WO1996003224A1 - Kompensation von querschwingungen an unwuchtvibratoren - Google Patents
Kompensation von querschwingungen an unwuchtvibratoren Download PDFInfo
- Publication number
- WO1996003224A1 WO1996003224A1 PCT/EP1995/002899 EP9502899W WO9603224A1 WO 1996003224 A1 WO1996003224 A1 WO 1996003224A1 EP 9502899 W EP9502899 W EP 9502899W WO 9603224 A1 WO9603224 A1 WO 9603224A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- unbalance
- partial
- control
- rotation
- angle
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
- B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
- B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
- 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 FE 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.
- a further feature of the type of vibrators relating to the invention is that each group has at least one drive motor of its own, and that both groups do not, or at least not, each other, but at least two partial unbalance bodies belonging to each other belong to each other are constantly forcibly synchronized via mechanical drive means in order to maintain a certain angular position.
- a vibrator of this type consists of two partial unbalance bodies rotating in opposite directions and synchronously around two axes arranged parallel to one another, each of which is driven by its own motor.
- Such vibrators are used for various tasks, the synchronous running being created in the simplest case by the so-called “self-synchronization", which is easy to achieve under the following conditions:
- the resulting acceleration or the resulting unbalance force in Dynamic mass mdyn to be displaced must be able to oscillate unhindered (for example supported by springs) and a straight line through the center of gravity in the direction of oscillation must be the perpendicular bisector on such a distance which is in the plane of the rotating unbalance center of gravity from one Axis of rotation extends to the other.
- Such vibrators are also used for ramming.
- the fact that a forced synchronization by mechanical drive means can be dispensed with between the two groups of partial unbalance bodies is regarded as a particular functional advantage, for example because of the contribution to noise reduction. Because the invention is special here can be used advantageously, it is described below in connection with ram vibrators.
- the dynamic mass mdyn which also vibrates, to which the mass of the rammed material belongs, is always via special vibration-isolating devices such as e.g. Spring yokes, is connected to a special carrier device (e.g. leader or crane).
- a special carrier device e.g. leader or crane.
- the entire weight of the dynamic mass is introduced into the carrier device via this vibration-isolating special device.
- the pulling force is also superimposed on the weight to be transmitted.
- Such transverse vibrations can arise from the incorrect alignment of the resulting excitation force FE of the partial unbalance body itself.
- the resulting excitation force is kinetically coupled to the dynamic mass and can therefore e.g. can also be influenced by external disturbing forces as a function of the disturbance of the oscillating movement of the dynamic mass.
- transverse vibrations can also be excited directly by disturbing forces acting on the dynamic mass. Possible causes of such disturbing forces are: asymmetrical loading of the pile, asymmetrical suspension of the dynamic mass, non-horizontal alignment of the exciter body, force excitation from the coupling of the exciter body to the spring yoke or the leader.
- vibrators are to be considered, which work according to the teaching of DE-PS 41 16 647.
- a separate drive motor is assigned to each partial unbalance body, with the motor needing a separate drive controller in a remarkable manner and each drive controller in turn being assigned its own angle measuring system for detecting the actual angle of rotation position of the associated partial unbalance body is.
- the associated control system also requires a higher-level position controller, which assigns the currently valid angle of rotation position to each drive controller based on the "master motor and slave motor" principle.
- Motor-controlled vibrators according to DE-PS 41 16 647 are in principle also not intended for the purpose of compensating for transverse vibrations, since it is the task of all drive controllers to synchronize the partial unbalance bodies as if they were synchronized via a gear transmission. The resulting
- Acceleration is always adjusted in the same, predetermined direction.
- a vibrator controlled in this way cannot compensate for transverse vibrations of the dynamic mass that are excited from the outside.
- the object of the invention is to provide a simpler and more robust device compared to the closest prior art, with the aid of which all types of undesirable transverse vibrations can be reduced in size or even avoided.
- the improvement sought should be limited to solutions using only hydraulic drive motors 30.
- the expected solution should be simpler to such an extent that it is possible, for example, to apply at least two hydraulic drive motors, which may be assigned to different groups, through a common pressure source (feature of the preamble of claims 1 and 10).
- the principle according to the invention can also steer the direction of the resulting excitation force (in the manner of overcompensation) in a direction deviating from the predetermined direction of oscillation.
- an internal acceleration generated by unbalanced forces
- the external acceleration which excites the transverse vibration
- the two independent claims 1 and 10 are based on the same general inventive concept. Thereafter, the undesirable transverse vibrations of the dynamic mass mdyn 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, the functional quantity In connection with the transverse oscillation, a correction is made to the direction of the resulting excitation force by influencing the resulting torque (which is the sum of driving and braking torques) causing the rotation of the unbalance bodies in at least one group.
- FIG. 1 shows in a schematic manner a directional oscillator with two partial unbalance bodies, with two electrical measuring devices for detecting the angles of rotation of two partial unbalanced bodies and for detecting vibration paths, and with a correction actuating device for influencing the torques of two drive motors,
- Figure 2 shows schematically the same overall device as in Fig. 1, with the only difference that the measuring device measures only a relative angle of rotation, and that hydraulically.
- 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 mdyn.
- the two hydraulic motors M1 and M2 of the same size are acted upon by a common pressure source 116 with variable pressure. After starting the motors with the opposite direction of rotation indicated by the arrows 118 and 120, because of the intended arrangement of the center of gravity 114, the rotational movement of the two unbalanced bodies 106 and 108 is self-synchronized, so that they rotate synchronously in opposite directions.
- 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 FE, which excitation force has to be imagined through the center of gravity 114.
- the rotating part unbalance bodies develop special "synchronous guidance torques" in connection with mass forces guided via the bearings 122, 124 and generated by the oscillating dynamic mass mdyn, which within a certain range of disturbing forces cause the synchronous operation of the two Ensure partial unbalanced bodies without having to be synchronized by mechanical drive means such as gears.
- the position sensor 136 shows a relative angle of rotation ⁇ which deviates from the real synchronous position and which stems from an advance of the partial unbalance body 108 in the direction of the 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 FE is deflected out of its desired direction and that consequently transverse vibrations occur with a travel component SQ (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, with the aid of which the volume flows emerging from the motors M1 and M2 can be selectively throttled.
- One or the other volume flow is throttled by moving the control piston 150 in the direction of the double arrow 148 from the center position shown.
- the control edge narrows 152 the inlet channel 156 of the volume flow originating from the engine Ml, with a shift to the right, the inlet channel 158 of the volume flow emerging from the engine M2 is reduced.
- the outflow channel 160 leading to the tank 162 is not affected by the displacement of the control piston, so that the unrestricted volume flow can flow off unhindered at any time.
- the control piston 150 is displaced by the difference between a force generated by a compression spring 166 on the one hand and a hydraulic pressure generated in the control pressure chamber 164
- the hydraulic pressure in the control pressure chamber is determined by the output pressure of an electrically controllable pressure control valve 168, with which the pressure specified by a constant pressure source 170 can be regulated down to arbitrarily specifiable pressures at the outlet 172.
- the size of the regulated output pressure which can be set at the output 172 is determined with the cooperation of the electrical control element 174 by the output signal of the regulating or control device RSEL supplied via the line 176.
- a sensor 180 for detecting the acceleration SQ "assigned to the vibration path SQ (142) is attached to the frame 100, the signal of which is fed to the regulating or control device RSE2 via the signal line 182.
- the information of the input signal becomes in the regulating or control device RSE2 processes that the output signal, which is supplied to the electrical control element 174 via the line 184, contains the necessary information about the value and direction of the size measured by the sensor 180, so that the pressure control valve 168 and the throttle device 146 on the motors Ml and M2 similar reactions can be caused, as can be achieved by the influence of the output signal from RSEl.
- a correction-setting process is carried out as follows:
- the regulating or control devices RSE1 or RSE2 cause the throttle device 146 to be adjusted via their output signals and thus to generate a setting device. Torque on one of the motors proportional to the measured value of the disturbance ⁇ or
- the regulating or control device RSE1 will ensure that the control piston 150 is shifted to the right, which reduces the torque of the motor M2 and thus compared to the motor Ml builds up a control torque with the help of which the relative angle of rotation ß is reduced again.
- the regulating or control devices RSE1 and RSE2 can, however, be provided with additional functions which they use depending on the operating situation of the vibrator. This includes e.g. an integration function in the sense of the control technology in order to be able to compensate for the disturbances without residual errors, or an algorithm which allows the output signals to take effect individually or together according to predetermined criteria.
- FIG. 2 shows an unbalance vibrator 201 which is said to have the same properties as that shown in FIG. 1 insofar as it relates to the features 200 to 220 and the motors M1 and M2.
- the same features in both figures have their key figures with identical combinations of the last two digits.
- the difference between the unbalance vibrator 201 in FIG. 2 and that according to FIG. 101 in FIG. 1 consists exclusively in another embodiment of the correction actuating device 225. In FIG. 2, this consists of the actuator 226 and the regulating or control device 228 with the sensor part 230.
- the sensor part 230 is formed by two control rotors 232 and 234 with a 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 on 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) are connected in a rotationally fixed manner to the shafts 202 and 204 and thus to these and the partial unbalance bodies. circulate synchronously.
- the outer cylinders 244, 246 of the control rotors 232, 234 are fitted with a narrow cylindrical sealing gap into the inner cylinders 240, 242 of the control stators 236, 238, so that the leakage flowing through these sealing gaps can be neglected.
- a control groove 252 is embedded in the outer cylinder 244, through which two control edges 252 and 254 are formed.
- the space of the control groove 252 can be connected to a pressure source 258 via the control opening 248.
- the control edge 256 is just about to connect the control opening 250 to the control groove 252.
- the control rotor 232 rotates further in the direction of the arrow 218, the control opening 250 is connected to the control opening 248 and thus to the pressure source 258. This connection exists via an angle of rotation ⁇ until the control edge 254 closes the control opening 248 again.
- the control opening 250 is connected with the throttle bodies 260 and 262 to the control lines 264 and 266 carrying the output signals of the regulating or control device 228. As a result of this, the pressure present in the control opening 250 is also present in the control lines 264, 266, unless one of these control lines is connected to the pressureless tank 268 by the influence of the control rotor 234.
- inlet channels 286, 288 can be blocked or throttled, while a central drain channel 290 to the unpressurized tank 297 always remains open.
- control piston 280 is held in the basic position shown by the action of two springs 292, 294.
- the control piston 280 maintains the basic position shown. However, as soon as the time pulse length of the pressure pulses on both sides of the control piston is changed at the same pressure level, it shifts Control piston 280 on one side or the other.
- 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, which are formed by the control groove 278 on the outer cylinder of the control rotor 234 become.
- the control edge 274 has just closed the control opening 272, taking into account the direction of rotation 220, while the control edge 276 has closed the control openings 280 after the further rotation of both control rotors to release the angle ⁇ , but at this point in time at the control opening 280 there is no longer any pressure from the pressure pulses generated by the control rotor 232.
- the path component SQ (142) of the transverse vibration could also be detected with a special hydraulic sensor part, comparable to that
- the oscillation acceleration would set an auxiliary mass in an oscillating movement, by means of which movement flow cross sections of hydraulic volume flows are changed in the sense of a desired blocking or throttling effect. (Claim 6).
- Braking elements to be acted upon by the actuators with actuating energy.
- the partial unbalance bodies including shafts and motors
- two groups of partial unbalance bodies are obtained with the same direction of rotation within the group and the opposite direction of rotation from group to group.
- the 4 motors can be controlled in a known manner (as shown, for example, in the publication PCT / EP93 / 01693) between the rotating motors in the same direction
- Partial unbalance bodies set a relative setting angle of a predetermined size, with which the entire resulting centrifugal moment is also set in a predeterminable manner.
- the present invention is particularly urgently required in order to ensure the functioning of the vibrator at all. To do this, one only needs to change the relative angle of rotation between two partial unbalance bodies of different groups in accordance with the type of FIG. 1 or 2 (claim 8).
- the determination of the actual value of the relative actuation angle which is also to be regulated when regulating the resulting centrifugal torque is carried out using an angle measuring device.
- Such vibrators are used only for Supply of the angle measuring device continuously records the angles of rotation of two partial unbalance bodies, which in this case can belong to the same group.
- the regulating and control device can contain the function of an integrating element, with which, as is known, the control deviation, that is the difference between the setpoint and actual value of the controlled variable, can be reduced to the value zero (claim 11).
- the actuators only have to be acted upon by another or differently operating control device.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP95927702A EP0801596B1 (de) | 1994-07-21 | 1995-07-20 | Kompensation von querschwingungen an unwuchtvibratoren |
KR1019970700482A KR970704587A (ko) | 1994-07-21 | 1995-07-20 | 불평형 질량 진동기 상의 가로 진동을 보상하기 위한 장치 및 방법(compensation for transverse vibrations in unbalanced mass vibrators) |
DE59505464T DE59505464D1 (de) | 1994-07-21 | 1995-07-20 | Kompensation von querschwingungen an unwuchtvibratoren |
US08/765,864 US5911280A (en) | 1994-07-21 | 1995-07-20 | Apparatus and method for reducing transverse vibrations in unbalanced-mass vibrators |
JP8505457A JPH10502868A (ja) | 1994-07-21 | 1995-07-20 | アンバランス−マス振動器における横振動の補正 |
Applications Claiming Priority (2)
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 |
DEP4425905.0 | 1994-07-21 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996003224A1 true WO1996003224A1 (de) | 1996-02-08 |
Family
ID=6523828
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1995/002899 WO1996003224A1 (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) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002087789A1 (de) * | 2001-05-02 | 2002-11-07 | Wacker Construction Equipment Ag | Steuerung für eine unwucht-verstelleinrichtung einer bodenverdichtungsvorrichtung |
US6981558B2 (en) | 2001-05-02 | 2006-01-03 | Wacker Construction Equipment Ag | Controller for an unbalanced mass adjusting unit of a soil compacting device |
US8268263B2 (en) | 2007-09-06 | 2012-09-18 | Siemens Healthcare Diagnostics Inc. | Reagent cartridge |
Families Citing this family (7)
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 |
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 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0467758A1 (de) * | 1990-07-20 | 1992-01-22 | Procedes Techniques De Construction | Mehrfrequenter Schwingungserzeuger |
DE4116647C1 (de) * | 1991-05-22 | 1992-07-02 | Hess Maschinenfabrik Gmbh & Co Kg, 5909 Burbach, De | |
DE4301368A1 (de) * | 1992-07-03 | 1994-01-05 | Gedib Ingbuero Innovation | Vorrichtung und Verfahren zur Schwingungserregung |
EP0577444A1 (de) * | 1992-06-19 | 1994-01-05 | Procedes Techniques De Construction | Steuervorrichtung eines Schwingungserregers mit einstellbarer Unwucht |
Family Cites Families (5)
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. |
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 JP JP8505457A patent/JPH10502868A/ja active Pending
- 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 US US08/765,864 patent/US5911280A/en not_active Expired - Fee Related
- 1995-07-20 DE DE59505464T patent/DE59505464D1/de not_active Expired - Fee Related
- 1995-07-20 EP EP95927702A patent/EP0801596B1/de not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0467758A1 (de) * | 1990-07-20 | 1992-01-22 | Procedes Techniques De Construction | Mehrfrequenter Schwingungserzeuger |
DE4116647C1 (de) * | 1991-05-22 | 1992-07-02 | Hess Maschinenfabrik Gmbh & Co Kg, 5909 Burbach, De | |
EP0577444A1 (de) * | 1992-06-19 | 1994-01-05 | Procedes Techniques De Construction | Steuervorrichtung eines Schwingungserregers mit einstellbarer Unwucht |
DE4301368A1 (de) * | 1992-07-03 | 1994-01-05 | Gedib Ingbuero Innovation | Vorrichtung und Verfahren zur Schwingungserregung |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002087789A1 (de) * | 2001-05-02 | 2002-11-07 | Wacker Construction Equipment Ag | Steuerung für eine unwucht-verstelleinrichtung einer bodenverdichtungsvorrichtung |
US6981558B2 (en) | 2001-05-02 | 2006-01-03 | Wacker Construction Equipment Ag | Controller for an unbalanced mass adjusting unit of a soil compacting device |
US8268263B2 (en) | 2007-09-06 | 2012-09-18 | Siemens Healthcare Diagnostics Inc. | Reagent cartridge |
Also Published As
Publication number | Publication date |
---|---|
EP0801596A1 (de) | 1997-10-22 |
EP0801596B1 (de) | 1999-03-24 |
JPH10502868A (ja) | 1998-03-17 |
ES2131324T3 (es) | 1999-07-16 |
KR970704587A (ko) | 1997-09-06 |
US5911280A (en) | 1999-06-15 |
DE59505464D1 (de) | 1999-04-29 |
DE4425905A1 (de) | 1996-01-25 |
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