EP0801596B1 - Kompensation von querschwingungen an unwuchtvibratoren - Google Patents

Kompensation von querschwingungen an unwuchtvibratoren Download PDF

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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
Authority
EP
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
Application number
EP95927702A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0801596A1 (de
Inventor
Hubert Bald
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.)
Gedib Ingenieurbuero und Innovationsberatung GmbH
Original Assignee
Gedib Ingenieurbuero und Innovationsberatung GmbH
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Publication of EP0801596A1 publication Critical patent/EP0801596A1/de
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Publication of EP0801596B1 publication Critical patent/EP0801596B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Vibration Prevention Devices (AREA)
EP95927702A 1994-07-21 1995-07-20 Kompensation von querschwingungen an unwuchtvibratoren Expired - Lifetime EP0801596B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4425905 1994-07-21
DE4425905A DE4425905A1 (de) 1994-07-21 1994-07-21 Vorrichtung und Verfahren zur Kompensation von Querschwingungen an Unwuchtvibratoren mit vorgegebener Schwingrichtung
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 (es)
EP (1) EP0801596B1 (es)
JP (1) JPH10502868A (es)
KR (1) KR970704587A (es)
DE (2) DE4425905A1 (es)
ES (1) ES2131324T3 (es)
WO (1) WO1996003224A1 (es)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
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 (en) 2007-09-06 2010-08-18 Siemens Healthcare Diagnostics REAGENT CARTRIDGE
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)

* Cited by examiner, † Cited by third party
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

Also Published As

Publication number Publication date
JPH10502868A (ja) 1998-03-17
US5911280A (en) 1999-06-15
EP0801596A1 (de) 1997-10-22
DE59505464D1 (de) 1999-04-29
ES2131324T3 (es) 1999-07-16
WO1996003224A1 (de) 1996-02-08
KR970704587A (ko) 1997-09-06
DE4425905A1 (de) 1996-01-25

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