EP0789801A1 - Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture - Google Patents

Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture

Info

Publication number
EP0789801A1
EP0789801A1 EP96929220A EP96929220A EP0789801A1 EP 0789801 A1 EP0789801 A1 EP 0789801A1 EP 96929220 A EP96929220 A EP 96929220A EP 96929220 A EP96929220 A EP 96929220A EP 0789801 A1 EP0789801 A1 EP 0789801A1
Authority
EP
European Patent Office
Prior art keywords
roller
vibration
drum
unbalanced
setting
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
EP96929220A
Other languages
German (de)
English (en)
Other versions
EP0789801B1 (fr
Inventor
Gülertan Vural
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.)
Wacker Werke GmbH and Co KG
Original Assignee
Wacker Werke GmbH and Co KG
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 Wacker Werke GmbH and Co KG filed Critical Wacker Werke GmbH and Co KG
Publication of EP0789801A1 publication Critical patent/EP0789801A1/fr
Application granted granted Critical
Publication of EP0789801B1 publication Critical patent/EP0789801B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • E01C19/288—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows adapted for monitoring characteristics of the material being compacted, e.g. indicating resonant frequency, measuring degree of compaction, by measuring values, detectable on the roller; using detected values to control operation of the roller, e.g. automatic adjustment of vibration responsive to such measurements
    • 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 vibratory roller according to the introductory part of patent claim 1.
  • Vibratory rollers of this type are known from EP 0 530 546 AI.
  • the two unbalanced shafts of the double-shaft vibration exciter are symmetrically rotatably mounted parallel to one another on opposite sides of the travel axis of the respective drum in a common exciter housing, which in turn is pivotably mounted in the common carrier in the respective drum drum is.
  • One of the two unbalance shafts is rotatably driven by a hydraulic drive motor via gearwheels and coupled to the other drive shaft via gearwheels such that the two unbalance shafts always rotate in opposite directions in the exciter housing at the same speed.
  • the flyweights of the two unbalanced shafts have the same mass and the same center of gravity, so that the vibration exciters located in the two bandages each generate a directional vibration that extends radially to the travel axis of the bandage in question and whose direction depends on the spatial setting of the housing of the unbalanced shafts is dependent.
  • the solution according to EP 0 530 546 AI can advantageously be used in connection with soil types which can best be compacted by the application of shear stresses and combinations of shear and compressive stresses, and it is also very well suited for economical compaction large layer thicknesses.
  • slippage caused by shear and compressive stress combinations can be counteracted and the traction of the roller can be supported.
  • This torque therefore increases proportionally with I and the angular acceleration ⁇ W / ⁇ t. This means that the greater the torques required, the shorter the pivoting time is applied and the greater the moment of inertia I of the excitation system. The greater the torque required, the more complicated the control process becomes.
  • pivotable exciter housings containing the complete structure of the exciter system and the additional pivot bearings require a high level of technical effort and are expensive.
  • Another known vibratory roller (EP 053 598 AO) has two unbalanced shafts arranged parallel to the roller axis, which rotate synchronously with the same direction of rotation, but are phase-shifted by 180 ° with respect to one another.
  • the arrangement is such that the vertical forces generated by the unbalanced shafts compensate each other while the oppositely directed horizontal forces generate a torque on the drum around the drum rotation or travel axis. This torque exerts a shear load that cannot be changed in size on the ground.
  • Investigations have shown that this solution can be used with advantage for the compression of thin-film, rolled and bituminous material and also leads to advantageous results for the operating personnel with regard to the required low noise and vibration nuisance.
  • this known vibratory roller is generally not economically usable with thicker layers and with non-rolling material, e.g. mixed soils, cohesive soils and rocks.
  • the known roller is very susceptible to slippage, which leads to traction problems, particularly on slopes or inclines.
  • the known roller according to EP 053 598 AO is structurally very complex because the unbalanced shafts must be stored far away from the drum axis so that they can generate the desired torque.
  • a vibration plate is shown and described with a vibration exciter placed on the ground contact plate, which has two unbalanced shafts arranged coaxially to one another, i.e. rotating around a common axis of rotation their mutual phase position are adjustable, so that it is possible to adjust the direction of action of the directional vibration generated by the unbalanced shafts with respect to the ground contact plate.
  • the vibration plate can thus be operated in a self-propelled manner in the forward and in the return.
  • DE-195 39 150 AI shows and describes in various embodiments vibration drives for vibrating machines, all of which have coaxial unbalanced shafts.
  • the vibration drives are specially designed for use with vibrating screens and conveying devices.
  • the unbalanced shafts are forcibly driven in opposite directions without the possibility of adjusting the mutual phase relationship during operation.
  • a drive with the same direction of rotation requires a separate drive for each imbalance shaft, which requires considerable technical effort.
  • the object of the invention is to create a universally applicable vibration roller which, depending on the setting, enables
  • centrifugal force which is introduced on the drum travel axis and which produces a rotating force and which can be changed in size in order to exert complex tensions on the soil to be compacted.
  • the vibratory roller according to the invention is to be distinguished by a simple construction, low susceptibility to malfunction and a long service life.
  • the vibratory roller according to the invention can in each case be optimally adapted to the different needs of the soil to be compacted, in such a way that the advantageous effects of the various known vibratory rollers are maintained, but the disadvantages of which are avoided.
  • a particular advantage of the vibration roller according to the invention is also that the moment of inertia of the vibration exciter with respect to the travel axis of the respective drum is extremely low, compared to the vibration roller according to EP 0 530 546 AI e.g. is practically at least ten times smaller, so that the vibration exciter in the setting for introducing a directional vibration force on the drum travel axis to change the direction of the directional vibration requires a much lower torque than in the known roller and accordingly essentially can be pivoted in the new direction for a shorter time, so that it is possible to minimize inhomogeneities and dents in the compacted soil.
  • the sub-claims 2 to 18 relate to preferred embodiments of the vibrating roller according to claim l.
  • the invention also relates to a particularly advantageous method for operating the vibratory roller according to claim 1. This method is the subject of claims 19 to 22.
  • FIG. 1 is a side view of a vibratory roller according to the invention with two roller bandages
  • FIG. 2 shows an axial cross section through one of the two mutually identical roller bandages of the vibratory roller according to FIG. 1,
  • FIG. 2 shows an end view in cross section along the section line III-III in FIG. 2,
  • FIG. 5 shows a schematic illustration of the force vector acting in the vertical direction compared to FIG. 4,
  • FIGS. 4 and 5 shows a schematic illustration of the force vector inclined at a swivel angle ⁇ with respect to the horizontal in the same basic basic setting as in FIGS. 4 and 5, 7 shows a schematic representation of a control circuit for the automatic correction of the angle of attack ⁇ of the force vector in the basic setting according to FIGS. 4 to 6, and
  • 8a and 8b are schematic representations of the force vector rotating in another possible basic setting (setting II) of the vibration exciter in different mutual phase positions of the unbalance shafts and accordingly different sizes of the centrifugal force.
  • the vibrating roller shown in FIG. 1 has two roller bandages 1 and 2 arranged one behind the other in the direction of travel.
  • a frame 2a is arranged on the roller drum 1
  • a frame 2b with a driver's station is located on the roller drum 2.
  • the frames 2a and 2b are connected to one another by means of a vertical swivel pendulum bearing 29 in order to steer the vibration roller.
  • a double-shaft vibration exciter S is arranged in each of the two roll bandages 1 and 2, the structure of which can be seen in detail in FIG. 2.
  • FIG. 2 there are two unbalanced shafts 3 and 4 arranged coaxially to one another in the interior of each roller bandage 1, 2, the one - inner - unbalanced shaft 3 with the help of roller bearings 3b being rotatably supported on the end face in the other - outer - unbalanced shaft 4 encasing it is.
  • the outer unbalanced shaft 4 is mounted at its ends with the aid of roller bearings 6, 7 in each case in one or the other of two in the roller bandages 1 and 2, which cross them diagonally at a mutual distance from one another and are rotatably supported in such a position that its axis of rotation 28, which at the same time represents the axis of rotation of the inner unbalanced shaft 3, coincides with the drum axis of travel, about which the drum bandages 1, 2 rotate relative to the drum carrier 23 or 24, which on the respective roller frame 2a or 2b is fastened on one or the other side of the bandages 1 or 2 and protrudes somewhat into the end of the bandage.
  • the outer unbalanced shaft 4 has a bevel gear 14 coaxial with the axis of rotation 28.
  • the inner unbalanced shaft 3 has an extension 13a extending through the left end face of the outer unbalanced shaft 4 and through the bevel gear 14 attached to it, on which, facing the bevel gear 14, an axially spaced bevel gear 11 is attached, which in the exemplary embodiment has the same diameter and the same number of teeth as the bevel gear 14 on the outer unbalanced shaft 4.
  • the two bevel gears 11 and 14 form, together with two diametrically opposite one another with respect to the extension 3a, rotatable about an axis of rotation perpendicular to the axis of rotation 28 , engaging in them conical gears 12 and 13, a differential gear with a web 15, which is designed as a housing surrounding the extension 3a all around, which for the viewer of FIG. 1 is also closed on the left end and on the left in a tubular end to the left open approach runs out, at the end a Gear 16 is attached.
  • the web 15 forms a pivotable housing, which is rotatably mounted by means of roller bearings in a coaxial to the driving axis 28 on the left lb for the observer of FIG. 2, surrounding the differential gear bearing housing 17.
  • the chassis bearing housing 17 On the left side for the viewer of FIG. 2, the chassis bearing housing 17 has a collar which is concentric with the drive axis 28 and with which it is mounted via a roller bearing 20 in a bearing plate 21 which is fastened to the drum support 23 via buffers 22.
  • the bearing plate 21, which forms a non-rotatable unit with the drum support 23, carries a drive motor 9 with a drive shaft coaxial with the driving axis 28, which is connected to the extension 3a of the inner unbalanced shaft 3 via a coupling 10 accommodated in the tubular extension on the web 15 of the differential gear.
  • the roller drum 1 or 2 is supported on the drum carrier 24 there by means of a bearing plate 26, which is fastened via buffers 27 to the carrier 1 a diagonally crossing the drum and coaxial to the travel axis 28 is mounted on the drum support 24 in a bearing (not shown in detail in FIG. 2).
  • a travel drive motor 25 is fastened to the drum support 24, with which the bearing plate 26 can be set in rotation with respect to the drum support 24 about the travel axis 28.
  • the vibration exciter S described above with its unbalanced shafts 3 and 4 connected at one end via the differential gear can be operated in two different settings of the differential gear with respect to the neighboring device parts.
  • setting I In a first basic setting, referred to below as setting I, the housing-like web 15 of the differential gear is fixed relative to the carrier plate 21 via the gearwheel 16, ie it stands still with the latter, but its angular position with respect to the bearing plate 21 with the aid of a Gear 16 engaging, adjustable by a motor 31 gear 30 (Fig. 3) controlled coaxially to the driving axis 28 can be changed.
  • the outer unbalanced shaft 4 is driven by the inner unbalanced shaft 3, which is rotated by the motor 9, via the bevel gears 11, 12, 13 and 14 in the opposite direction to the inner unbalanced shaft 3, so that the Vibration exciter S generates a directional vibration, the vector of which intersects the travel axis 28 perpendicularly because of the coaxial arrangement of the unbalanced shafts 3 and 4.
  • the spatial phase position of the unbalanced shafts 3 and 4 and, with this, the direction of action of the vector of the directional vibration by 360 ° around the travel axis 28 changeable around, but this adjustment option is used only within a predetermined angular range.
  • 4, 5 and 6 show various different settings of the spatial phase position of the unbalanced shafts 3 and 4 in the basic setting I and the associated direction of action of the vector F 2 of the directional vibration. It can be seen that the spatial phase position of the two unbalanced shafts 3 and 4, ie the swivel angle ⁇ of the vibration exciter S, is selected such that the centrifugal forces generated by the unbalances increase in the horizontal direction in the vertical direction in the phase position shown in FIG.
  • the motor 9 is preferably a hydraulic motor.
  • phase adjustment by means of the servomotor 31 and the gearwheels 30 and 16 can be carried out under manual control, but can also be carried out automatically.
  • Fig. 7 shows the function of a control circuit for automatic control of the phase position of the unbalanced shafts 3 and 4 in such a way that a slippage of the roller bandages 1 and 2 is counteracted on the soil to be compacted.
  • a roller drum tends to look at its tolerance range compared to the non-slipping roller drum- lent h (t) and ⁇ (t)
  • the difference values ⁇ and ⁇ are determined by a comparison element 37, which is also not shown in detail in the drawing. If the values ⁇ and ⁇ above a predetermined, by means of a setpoint generator 40 vor ⁇ settable value, as a Amplifier 38, the two one part motors 31i and 31 2 of the roller tires are l and activated 2 in such a way that the angular position of the vibration exciter S in the sense an increase in the horizontal component of the resulting centrifugal force is changed until the slip determined by the comparison element 37 is below the set limit value.
  • This new swivel angle value is set synchronously for both roller bandages 1 and 2.
  • the set or adjusted pivoting angle value of the centrifugal force is automatically positioned in mirror image with respect to the vertical in the direction of travel. The positioning is preferably carried out as follows:
  • the swivel angle of the excitation force vector is in the range from 0 ° to 45 °, it moves mirror image clockwise, and if it is in the range 45 ° to 90 °, it moves mirror image counterclockwise.
  • the resulting force vector has a horizontal component pointing in the direction of travel, which has two functions, namely on the one hand Generate the shear stresses required for compression and secondly to support traction.
  • the other, vertical force component is directed at the Boiden and generates the compressive stresses necessary for the compaction, while at the same time increasing the frictional force between the drum and the ground. This in turn plays an important role for the shear stress transmission to the soil to be compacted.
  • the setting angle ⁇ should vary from 0 ° to 45 ° and should reach a value of 45 ° with increasing layer thickness of the material.
  • the setting angle ⁇ should vary in the range from 45 ° to 90 ° and reach a value of 90 ° with increasing layer thickness of the material.
  • a basic value of the setting angle of the force vector should take into account a certain reserve for a traction support and an increase in frictional force between the roller drum and the soil, and
  • a preprogrammed command instrument installed on the vibration roller for this purpose can enable the driver to make the basic settings manually.
  • the simple regulation already discussed above is preferably used, according to which the preprogrammed basic settings of the excitation system intervene in a corrective manner, specifically in the case of a tandem roller with both roller drums.
  • the unbalanced shafts 3 and 4 in deviation from the basic setting I described above, can also be set to a basic setting II in which they rotate in the same direction and in which their relative phase position for setting the size of the resulting centrifugal force can be set and fixed.
  • the unbalanced shaft 3 is driven by means of the hydraulic motor 9 via the coupling 10 installed between it and it.
  • Changes and fixations of the phase position of the unbalanced shaft 3 with respect to the unbalanced shaft 4 are carried out in a simple manner as follows:
  • the unbalanced shaft 3 is first held in its current position by means of the hydraulic motor 9 and then the housing-like web 15 of the differential gear is manually (not shown in the drawing) or with an adjustment mechanism, for example the one in FIG 3 to be seen, that is to say adjusted with the hydraulic motor 31 and the gear pair 30, 16, if necessary, in such a way until the changing phase position between the unbalanced shafts 3 and 4 has reached a desired value. Then the prevailing mutual phase position of the unbalanced shafts 3 and 4 is fixed, for which purpose a rigid connection is only established between the output shaft of the hydraulic motor 9 and the web 15, for example by means of a switchable coupling (not shown in the drawing), and at the same time the connection between the Gears 16 and 30 need to be solved.
  • the housing-like web 15, the bevel gears 11, 12, 13 and 14 and the unbalanced shafts 3, 4 positioned and fixed to one another form a single vibration unit rotating in the same direction of rotation and exert a centrifugal force acting on the roller drum around the roller travel axis 28, the size of which depends on the set mutual phase position of the unbalanced shafts 3 and 4.
  • This mode of operation is shown schematically in FIGS. 8a and 8b for different settings of the phase relationship of the unbalanced shafts 3 and 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

Le rouleau vibrant décrit comprend au moins une garniture (1, 2) ayant un générateur de vibrations (S) incorporé comportant deux arbres, qui peut exercer sélectivement une vibration circulaire ou une vibration directionnelle sur l'axe de rotation (28) de la garniture correspondante (1, 2). A cet effet, les arbres déséquilibrés (3, 4) sont disposés coaxialement l'un par rapport à l'autre et par rapport à l'axe de rotation (28) et peuvent être mutuellement couplés de façon à pouvoir tourner dans le même sens de rotation et en sens opposés. Dans les deux cas, la relation des phases entre les arbres déséquilibrés (3, 4) peut être modifiée.
EP96929220A 1995-08-08 1996-08-07 Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture Expired - Lifetime EP0789801B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19529115A DE19529115A1 (de) 1995-08-08 1995-08-08 Vibrationsmechanismus, insbesondere zur Verwendung zur Verdichtung von Böden
DE19529115 1995-08-08
PCT/EP1996/003499 WO1997006308A1 (fr) 1995-08-08 1996-08-07 Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture

Publications (2)

Publication Number Publication Date
EP0789801A1 true EP0789801A1 (fr) 1997-08-20
EP0789801B1 EP0789801B1 (fr) 2001-09-26

Family

ID=7768981

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96929220A Expired - Lifetime EP0789801B1 (fr) 1995-08-08 1996-08-07 Rouleau vibrant avec au moins une garniture et un generateur de vibrations a deux arbres monte dans cette garniture

Country Status (6)

Country Link
US (1) US5934824A (fr)
EP (1) EP0789801B1 (fr)
JP (1) JP3778939B2 (fr)
CA (1) CA2202132C (fr)
DE (2) DE19529115A1 (fr)
WO (1) WO1997006308A1 (fr)

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DE102019113947A1 (de) * 2019-05-08 2020-11-12 Liebherr-Components Biberach Gmbh Schwingungserzeuger sowie Baumaschine mit einem solchen Schwingungserzeuger
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Also Published As

Publication number Publication date
JP3778939B2 (ja) 2006-05-24
JPH10507504A (ja) 1998-07-21
DE59607775D1 (de) 2001-10-31
DE19529115A1 (de) 1997-03-06
WO1997006308A1 (fr) 1997-02-20
CA2202132C (fr) 2001-07-10
US5934824A (en) 1999-08-10
CA2202132A1 (fr) 1997-02-20
EP0789801B1 (fr) 2001-09-26

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