EP0088071A2 - 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
EP0088071A2
EP0088071A2 EP83890022A EP83890022A EP0088071A2 EP 0088071 A2 EP0088071 A2 EP 0088071A2 EP 83890022 A EP83890022 A EP 83890022A EP 83890022 A EP83890022 A EP 83890022A EP 0088071 A2 EP0088071 A2 EP 0088071A2
Authority
EP
European Patent Office
Prior art keywords
shaft
unbalanced mass
wedge
arrangement according
counter
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
EP83890022A
Other languages
German (de)
English (en)
Other versions
EP0088071B1 (fr
EP0088071A3 (en
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, the eccentricity of the total center of gravity of the rotating masses being continuously variable during rotation by an actuating element arranged outside the roller body is and the unbalanced mass is guided axially immovable and radially displaceable 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 invention now relates to such 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, the overall center of gravity of the masses being eccentric to the axis of rotation and the eccentricity being variable. The amplitude of the vibrations depends on the extent of the eccentricity of the overall center of gravity of the masses.
  • 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. If the amplitudes are too small with slightly compacted soil, the efficiency is Unfavorable compaction. If, however, the amplitudes are too large, the road roller will run rough. The vibrations are then transferred to the machine frame and frame damage can occur. It is known to change the eccentricity of the overall center of gravity of the masses with such an unbalance arrangement.
  • DE-OS 2 131 853 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-OS 1 634 474, to change the effect of the unbalance in that several unbalances are rotated relative to one another. Finally, from DE-PS 926 308 an unbalance arrangement of the type mentioned 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 prone to failure.
  • the invention now aims to achieve the adaptation of the amplitude of the vibrations to the particular task in a besender simple, robust and reliable training.
  • Invention essentially in that at least one wedge cooperating with the unbalanced mass is axially displaceably mounted and that a counter-holder arranged on the opposite side of the shaft is rigidly connected to the unbalanced mass and has counter-wedge surfaces for the wedge or wedges.
  • a wedge By using a wedge, the stepless change of the eccentricity and thus the stepless change of the vibration amplitude is made possible in a simple manner.
  • the arrangement of a counter holder rigidly connected to the unbalanced mass enables the simple formation of counter wedge surfaces for the wedges for adjusting the unbalanced mass.
  • 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 Geekenkeil perennial.for the wedges, these wedges are constantly subjected to pressure and By driving the wedges, the unbalance mass can be pulled centrally inwards, 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.
  • a hydraulically actuated piston is axially displaceably guided in a central bore of the shaft and is coupled to the wedge or wedges.
  • the transmission of the hydraulic pressure to the piston is not a problem, since the sealing of the pressure connection arranged coaxially with the shaft presents no difficulties.
  • the invention expediently has the piston in the region of its end facing away from its end face which is subjected to impact, a transverse bolt which projects through at least one axial slot of the shaft and engages the wedge or wedges.
  • the wedge or the wedges are preferably loaded against the pressure of the hydraulic medium acting on the piston by at least one spring supported against a part rigidly connected to the axis.
  • two wedges lying axially apart from one another are rigidly connected to one another, preferably by bolts running in the axial direction. This makes the radial adjustment of the unbalanced mass easier. Such an unbalanced mass extends over a certain axial length and the arrangement of two wedges coupled to one another avoids corners of the unbalanced mass during the adjustment.
  • the wedge surface of each wedge is preferably formed by the base surface of a recess formed on the circumference of a disk, the edges of which engage around the counter-holder.
  • the disk having the wedge surface preferably has a recess encompassing the unbalanced mass on the side opposite the wedge surface. Through the edges of this recess, the rigid unit of unbalanced mass and counter-holder and the wedges are supported against each other 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 unbalanced mass and 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 unbalanced mass and the counter-holder again support the wedges in the direction of rotation .
  • the arrangement is such that the disk rigidly connected to the shaft forms the support for the springs loading 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 maximum eccentricity
  • FIG. 3 shows a section along line III-III of FIG. 2
  • FIG. 4 shows a section along line IV-IV of FIG. 2
  • FIG. 5 shows a section along line VV of FIG. 2
  • Fi g . 6 shows an axial section when the unbalance mass is set to the smallest eccentricity
  • FIG. 7 shows a section along line VII-VII of FIG. 6 and
  • FIG. 8 shows a diagram.
  • 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 in order 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 advantageously 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 I5 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 thus 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 holder 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.
  • the wedges are in the extreme 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. Also through these bolts and bores, the disks 20 and 21 are coupled 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)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Road Paving Machines (AREA)
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
AT611/82 1982-02-17
AT61182A AT376728B (de) 1982-02-17 1982-02-17 Unwuchtanordnung zur erzeugung von vibrationen

Publications (3)

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

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

Cited By (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

Cited By (2)

* 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
US5797699A (en) * 1994-09-29 1998-08-25 Bomag Gmbh Process and apparatus for dynamic soil packing

Also Published As

Publication number Publication date
DE3367742D1 (en) 1987-01-08
AT376728B (de) 1984-12-27
EP0088071B1 (fr) 1986-11-20
EP0088071A3 (en) 1984-04-04
ATA61182A (de) 1984-05-15

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