EP2558649B1 - Agencement pour fournir une force de pression pulsée - Google Patents

Agencement pour fournir une force de pression pulsée Download PDF

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Publication number
EP2558649B1
EP2558649B1 EP10714159.0A EP10714159A EP2558649B1 EP 2558649 B1 EP2558649 B1 EP 2558649B1 EP 10714159 A EP10714159 A EP 10714159A EP 2558649 B1 EP2558649 B1 EP 2558649B1
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EP
European Patent Office
Prior art keywords
exciter
spring
vibration damper
force
mass
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.)
Not-in-force
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EP10714159.0A
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German (de)
English (en)
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EP2558649A2 (fr
Inventor
Roland Anderegg
Martin Gerhard
Kuno Kaufmann
Dominik Anton Von Felten
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Ammann Schweiz AG
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Ammann Schweiz AG
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Publication of EP2558649A2 publication Critical patent/EP2558649A2/fr
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Publication of EP2558649B1 publication Critical patent/EP2558649B1/fr
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses

Definitions

  • the invention relates to an arrangement for providing a pulsating compressive force, a soil compacting device comprising such an arrangement, a method for operating such an arrangement or such a soil compacting device and the use of such a device for soil compaction according to the preambles of the independent claims.
  • the desired resonance state can be produced by changing the excitation frequency in a wide range, so that at least the latter problem can be avoided.
  • the exciter frequency required to produce the resonant state is often energetically sub-optimal, which in turn means that even these devices can not fully exploit their performance potential.
  • a vibration plate for soil compaction is known in which the superstructure with the drive motor is substantially vibration coupled from the bottom plate.
  • Such vibration plates react less sensitive to changing soil conditions with respect to their operating behavior, but also have a much lower maximum soil compaction force than equally heavy vibrating plates, which operate on the absorber principle.
  • a first aspect of the invention relates to an arrangement for providing a pulsating Compressive force.
  • the arrangement comprises an exciter part with an unbalance exciter for generating an intermittent excitation force and with a contact surface for transmitting a perpendicular to the contact surface force component of the excitation force as a pulsating pressure force on a tool or on a force to be acted upon by the pressure working surface.
  • the arrangement comprises a Tilgerteil, which is connected to the exciter part via a spring-damper unit, for forming a oscillatory system excitable by the unbalance exciter to resonant oscillations.
  • the arrangement is such that the spring stiffness (also called the spring constant) of the spring-damper unit, the damping of the spring-damper unit, the spring preload of the spring-damper unit, the mass of the absorber part, at the spring Damper unit becoming effective mass moment of inertia of Tilgerteils, the mass of the excitation part and / or acting on the spring-damper unit mass moment of inertia of the excitation part is changed in operation or are.
  • the spring stiffness also called the spring constant
  • the unbalance exciter of the inventive arrangement is designed as a directional oscillator or as a circular oscillator.
  • one or the other alternative may be more advantageous. So it is for example in the event that with the arrangement of a vibrating plate is to be formed for soil compaction, advantageous if the unbalance exciter is designed as a directional oscillator, because so By tilting the direction of vibration relative to the vertical at the same time the drive of the vibrating plate can be realized. If, however, a compactor with a separate drive to be formed with the arrangement, it is preferable to perform the unbalance exciter as a simple circular oscillator, since such unbalance exciters are structurally simple to implement and are correspondingly robust and inexpensive.
  • the arrangement is designed such that the Tilgerteil the arrangement during normal operation in the direction of gravity exclusively on the exciter part is supported by the spring-damper unit.
  • the Tilgerteil this is arranged over the exciter part, so that there is a simple structure.
  • Such embodiments of the arrangement are preferably used for the formation of vibrating plates for soil compaction, in which the entire device unit is supported exclusively on the bottom plate on the ground.
  • the arrangement is designed such that the Tilgerteil part of the intended operation is partially supported by the spring-damper unit on the exciter part and partly on support means, which are formed separately from the excitation part.
  • the Tilgerteil performs the intended operation, an intermittent tilting oscillation about a tilt axis in the region of the vibration moderately decoupled from the exciter part support means around.
  • the mass moment of inertia of the absorber part that becomes effective on the spring-damper unit and the spring preload of the spring-damper unit can be changed in a simple manner and thus influence the oscillation behavior of the arrangement by the weight distribution between that of the exciter part to be carried weight fraction of the absorber part and that of the support means to be carried weight fraction of the absorber part is changed.
  • This can be done for example by moving a weight on the absorber part and is possible with simple means, such as a motor spindle, even during operation.
  • the arrangement comprises a rest part, which is connected to the excitation part or the absorber part, such that it forms a coherent unit with this part, but is substantially decoupled from it in terms of vibration.
  • the rest part is fully worn during normal operation as intended by the exciter part or by the Tilgerteil.
  • the guide shaft of the vibrating plate which also carries the controls, such a rest part by being mounted with a vibration isolating bearing assembly on Tilgerteil or on the exciter part and is supported by this.
  • the rest part is worn during intended operation completely by support means, which are substantially decoupled from the excitation part and the absorber part in terms of vibration.
  • the inventive arrangement as a soil compaction device consisting of a soil compaction attachment and an associated wheel loader or excavator, which in the normal operation exclusively the leadership and the drive of the arrangement in horizontal direction but takes over in the vertical direction, the arrangement neither supports nor exerts a force on them to train.
  • the soil compacting attachment can be designed as a vibrating plate or as a vibration-excited roller body.
  • the rest part is partially carried by the exciter part or the absorber part during normal operation and partly by suspension elements which are substantially decoupled from the excitation part and the absorber part in terms of vibration.
  • the drive unit with the driver's cab forms such a resting part by supporting itself on one end with vibration-isolating bearings on the exciter part designed as a roller body or on the absorber part and on the other end via drive wheels the floor.
  • the arrangement is designed such that in operation, a change in the weight distribution between the exciter part or the absorber part to be supported weight portion of the rest portion and the weight of the rest part to be supported by the support means possible is, preferably by shifting a weight on the rest part. As a result, it is easy to influence the vibration behavior of the arrangement.
  • the arrangement is designed such that a change in the mass of the absorber part, the moment of inertia of the absorber part, the mass of the excitation part and / or the moment of inertia of the excitation part is possible in that a or a plurality of liquid volumes between the rest portion and the excitation part and / or the absorber part is or will be replaced. In this way can be influenced in many areas on the vibration behavior of the arrangement.
  • the arrangement according to the invention is designed such that a change in the mass of the absorber part, the mass moment of inertia of the absorber part, the mass of the excitation part and / or the mass moment of inertia of the exciter part is possible because one or more liquid volumes are exchanged between the absorber part and the exciter part , which is preferred, it can be influenced in many areas without the presence of a rest part on the vibration behavior of the arrangement.
  • the arrangement according to the invention is designed such that the absorber part and / or the excitation part has at least two masses which are movable against one another when the absorber part or excitation part is accelerated in a direction perpendicular to the contact surface, wherein the spring force is changeable during operation.
  • the inventive arrangement is designed such that a change in the spring stiffness of the spring-damper unit by stiffening of spring elements of the spring-damper unit and / or by changing the application of force in spring elements of the spring-damper unit possible is.
  • it is for example intended to use elastomeric hollow springs whose spring stiffness by applying their Interior can be changed with a pressurized fluid via a change in the fluid pressure.
  • the change of the force is preferably carried out by changing a translation of the introduced forces, eg by means of length-variable toggle.
  • the arrangement according to the invention is designed in such a way that the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter can be changed during operation, which is likewise preferred, the advantage arises that the arrangement has a maximum Has flexibility to adapt to different or changing operating conditions.
  • the arrangement comprises a particular electronic control unit, with which the spring stiffness of the spring-damper unit, the damping of the spring-damper unit, the spring bias of the spring-damper unit, the mass of Tilgerteils, the mass moment of inertia of Tilgerteils, the mass of the excitation part and / or the moment of inertia of the excitation part in operation is automatically adjustable depending on measured system variables or are, preferably such that the Tilgerteil resonates with the exciter part, advantageously with the same Frequency or at half the frequency of the excitation part.
  • the arrangement according to the invention is designed in such a way that the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter can be changed during operation, which is preferred, then it is advantageous that the control
  • the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter in operation automatically adjustable in dependence on measured system variables or control unit is or are, preferably, such that the Tilgerteil resonates with the exciter part, advantageously with the same frequency or with half the frequency of the excitation part.
  • a second aspect of the invention relates to a soil compaction device with an arrangement according to the first aspect of the invention, in which the claimed contact surface of the arrangement serves as a tool for compaction of the soil during normal operation.
  • the advantages of the invention are particularly evident.
  • the soil compaction device is a vibrating plate or a roller, in particular a roller with one or two vibratory roller bodies (bandages) arranged one behind the other in the unwinding direction.
  • a third aspect relates to a method of operating the arrangement according to the first aspect of the invention or the soil compacting device according to the second aspect of the invention.
  • the arrangement is intended with the contact surface in contact with a work performing tool or a work surface to be processed, preferably to be compacted, such as e.g. a floor area to be compacted.
  • the spring stiffness (also called spring constant) of the spring-damper unit, the damping of the spring-damper unit, the spring preload of the spring-damper unit, the mass of the absorber part, the moment of inertia of the absorber part, the mass of the excitation part and / or the mass moment of inertia of the exciter part changed, so that the vibration behavior of the oscillatory system formed by exciter part, spring-damper unit and Tilgerteil changed.
  • the spring stiffness also called spring constant
  • the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter is additionally changed during normal operation, whereby an even better adaptation of the arrangement or soil compaction device to a variety of operating conditions is possible.
  • a pulsating pressure force of maximum size can be made available at the contact surface of the arrangement according to the invention.
  • a fourth aspect of the invention relates to the use of the arrangement according to the first aspect of the invention for soil compaction. In such use, the advantages of the invention are particularly evident.
  • Fig. 1 shows a first inventive, designed as a vibrating plate soil compacting device in side view.
  • Fig. 2 schematically shows the vibrational model of the oscillatory system of this vibrating plate.
  • the vibrating plate on an undercarriage 1 (demanding Erregerteil) and a superstructure 5 (claims Tilgerteil) on.
  • the undercarriage 1 comprises a ground contact plate 13, which has on its underside a contact surface 3 for the initiation of the vibrating plate generated by the pulsating pressure force in the bottom 4 to be compacted, and designed as a directional vibrator unbalance exciter 2 with a hydraulic motor, which is a substantially vertically directed generates intermittent excitation force, which is introduced into the ground contact plate 13.
  • the uppercarriage 5 comprises a drive unit 14 with a diesel engine which drives a hydraulic pump and an air compressor.
  • the hydraulic pump supplies via hydraulic hoses the hydraulic motor of the unbalance exciter 2 with a stream of pressurized hydraulic fluid, for driving the unbalance exciter 2.
  • the chassis of the superstructure 5 is weighted dimensioned such that together with the drive unit 14 results in a certain total mass of the superstructure as absorber mass ,
  • the superstructure 5 is supported in the direction of gravity via four in their spring stiffness and their damping behavior changeable elastomeric hollow springs 15 (claimed spring-damper unit) on the undercarriage 1 from. Another support of the superstructure 5 in the direction of gravity does not exist.
  • the elastomeric hollow springs 15 are represented by the spring 15a with the spring stiffness k2 and the damper 15b with the damping d2.
  • the mass of the superstructure 5 is designated m2g and that of the undercarriage 1 m1g, the movements of the upper and lower carriage in the vertical direction x2 and x1.
  • the spring stiffness of the bottom 4 is denoted by k1 and its damping by d1.
  • the rotational frequency of the unbalance exciter 2 with ⁇ 1 and its excitation force denoted by F1.
  • the structure of the elastomeric hollow springs 15 is from the FIGS. 3a to 3c It can be seen which sections through one of the elastomeric hollow springs 15 at an overpressure in the interior 16 of 0 bar ( Fig. 3a ), from 2 bar ( Fig. 3b ) and 4 bar ( Fig. 3c ) demonstrate.
  • the elastomeric body 17 of the elastomeric hollow spring 15 increasingly stretches in the axial direction (loading direction) with increasing pressure in the interior 16 and bulges progressively in the radial direction. It increases with increasing pressure in the interior 16, the stiffness of the elastomeric hollow spring 15.
  • the interiors 16 of the elastomeric spring elements 15 are connected via lines and control valves to the air compressor of the drive unit 14 and can be targeted so with an overpressure between 0 bar and 6 bar, to change the spring stiffness of the elastomeric spring elements 15th
  • vibration-isolating fastening elements 8 Attached to the superstructure 5 by means of vibration-isolating fastening elements 8 is a guide tongue 9 (demanding rest part) which carries the operating elements and serves to guide the vibration plate by an operator.
  • the vibration-isolating fasteners 8 are designed such that the guide tongue 9 forms a coherent unit with the superstructure 5, but is substantially decoupled from this vibrationally.
  • the vibration plate comprises an electronic control unit, by means of which in operation the accelerations of the undercarriage 1 and the undercarriage 1 in the vertical direction, ie perpendicular to the contact surface 3, as well as the rotational frequency ⁇ 1 of the unbalance exciter 2 can be determined and in dependence thereon determined system parameters, the rigidity and damping of the elastomeric spring elements 15 by Change in the pressure in the interior 16 can be changed automatically such that the superstructure 5 always resonates with the undercarriage 1.
  • the control or regulation unit automatically regulate the rotational frequency of the unbalance exciter 2 during operation in such a way that a maximum compaction power is achieved.
  • Fig. 4 shows a second invention, designed as a vibrating plate soil compaction device in side view and Fig. 5 schematically the vibration model of the oscillatory system of this second vibrating plate.
  • this vibrating plate apart from a few details, has the same structure as the first vibrating plate in accordance with FIGS Figures 1 and 2 , An essential difference, however, is that in the vibrating plate shown here, the superstructure 5 is supported on the stiffness not changeable elastomer springs 18 on the undercarriage 1.
  • the elastomer springs 18 are represented by the spring 18a with the spring stiffness k2 and the damper 18b with the damping d2.
  • ballast tanks designed as piston accumulators are provided both in the undercarriage 1 and in the superstructure 5, the volume of which can be selectively and oppositely changed by means of hydraulic drives and an associated control or regulation unit.
  • the electronic control unit is also designed such that in operation, the accelerations of the upper carriage 5 and the lower carriage 1 in the vertical direction, ie perpendicular to the contact surface 3, as well as the rotational frequency ⁇ 1 of the unbalance exciter can determine.
  • the control or regulation unit changes the masses m1g, m2g of the undercarriage 1 and the uppercarriage 5 automatically in operation as a function of these determined system parameters in such a way that the uppercarriage 5 resonates with the undercarriage 1.
  • Fig. 6 shows a first embodiment of a trained as a compactor invention soil compaction device in side view and Fig. 7 schematically the vibrational model of the oscillatory system of this compactor.
  • the compactor comprises a front part 19 and a rear part 20, which are connected to one another via an articulated joint 21.
  • the front part 19 of the roller compactor consists essentially of a roller body 23 (demanding Erregerteil) and a chassis frame 25 (claim damper Tilgerteil).
  • the roller body 23 comprises a bandage 11, which has the contact surface 3 for the initiation of the generated pulsating pressure force in the bottom 4 to be compacted, and formed as a circular vibrator unbalance exciter 2 with a hydraulic motor which generates a respect to their direction of action intermittent excitation force in the Bandage 11 is initiated.
  • the chassis frame 25 is supported in the direction of gravity via two spring-damper assemblies 22 (claimed spring-damper unit) with fixed stiffness and damping on the two end-side bearings of the roller body 23 and is connected via vibration-isolating fasteners 8 with the articulated joint 21 which is carried by the rear part 20 of the compactor.
  • the vibration isolating fasteners 8 are designed such that the rear part 20 of the compactor with the chassis frame 25 forms a coherent unit, but is vibrationally decoupled substantially from this and thus represents a claim according Oxfordteil.
  • the rear part 20 of the roller compactor consists essentially of a drive unit 14 with a diesel engine, which drives a hydraulic pump, and a driver's cab 6. It is supported by two drive wheels 10 driven by hydraulic motors on the floor 4.
  • the hydraulic pump supplies the hydraulic motor of the unbalance exciter 2 of the roller body 23 via hydraulic hoses and the hydraulic motors of the drive wheels 10 each with a flow of pressurized hydraulic fluid for driving the drive wheels 10 and the unbalance exciter 2 of the roller body 23.
  • chassis frame 25 is additionally supported via the articulated joint 21 on the rear part 20 of the compactor, or the rear part 20 is additionally supported on the chassis frame 25 via the articulated joint 21.
  • spring-damper assemblies 22 are represented by spring 22a having spring stiffness k2 and damper 22b having damping d2.
  • the mass of the chassis frame 25 is designated by m2g and that of the roller body 23 by m1g.
  • the movement of the chassis frame 25 is indicated by x2 and that of the roller body 23 by x1.
  • the spring stiffness of the bottom 4 is denoted by k1 and its damping by d1.
  • F1 the rotational frequency of the unbalance exciter 2 with ⁇ 1 and its excitation force
  • the compactor is equipped with an electronic control unit, which makes it possible to determine during operation, the accelerations of the chassis frame 25 and the roller body 23 in the vertical direction and the rotational frequency ⁇ 1 of the unbalance exciter and in dependence on these determined system parameters Mass m2g of the chassis frame 25 automatically adjust such that the chassis frame 25 always resonates with the roller body 23.
  • Fig. 8 shows a second embodiment of a trained as a compactor invention soil compaction device in side view.
  • This second compactor is different from the one in Fig. 6 shown only by the fact that the rear part 20 of the roller is formed by a wheel loader which is completely supported on four drive wheels 10a, 10b of two successively arranged axes and is so connected to the chassis frame 25, that he only in normal operation in the horizontal direction and drives, but does not absorb any forces acting in the vertical direction of this or transmits to this.
  • the rear part 20 is vibrationally decoupled from the chassis frame 25 and of the roller body 23 of the front part 19 of the drum and thus forms a claimed rest part.
  • Fig. 9 shows a third embodiment of a trained as a compactor according to the invention Bodenverdichtungsvorraum in side view. This is an unmanned compactor, which is operated via a radio remote control.
  • this third compactor comprises a roller body 23 (damper energizing part) and a chassis frame 25 (damper damper part), which in the direction of gravity at one end via two spring-damper assemblies 22 (spring-damper assembly according to claim) with constant rigidity and damping on the two end-side bearings of the roller body 23 is supported and at its other end on two driven by hydraulic motors drive wheels 10th
  • the roller body 23 comprises a bandage 11, which has the contact surface 3 for the initiation of the generated pulsating pressure force in the bottom 4 to be compacted, and formed as a circular vibrator unbalance exciter 2 with a hydraulic motor which generates a respect to their direction of action intermittent excitation force in the Bandage 11 is initiated.
  • the chassis frame 25 carries in the area in which it is supported on the drive wheels 10, a drive unit 14 with a diesel engine, which drives a hydraulic pump.
  • the hydraulic pump supplies the hydraulic motor of the unbalance exciter 2 of the roller body 23 via hydraulic hoses and the hydraulic motors of the drive wheels 10 each with a flow of pressurized hydraulic fluid for driving the drive wheels 10 and the unbalance exciter 2 of the roller body 23.
  • the chassis frame 25 carries a trim weight 26 which can be displaced in operation in the longitudinal direction L by means of a hydraulic motor and a threaded spindle.
  • the mass moment of inertia of the chassis frame 25 which becomes active on the spring-damper arrangements 22 and which during operation performs a tilting oscillation around an axis of rotation in the area of the contact surfaces of the drive wheels 10 can be changed and the supporting load of the spring-damper arrangements 22 , whereby the spring bias changes.
  • this third compactor is equipped with an electronic control unit, which makes it possible, in operation, the accelerations of the chassis frame 25 and the roller body 23 in vertical direction and the rotational frequency ⁇ 1 of the unbalance exciter to determine and, depending on these determined system parameters, the mass m2g of the chassis frame 25 automatically such that the chassis frame 25 always resonates with the roller body 23.
  • Fig. 10 shows in a conceptual representation of a spring-damper assembly 31, the spring stiffness can be changed by changing the application of force in the spring-damper unit.
  • the spring-damper unit of this arrangement 31 is formed by two polymer spring elements 18, which are attached at one end tilted relative to the intended loading direction B to a first connection plate 27.
  • the polymer spring elements 18 are pivotally attached to spindle nuts 28, which can be moved towards or away from each other by means of an adjusting spindle 29 in a direction perpendicular to the loading direction B, so that the polymer spring elements 18 are inclined by a desired angle ⁇ with respect to the loading direction B. can be.
  • the spindle nuts 28 are arranged in a guide 32 in a second connection plate 30, such that when the second connection plate 30 is loaded with a force acting in the intended loading direction B, this force is introduced into the polymer spring elements 18 and transmitted to the first connection plate 27.
  • Fig. 11 shows a section through a Tilgerteil with variable moment of inertia.
  • the absorber part comprises a base plate 33 and a cover 34, which together form a closed space 35.
  • two absorber weights 36 each having a constant mass, which via joint arrangements 37 and pneumatic spring elements 38 are connected to each other and to the base plate 33 in such a way that, when the absorber part is accelerated in and against the direction of gravity S, they are movable relative to one another against the spring force of the spring elements 38.
  • the spring force of the spring elements 38 can be changed during operation by the pressure in the cylinder chambers via compressed air hoses (not shown) is changed. As a result, the mass moment of inertia of this absorber part can be changed in and against the direction of gravity.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Soil Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Agronomy & Crop Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Road Paving Machines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Vibration Prevention Devices (AREA)

Claims (24)

  1. Arrangement pour la génération d'une force de pression pulsante, comprenant,
    a) une partie d'excitation (1, 23) avec un excitateur à balourd (2) pour générer une force d'excitation intermittente et avec une surface de contact (3) pour transmettre une composante de force de la force d'excitation, dirigée perpendiculairement par rapport à la surface de contact, comme force de pression pulsante, à un outil ou une surface de travail (4) sur lequel ou bien laquelle la force de pression doit être appliquée, et
    b) une partie d'amortissement de vibration (5, 25) connectée à la partie d'excitation (1, 23) par une unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), pour former un système capable d'être excité aux oscillations résonantes par l'excitateur à balourd (2),
    caractérisé en ce que, pendant l'opération, l'arrangement est adapté à varier la rigidité du ressort (k2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), l'amortissement (d2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la précharge du ressort de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la masse (m2) de la partie d'amortissement de vibration (5, 25), le moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), la masse (m1) de la partie d'excitation (1, 23), et/ou le moment d'inertie de masse de la partie d'excitation (1, 23).
  2. Arrangement selon la revendication 1, caractérisé en ce que l'excitateur à balourd (2) est formé comme vibrateur dirigé ou vibrateur circulaire, afin de générer une force d'excitation intermittente.
  3. Arrangement selon l'une des revendications précédentes, caractérisé en ce que l'arrangement est formé de sorte que la partie d'amortissement de vibration (5, 25) soit uniquement supportée sur la partie d'excitation (1, 23) dans la direction de gravité par l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), quand utilisé comme prévu.
  4. Arrangement selon l'une des revendications 1 à 2, caractérisé en ce que l'arrangement est formé de sorte que la partie d'amortissement de vibration (5, 25) est partiellement supportée sur la partie d'excitation (1, 23) par l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) et sur des moyens de support (8, 10) formés de manière séparée de la partie d'excitation (1, 23), quand utilisé comme prévu.
  5. Arrangement selon l'une des revendications précédentes, caractérisé en ce que l'arrangement a une partie inactive (9, 20) connectée avec la partie d'excitation (1, 23) ou avec la partie d'amortissement de vibration (5, 25) de sorte qu'elle forme une seule unité avec la partie d'excitation (1, 23) ou la partie d'amortissement de vibration (5, 25), cependant étant essentiellement découplée d'eux en ce que concerne les oscillations.
  6. Arrangement selon la revendication 5, caractérisé en ce que la partie inactive (9, 20) est supportée entièrement par la partie d'excitation (1, 23) ou par la partie d'amortissement de vibration (5, 25), quand utilisée comme prévu.
  7. Arrangement selon la revendication 5, caractérisé en ce que la partie inactive (9, 20) est supportée entièrement par des moyens de support (10a, 10b) essentiellement découplés de la partie d'excitation (1, 23) et de la partie d'amortissement de vibration (5, 25) en ce que concerne les oscillations, quand utilisée comme prévu.
  8. Arrangement selon la revendication 5, caractérisé en ce que la partie inactive (9, 20) est supportée partiellement par la partie d'excitation (1, 23) ou par la partie d'amortissement de vibration (5, 25), et partiellement par des moyens de support (10) essentiellement découplés de la partie d'excitation (1, 23) et de la partie d'amortissement de vibration (5, 25) en ce que concerne les oscillations, quand utilisée comme prévu.
  9. Arrangement selon la revendication 8, caractérisé en ce que l'arrangement est formé de sorte que, en opération, une variation de la distribution de poids entre la portion de poids de la partie inactive (9, 20) supportée par la partie d'excitation (1, 23) ou par la partie d'amortissement de vibration (5, 25), et la portion de poids de la partie inactive (9, 20) supportée par les moyens de support (10) est possible, particulièrement en déplaçant un poids sur la partie inactive (9, 20).
  10. Arrangement selon l'une des revendications 5 à 9, caractérisé en ce que l'arrangement est formé de sorte qu'une variation de la masse (m2) de la partie d'amortissement de vibration (5, 25), du moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), de la masse (m1) de la partie d'excitation (1, 23), et/ou du moment d'inertie de masse de la partie d'excitation (1, 23) est possible en échangeant un ou plusieurs volumes de liquide entre la partie inactive (9, 20) et la partie d'excitation (1, 23) et/ou la partie d'amortissement de vibration (5, 25).
  11. Arrangement selon l'une des revendications précédentes, caractérisé en ce que l'arrangement est formé de sorte qu'une variation de la masse (m2) de la partie d'amortissement de vibration (5, 25), du moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), de la masse (m1) de la partie d'excitation (1, 23), et/ou le moment d'inertie de masse de la partie d'excitation (1, 23) est possible en échangeant un ou plusieurs volumes de liquide entre la partie d'amortissement de vibration (5, 25) et la partie d'excitation (1, 23).
  12. Arrangement selon l'une des revendications précédentes, caractérisé en ce que la partie d'amortissement de vibration (5, 25) et/ou la partie d'excitation (1, 23) a au moins deux masses amovibles l'une vers l'autre quand la partie d'amortissement de vibration (5, 25) ou bien la partie d'excitation (1, 23) sont accélérées, dans une direction perpendiculaire par rapport à la surface de contact (3) contre une force de ressort, la force de ressort étant variable en opération, afin de changer le moment d'inertie de masse de la partie d'amortissement de vibration (5, 25) ou bien de la partie d'excitation (1, 23).
  13. Arrangement selon l'une des revendications précédentes, caractérisé en ce que l'arrangement est formé de sorte qu'une variation de la rigidité du ressort (k2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) est possible en rigidifiant des éléments du ressort (6) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) et/ou en variant l'introduction de force dans des éléments du ressort (6) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), particulièrement en variant une transmission des forces introduites.
  14. Arrangement selon l'une des revendications précédentes, caractérisé en ce que l'arrangement est formé de sorte que la fréquence (Ω1) de la force d'excitation (F1), la quantité de la force d'excitation (F1) et/ou la direction d'action de la force d'excitation (F1) de l'excitateur à balourd (2) sont variables pendant l'opération.
  15. Arrangement selon l'une des revendications précédentes, caractérisé en ce qu'il comprend une unité de commande ou bien une unité de régulation, à l'aide de laquelle la rigidité du ressort (k2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), l'amortissement de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la précharge de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la masse (m2) de la partie d'amortissement de vibration (5, 25), le moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), la masse (m1) de la partie d'excitation (1, 23), et/ou le moment d'inertie de masse de la partie d'excitation (1, 23) est ajustable ou sont ajustables de manière automatique pendant l'opération dépendant des variables de système mesurées, particulièrement de sorte que la partie d'amortissement de vibration (5, 25) oscille en résonance avec la partie d'excitation (1, 23), particulièrement avec la même fréquence de la partie d'excitation (1, 23).
  16. Arrangement selon les revendications 14 et 15, caractérisé en ce qu'en outre la fréquence (Ω1) de la force d'excitation (F1), la quantité de la force d'excitation (F1) et/ou la direction d'action de la force d'excitation (F1) de l'excitateur à balourd (2) est automatiquement ajustable ou sont automatiquement ajustables pendant l'opération, dépendant de variables de système mesurées, particulièrement de sorte que la partie d'amortissement de vibration (5, 25) oscille en résonance avec la partie d'excitation (1, 23), particulièrement avec la même fréquence ou avec la moitié de la fréquence de la partie d'excitation (1, 23), à l'aide de l'unité de commande ou bien de l'unité de régulation.
  17. Dispositif de compactage de sols comprenant un arrangement selon l'une des revendications précédentes.
  18. Dispositif de compactage de sols selon la revendication 17, caractérisé en ce qu'il est une plaque de vibration ou un rouleau, particulièrement un rouleau avec un ou deux tambours (11) excités par des vibrations.
  19. Procédé pour l'exploitation d'un arrangement ou d'un dispositif de compactage de sols selon l'une des revendications précédentes, caractérisé par les étapes de:
    a) faire fonctionner comme prévu l'arrangement avec la surface de contact (3) en contact avec un outil effectuant une action ou une surface de travail (4) à être traitée, particulièrement à être compactée;
    b) varier la rigidité du ressort (k2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), l'amortissement (d2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la précharge du ressort de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la masse (m2) de la partie d'amortissement de vibration (5, 25), le moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), la masse (m1) de la partie d'excitation (1, 23), et/ou le moment d'inertie de masse de la partie d'excitation (1, 23) pendant l'opération de l'arrangement comme prévu.
  20. Procédé selon la revendication 19, caractérisé en ce que la fréquence (Ω1) de la force d'excitation (F1), la quantité de la force d'excitation (F1) et/ou la direction d'action de la force d'excitation (F1) de l'excitateur à balourd (2) est ajustable ou sont ajustables pendant l'opération de l'arrangement comme prévu.
  21. Procédé selon l'une des revendications 19 ou 20, caractérisé en ce que la rigidité du ressort (k2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), l'amortissement (d2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la précharge du ressort de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), la masse (m2) de la partie d'amortissement de vibration (5, 25), le moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), la masse (m1) de la partie d'excitation (1, 23), et/ou le moment d'inertie de masse de la partie d'excitation (1, 23) et/ou, si applicable, la fréquence (Ω1) de la force d'excitation (F1), la quantité de la force d'excitation (F1) et/ou la direction d'action de la force d'excitation (F1) de l'excitateur à balourd (2) est ajustable ou sont ajustables de sorte que la partie d'amortissement de vibration (5, 25) oscille en résonance avec la partie d'excitation (1, 23), particulièrement avec la même fréquence ou la moitié de la fréquence de la partie d'excitation (1, 23).
  22. Procédé selon l'une des revendications 19 à 21, caractérisé en ce que des paramètres du système excité aux oscillations par l'excitateur à balourd (2), formé par la partie d'excitation (1, 23), l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) et la partie d'amortissement de vibration (5, 25) sont déterminés, particulièrement l'accélération de la partie d'excitation (1, 23) et/ou de la partie d'amortissement de vibration (5, 25) dans une direction perpendiculaire par rapport à la surface de contact (3), et également la fréquence de rotation (Ω1) de l'excitateur à balourd (2), et en ce que la variation de la rigidité du ressort (k2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), de l'amortissement (d2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), de la précharge du ressort de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), de la masse (m2) de la partie d'amortissement de vibration (5, 25), du moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), de la masse (m1) de la partie d'excitation (1, 23), et/ou du moment d'inertie de masse de la partie d'excitation (1, 23) et/ou, si applicable, la fréquence (Ω1) de la force d'excitation (F1), la quantité de la force d'excitation (F1) et/ou la direction d'action de la force d'excitation (F1) de l'excitateur à balourd (2) est effectuée dépendant d'un ou plusieurs paramètres du système déterminés, pendant l'opération de l'arrangement comme prévu.
  23. Procédé selon l'une des revendications 19 à 22, caractérisé en ce que la variation de la rigidité du ressort (k2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), de l'amortissement (d2) de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), de la précharge du ressort de l'unité ressort-amortisseur (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), de la masse (m2) de la partie d'amortissement de vibration (5, 25), du moment d'inertie de masse de la partie d'amortissement de vibration (5, 25), de la masse (m1) de la partie d'excitation (1, 23), et/ou du moment d'inertie de masse de la partie d'excitation (1, 23) et/ou, si applicable, la fréquence (Ω1) de la force d'excitation (F1), la quantité de la force d'excitation (F1) et/ou la direction d'action de la force d'excitation (F1) de l'excitateur à balourd (2) est effectuée automatiquement par une unité de commande ou bien par une unité de régulation.
  24. Usage de l'arrangement selon l'une des revendications 1 à 16 pour le compactage de sols.
EP10714159.0A 2010-04-16 2010-04-16 Agencement pour fournir une force de pression pulsée Not-in-force EP2558649B1 (fr)

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DE102008011208B3 (de) 2008-02-26 2009-09-17 Ammann Verdichtung Gmbh Vibrationsplatte mit geteiltem Riementrieb
US8206061B1 (en) * 2011-05-26 2012-06-26 Caterpillar Inc. Eccentric vibratory weight shaft for utility compactor

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WO2011127611A3 (fr) 2013-03-21
BR112012026543A2 (pt) 2016-07-12
US20130058717A1 (en) 2013-03-07
AU2010351124A1 (en) 2012-11-29
US8727660B2 (en) 2014-05-20
EP2558649A2 (fr) 2013-02-20
WO2011127611A2 (fr) 2011-10-20

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