EP1727979B1 - Dispositif et procede de commande d'une pompe a pates - Google Patents

Dispositif et procede de commande d'une pompe a pates Download PDF

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Publication number
EP1727979B1
EP1727979B1 EP05716190A EP05716190A EP1727979B1 EP 1727979 B1 EP1727979 B1 EP 1727979B1 EP 05716190 A EP05716190 A EP 05716190A EP 05716190 A EP05716190 A EP 05716190A EP 1727979 B1 EP1727979 B1 EP 1727979B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
time
pump
reversing
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.)
Active
Application number
EP05716190A
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German (de)
English (en)
Other versions
EP1727979A1 (fr
Inventor
Wilhelm Hofmann
Stefan Höfling
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.)
Putzmeister Concrete Pumps GmbH
Original Assignee
Putzmeister AG
Putzmeister Werk Maschinenfabrik GmbH
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Publication date
Application filed by Putzmeister AG, Putzmeister Werk Maschinenfabrik GmbH filed Critical Putzmeister AG
Publication of EP1727979A1 publication Critical patent/EP1727979A1/fr
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Publication of EP1727979B1 publication Critical patent/EP1727979B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • F04B15/023—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous supply of fluid to the pump by gravity through a hopper, e.g. without intake valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • F04B7/0233—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated a common distribution member forming a single discharge distributor for a plurality of pumping chambers
    • F04B7/0241—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated a common distribution member forming a single discharge distributor for a plurality of pumping chambers and having an oscillating movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F04B9/1178—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0201—Position of the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/09—Motor parameters of linear hydraulic motors
    • F04B2203/0903—Position of the driving piston
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/90—Slurry pumps, e.g. concrete

Definitions

  • the invention relates to an apparatus and a method for controlling a sludge pump with two opening on the front side openings in a material feed container, by means of a hydraulic reversing and controlled by these hydraulic drive cylinder push-pull delivery cylinders, arranged with an inside of the material feed container, the inlet side alternately to the openings of the Conveyor cylinder connectable and the other opening releasing and the outlet side connected to a feed line, hydraulically actuated diverter, wherein at each delivery stroke in at least two at predetermined distances from each other and located by the rod and / or bottom ends of the drive cylinder sensor positions detected the passage of the piston and at the end of a delivery stroke, a reversing operation of the reversing pump and the pipe switch is triggered.
  • the pipe switch is also reversed with one and the same hydraulic pump. This must be done exactly in the time in which the pistons have arrived at the bottom or rod end. Only then is the pump pressure sufficient for reversing the diverter valve.
  • a particular problem of the single-circuit pump is therefore that the times of reversing the reversing pump, the stopping of the piston and the reversal of the pipe switch must be exactly matched.
  • the voting problems are somewhat lower. However, however, it is also here by means of a suitable vote to ensure that the piston moves off the cylinder completely to avoid unwanted residues in the cylinders.
  • the present invention seeks to develop a device and a method for controlling a sludge pump of the type described above, whereby a complete emptying of the cylinder at each piston stroke is possible and yet undesirable striking the piston is avoided at the ends of the drive cylinder ,
  • a device, or a method, with the features of the preambles of claims 1 and 6 is eg from the document DE 42 06 576 A1 known.
  • the solution according to the invention is based on the idea that with at least two cylinder shift sensors arranged at arbitrary positions of the working cylinder, which are arranged at a distance from each other and from the two end positions, a movement detection of the drive pistons is possible, with the aid of a computer-aided reversing device with suitable software complete detection of the movement of the pistons along the cylinder and thus allow a solution to the above problem.
  • the computer-aided reversing device a measurement and evaluation routine for metrological and / or arithmetic detection of the temporal movement of the pistons on their way between the two cylinder ends and for calculating a triggering time derived therefrom for a reversal the reversing pump and the pipe switch has.
  • a preferred embodiment of the invention provides that the measurement and evaluation routine an algorithm for time detection of the piston passage at the location of the cylinder switching sensors and for calculating a triggering time derived therefrom for reversing the reversing and diverter valve in each piston stroke under consideration a predetermined or calculated braking time of the piston has up to the respective stop at the cylinder end.
  • the braking time of the pistons is essentially composed of the response time of the reversing relay and the switching time of the reversing pump.
  • each time interval which is measured as the reference value for the speed, can be assigned a release time for reversing the reversing pump and the diverter valve.
  • the time recording can be done in this case, for example, via the switching pulse for the pipe switch.
  • the distance between two diverter switches then corresponds to the stroke duration.
  • the triggering time for the reversal is then determined during the passage of the piston through one of the two cylinder shift sensors. This value is approximately constant for the same pump type.
  • a special feature arises when the flow rate is changed within a pump stroke. In this case, the new flow rate must be taken into account and converted into a corresponding residual maturity to determine the exact triggering time.
  • a preferred embodiment of the invention accordingly provides that the measurement and evaluation routine an algorithm for calculating the speed of the piston on its way between the cylinder switch sensors and a triggering time derived therefrom for Um tenutexrud taking into account a predetermined or calculated braking time of the piston to the respective End stops in the cylinders has.
  • a preferred embodiment of the invention provides that the measurement and evaluation routine responds to preferably set to a remote control device default values for the flow rate of the reversing and an algorithm for determining the course of the piston speed and the next derived triggering time for the Um Kunststoffvorentrée in accordance with the currently set default values. It is of particular advantage if the measurement and evaluation routine has an algorithm for determining the braking time or the braking distance of the pistons in accordance with the momentarily measured or calculated piston speed and a triggering time point derived therefrom for the switching operations.
  • the chronological sequence of movement of the pistons is measured and / or calculated on their way between the two cylinder ends and from this the respective next triggering time for the reversal operations is derived.
  • a preferred embodiment of the invention provides that the piston passages are detected at the location of the cylinder shaft sensors in temporal relation to each other and that from the triggering time for the respective subsequent reversal of the reversing and diverter under consideration of a predetermined or calculated braking time of the piston to the respective end stop on Cylinder is calculated.
  • the speed of the piston can be calculated on its way between the selected cylinder switch sensors and from this the next point in time for the Um tenuvortician be derived.
  • a further preferred procedure is that the time sequence of movement of the piston is changed by remote controlled values for the flow rate and that is derived from the calculated according to the default values movement sequence of the piston taking into account a thus modified braking time of the next triggering time for Um tenuvortician.
  • the braking time or the braking distance of the piston from the measured or calculated instantaneous piston speed, taking into account the device-specific response and switching times of the reversible pump determined and from this the next triggering time is calculated.
  • the control arrangement shown in Fig. 2 and 3 is determined for a slurry pump according to FIG. 1.
  • the sludge pump has two delivery cylinders 50,50 ', the front-side openings 52 open into a material feed tank 54 and alternately during the pressure stroke via a diverter 56 to a delivery line 58 are connectable.
  • the delivery cylinders 50,50 ' are driven in a push-pull manner via hydraulic drive cylinders 5,5' and a reversible hydraulic pump 6.
  • the delivery pistons 60, 60 'of the delivery cylinders 50, 50' are connected to the pistons 8, 8 'of the drive cylinders 5, 5' via a common piston rod 9, 9 '.
  • the drive cylinder 5,5 ' are in the embodiment shown on the bottom side via hydraulic lines 11, 11' of the hydraulic circuit with the aid of Reverse pump 6 pressurized oil and are hydraulically connected to each other at its rod end via a swing oil line 12.
  • the direction of movement of the drive pistons 8,8 'and thus of the common piston rod 9,9' is thereby reversed, that the direction of flow of the reversing pump 6 is reversed via a reversing device 18 containing a computer 14 and an adjusting mechanism 16.
  • the reversing pump 6 has a swash plate 62, which is swiveled through its zero position during the reversal, so that the conveying direction of the pressure oil in the hydraulic lines 11, 11 'is reversed.
  • the delivery rate of the reversing pump 6 can be varied by the swivel angle of the swash plate 62 at a predetermined speed of a drive motor, not shown.
  • the swivel angle of the swash plate 62 can be adjusted via a remote control device 64 with the assistance of the computer 14.
  • the reversal of the reversing pump and the pipe switch 56 takes place as soon as the pistons 8, 8 'of the drive cylinders 5, 5' reach their end position.
  • the reversing device utilizes output signals of each of the rod-side and bottom ends of the two drive cylinders 5,5 'arranged Zylinderschaltsensoren 20,22 and 20', 22 ', which are connected on the output side to the computer 14 of the reversing device 18.
  • the cylinder switch sensors respond to the drive piston 8,8 'passing by during the pumping operation and signal this event to the computer input 66,68.
  • a reversing signal 76 is triggered in the reversing device with a time delay, which reverses the reversing pump 6 via the adjusting mechanism 16.
  • Um variably a reversal of the diverter 56 via the directional control valve 79 and the plunger cylinder 72,72 'is also triggered by a signal 77.
  • the computer 14 has a measurement and evaluation routine 40 (see Fig. 5), in which the output signals of the rod-side Zylinderschaltsensoren 20,20 'are evaluated to form a reversing signal 76,77 for the reversing pump 6 and / or the diverter 56.
  • the rod-side Zylinderschaltsensoren 20,20 'with S 1 and S 2 are designated. Accordingly, the sensor positions from the bottom end of the drive cylinder with X S1 and X S2 are designated, while the useful length of the cylinder, which is calculated from the cylinder length minus the piston length, designated X Zyl . This is the maximum piston stroke.
  • the positions X S1 , X S2 of the cylinder shift sensors and the effective length X Zyl are known.
  • the aim of the invention is the calculation of a position X x or the associated time t x for the piston travel at the point X x , from which the reversible pump must be reversed, so that a complete piston stroke can be achieved without hard hitting the cylinder bottom.
  • This position is dependent on the delivery rate, but independent of the position of the cylinder shift sensors (see Fig. 4).
  • the velocity V K of the piston results from the usage length X Zyl and the stroke time t stroke as well as the acceleration and braking paths and times X Acc , X Brake , t Acc , t Brake to:
  • V K X Zyl - X Accel - X brake t stroke - t Accel - t brake
  • the time .DELTA.t x1 or .DELTA.t x2 will begin after passing the cylinder switch sensor. If the cylinder switch sensors are behind the tripping position, the tripping time is calculated from the beginning of the stroke.
  • the triggering time can also be determined when the delivery rate changes.
  • the effective length X Zyl is divided as a function of the flow rate change and to set the new speed V K of the piston for the calculation of the braking time. This is known due to the given flow rate.
  • the flow chart of the measurement and evaluation routine 40 in FIG. 5 illustrates the measurement and control operations during the piston movement in the working cylinders.
  • the time t s1 and t s2 of the passing piston is determined and from this the theoretical stroke time t stroke is calculated. If in between the flow rate is changed, this affects the stroke time t stroke and thus also on the piston speed. These values are then taken into account in the calculation of the tripping time, which finally lead to the triggering of the reversing movements in the diverter switch and in the reversing pump at the time t x or ⁇ t x .
  • a lead time for the stroke time is set parallel to the event measurements on the cylinder switch sensors, which independently of the measuring operations on the cylinder switch sensors via a parallel branch a reversal of the pipe switch and the reversing pump can trigger.
  • the invention relates to an apparatus and a method for controlling a two-cylinder slurry pump, whose delivery pistons are actuated in push-pull mode by means of a hydraulic reversing pump 6 and via these actuated hydraulic drive cylinders.
  • the delivery cylinders 50, 50 ' are connected to a delivery line 58 via a diverter 56 at each pressure stroke. At the end of each pressure stroke, a reversing operation of the reversing pump 6 and the pipe switch 56 is triggered.
  • a computer-aided reversing device is provided, the measuring and Evaluation routine for metrological and / or arithmetic detection of the temporal movement of the piston on its way between the two cylinder ends and to calculate a derived triggering time for the next reversal of the reversing pump and the pipe switch has.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (10)

  1. Dispositif de commande d'une pompe pour substances épaisses comprenant deux cylindres convoyeurs (50, 50') qui débouchent, par des orifices frontaux (52), dans un réceptacle (54) de délivrance de matière et peuvent être actionnés, en opposition symétrique, à l'aide d'au moins une pompe hydraulique réversible (6) et de vérins hydrauliques d'entraînement (5, 5') activés par cette dernière ; une bifurcation tubulaire (56) qui est actionnable hydrauliquement, est logée à l'intérieur dudit réceptacle (54) de délivrance de matière, peut être raccordée en alternance aux orifices (52) des cylindres convoyeurs (50, 50'), côté entrée, en dégageant l'autre orifice considéré, et est reliée côté sortie à un conduit d'acheminement (58), sachant que les vérins d'entraînement (5, 5') sont reliés par l'une de leurs extrémités, par l'intermédiaire d'un conduit hydraulique respectif (11, 11'), à un raccord de la pompe réversible (6), et sont reliés hydrauliquement l'un à l'autre par leur autre extrémité, par l'intermédiaire d'un conduit (12) à huile instable ; au moins deux capteurs (20, 20' ; 22, 22') de commutation des vérins, qui sont agencés à des espacements préétablis l'un vis-à-vis de l'autre, et vis-à-vis des extrémités situées du côté des tiges et/ou du côté des fonds desdits vérins d'entraînement (5, 5'), et réagissent à un piston (8, 8') en mouvement dans lesdits vérins d'entraînement ; et un dispositif (18) réagissant à des signaux de sortie émanant de capteurs sélectionnés de commutation des vérins, en vue d'inverser la commande de la pompe réversible (6) et de la bifurcation tubulaire (56), caractérisé par le fait que ledit dispositif d'inversion de commande, assisté par ordinateur, renferme un programme de mesure et d'interprétation en vue de détecter, par des mesures techniques et/ou par des calculs, le déroulement temporel des mouvements des pistons sur leur trajet entre les deux extrémités des cylindres ; ainsi qu'en vue de calculer, par dérivation sur cette base, un instant du déclenchement de l'inversion de commande de la pompe réversible et de la bifurcation tubulaire.
  2. Dispositif selon la revendication 1, caractérisé par le fait que le programme de mesure et d'interprétation comporte un algorithme en vue de la détection temporelle du franchissement, par les pistons, de l'emplacement des capteurs de commutation des vérins ; ainsi qu'en vue du calcul, par dérivation sur cette base, d'un instant de déclenchement d'une inversion de commande de la pompe réversible et de la bifurcation tubulaire, lors de chaque course des pistons, avec prise en compte d'un temps de freinage préétabli ou calculé desdits pistons, jusqu'à la venue en butée définitive considérée contre le cylindre.
  3. Dispositif selon la revendication 1 ou 2, caractérisé par le fait que le programme de mesure et d'interprétation comporte un algorithme en vue du calcul de la vitesse des pistons, sur leur trajet entre les capteurs de commutation des vérins ; et, par dérivation _sur cette base, d'un instant de déclenchement des processus ultérieurs d'inversion de commande, avec prise en compte d'un temps de freinage préétabli ou calculé desdits pistons, jusqu'à la venue en butée définitive considérée contre le cylindre.
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé par le fait que le programme de mesure et d'interprétation réagit à des valeurs préétablies de la quantité refoulée par la pompe réversible, de préférence réglées par l'intermédiaire d'un organe de télécommande ; et comporte un algorithme en vue de la détermination de l'allure de la vitesse des pistons et, par dérivation sur cette base, de l'instant du déclenchement des processus ultérieurs d'inversion de commande, en fonction desdites valeurs préétablies réglées à l'instant considéré.
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé par le fait que le programme de mesure et d'interprétation comporte un algorithme en vue de la détermination du temps de freinage ou de la course de freinage des pistons, en fonction de la vitesse desdits pistons mesurée ou calculée à l'instant considéré ; et, par dérivation sur cette base, d'un instant du déclenchement des processus de commutation.
  6. Procédé de commande d'une pompe pour substances épaisses comprenant deux cylindres convoyeurs (50, 50') qui débouchent, par des orifices frontaux (52), dans un réceptacle (54) de délivrance de matière et peuvent être actionnés, en opposition symétrique, à l'aide d'au moins une pompe hydraulique réversible (6) et de vérins hydrauliques d'entraînement (5, 5') activés par cette dernière ; et une bifurcation tubulaire (56) qui est actionnable hydrauliquement, est logée à l'intérieur dudit réceptacle (54) de délivrance de matière, peut être raccordée en alternance aux orifices (52) des cylindres convoyeurs (50, 50'), côté entrée, en dégageant l'autre orifice considéré, et est reliée côté sortie à un conduit d'acheminement (58), sachant que lors de chaque course de refoulement, en au moins deux emplacements de détection agencés à des espacements préétablis l'un vis-à-vis de l'autre, et vis-à-vis des extrémités situées du côté des tiges et des fonds des vérins d'entraînement, le passage des pistons est détecté, puis un processus d'inversion de commande de la pompe réversible (6) et/ou de la bifurcation tubulaire (56) est déclenché, caractérisé par le fait que le déroulement temporel des mouvements des pistons est mesuré et/ou calculé sur leur trajet entre les deux extrémités des cylindres, et l'instant du déclenchement des processus d'inversion de commande, respectivement successifs, est dérivé sur cette base.
  7. Procédé selon la revendication 6, caractérisé par le fait que les passages des pistons, à l'emplacement des capteurs de commutation des vérins, sont détectés en relation temporelle réciproque ; et par le fait que, sur cette base, l'instant du déclenchement de l'inversion de commande, respectivement successive, de la pompe réversible et de la bifurcation tubulaire est calculé avec prise en compte d'un temps de freinage préétabli ou calculé desdits pistons, jusqu'à la venue en butée définitive considérée contre le cylindre.
  8. Procédé selon la revendication 6 ou 7, caractérisé par le fait que la vitesse des pistons est calculée sur leur trajet entre les capteurs sélectionnés de commutation des vérins ; et par le fait que, sur cette base, l'instant du déclenchement de l'inversion de commande, respectivement successive, de la pompe réversible et de la bifurcation tubulaire est dérivé avec prise en compte d'un temps de freinage préétabli ou calculé desdits pistons, jusqu'à la venue en butée définitive considérée contre le cylindre.
  9. Procédé selon l'une des revendications 6 à 8, caractérisé par le fait que le déroulement temporel des mouvements des pistons est modifié par l'intermédiaire de valeurs préétablies télécommandées, relatives à la quantité refoulée ; et par le fait que l'instant du déclenchement des processus successifs d'inversion de commande est dérivé sur la base du déroulement des mouvements des pistons, calculé en fonction desdites valeurs préétablies, avec prise en compte d'un temps de freinage conséquemment modifié.
  10. Procédé selon l'une des revendications 6 à 9, caractérisé par le fait que le temps de freinage ou la course de freinage des pistons est établi(e) sur la base de la vitesse desdits pistons mesurée ou calculée, avec prise en compte respective des temps de réponse et de commutation spécifiques de l'appareillage de la pompe réversible ; et l'instant du déclenchement respectivement successif est calculé sur cette base.
EP05716190A 2004-03-26 2005-03-18 Dispositif et procede de commande d'une pompe a pates Active EP1727979B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004015416A DE102004015416A1 (de) 2004-03-26 2004-03-26 Vorrichtung und Verfahren zur Steuerung einer Dickstoffpumpe
PCT/EP2005/002893 WO2005093251A1 (fr) 2004-03-26 2005-03-18 Dispositif et procede de commande d'une pompe a pates

Publications (2)

Publication Number Publication Date
EP1727979A1 EP1727979A1 (fr) 2006-12-06
EP1727979B1 true EP1727979B1 (fr) 2007-07-18

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EP05716190A Active EP1727979B1 (fr) 2004-03-26 2005-03-18 Dispositif et procede de commande d'une pompe a pates

Country Status (10)

Country Link
US (1) US7581935B2 (fr)
EP (1) EP1727979B1 (fr)
JP (1) JP2007530853A (fr)
KR (1) KR101148579B1 (fr)
CN (1) CN100547239C (fr)
AT (1) ATE367523T1 (fr)
DE (2) DE102004015416A1 (fr)
EA (1) EA007861B1 (fr)
ES (1) ES2290896T3 (fr)
WO (1) WO2005093251A1 (fr)

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RU2012147256A (ru) * 2010-04-07 2014-05-27 Вейр Минералз Незерландс Б.В. Контроллер сдвига фазы для системы поршневых насосов
CN102094799B (zh) * 2010-12-28 2012-03-07 长沙中联重工科技发展股份有限公司 控制混凝土泵在停机后再次泵送和反泵的方法
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KR20060127381A (ko) 2006-12-12
CN1788160A (zh) 2006-06-14
DE502005001072D1 (de) 2007-08-30
EA007861B1 (ru) 2007-02-27
US7581935B2 (en) 2009-09-01
DE102004015416A1 (de) 2005-10-13
ES2290896T3 (es) 2008-02-16
US20060245942A1 (en) 2006-11-02
WO2005093251A1 (fr) 2005-10-06
EP1727979A1 (fr) 2006-12-06
ATE367523T1 (de) 2007-08-15
EA200600260A1 (ru) 2006-06-30
KR101148579B1 (ko) 2012-05-25
JP2007530853A (ja) 2007-11-01
CN100547239C (zh) 2009-10-07

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