EP2242590A1 - Excitateur à balourds comprenant un ou plusieurs balourds rotatifs - Google Patents

Excitateur à balourds comprenant un ou plusieurs balourds rotatifs

Info

Publication number
EP2242590A1
EP2242590A1 EP08783460A EP08783460A EP2242590A1 EP 2242590 A1 EP2242590 A1 EP 2242590A1 EP 08783460 A EP08783460 A EP 08783460A EP 08783460 A EP08783460 A EP 08783460A EP 2242590 A1 EP2242590 A1 EP 2242590A1
Authority
EP
European Patent Office
Prior art keywords
tool
force
exciter
frequency
machine
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
EP08783460A
Other languages
German (de)
English (en)
Other versions
EP2242590B1 (fr
Inventor
Ulrich Abdreas Ammann
Kuno Kaufmann
Roland Anderegg
Jochen Hörster
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.)
Ammann Schweiz AG
Original Assignee
Ammann Schweiz 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 Ammann Schweiz AG filed Critical Ammann Schweiz AG
Publication of EP2242590A1 publication Critical patent/EP2242590A1/fr
Application granted granted Critical
Publication of EP2242590B1 publication Critical patent/EP2242590B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • B06B1/167—Orbital vibrators having masses being driven by planetary gearings, rotating cranks or the like

Definitions

  • the invention relates to an unbalance exciter with one or more rotatable imbalances, a machine comprising the unbalance exciter and a method for operating the machine according to the preambles of the independent claims.
  • Unbalance exciters with rotatable imbalances serve to generate time-varying excitation forces and are used in many areas of technology, for example in vibration conveyors, in vibrating screens, in compactors such as vibratory plates and vibratory rollers, in vibratory rams and in vibratory boring and milling machines.
  • the monofrequency imbalance exciters known today, in which all imbalances rotate at the same speed, can basically be classified according to the excitation principle in the circular oscillator and the directional oscillator.
  • Monofrequency circular oscillators produce an exciter force which is temporally variable only with regard to their direction.
  • Monofrequency directional oscillators generate an exciter force, the amount of which changes with time along with its effective direction, such that seen over a full rotation of the imbalance masses two excitation force maxima are formed with opposite directions of action. While the circular oscillator manages with a rotating imbalance mass, the rocker requires system - induced at least two counter - rotating imbalance masses. Since such unbalance exciters generate the same amount of excitation force components in opposite directions of action in each case, the maximum compaction or ramming force that can be provided with them when used in compactors and rams is Limits 2 to 3 times the weight of the machine, depending on whether you need to work in a load operation mode or if operation with temporary lifting of the tool from the work surface is permitted or desired.
  • bifrequente unbalance exciters are known in which the time-varying excitation force is generated by superimposing the excitation force of a rotating at a basic speed first imbalance mass with the excitation force of a phase in phase with twice the speed rotating second imbalance mass. These unbalance exciters generate an exciter force with a single maximum force in a particular direction.
  • a first aspect of the invention relates to an unbalance exciter with one or more roughness usable unbalanced masses for generating a multi-frequency time-varying excitation force.
  • a single imbalance mass it performs several superimposed rotations, which may be rotationally rectified or rotationally opposite, for example.
  • these preferably each perform a single rotation, it being provided that identical and / or opposite rotational directions are used.
  • the excitation force is generated by the superposition of a basic exciter force, which is time-variable with a fundamental frequency, with one or more additional excitation forces which are time-variable with additional frequencies greater than the fundamental frequency.
  • the unbalance exciter is designed such that the phase Läge between the time-varying basic excitation force and at least one of the time-varying auxiliary excitation forces is adjustable, preferably continuously.
  • the inventive multi-frequency unbalance exciters in compactors for soft or highly elastoplastic substrates, such as, for example, Soil and asphalt, by a targeted adjustment of the phase angle between the basic excitation force and the additional excitation forces or depending on the substrate to be compacted, a significant increase in the compaction performance compared to the corresponding compaction equipment can be achieved with today known unbalance exciters. Accordingly, the invention allows for the same compaction performance a significant reduction in the required machine weight, which in turn favors the construction of cheaper and more efficient compactors and makes a reduction in the drive power possible.
  • the phase position between the basic exciter force and at least one of the additional exciter forces during operation can be set, so that a running Adaptation to the respective soil conditions for the purpose of optimizing the compaction performance is possible without the operation having to be interrupted for this purpose.
  • At least one of the additional excitation forces having a supplementary frequency corresponding to an integer multiple of the fundamental frequency is time-variable, preferably with a frequency corresponding to twice the fundamental frequency. It has been shown that at integer frequency ratios the greatest performance gains are possible.
  • the unbalance exciter comprises separate imbalance masses for generating the basic excitation force and the additional exciter forces, which each perform separate rotational movements.
  • Such solutions are based on relatively simple and proven design principles and can also be retrofitted to existing multi-wave unbalance exciters.
  • this has to generate the basic exciter force and at least one of the additional excitation forces on a common imbalance mass, which performs at least two superimposed rotational movements.
  • the unbalance exciter has a counterweight, which reduces the imbalance generated by the imbalance mass in the rotation with the fundamental frequency and thus reduces the basic exciter force. This makes it possible to influence the relationship between the basic exciter force and the or the additional excitation forces by structural measures in many areas.
  • the fundamental frequency and / or the additional frequencies are preferably infinitely adjustable, preferably during operation. Usually their ratio to each other is fixed, ie that a change in the fundamental frequency automatically leads to a corresponding change in the additional frequencies, as is the case with a forced coupling via gears. However, it is also intended to allow variable frequency ratios for specific applications.
  • the amplitude of the basic exciter force and / or the amplitude of one or more of the additional excitation forces are preferably infinitely adjustable, and to advantage during operation.
  • the amplitudes are adjustable independently of the respective excitation frequency, for example by changing the center of gravity distance of the respective imbalance mass from the center of rotation, or by superimposing equally fast and uniformly rotating imbalances.
  • a second aspect of the invention relates to a machine comprising an unbalance exciter according to the first aspect of the invention and a tool for acting on a work surface coupled to the unbalance exciter for vibrational excitation.
  • the machine is preferably a vibration-activated drilling machine, road milling machine or tunneling machine, a vibrating ram or a soil compaction machine, in particular a vibrating plate or a vibrating roller.
  • the machine comprises means for determining the vibration response of the tool to the vibration excitation of the unbalance exciter during normal operation of the machine.
  • Such means typically include acceleration sensors and a computerized computing unit which evaluates the signals provided by the sensors.
  • Means for determining the course of the working surface reaction force during normal operation of the machine which results from a superimposition of the resulting from the vibration response of the tool and its oscillating massratiskraftsverlaufs the tool with the exciter force profile of the exciter and the static weight of the machine.
  • the working surface reaction force is also referred to as the soil reaction force.
  • Such means for determining the progression of the work surface reaction force typically comprise acceleration sensors, positional sensors for rotating imbalances and a computer-aided processing unit which evaluates the signals supplied by the sensors.
  • the machine additionally comprises a machine control, by means of which the phase position between the basic excitation force and the at least one additional excitation force is automatically and preferably continuously adjustable during operation such that a vibration response of the tool or a progression of the working surface reaction force results at which or which the quotient of the maximum amplitude of the vibration response in the tool working direction and the maximum amplitude of the vibration response in the direction opposite to the tool working direction or the quotient of the maximum force of the course of the working surface reaction force in the tool working direction and the maximum force of the course of Work surface reaction force in the direction opposite to the Malawiarbeitsraum for given frequencies and amplitudes of the basic and additional excitation forces is maximum.
  • a machine control by means of which the phase position between the basic excitation force and the at least one additional excitation force is automatically and preferably continuously adjustable during operation such that a vibration response of the tool or a progression of the working surface reaction force results at which or which the quotient of the maximum amplitude of the vibration response in the tool working direction and the maximum amplitude of the
  • the machine comprises a machine control, by means of which the phase position, the frequency and / or the amplitude of the basic exciter force and / or one or more of the additional exciter forces are automatically and preferably continuously adjustable during operation such that a vibration response of the tool or a progression of the work surface reaction force, at or the maximum amplitude of the vibration response in a direction opposite to the pressing of the tool on the working surface or the maximum force of the surface reaction force curve in a direction opposite to the pressing direction of the tool the work surface does not exceed a certain maximum value to prevent temporary loss of contact between the tool and the work surface during normal operation.
  • This is particularly important for vibratory rollers for the compaction of asphalt, which must be operated in on-load operation, since a temporary lifting of the roller from the asphalt surface to be compacted would lead to poor surface quality (chatter marks), which should be avoided.
  • the machine also has means for, in particular, continuous determination of the resonant frequency of the machine-tool-work surface system during normal operation.
  • These means typically comprise acceleration sensors, sensors for position detection of the pathogen (s) and a computer-aided processing unit which evaluates the signals supplied by the sensors and are preferably together with means for determining the vibration response of the tool and / or for determining the course of the working surface. Reaction formed.
  • the machine further comprises a machine control with which the fundamental frequency is automatically and preferably continuously adjustable during operation to a frequency slightly above the determined resonant frequency, preferably to a frequency in the range between 105% and 130%. , More preferably between 110% and 120% of the determined resonant frequency.
  • a machine control with which the fundamental frequency is automatically and preferably continuously adjustable during operation to a frequency slightly above the determined resonant frequency, preferably to a frequency in the range between 105% and 130%. , More preferably between 110% and 120% of the determined resonant frequency.
  • a third aspect of the invention relates to a method of operating the machine according to the second aspect of the invention.
  • the machine is operated in such a way that with the unbalance exciter to Vibrations excited tool acts as intended on a work surface, so performs a work as intended.
  • the vibration response of the tool to the vibration excitation of the unbalance exciter and / or the course of the working surface reaction force is determined and this or compared with a desired target vibration response or a desired target working surface reaction force profile. How the vibration response or the working surface reaction force profile can be determined by measurement is known to the person skilled in the art and therefore need not be explained in more detail here.
  • the phase position between the time-varying basic excitation force and at least one of the time-varying additional excitation forces for changing the total excitation force and thus the vibration excitation is set such that a vibration response of the tool or a progression of the working surface reaction force results, which or which an improved and preferably the greatest possible match the desired vibration response or the target work surface reaction force curve has. In this way, an optimization of the movement of the tool or the force exerted by the tool on the work surface and thus the performance of the machine is achieved.
  • the phase position between the time-varying basic excitation force and at least one of the time-varying additional excitation forces is set or changed during operation of the machine, which enables a continuous operation and preferably as an automated control intervention with a new comparison of the resulting vibration response or the resulting course of the work surface reaction force with the desired vibration response or the SoIl work surface reaction force course is carried out.
  • the phase position is adjusted such that a vibration response of the tool or a work surface reaction force curve results, at which or which the quotient of the maximum amplitude of the vibration response of the tool in the tool working direction and the maximum amplitude of the vibration response of the tool in the direction opposite to the tool working direction or the quotient of the maximum force of the working surface reaction force course in the tool working direction and the maximum force of the working surface reaction force course in the direction counter to the tool working direction for given frequencies and amplitudes of the basic and additional exciter forces.
  • the phase position, the frequency and / or the amplitude of the basic excitation force and / or one or more of the additional exciter forces are preferably set independently of one another such that a vibration response of the tool or a progression of the working surface Reaction force at which the maximum amplitude of the vibration response of the tool in a direction opposite to the pressing direction of the tool on the working surface or the maximum force of the working surface reaction force curve in a direction opposite to the pressing of the tool to the working surface does not exceed a certain maximum value, to prevent temporary loss of contact between the tool and the work surface during normal operation.
  • This is, as already mentioned, particularly important for vibratory rollers for the compaction of asphalt, since they must be operated in on-load operation to a temporary Lifting of the roll from the asphalt surface to be compacted safely prevented.
  • the resonant frequency of the machine-tool-work surface system is determined continuously during the intended operation and the fundamental frequency is in particular adjusted continuously to a frequency slightly above the determined resonant frequency, preferably to a frequency typically in the range between 105 % and 130%, preferably between 110% and 120% of the determined
  • the fundamental frequency can be kept selectively in a range slightly above the resonance frequency, which allows a further performance optimization.
  • the determination of the oscillation response and / or the working surface reaction force course and optionally the resonance frequency, the comparison with a desired target oscillation response and / or a target working surface reaction force and the method Adjusting the phase position and optionally the frequency and / or amplitude carried out automatically by means of a machine control, preferably continuously during operation of the machine. This can be ensured at any time operation with optimal operating parameters.
  • FIGS. 1 and 2 show two basic design principles for unbalance exciters according to the invention; 3 shows a perspective basic representation of an imbalance exciter according to the design principle shown in FIG. 2;
  • FIG. 4 shows a side view of a vibration roller according to the invention
  • 5 shows a perspective top view of the imbalance exciter according to the invention of the vibrating roller from FIG. 4;
  • FIG. 6 shows a longitudinal section through the unbalance exciter from FIG. 5; 7 is a schematic diagram of the phase adjustment of the unbalance exciter from FIGS. 5 and 6; Figures 8a to 8d, the position of the rotating imbalances and the course of the excitation force of the unbalance exciter, the vibration response of the rollers and the course of the floor reaction force in vibration response-optimized operation of the trench roller of Fig. 4; FIGS. 9a to 9d show the phase position of the rotating imbalances and the progression of the exciter force of the imbalance exciter, the oscillation response of the rollers and the profile of the floor reaction force in a soil reaction force optimized operation of the trench roller of FIG.
  • FIG. 4 is a perspective plan view of an inventive unbalance exciter according to the schematic diagram in FIG. 3;
  • FIGS. 11a and 11b show the position of the imbalance mass of the imbalance exciter from FIG. 10 in different angular positions of the basic rotation in two different phase positions;
  • FIG. 12 is a plan view of the lower part of a vibrating plate equipped with two unbalance exciters according to FIG. 10; FIG. and
  • FIG. 1 Two basic design principles for inventive unbalance exciters are shown in Figures 1 and 2 in a perspective view.
  • the operating principle shown in FIG. 1 is based on the use of two rotating shafts 1, 2 which each carry an imbalance weight 3 and are synchronized about parallel axes of rotation r 1, r 2, eg via a toothed gearing or a toothed belt 4, with different rotational speeds f 1, be driven f2.
  • the phase position between the two rotating shafts 1, 2 is adjustable, for example via a differential gear fifth
  • the operating principle shown in FIG. 2 is based on the use of a single guided mass 3, which performs two superimposed rotations.
  • the mass 3 is at a first speed fl spaced around a first axis of rotation rl rotated, while at the same time with a second speed f2, which is greater than the first speed fl and is synchronized with this, is rotated about a second axis of rotation r2, which in turn rotated at the first speed fl and at a fixed distance about the first axis of rotation rl. Due to the second superimposed rotation, the distance of the mass 3 to the first axis of rotation rl changes continuously.
  • FIG. 3 shows a perspective basic representation of a further developed unbalance exciter according to the construction principle shown in FIG. 2.
  • the unbalance exciter comprises a crankshaft-type main body 8, which is rotatably mounted about two end-mounted bearing pins 10 about a first axis of rotation r 1 and connected to a drive motor 9. is that with which he is drivable with a first speed fl.
  • the crank pin is formed by a shaft 11 which carries an imbalance weight 3.
  • the shaft 11 is rotatably supported at its ends about a second axis of rotation r2. At one end, the shaft 11 has a projection with a pinion 6, which runs on the outer circumference of a fixed and concentric with the rotation axis rl of the main body 8 gear 7.
  • FIG. 4 shows a side view of a trench roller according to the invention with an unbalance exciter according to the invention, which implements the construction principle according to FIG.
  • the trench roller consists of an undercarriage 14 with the rollers 15 and the unbalance exciter 16 and an uppercarriage 17 with the drive motor (not shown), which is isolated in vibration with respect to the undercarriage.
  • FIG. 5 shows a perspective top view of the unbalance exciter according to the invention of the trench roller from FIG. 4.
  • the unbalance exciter 16 has two imbalance shafts (not visible) arranged one above the other, which because they are rotated around their own rotation axes rl, r2.
  • a hydraulic motor 9 is arranged, with which the lower imbalance shaft with the fundamental frequency fl can be rotated about the rotation axis rl.
  • FIG. 5 is shown in FIG.
  • Fig. 7 shows the principle of the toothed belt coupling between the two unbalanced shafts 1, 2 greatly simplified
  • the phase position of the rotations fl, f2 of the two shafts 1, 2 to each other can be adjusted by an arrangement of two Auxiliary pulleys 28a, 28b, whose bearings are connected to each other via a bridge 29, in a direction V transversely to a straight line through the centers of rotation of the lower 18 and the upper toothed belt pulley 19 by means of a drive, for example a hydraulic cylinder 13, is moved.
  • a drive for example a hydraulic cylinder 13
  • the ratio of the free timing belt length between the upper and lower timing pulleys 18, 19 on the load side changes to the free timing belt length between the lower and upper timing pulleys 18, 19 on the load-free side (side on which the auxiliary pulley 28a engages the toothed belt 4), so that the lower and the upper pulley 18, 19 and thus the unbalanced shafts 1, 2 are rotated relative to each other.
  • additional pulleys 30 are provided here, which also can serve as tension rollers.
  • the bridge 29 as a tensioning element, which in operation additionally forces the two auxiliary belt disks away from one another and against the toothed belt 4 with a certain prestressing force.
  • FIG. 8 a shows the upper and lower unbalance shafts of the unbalance exciter from FIGS. 5 and 6 during rotation with a first phase position relative to one another.
  • the imbalance masses of the two unbalanced shafts 1, 2 in the illustrated situation have a twist angle ⁇ of 105 ° with respect to one another.
  • the unbalanced shafts 1, 2 generate the exciting force profiles shown in FIG. 8b (exciter force Ferr in kN over the time t shown), which together result in the total exciter force curve (not shown).
  • the vibrational response of the rollers resulting from this unbalance exciter on sandy soil is shown in FIG. 4c and the resulting course of the ground reaction force (floor reaction force Frea in kN over time t) in Fig. 8d.
  • FIGS. 9a to 9d show illustrations such as FIGS. 8a to 8d, with the difference that here there is a second phase position of the imbalance shafts, in which the imbalance masses of the two imbalance shafts 1, 2 have a twist angle ⁇ of only 15 ° to one another in the illustrated situation.
  • FIG. 9b shows the courses of the excitation forces Ferr, so that a different total excitation force curve (not shown) results.
  • a vibrational response of the rollers 15 results in this phase position on sandy ground, in which vibration amplitude maxima result practically equally in the working direction of the rollers as well as in opposite directions, while a floor reaction force curve occurs in which the Ratio of the maximum force of the course of the floor reaction force in the working direction to the maximum force of the course of the floor reaction force in the direction opposite to the working direction is maximum.
  • This is therefore a soil reaction force optimized operation of the trench roller.
  • FIG. 10 shows a perspective plan view of an unbalance exciter according to the invention, which implements the construction principle according to FIG. 2 in the conception according to FIG. 3.
  • the main body 8 has two circular disks 20, which can be rotated around its center around a first axis of rotation r 1.
  • the bearings are not visible here.
  • the discs 20 each form a bearing point 21, on each of which one of the ends of an imbalance shaft consisting of a shaft 11 and an imbalance mass 3 is rotatably mounted about a second axis of rotation r 2.
  • the discs 20 counterweights 31 which reduce the imbalance generated by the imbalance masses 3 during rotation with the fundamental frequency around the first axis of rotation rl and thereby deliberately reduce the Grunderregerkraft such that under normal operation, a certain ratio between the basic excitation force and the additional excitation force is present ,
  • the shaft 11 has a pinion 6, which runs on the outer periphery of a stationary during operation, with the rotation axis rl of the main body 8 and with the center of the discs 20 concentric gear 7.
  • the shaft 11 with the imbalance mass 3 attached thereto is rotated at a fixed distance about the axis of rotation r1.
  • the shaft 11 is rotated about the second axis of rotation r2.
  • the shaft 11 rotates here at a speed f2, which corresponds to twice the drive speed fl.
  • FIG. IIa and IIb show schematically the position of the unbalanced mass of the unbalance exciter of Figure 8 in different angular positions with respect to the basic rotation at two different phase positions, wherein Fig. IIa shows a first phase position and Fig. IIb shows a second, compared to the first rotated by 45 ° phasing.
  • the imbalance weight 3 in each case performs a rotation of 180 ° around the second rotation axis r2 at a basic rotation of the exciter of 90 ° around the first rotation axis r1 and a resulting total rotation of 270 °.
  • FIG. 12 shows a schematic plan view of the lower part of a vibrating plate equipped with two unbalance exciters 16 according to FIG. 10.
  • the upper part with the drive motor is not shown.
  • the housing 27 of the exciter assembly is rigidly connected to the work plate 26 of the vibrating plate.
  • the discs 20 of the unbalance exciter 16 are rotatably mounted about the first axis of rotation rl and each unbalance exciter 16 via a central sleeve 22 torsionally rigidly interconnected.
  • One of the two sleeves 22 is penetrated by an axle (not shown), which carries the gear 7 and connects it with an external gear 24.
  • the unbalanced masses 3 of both unbalance exciters 16 are carried by a common shaft 11, which carries the pinion 6 at a central position, which runs on rotation of the unbalance exciter 16 on the circumference of the gear 7.
  • the drive of the unbalance exciter 16 via a pulley 23 and on the other hand, the rotation of the gear 7 for the purpose of adjusting the phase position via a rack 25 which engages the gear 24.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Road Paving Machines (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)

Abstract

L'invention concerne un excitateur à balourds (16) servant à générer une force d'excitation à double fréquence pouvant varier dans le temps. Cette force d'excitation est générée par superposition d'une force d'excitation de base, pouvant varier dans le temps avec une fréquence de base (f1), et d'une force d'excitation additionnelle (f2), pouvant varier dans le temps avec la double fréquence de base. Cet excitateur à balourds (16) est conçu de telle sorte que la position de phase entre la force d'excitation de base et la force d'excitation additionnelle soit réglable. Il a été démontré que l'utilisation d'excitateurs à balourds de ce type dans des engins de compactage destinés à des sols tendres ou fortement élastoplastiques, tels que la terre et l'asphalte, permet d'accroître considérablement la puissance de compactage par comparaison avec des engins de compactage correspondants équipés d'excitateurs à balourds actuellement connus, ce qui permet de réduire sensiblement le poids de la machine sans diminution de la puissance de compactage.
EP08783460.2A 2008-02-12 2008-08-27 Excitateur à balourds comprenant un ou plusieurs balourds rotatifs Not-in-force EP2242590B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008008802A DE102008008802B4 (de) 2008-02-12 2008-02-12 Bodenverdichtungsgerät mit einem Schwingungserreger
PCT/CH2008/000360 WO2009100543A1 (fr) 2008-02-12 2008-08-27 Excitateur à balourds comprenant un ou plusieurs balourds rotatifs

Publications (2)

Publication Number Publication Date
EP2242590A1 true EP2242590A1 (fr) 2010-10-27
EP2242590B1 EP2242590B1 (fr) 2019-02-27

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EP08783460.2A Not-in-force EP2242590B1 (fr) 2008-02-12 2008-08-27 Excitateur à balourds comprenant un ou plusieurs balourds rotatifs

Country Status (3)

Country Link
EP (1) EP2242590B1 (fr)
DE (1) DE102008008802B4 (fr)
WO (1) WO2009100543A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN102107181A (zh) * 2011-03-24 2011-06-29 潘国梁 齿轮激振机构
CN102107181B (zh) * 2011-03-24 2012-10-10 潘国梁 齿轮激振机构

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DE102008008802B4 (de) 2011-12-15
EP2242590B1 (fr) 2019-02-27
DE102008008802A1 (de) 2009-08-13
WO2009100543A1 (fr) 2009-08-20

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