EP1568420B1 - Dispositif et méthode de commande pour une machine vibrante - Google Patents

Dispositif et méthode de commande pour une machine vibrante Download PDF

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Publication number
EP1568420B1
EP1568420B1 EP05001429.9A EP05001429A EP1568420B1 EP 1568420 B1 EP1568420 B1 EP 1568420B1 EP 05001429 A EP05001429 A EP 05001429A EP 1568420 B1 EP1568420 B1 EP 1568420B1
Authority
EP
European Patent Office
Prior art keywords
pulse width
width modulation
modulation signal
relative position
adjusting cylinder
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.)
Ceased
Application number
EP05001429.9A
Other languages
German (de)
English (en)
Other versions
EP1568420A3 (fr
EP1568420A2 (fr
Inventor
Niels Laugwitz
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.)
Bomag GmbH and Co OHG
Original Assignee
Bomag GmbH and Co OHG
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
Priority claimed from DE102004015589A external-priority patent/DE102004015589A1/de
Application filed by Bomag GmbH and Co OHG filed Critical Bomag GmbH and Co OHG
Publication of EP1568420A2 publication Critical patent/EP1568420A2/fr
Publication of EP1568420A3 publication Critical patent/EP1568420A3/fr
Application granted granted Critical
Publication of EP1568420B1 publication Critical patent/EP1568420B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • the invention relates to a control for an unbalance adjusting device in a vibration machine, in particular in a device for controlling the direction of travel of a soil compaction machine.
  • the invention further relates to a method for controlling an unbalance adjusting device in a vibration machine.
  • Soil compaction machines usually have vibratory plates which move at a certain frequency to compact a soil material by vertical impacts.
  • the shocks are caused by vertically directed vibration of the vibrating plate, which are generated by a pair of imbalance counterweights.
  • the imbalances rotate synchronously, but with opposite direction of rotation and generate a resulting centrifugal force in a direction of vibration.
  • a desired directional vibration direction can be set, which can deviate from the vertical direction of vibration, so that in addition to the vertically directed vibration component and a horizontally directed vibration component is generated.
  • the horizontally directed vibration component causes a forward or backward movement of the soil compaction machine.
  • a controller for an unbalance adjustment device with a vibration exciter of a soil compaction machine is known.
  • an adjusting cylinder for adjusting phase positions of imbalances in the vibration exciter by means of a reference piston, which is coupled to a switching valve are controlled.
  • the switching valve serves to control an oil inflow from a pressure oil source or an oil drain to an oil return to and from the reference piston.
  • the user of the soil compacting machine can adjust the switching valve electrically or mechanically between two positions thereby enabling the movement of the adjusting cylinder in both directions to the forward or backward movement of the soil compaction machine select.
  • a disadvantage of such direction control is that transducers are required.
  • a direction of travel control for a soil compaction machine includes a movable travel lever whose positions are detected by a button that controls a switching valve.
  • the switching valve controls an adjusting cylinder in a vibration generating device so that it is moved between a starting position and an end position.
  • the soil compaction device moves the soil compaction device in the forward or reverse direction.
  • this soil compaction machine only a forward or backward movement can be set, which is determined in each case by the resulting centrifugal force in the end positions of the adjusting cylinder.
  • the JP 05-321904 A is directed to a drive control of a pneumatic cylinder.
  • the aim is to move a pneumatic cylinder smoothly and to improve the stop accuracy of a piston in a central position.
  • an actual position of an adjusting piston to be controlled is detected with a sensor and fed via a feedback branch into a control loop.
  • the pulse width modulation technology for operating control valves of the adjusting piston is used in the control loop to regulate the position of the adjusting piston in an adjusting cylinder.
  • a controller for an imbalance adjusting device is provided in a vibration machine. It has an adjusting cylinder which is hydraulically adjustable to adjust a relative position of counter-rotating imbalances in the vibrating machine.
  • a control valve is provided in order to adjust the adjustment cylinder in such a way that the vibration behavior of the vibration machine, in particular the vibration direction of the vibration machine, is adjusted.
  • It is a control unit for driving the control valve according to a Pulse width modulation signal provided to adjust the relative position of the imbalance depending on the duty cycle of the pulse width modulation signal.
  • a pulse width modulation signal is periodic and has two states within the period, namely a first state and a second state. The ratio of the time duration, while the first state is taken to the period represents the duty cycle.
  • the pulse width modulation signal causes when driving the control valve that the adjusting cylinder during the first state in the direction of the first end position and during the second state in the direction of the second End position moved.
  • the adjusting cylinder does not take the respective end position directly, but moves to this during a certain period of time. If the state of the control valve changes according to a change of state of the pulse width modulation signal, then the adjusting cylinder also changes the direction of the method if the previously desired end position has not yet been reached.
  • the vibration direction of the vibrating machine adjusts itself to the average value by the constant change of the position of the adjusting cylinder.
  • the control valve By switching the control valve in accordance with the pulse width modulation signal, it is thus possible to move the adjusting cylinder back and forth between the two periods during the period.
  • the travel speed of the compacting machine results from the mean value of the travel speeds resulting from the respective positions of the adjusting cylinder.
  • the traveling speed against the traveling speed corresponding to the end positions of the adjusting cylinder can be reduced by reducing the effective inclination angle of the oscillation direction with respect to the vertical oscillation direction.
  • the control unit can thus be connected to the control valve in order to control the adjusting cylinder according to a first level of the pulse width modulation signal, so that the relative position of the imbalances are adjusted in the direction of a first fixed end position and to control the adjusting cylinder according to a second level of the pulse width modulation signal, so that the Relative position of the imbalances are adjusted in the direction of a second predetermined end position.
  • the pulse width modulation signal occupies the first level for a first time duration and the second level for a second time duration during a period duration.
  • the sum of the first and second time periods corresponds to the period of the pulse width modulation signal.
  • control valve is designed with respect to the adjusting cylinder so that the adjusting cylinder at a duty cycle of the pulse width modulation signal of 50% and a predetermined period is completely movable between the first and second end position.
  • control unit can be connected to an input unit in order to set the pulse width modulation signal as a function of a user default.
  • the input unit is preferably arranged on the vibration machine so that a user can control the speed of travel via the input unit during operation.
  • a soil compacting machine having a controller according to the invention comprising a vibrating plate coupled to imbalances so as to cause forward or backward movement depending on the relative position of the imbalances.
  • a method for controlling an imbalance adjustment device in a vibration machine is provided.
  • the relative position of counter-rotating imbalances in the vibration machine is chosen so that the vibration behavior of the vibration machine can be adjusted.
  • the relative position of the imbalances is controlled as a function of a pulse width modulation signal.
  • the relative position of the imbalances is controlled as a function of a pulse width modulation signal.
  • the relative position of the imbalances is set as a function of the duty cycle of the pulse width modulation signal.
  • the relative position of the imbalances is adjusted at a first level of the pulse width modulation signal in the direction of a first fixed end position and that the relative position of the imbalance is adjusted in the direction of a second predetermined end position at a second level of the pulse width modulation signal.
  • the relative position of the imbalances can change completely from the first to the second end position at a duty cycle of 50% and at a predetermined period duration.
  • the relative position may change at least partially in the direction of one of the fixed end positions at a duty cycle different from the 50% and the predetermined period duration without reaching it during the first time period for the first level or the second time duration for the second level.
  • the adjusting cylinder is not in the stop position during the entire period of time, so that on average reduces the inclination angle of the vibration direction in the direction of the vertical direction of vibration.
  • Fig. 1 schematically the generation of a forward and backward movement of a vibrating machine, in particular a soil compaction machine is shown with a vibrating plate.
  • the vibrating plate is vibrated by rotating imbalance masses 2, which have a mutually opposite direction of rotation.
  • a resulting centrifugal force F of the imbalance masses 2 is generated.
  • the resulting centrifugal force F acts in the vertical direction.
  • the resulting centrifugal force F is inclined to the vertical at an inclination angle, so that in addition to the vertical vibration component of the resulting centrifugal force F also acts a horizontal vibration component, which causes a driving movement of the vibratory machine.
  • Fig. 1 move two unbalanced shafts 1 in opposite directions with the imbalance masses 2 shown as a point.
  • the imbalance masses 2 are arranged to generate phase-shifted centrifugal forces angularly offset on the unbalanced shafts 1, so that depending on the relative position of the respective imbalances to each other, the resulting centrifugal force F is more or less inclined to the vertical.
  • Fig. 1 the resulting centrifugal forces at different relative positions of the imbalance masses 2 are shown. It can be seen that the resulting centrifugal force can be inclined to the vertical depending on the relative positions of the imbalance masses 2, wherein a movement in the direction of the horizontal portion of the resulting centrifugal force is effected.
  • the unbalanced shafts 1 are rotatably coupled to each other by a positive power transmission means, so that the directions of rotation and phase assignments are ensured.
  • a positive power transmission means With the help of an adjusting cylinder, the relative position of the unbalanced masses 2 can be adjusted to the unbalanced shafts 1 to each other, such as in the DE 199 12 813 C1 is described in detail.
  • the speed of travel of the vibration machine can not be set by the user in a targeted manner, since the piston position is not recognizable.
  • the traveling speed of ground compacting machines is determined by the degree of inclination of the resultant centrifugal force of the unbalanced shafts 1, the vertical amplitude of the vibration decreases with increasing traveling speed. On very soft ground, it may happen that at maximum inclination of the resulting centrifugal force, the remaining vertical amplitude for lifting the base plate is no longer sufficient. However, if the vibrating plate can not lift, no movement is possible. If, in this situation, one were able to reduce the angle of inclination of the resulting centrifugal force in the direction of the vertical amplitude, it would again be possible to achieve a travel movement since the proportion of the vertical amplitude would increase.
  • a control for a hydraulic adjusting cylinder 4 for adjusting the relative position of imbalance masses 2 in a soil compaction machine is shown schematically at successive times t0 to t5.
  • the machine moves in forward or reverse gear.
  • the adjusting cylinder 4 is located in an open oil circuit with a variable displacement pump 6, which provides an oil volume flow available, and is controlled by a control valve 5, which is designed here as a directional control valve.
  • the variable displacement pump 6 takes the flow 7 from a tank 8, in which the reflux 9 is returned.
  • the volume flow is as equal and constant as possible.
  • Fig. 8 shows the dependence of the piston travel as a function of a pulse width modulation signal (PwM signal) with a pulse-pause ratio of 50%.
  • PwM signal pulse width modulation signal
  • Fig. 9 is a second path / time charts shown at a pulse-pause ratio of 80%.
  • the control valve 5 is controlled by a control unit 10 with a control signal so that it is set according to a first level of the control signal in the first switching position and according to a second level of the control signal in the second switching position.
  • the control unit 10 is connected to an input device, by means of which an operator of the soil compaction machine can set the desired travel motion substantially continuously or in several stages according to a default value.
  • the control unit 10 generates from the default value a pulse width modulation signal which is made available to the control valve 5.
  • the pulse width modulation signal is periodic and is at the first signal level during a first time period and at the second signal level during a second time period. The sum of the first and second time periods corresponds to the period duration.
  • the duty cycle gives the ratio between the time duration of the first signal level to the period duration and the pulse-pause ratio indicates the ratio of the first time duration to the second time duration.
  • the pulse width modulation signal is used to control the control valve 5 and thereby to reciprocate the piston of the adjusting cylinder 4.
  • the period of the pulse width modulation signal is preferably selected so that at a duty cycle of 50% of the first signal level is sufficient to move the piston completely from the second end position to the first end position.
  • the period can be between 0.5 and 2 seconds, in particular 1 second. Other values for the period are possible.
  • the hydraulic system is designed to reciprocate the piston of the variable displacement cylinder 4 at the 50% duty cycle (pulse / pause ratio) between the first and second end positions. This corresponds to the state of vibration, since the horizontal parts of the resulting Centrifugal forces cancel each other on average and thus no movement is achieved.
  • a forward movement of the piston 3 is started from the rear starting position ( Fig. 2 ). At time t1 it is in the forward motion ( Figure 3 ). At time t2 he has reached his second end position ( Fig. 4 ). At time t3, the control valve 5 switched over ( Fig. 5 ) and the piston 3 moves back at time t4 ( Fig. 6 ) to the starting position at time t5 ( Fig. 7 ).
  • the piston of the adjusting cylinder remains most of the time (80% of the period) in the first end position. Only during 20% of the period, the piston moves from time t7 and t9 towards the second end position. The end position is not reached, but the movement reverses again at time t6 and t8 during the process from the first to the second end position, and the piston is then again in the first end position. In terms of time, the piston is thus just before the first end position. Since only the time average of the piston position is of interest for the operation of the soil compaction machine, this type of control is sufficient for the travel speed. A sensor and the like for controlling the piston position is not required because the movement of the piston is limited by the end positions, and thus the adjusting cylinder is moved back to a defined position during each cycle.

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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)
  • Mechanical Engineering (AREA)
  • Road Paving Machines (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (13)

  1. Unité de commande pour un dispositif de réglage de balourds dans un engin vibrant, en particulier dans un engin de compactage du sol,
    - avec un cylindre de réglage qui est réglable hydrauliquement pour fixer une position relative de balourds tournant dans des directions opposées dans l'engin vibrant, et
    - avec une vanne de commande pour régler le cylindre de réglage afin de régler le comportement vibratoire de l'engin vibrant,
    caractérisée par
    une unité de commande pour commander la vanne de commande au moyen d'un signal de modulation d'impulsions en largeur de manière à régler la position relative des balourds en fonction du cycle de fonctionnement du signal de modulation d'impulsions en largeur par le déplacement du cylindre de réglage selon un va-et-vient pendant la durée de la période du signal de modulation d'impulsions en largeur en fonction de l'état du signal de modulation d'impulsions en largeur.
  2. Unité de commande selon la revendication 1,
    caractérisée en ce que
    l'unité de commande est connectée à la vanne de commande de manière à commander le réglage du cylindre selon un premier niveau du signal de modulation d'impulsions en largeur d'une façon telle que la position relative des balourds soit réglée dans la direction d'une première position définie et de manière à commander le cylindre de réglage selon un second niveau du signal de modulation d'impulsions en largeur d'une façon telle que la position relative des balourds soit réglée dans la direction d'une seconde position définie.
  3. Unité de commande selon la revendication 2,
    caractérisée en ce que
    le signal de modulation d'impulsions en largeur adopte un premier niveau pendant une première durée et un second niveau pendant une seconde durée.
  4. Unité de commande selon la revendication 3,
    caractérisée en ce que
    le système hydraulique est conçu par rapport au cylindre de réglage d'une manière telle que le cylindre de réglage soit totalement réglable entre la première position et la seconde position pour un cycle de fonctionnement de 50 % et une durée de période prédéterminée.
  5. Unité de commande selon la revendication 3 ou 4,
    caractérisée en ce que
    le système hydraulique est conçu par rapport au cylindre de réglage d'une manière telle que le cylindre de réglage puisse être réglé au moins partiellement dans la direction de l'une des positions définies pour un cycle de fonctionnement différent de 50 % et une durée de période prédéterminée.
  6. Unité de commande selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    l'unité de commande est conçue d'une manière telle que le signal de modulation d'impulsions en largeur puisse être fixé en fonction d'une spécification de l'utilisateur.
  7. Engin de compactage du sol avec une unité de commande selon l'une quelconque des revendications 1 à 6,
    dans lequel une plaque vibrante est prévue, qui est connectée aux balourds d'une manière telle qu'elle provoque un mouvement vers l'avant ou inverse en fonction de la position relative des balourds.
  8. Procédé de commande d'un dispositif de réglage de balourds dans un engin vibrant, en particulier dans un engin de compactage du sol, dans lequel la position relative des balourds tournant dans des directions opposées dans l'engin vibrant est choisie de manière à fixer le comportement vibratoire de l'engin vibrant,
    caractérisé en ce que
    la position relative des balourds est fixée en fonction du cycle de fonctionnement d'un signal de modulation d'impulsions en largeur par le déplacement du cylindre de réglage selon un va-et-vient pendant la durée de la période du signal de modulation d'impulsions en largeur en fonction de l'état du signal de modulation d'impulsions en largeur.
  9. Procédé selon la revendication 8,
    caractérisé en ce que
    la position relative des balourds est réglée en fonction du cycle de fonctionnement du signal de modulation d'impulsions en largeur.
  10. Procédé selon la revendication 8,
    caractérisé en ce que
    la position relative des balourds est réglée dans la direction d'une première position définie à un premier niveau du signal de modulation d'impulsions en largeur et en ce que la position relative des balourds est réglée dans la direction d'une seconde position définie à un second niveau du signal de modulation d'impulsions en largeur.
  11. Procédé selon la revendication 10,
    caractérisé en ce que
    le signal de modulation d'impulsions en largeur adopte le premier niveau pendant une première durée pendant une durée de période et un second niveau pendant une seconde durée.
  12. Procédé selon la revendication 11,
    caractérisé en ce que
    la position relative des balourds change complètement de la première position à la seconde position pour un cycle de fonctionnement de 50 % et une durée de période prédéterminée.
  13. Procédé selon la revendication 11 ou 12,
    caractérisé en ce que
    la position relative des balourds change au moins partiellement dans la direction de l'une des positions définies pour un cycle de fonctionnement différent de 50 % et une durée de période prédéterminée.
EP05001429.9A 2004-02-29 2005-01-25 Dispositif et méthode de commande pour une machine vibrante Ceased EP1568420B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102004009841 2004-02-29
DE102004009841 2004-02-29
DE102004015589 2004-03-30
DE102004015589A DE102004015589A1 (de) 2004-02-29 2004-03-30 Steuerung und Steuerungsverfahren für eine Vibrationsmaschine

Publications (3)

Publication Number Publication Date
EP1568420A2 EP1568420A2 (fr) 2005-08-31
EP1568420A3 EP1568420A3 (fr) 2011-06-29
EP1568420B1 true EP1568420B1 (fr) 2018-08-15

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05001429.9A Ceased EP1568420B1 (fr) 2004-02-29 2005-01-25 Dispositif et méthode de commande pour une machine vibrante

Country Status (4)

Country Link
US (1) US7567857B2 (fr)
EP (1) EP1568420B1 (fr)
JP (1) JP4287828B2 (fr)
CN (1) CN100403200C (fr)

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DE102009016039A1 (de) * 2008-04-03 2009-12-10 Wacker Neuson Se Vibrationsplatte mit Riemenantrieb
US20110158745A1 (en) * 2009-12-31 2011-06-30 Caterpillar Paving Products Inc. Vibratory system for a compactor
UA99421C2 (uk) 2011-11-18 2012-08-10 Юрій Валентинович Трубянов Генератор енергії
KR101523352B1 (ko) * 2014-10-29 2015-05-28 파스코이엔지(주) 전자 바이브레이터
AT517480B1 (de) * 2015-11-18 2017-02-15 Plasser & Theurer Export Von Bahnbaumaschinen Gmbh Stopfaggregat sowie Verfahren zum Unterstopfen eines Gleises
KR200480690Y1 (ko) * 2015-12-01 2016-06-24 임광주 하수관 진동 세척장치
KR102081435B1 (ko) * 2018-08-09 2020-02-25 (주) 에스엔지 아이시티 컴팩터
KR102444182B1 (ko) * 2020-09-07 2022-09-16 파스코이엔지(주) 정현파 듀티 변조를 적용한 전자 바이브레이터 구동 알고리즘

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Also Published As

Publication number Publication date
CN100403200C (zh) 2008-07-16
EP1568420A3 (fr) 2011-06-29
JP4287828B2 (ja) 2009-07-01
EP1568420A2 (fr) 2005-08-31
JP2005238235A (ja) 2005-09-08
CN1661165A (zh) 2005-08-31
US20050193843A1 (en) 2005-09-08
US7567857B2 (en) 2009-07-28

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