EP0801596B1 - Kompensation von querschwingungen an unwuchtvibratoren - Google Patents
Kompensation von querschwingungen an unwuchtvibratoren Download PDFInfo
- Publication number
- EP0801596B1 EP0801596B1 EP95927702A EP95927702A EP0801596B1 EP 0801596 B1 EP0801596 B1 EP 0801596B1 EP 95927702 A EP95927702 A EP 95927702A EP 95927702 A EP95927702 A EP 95927702A EP 0801596 B1 EP0801596 B1 EP 0801596B1
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- European Patent Office
- Prior art keywords
- unbalanced
- drive motor
- regulating
- vibration
- control
- 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.)
- Expired - Lifetime
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Classifications
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- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
- B06B1/186—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with rotary unbalanced masses
Definitions
- the invention relates to a device and a method for compensating transverse vibrations on unbalance vibrators with a predetermined direction of vibration.
- the resulting excitation force F E which determines the direction of vibration, is generated by two synchronously and oppositely rotating groups of partial unbalance bodies, in the simplest case each group having only a single partial unbalance body.
- each group has at least one own drive motor and that both groups among themselves, at least but two partial unbalance bodies belonging to a different group not with each other, or at least not constantly via mechanical drive means are positively synchronized to a certain rotational angular position to adhere to.
- Such vibrators are used for various tasks, the synchronous operation in the simplest case being created by the so-called “self-synchronization", which is easy to achieve under the following conditions:
- the dynamic mass m to be set into vibration by the resulting acceleration or the resulting unbalance force dyn must be able to swing unhindered (e.g. supported by springs) and a straight line through the center of gravity in the direction of oscillation must be the perpendicular to such a distance that extends in the plane of the rotating unbalance centers of gravity from one axis of rotation to the other.
- Such vibrators are also used for ramming.
- the Circumstance that between two groups of partial unbalance bodies on one Forced synchronization by mechanical drive means can be dispensed with can be regarded as a special functional advantage, e.g. because of the Contribution to noise reduction. Because the invention is special here can be used advantageously, it will be related below described with ram vibrators.
- the vibrating dynamic mass m dyn which also includes the mass of the pile, is always connected to a special carrier device (e.g. leader or crane) via vibration-isolating devices, such as spring yokes is.
- a special carrier device e.g. leader or crane
- vibration-isolating devices such as spring yokes
- vibration path components can occur on the dynamic mass transverse to the intended direction of vibration in one Size occur that proper work with the vibrator fails is more possible.
- Such transverse vibrations can arise from the incorrect alignment of the resulting excitation force F E of the partial unbalance body itself.
- the resulting excitation force is kinetically coupled to the dynamic mass and can therefore also be influenced, for example, as a function of the disturbance of the oscillating movement of the dynamic mass by external disturbing forces.
- transverse vibrations can also occur directly disturbing forces attacking the dynamic mass are excited.
- asymmetrical loading of the pile asymmetrical suspension of the dynamic mass
- non-horizontal alignment of the exciter body force excitations the coupling of the exciter body to the spring yoke or to the leader.
- This directional oscillator according to DE-PS 41 16 647 comprises two two-shaft vibrators, which one has to imagine as being placed on top of each other, whereby the each interacting (conceivable one above the other) partial unbalance body one have a direction of rotation that is opposite to is that of the other.
- the person skilled in the art knows that these interacting partial unbalance bodies can also circulate in the same direction, as with the later discussed WO 93/01693 is realized; both types are equivalent to each other.
- EP-A-0 467 758 discloses a directional vibrator, also with two superimposed two-shaft vibrators, their respective Imbalances are coupled via gears and are therefore positively synchronized.
- the phase position of the two vibrators is relative to one another via one Superimposition gearbox hydraulically adjustable, but because of the Forced synchronization cannot change the direction of vibration.
- the object of the invention is to compare one with the closest State of the art to create simpler and more robust device with Help those of all kinds of unwanted transverse vibrations in their Size can be reduced or even avoided.
- the desired improvement should come closer to robustness on solutions using only hydraulic drive motors may restrict.
- the expected solution is said to be simpler to such an extent be that it is possible, for example, at least two hydraulic Drive motors that are assigned to different groups may be acted upon by a common pressure source (characteristic of the Preamble of claims 1 and 10).
- the advantage of the solution according to the invention can be seen in the fact that the regulating Intervention in the rotary drive to influence the direction of the resulting excitation force only refers to throttle measures that can be realized with little equipment and for what, for example the pressure of the pressure source does not have to be changed.
- the one in Purchase depending on the size of the transverse vibrations Throttle losses are low since the transverse vibrations in principle prevent it become.
- the chosen principle of influencing the direction of the resulting excitation force more than the complex Technology according to the closest prior art cited.
- the principle according to the invention is capable of Direction of the resulting excitation force too (in the manner of a Overcompensation) in a direction that deviates from the specified vibration direction To steer direction. This can help with the control process achieved reduction of the transverse vibrations to minimum values, for example generates an internal acceleration (generated by unbalance forces) which of the external (excitation for transverse vibration) acceleration is opposite.
- the two independent claims 1 and 10 are based on the same general inventive concept. Thereafter, the undesirable transverse vibrations of the dynamic mass m dyn are not combated with passive means (damping), but are compensated with an active measure in such a way that depending on the value of a physical quantity to be measured or taken into account, which is functionally related to the Transverse oscillation stands, makes a correction to the direction of the resulting excitation force by influencing the resultant torque causing the rotation of the unbalance bodies (that is the sum of driving and braking torques) in at least one group.
- the path s Q of the transverse oscillation movement itself, or the quantities derived therefrom, such as, for example, s Q 'or s Q '', is indicated as the physical quantity to be measured or evaluated the relative angle of rotation of the partial unbalance bodies generating the excitation forces.
- the "relative angle of rotation” is an angle that has to be determined by comparing the angle of rotation position of two partial unbalance bodies.
- the frame 100 represents the housing of an unbalance vibrator 101, which is operated with two partial unbalance bodies 106 and 108 attached to the two shafts 102 and 104, driven by two hydraulic motors M1 and M2.
- the center of gravity of the dynamic mass is identified by the cross 114. If the vibrator is used to ram rammed material, the center of gravity of the rammed material coincides with the center of gravity 114 and the rammed material mass belongs to the dynamic mass m dyn .
- the two equally large hydraulic motors M1 and M2 are shared by one Pressure source 116 is subjected to variable pressure. After the starting of the motors marked with arrows 118 and 120 opposite direction of rotation is due to the proposed arrangement of the center of gravity 114 a self-synchronization of the rotary movement both partial unbalance bodies 106 and 108, so that these in opposite directions circulate synchronously.
- the centrifugal forces compensate each other in a plane that can be laid through the center lines of the shafts 102 and 104, while in a direction perpendicular to the plane of the drawing they add to the resulting excitation force F E , which excitation force has to be imagined through the center of gravity 114.
- the rotating part unbalance bodies develop special "synchronous guidance torques" in conjunction with mass forces guided via the bearings 122, 124 and generated by the oscillating dynamic mass m dyn , which synchronize the synchronism within a certain range of disturbing forces Ensure the two partial unbalance bodies without these having to be positively synchronized by mechanical drive means such as gears.
- Circumferential feature carriers 126, 128 are connected to the shafts 102, 104, which carry position features 130, 132 on their circumference, the are detected by the position sensors 134, 136 during the circulation, the sensors emitting signals via the signal lines 138, 140. These signals are processed in the regulating or control device RSE1, such that there are deviations from a predetermined relative angular position both partial unbalance bodies as "relative rotation angle" according to their Course and their direction can be determined.
- a relative angle of rotation ⁇ deviating from the real synchronous position is shown in position sensor 136, which originates from an advance of partial unbalance body 108 in the direction of arrow 120. If such a relative rotation angle ⁇ deviates from the value zero, it can be assumed that the direction of the resulting excitation force F E is deflected from its desired direction and that consequently transverse vibrations occur with a travel component s Q (142). With the aid of the correction actuating device 178, which in addition to the regulating or control device RSE1 also includes the actuator 144, the relative angle of rotation should then be brought back to the value zero.
- the actuator 144 has a throttle device 146, by means of which the volume flows emerging from motors M1 and M2 are optionally throttled can be.
- the throttling of one or the other volume flow happens through that made in the direction of the double arrow 148 Displacement of the control piston 150 from the center position shown out.
- the control edge narrows 152 the inlet duct 156 of the volume flow originating from engine M1, with a shift to the right, the inlet channel 158 of the from Motor M2 emerging volume flow reduced. From the shift of the control piston, the drain channel 160 leading to the tank 162 is not affected, so that the unrestricted volume flow is unimpeded at all times can drain off.
- the control piston 150 is displaced by the difference of one force generated by a compression spring 166 on the one hand and one by Pressure in the control pressure chamber 164, on the other hand, generated hydraulic Force.
- the hydraulic pressure in the control pressure chamber is determined by the outlet pressure an electrically controllable pressure control valve 168, with which the pressure predetermined by a constant pressure source 170 can be regulated down to any presettable pressures at outlet 172 can.
- the size of the regulated outlet pressure that can be set at outlet 172 is performed with the cooperation of the electrical control element 174 the control or output signal supplied via line 176 Control device RSE1 determined.
- a sensor 180 for detecting the acceleration s Q ′′ assigned to the oscillation travel s Q (142) is attached to the frame 100, the signal of which is supplied to the regulating or control device RSE2 via the signal line 182.
- the information of the input signal is processed in such a way that the output signal, which is fed to the electrical control element 174 via the line 184, contains the necessary information about the value and direction of the quantity measured by the sensor 180, so that about the Pressure control valve 168 and the throttle device 146 on the motors M1 and M2 can be caused similar reactions as can be achieved by the influence of the output signal from RSE1.
- a correction-setting process is carried out as follows: In the simplest case, when a relative angle of rotation ⁇ or an oscillation path component s Q occurs, the regulating or control devices RSE1 or RSE2 cause an adjustment of the throttle device 146 via their output signals and thus the generation of a setting torque on one of the motors proportional to the measured value of the disturbance ⁇ or s Q.
- the regulating or control device RSE1 will ensure that the spool 150 is shifted to the right, which the Torque of the motor M2 is reduced and what is compared to the motor M1 builds a torque, with the help of the relative angle of rotation ⁇ is reduced again.
- the regulating or control devices RSE1 and RSE2 can, however, with other additional functions, which you can use depending on the operating situation the vibrator. This includes e.g. an integration function in terms of control technology, to ensure that the faults are also free of residual errors to be able to compensate, or an algorithm based on predetermined criteria, the output signals individually or together Effect.
- an unbalance vibrator 201 is shown, which has the same Properties as that shown in Figure 1 should have, as far as the Features 200 to 220 and the motors M1 and M2 are concerned. Wear it same characteristics in both figures their identifiers with identical Combinations of the last two digits.
- the sensor part 230 is formed by 2 control rotors 232 and 234 with Control groove and control edges on the circumference of their outer cylinders 244, 246 and by two control stators 236 and 238 with control openings the circumference of their inner cylinders 240, 242.
- the two control rotors 232 and 234 are designed as cylindrical bodies, which (in a manner not shown) rotatably with the shafts 202 and 204 are connected and thus with these and the partial unbalance bodies circulate synchronously.
- the outer cylinders 244, 246 of the control rotors 232, 234 are with a narrow cylindrical sealing gap in the inner cylinder 240, 242 of the control stators 236, 238 fitted so that the through this leakage leakage can be neglected.
- a control groove 252 is let into the outer cylinder 244, through which 2 control edges 252 and 254 are formed.
- the area of the tax groove 252 can be connected to a pressure source 258 via the control opening 248 become.
- the control edge 256 is just about to open the control 250 to connect with the control groove 252.
- This connection exists through an angle of rotation ⁇ until the control edge 254 closes the control opening 248 again.
- the control opening 250 is with the throttle bodies 260 and 262 with the output signals of the regulating or control device 228 leading control lines 264 and 266 connected. Due to this, stands the pressure in the control opening 250 also in the control lines 264, 266, unless one of these control lines is influenced of control rotor 234 is connected to the unpressurized tank 268.
- control piston 280 In the actuator 226 there is a control piston 280, the side of which Movement through the control edges 282, 284 inlet channels 286, 288 blocked or can be throttled while a central drainage channel 290 to the unpressurized tank 297 always remains open. With the throttling the volume flows flowing through the inlet ducts from the engines can have the same effects with regard to the generation of actuating torques can be achieved, as explained in connection with Figure 1 has been.
- a change in the pulse length on one or the other control line depending on the relative angle of rotation of both partial unbalance bodies or both control rotors is the task of the control edges 274, 276, the formed by the control groove 278 on the outer cylinder of the control rotor 234 become.
- the zero value of a relative angle of rotation corresponds, has - taking into account the direction of rotation 220 - the Control edge 274 just closed the control opening 272 while the Control edge 276 the control openings 280 after the further rotation of both Control rotors begin to release the angle ⁇ , but too straight no pressure from the control port 280 at this time pressure pulses generated by the control rotor 232 are present.
- This directional pulse ⁇ I which acts on the actuator 226, can also be regarded as the information content of the output signal of the regulating or control device 228 which is passed on via both control lines 264 and 266.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
- Vibration Prevention Devices (AREA)
Description
- Auch die Wegkomponente sQ (142) der Querschwingung könnte mit einem speziellen hydraulischen Sensorteil erfaßt werden, vergleichbar mit der Arbeitsweise des Sensorteiles 230 in Figur 2. Dabei würde die Schwingbeschleunigung eine Hilfsmasse in eine schwingende Bewegung versetzen, durch welche Bewegung Strömungsquerschnitte von hydraulischen Volumenströmen im Sinne einer gewünschten Sperr- oder Drosselwirkung verändert werden. (Anspruch 6).
- Anstelle der Maßnahme, ein Stell-Drehmoment durch Veränderung von Motor-Drehmomenten herbeizuführen, könnte auch vorgesehen werden, daß kraftbetätigte Bremsorgane zur Erzeugung eines an den Unwuchtwellen bremsend wirkenden Stell-Drehmomentes herangezogen werden, welche Bremsorgane durch die Stellglieder mit Stellenergie zu beaufschlagen wären.
- Falls man bei den Unwuchtvibratoren 101 und 201 die Teil-Unwuchtkörper samt Wellen und Motoren in doppelter Ausführung anordnet, erhält man zwei Gruppen von Teil-Unwuchtkörpern mit innerhalb der Gruppe gleichem Drehsinn und von Gruppe zu Gruppe entgegengesetztem Drehsinn. Mit einer derartigen Anordnung läßt sich bei entsprechender Ansteuerung der 4 Motoren in bekannter Weise (wie z.B. in der Druckschrift PCT/EP93/01693 gezeigt) zwischen den jeweils gleichsinnig umlaufenden Teil-Unwuchtkörpern ein Relativ-Stellwinkel vorgegebener Größe einstellen, womit auch das gesamte, resultierende Fliehmoment in vorgebbarer Weise eingestellt ist.
- Die Regel- und Steuereinrichtung kann die Funktion eines Integriergliedes enthalten, womit bekanntlich die Regelabweichung, das ist die Differenz zwischen Sollwert und Istwert der Regelgröße, bis auf den Wert Null zurückgeführt werden kann (Anspruch 11).
- Anstelle der Kompensation unerwünschter Querschwingungen können die beschriebenen Einrichtungen alternativ auch dazu eingesetzt werden, Querschwingungen künstlich zu erzeugen. Dazu müssen die Stellglieder lediglich von einer anderen oder anders arbeitenden Steuereinrichtung beaufschlagt werden.
Claims (12)
- Unwuchtvibrator mit vorgegebener Schwingrichtung,mit zwei Gruppen (106, 108) von umlaufenden Teil-Unwuchtkörpern (106, 108), wobei die Teil-Unwuchtkörper innerhalb einer Gruppe gleichsinnig oder gegensinnig synchron und wobei von den zu unterschiedlichen Gruppen gehörenden Teil-Unwuchtkörpern je zwei gegensinnig und synchron umlaufen,mit wenigstens je einem Teil-Unwuchtkörper pro Gruppe,mit wenigstens je einem hydraulischen Antriebsmotor (M1, M2) pro Gruppe, wobei wenigstens zwei Antriebsmotoren, die unterschiedlichen Gruppen zugeordnet sind, von einer gemeinsamen Druckquelle beaufschlagt sind oder wenigstens unter Einbehaltung der für sie vorgesehenen prinzipiellen Funktion beaufschlagt werden können,mit einem zwischen den Gruppen bei Verzicht auf mechanische Synchronisierungsmittel durch die Wirkung von Massenkräften der schwingenden dynamischen Masse (200) herbeigeführten Synchronlauf,
gekennzeichnet durch die Kombination folgender Merkmale:Sensoren (134, 136, 180, 230) enfassen eine als Differenz zwischen Sollwert und Istwert definierbare Regelabweichung "e" einer durch eine Regeleinrichtung (RSE1, RSE2, 228) zu regelnden physikalischen Größe "Relativ-Drehwinkel'' und/oder "Schwingweg", wobei der "Relativ-Drehwinkel" von dem Drehwinkel wenigstens eines Teil-Unwuchtkörpers abgeleitet ist und wobei der "Schwingweg" von der senkrecht zur vorgegebenen Schwingrichtung meßbaren Schwingweg-Komponente sQ abgeleitet ist oder ersetzbar ist durch eine von der zeitlichen Ableitung sQ' bzw. sQ'' herleitbaren anderen physikalischen Größe,ein Stellglied (144, 178, 226) der Regeleinrichtung (RSE1, RSE2, 228) wird in Abhängigkeit von der Regelabweichung "e" gesteuert, durch welches Stellglied wenigstens bei einem Antriebsmotor die am Antriebsmotor in ein Drehmoment umsetzbare Druckdifferenz des den Antriebsmotor durchfließenden Fluid-Volumenstromes im Sinne einer Verkleinerung der Regelabweichung "e" beeinflußt ist. - Unwuchtvibrator nach Anspruch 1, dadurch gekennzeichnet, daß die am Antriebsmotor in ein Drehmoment umsetzbare Druckdifferenz bei wenigstens je einem Antriebsmotor einer Gruppe durch ein Stellglied beeinflußbar ist.
- Unwuchtvibrator nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß für jede Gruppe wenigstens zwei Teil-Unwuchtkörper vorgesehen sind.
- Unwuchtvibrator nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die am Antriebsmotor in ein Drehmoment umsetzbare Druckdifferenz durch Drosselung des den Antriebsmotor durchfließenden Fluid-Volumenstromes vor dem Eintritt in den Antriebsmotor und/oder nach dem Austritt aus dem Antriebsmotor beeinflußt ist
- Unwuchtvibrator nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die laufende Erfassung der Regelabweichung "e" durch den Sensorteil (230) einer hydraulischen Regel- oder Steuereinrichtung (228) erfolgt ist, wobei die Wandlung des Wertes der der Regelabweichnug "e" entsprechenden Winkelabweichung in ein Ausgangssignal (264, 266) der Regel- oder Steuereinrichtung durch die Einwirkung der Lage des Drehwinkels zweier Teil-Unwuchtkörper (206, 208) auf die Drosselwirkung von ihnen zugeordneten hydraulischen Drosselstellen (248, 250; 272, 280) bewirkt ist.
- Unwuchtvibrator nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die laufende Erfassung der von der Weggröße sQ, sQ' oder sQ'' abgeleiteten Regelabweichung "e" durch den Sensorteil einer hydraulischen Regel- oder Steuereinrichtung erfogt ist, wobei die Wandlung der Weg-Größen in das Ausgangssignal der Regel- oder Steuereinrichtung durch die Einwirkung der senkrecht zur vorgegebenen Schwingrichtung wirksamen Schwingbeschleunigung auf eine bewegliche Hilfsmasse erfolgt ist, welche Hilfsmasse bei ihrer Schwingbewegung die Drosselwirkung einer hydraulischen Drosselstelle beeinflußt.
- Unwuchtvibrator nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die laufende Erfassung der Regelabweichung "e" unter Zuhilfenahme elektrischer Sensoren erfolgt ist, und zwarentweder als von der Weggröße sQ bzw. sQ' bzw. sQ'' unter Einsatz eines Weg- bzw. Geschwindigkeits- bzw. Beschleunigungssensors (180) abgeleitet,oder als von dem Relativ-Drehwinkel abgeleitet, welcher Relativ-Drehwinkel mittels elektrischer Sensoren aus der Dreh-Lage zweier Teil-Unwuchtkörper ermittelt ist.
- Unwuchtvibrator nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß innerhalb jeder Gruppe wenigstens 2 Teil-Unwuchtkörper mit ihnen zugeordneten Antriebsmotoren vorgesehen sind, zwischen denen zwecks Verstellung des sogenannten statischen Momentes ein Relativ-Stellwinkel variabel einstellbar ist.
- Unwuchtvibrator nach Anspruch 8, dadurch gekennzeichnet, daß die den Relativ-Stellwinkel definierende Dreh-Lage zweier Teil-Unwuchtkörper durch zu einer Winkel-Meßeinrichtung zugehörige elektrische Sensoren erfaßt ist und daß die Regelabweichung "e" ebenfalls unter Zuhilfenahme von elektrischen Sensoren erfaßt ist, wobei die zur Ermittlung der Regelabweichung "e" benötigte Informationsverarbeitung in einer Steuerungs-hardware durchgeführt ist, mit welcher gleichzeitig auch Aufgaben der Informationsverarbeitung für die Winkel-Meßeinrichtung bearbeitet sind.
- Verfahren zur Kompensation von unerwünschten Schwingwegkomponenten quer zur vorgegebenen Schwingrichtung eines Unwuchtvibrators (101, 201) nach dem Oberbegriff des Anspruchs 1,
gekennzeichnet durch die Kombination folgender Verfahrensmerkmale:Laufende Erfassung (180) der Weg-Größe so der Querschwingung oder der zeitlichen Ableitungen sQ' oder sQ'' bezüglich ihres Wertes und/oder ihrer Richtung,und/oder laufende Erfassung (134, 136) des Wertes und/oder der Richtung des durch die Dreh-Lage eines Teil-Unwuchtkörpers aus der einen Gruppe und durch die Dreh-Lage eines Teil-Unwuchtkörpers aus der anderen Gruppe definierbaren Relativ-Drehwinkels (β), wobei der Relativ-Drehwinkel (β) ein Maß oder wenigstens ein Indikator einer quer zur vorgegebenen Schwingrichtung vorhandenen Schwingbewegung ist.Umwandlung der erfaßten Werte und/oder Richtungen in einer Regel- oder Steuerungseinrichtung (RSE1, RSE2, 228) derart, daß in den Aus gangssignalen der Regel- oder Steuereinrichtung Informationen über die Werte und/oder die Richtungen der erfaßten Größen enthalten sind,Beaufschlagung eines Stellgliedes (144, 178 226) mit den Ausgangssignalen der Regel-oder Steuereinrichtung, welches Stellglied zur Durchführung eines vom Informationsgehalt des Ausgangssignals abhängigen Steilvorganges vorgesehen ist,Eingreifen (156, 158; 286, 288) des Stellgliedes bei wenigstens einem der Antriebsmotoren in den ihn durchfließenden Fluid-Volumenstrom zur Beeinflussung des zwischen Eingang und Ausgang des Antriebsmotors meßbaren Differenzdruckes zwecks Erzeugung eines Korrektur-Stell-Drehmomentes und damit gleichzeitig Erzeugung einer Korrektur des Relativ-Drehwinkels im Sinne der Verkleinerung seines Wertes. - Unwuchtvibrator nach einem der voranstehenden Ansprüche 1 bis 9 oder Verfahren nach Anspruch 10, dadurch gekennzeichnet, daß die Regeleinrichtung mit einer Integrier-Funktion versehen ist.
- Unwuchtvibrator nach Anspruch 1, dadurch gekennzeichnet, daß der "Drehwinkel" ein Relativ-Drehwinkel ist, welcher abgeleitet ist von einem Vergleich der Dreh-Lage eines Teil-Unwuchtkörpers aus der einen Gruppe und der Dreh-Lage eines Teil-Unwuchtkörpers aus der anderen Gruppe.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4425905A DE4425905A1 (de) | 1994-07-21 | 1994-07-21 | Vorrichtung und Verfahren zur Kompensation von Querschwingungen an Unwuchtvibratoren mit vorgegebener Schwingrichtung |
DE4425905 | 1994-07-21 | ||
PCT/EP1995/002899 WO1996003224A1 (de) | 1994-07-21 | 1995-07-20 | Kompensation von querschwingungen an unwuchtvibratoren |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0801596A1 EP0801596A1 (de) | 1997-10-22 |
EP0801596B1 true EP0801596B1 (de) | 1999-03-24 |
Family
ID=6523828
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95927702A Expired - Lifetime EP0801596B1 (de) | 1994-07-21 | 1995-07-20 | Kompensation von querschwingungen an unwuchtvibratoren |
Country Status (7)
Country | Link |
---|---|
US (1) | US5911280A (de) |
EP (1) | EP0801596B1 (de) |
JP (1) | JPH10502868A (de) |
KR (1) | KR970704587A (de) |
DE (2) | DE4425905A1 (de) |
ES (1) | ES2131324T3 (de) |
WO (1) | WO1996003224A1 (de) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19543910A1 (de) * | 1995-11-26 | 1997-05-28 | Gedib Ingbuero Innovation | Verstelleinrichtung für einen Unwucht-Richtschwinger mit verstellbarem Fliehmoment |
US6981558B2 (en) | 2001-05-02 | 2006-01-03 | Wacker Construction Equipment Ag | Controller for an unbalanced mass adjusting unit of a soil compacting device |
DE10121383C2 (de) * | 2001-05-02 | 2003-04-03 | Wacker Werke Kg | Steuerung für eine Unwucht-Verstelleinrichtung in einem Vibrationserreger einer Bodenverdichtungsvorrichtung |
EP2183352A4 (de) | 2007-09-06 | 2010-08-18 | Siemens Healthcare Diagnostics | Reagenzkartusche |
EP2067533B2 (de) * | 2007-12-06 | 2016-12-07 | ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH | Schwingungserzeuger für ein Vibrationsrammgerät |
EP2085149B2 (de) * | 2008-01-29 | 2021-12-22 | ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH | Schwingungserzeuger für ein Vibrationsrammgerät |
US20110110725A1 (en) * | 2009-11-06 | 2011-05-12 | International Construction Equipment, Inc. | Vibratory pile driving apparatus |
US8931597B2 (en) * | 2012-11-19 | 2015-01-13 | American Piledriving Equipment, Inc. | Inertia pump for vibratory equipment |
EP3165290B1 (de) | 2015-11-06 | 2021-04-07 | BAUER Maschinen GmbH | Schwingungserzeuger und verfahren zum einbringen eines rammgutes in einen boden |
GB2573535B (en) * | 2018-05-08 | 2021-05-05 | Terex Gb Ltd | Adjustable vibratory drive system |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2732934C2 (de) * | 1977-07-21 | 1985-09-12 | Bomag-Menck GmbH, 5407 Boppard | Verfahren und Vorrichtung zum Rammen und Ziehen |
DE3709112C1 (de) * | 1986-08-27 | 1988-01-28 | Knauer Maschf Gmbh | Ruettelvorrichtung fuer eine Betonsteinformmaschine |
FI85178C (fi) * | 1987-12-21 | 1992-03-10 | Tampella Oy Ab | Foerfarande i rotationsborrning och rotationsborrningsanordning. |
FR2664831B1 (fr) * | 1990-07-20 | 1993-06-11 | Procedes Tech Con | Vibrateur multi-frequence. |
DE4116647C5 (de) * | 1991-05-22 | 2004-07-08 | Hess Maschinenfabrik Gmbh & Co. Kg | Rüttelvorrichtung |
FR2692523B1 (fr) * | 1992-06-19 | 1994-10-07 | Procedes Tech Construction | Dispositif pour la commande d'un vibrateur à moment variable. |
DE4301368A1 (de) * | 1992-07-03 | 1994-01-05 | Gedib Ingbuero Innovation | Vorrichtung und Verfahren zur Schwingungserregung |
US5281775A (en) * | 1992-10-16 | 1994-01-25 | Richard A. Gremillion | Vibrating hole forming device for seismic exploration |
US5355964A (en) * | 1993-07-12 | 1994-10-18 | White John L | Pile driving and/or pile pulling vibratory assembly with counterweights |
-
1994
- 1994-07-21 DE DE4425905A patent/DE4425905A1/de not_active Withdrawn
-
1995
- 1995-07-20 KR KR1019970700482A patent/KR970704587A/ko active IP Right Grant
- 1995-07-20 ES ES95927702T patent/ES2131324T3/es not_active Expired - Lifetime
- 1995-07-20 WO PCT/EP1995/002899 patent/WO1996003224A1/de active IP Right Grant
- 1995-07-20 EP EP95927702A patent/EP0801596B1/de not_active Expired - Lifetime
- 1995-07-20 US US08/765,864 patent/US5911280A/en not_active Expired - Fee Related
- 1995-07-20 JP JP8505457A patent/JPH10502868A/ja active Pending
- 1995-07-20 DE DE59505464T patent/DE59505464D1/de not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE59505464D1 (de) | 1999-04-29 |
KR970704587A (ko) | 1997-09-06 |
US5911280A (en) | 1999-06-15 |
DE4425905A1 (de) | 1996-01-25 |
JPH10502868A (ja) | 1998-03-17 |
EP0801596A1 (de) | 1997-10-22 |
WO1996003224A1 (de) | 1996-02-08 |
ES2131324T3 (es) | 1999-07-16 |
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