A3 (en) 1984-04-04
EP0088071B1 true EP0088071B1 (fr) 1986-11-20

Family

ID=3495176

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19830890022 Expired EP0088071B1 (fr) 1982-02-17 1983-02-17 Dispositif à balourd pour la génération de vibrations

Country Status (3)

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EP (1) EP0088071B1 (fr)
AT (1) AT376728B (fr)
DE (1) DE3367742D1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4434779A1 (de) * 1994-09-29 1996-04-04 Bomag Gmbh Verfahren und Vorrichtung zum dynamischen Verdichten von Boden

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2542227A (en) * 1946-07-02 1951-02-20 Rudolf K Bernhard Testing apparatus
DE926308C (de) * 1951-08-10 1955-04-14 Albert Linz Walze zur Verdichtung von Bodenmassen, Schuettguetern od. dgl., insbesondere fuer den Strassenbau
CH321239A (de) * 1954-04-23 1957-04-30 Lehmann Pottkaemper Gerhard Verfahren zur stufenlosen Regelung der Wuchtkraft von Schwingungserzeugern und Schwingungserzeuger zum Durchführen des Verfahrens
DE1484594C3 (de) * 1962-12-31 1974-01-10 Fa. Hubert Zettelmeyer, 5503 Konz Unwuchtwelle für eine Rüttelwalze
AT250423B (de) * 1963-10-17 1966-11-10 Buckau Wolf Maschf R Selbstbewegliche Verdichtungsmaschine
DE1634474A1 (de) * 1966-02-24 1970-08-06 Buckau Wolf Maschf R Ruettelwalze
US3616730A (en) * 1970-06-29 1971-11-02 American Hoist & Derrick Co Vibratory roller
DE2051615C3 (de) * 1970-10-21 1975-07-17 Frenking, Hubert, Dr.-Ing., 5100 Aachen Verdichtungswalze für den Baugrund od.dgl
DE2131853A1 (de) * 1971-06-26 1973-01-11 American Hoist & Derrick Co Ruettelwalze
DE7125082U (de) * 1971-06-30 1971-12-02 Weller W Gmbh Vibrationswalze
GB1407422A (en) * 1972-02-04 1975-09-24 Raygo Inc Fluid motor control mechanism

Also Published As

Publication number Publication date
DE3367742D1 (en) 1987-01-08
AT376728B (de) 1984-12-27
EP0088071A3 (en) 1984-04-04
ATA61182A (de) 1984-05-15
EP0088071A2 (fr) 1983-09-07

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