WO2015067584A1 - Pompe pour liquide épais et unité d'amenée - Google Patents

Pompe pour liquide épais et unité d'amenée Download PDF

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Publication number
WO2015067584A1
WO2015067584A1 PCT/EP2014/073638 EP2014073638W WO2015067584A1 WO 2015067584 A1 WO2015067584 A1 WO 2015067584A1 EP 2014073638 W EP2014073638 W EP 2014073638W WO 2015067584 A1 WO2015067584 A1 WO 2015067584A1
Authority
WO
WIPO (PCT)
Prior art keywords
unit
filling
drive
degree
feed unit
Prior art date
Application number
PCT/EP2014/073638
Other languages
German (de)
English (en)
Inventor
Hans-Peter Dicks
Waldemar Klassen
Dieter Schwarz
Original Assignee
Schwing Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schwing Gmbh filed Critical Schwing Gmbh
Publication of WO2015067584A1 publication Critical patent/WO2015067584A1/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
    • 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
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/10—Other safety measures
    • F04B49/106—Responsive to pumped volume
    • 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
    • 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
    • F04B2207/00—External parameters
    • F04B2207/04—Settings
    • F04B2207/041—Settings of flow
    • F04B2207/0412—Settings of flow minimum
    • 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
    • F04B2207/00—External parameters
    • F04B2207/70—Warnings
    • F04B2207/703—Stopping

Definitions

  • the invention relates to a slurry pump with a conveyor unit and a feed unit, in which the conveyor unit is designed, for example, as a two-cylinder piston pump and the feed unit as a screw conveyor.
  • Slurry pumps of this type have been proven for many years, for example, to transport sewage sludge, remove residues from mines or to feed industrial furnaces.
  • Object of the present invention is a further optimization of the interaction of the feed unit and the feed unit of a slurry pump in order to ensure the highest possible energy and flow rate efficient function of the slurry pump at changing operating conditions and flow rates.
  • a sludge pump comprises a delivery unit with a pumping volume, a feed channel for sucking up the thick matter and an outlet, a control device which determines a filling level of the delivery unit by means of a measuring device and determines the actual delivery rate of the delivery unit from the pumping volume of the delivery unit and the determined filling degree.
  • a feed unit with a drive which supplies the feed unit with the thick matter via the feed channel wherein the control device controls the drive of the feed unit as a function of the degree of filling of the feed unit and an input unit, wherein via the input unit a desired flow rate and a desired degree of filling of the feed unit adjustable is and controls the control of the drive of the feed unit so that the conveyor unit complies with a change in the set target flow rate the target filling level.
  • the High-viscosity pump is characterized in that the control device determines the power required for the desired degree of filling for the drive of the feed unit and determines from the ratio of the delivery rate and the determined power of the feed unit an excess power of the feed unit.
  • the control device determines when reaching the desired filling level the corresponding optimum drive power and then from the ratio of the delivery of the thick matter pump and the determined power of the feed unit, an excess power of the feed unit, which is necessary for achieving the desired filling level.
  • the control device transmits the excess power of the drive of the feed unit, determined with a change in the nominal delivery quantity, to the new delivery setpoint value for the drive of the feed unit.
  • the speed of the conveyor unit is doubled at the same time in this example in order to achieve the increase of the flow rate from 1 to 2 m 3 / h.
  • the feed unit which pumps the thick matter into an outlet, fed by means of a feed unit of the thick matter via a feed channel.
  • the degree of filling of the delivery unit is preferably determined by sensor data of a measuring device by a control device.
  • the drive power of the feed unit is increased or reduced via the control device, resulting in a change of the filling level of the conveyor unit.
  • the drive of the delivery unit is controlled such that the desired nominal filling level is maintained.
  • the feed unit with the drive is preferably dimensioned such that the theoretically possible throughput of the feed unit is slightly higher, for example by about 40%, than the maximum possible delivery rate of the conveyor unit. This ensures that the delivery unit can always be supplied with sufficient thick material.
  • the feed unit when starting the conveyor unit, for which a desired flow rate has been specified, the feed unit starts with a defined excess capacity. So that the feed unit does not start at full power when the slurry pump starts up and then has to be downshifted to achieve the optimum filling level, a preliminary optimum drive power of the feed unit can be determined when starting the slurry pump from the desired delivery rate of the delivery unit.
  • this drive power can be so high that the supply unit has a defined volume or power surplus of 20% with respect to the delivery unit, with which the delivery unit is then supplied with the thick stock. This leaves enough leeway up and down to readjust the drive power of the feed unit according to the invention until reaching the desired filling level.
  • the optimal degree of filling a thick matter pump may vary in particular depending on the thick material to be pumped and the type of feed to some extent. It is rarely desirable to achieve a degree of filling of the delivery unit of 100%, because for a disproportionate pressure of the feed unit would be required to supply the feed unit to be pumped thick material. In addition to a high energy consumption, this could also lead to a clogging in the feed channel between the feed unit and the conveyor unit, when the feed unit attempts by high pressure to reach too high a filling level of the conveyor unit. In addition, under certain circumstances, the wear of the feed unit would increase sharply at a too high degree of filling of the delivery unit.
  • the optimum degree of filling can vary between about 70% and 90% for the pump to pump in its optimum working range.
  • the optimal for the pumped thick matter Filling level can be preset on the slurry pump via an input unit. Even with a change in the target flow rate of the slurry pump, the drive of the feed unit is controlled so that the desired degree of filling is maintained as accurately as possible. That is, for example, if the degree of filling should be 85%, but a degree of filling of the conveyor unit of 90% was determined, the drive power of the feed unit is reduced until the filling rate is 85% at the following pumping strokes of the conveyor unit. Conversely, when the actual filling degree determined at a target filling degree of 85% is 80%, the driving power of the feeding unit is correspondingly increased.
  • a lower limit (W min ) for the degree of filling of the slurry pump can be preset. For example, if a target filling level of 80% has been preset, but a blockage in the area of the feed unit can not reach a minimum filling level Wmin, which has been defined as 60%, for example, the pump is switched off or an alarm signal is triggered so that the Condition of the machine can be checked by a central office or by the operating staff on site and, if necessary, a blockage or other malfunction can be eliminated.
  • the control speed for the control of the drive of the feed unit is adjustable, i.
  • the drive power of the feed unit can be increased or decreased faster or slower until the desired filling level is reached.
  • the feed unit When the feed unit is designed as a cyclically operating cylinder-piston pump, it has proved to be advantageous after starting the First pump unit wait a few pump strokes until a relatively constant actual filling level of the delivery cylinder has set and only then begin to readjust the drive power of the feed until the desired filling level is reached.
  • the number of pump strokes to readjusting the drive power of the feed unit will advantageously vary between two and six pump strokes and can be preselected on the slurry pump via an input unit by the operator. The number of pump strokes may also be higher depending on the design, size of the liquid end and the type of thick material to be pumped.
  • a filling level of the delivery unit is determined for each pumping operation by means of a measuring device and the actual delivery rate of the delivery unit is determined from the volume of the delivery unit and the determined filling level, and the drive of the delivery unit is controlled as a function of the filling level of the delivery unit.
  • a target flow rate and a target filling level of the conveyor unit are adjustable and the drive of the feed unit is controlled so that when a change in the set target flow rate of the desired filling level is maintained.
  • the power required for driving the feed unit is determined according to the invention and an excess power of the feed unit is determined from the ratio of the delivery rate of the delivery unit and the determined power of the drive of the feed unit.
  • the thick material to be pumped by the thick matter pump 10 is first fed to the conveyor screw 30 via a filling opening 33.
  • the auger 30 has a hydraulic drive 31 and a helical coil 32.
  • the thick material is pressed by a rotational movement of the coil 32 in the direction of the feed channel 1 1 to the two-cylinder piston pump 20.
  • the two-cylinder piston pump 20 sucks the thick matter through the feed channel 1 1 of the screw conveyor and pumps it at high pressure through the pressure valve housing 25c (s.Fig.2) in the outlet 21, which is connected for example to a feed line, thereby the thick matter is pumped to its actual destination.
  • the slurry pump 10 further has a hydraulic drive unit 43 with a drive motor 43a, for example, an electric or internal combustion engine, a hydraulic pump 43b, for driving the two-cylinder slurry pump 20, and a hydraulic pump 43c, for driving the screw conveyor 30, drives.
  • a hydraulic drive unit 43 On the hydraulic drive unit 43 is also a valve unit 43 d, which is controlled by the control device 40, with the example, the direction of rotation of the drive 31 of the screw conveyor 30 is controlled.
  • the flow rates of the hydraulic pumps 43b and 43c are separately controlled via control lines of the control device 40, respectively.
  • a hydraulic control block 44 is arranged, which of the hydraulic pump 43 b with Hydraulic oil is supplied.
  • the hydraulic control block 44 controls the functions of the hydraulic cylinders 28a, b (forward, backward, neutral) and the hydraulic cylinders (open, close, neutral) of the intake and exhaust valve actuators (11 e, f; 12e, f).
  • a speed sensor 34 On the drive motor 31 of the screw conveyor 30, a speed sensor 34 is arranged, the speed sensor signal is passed via a sensor line 35 to the control device 40. From the sensor signal of the sensor 34, the controller 40 may determine the theoretical flow rate of the screw conveyor 30, i. the amount of thick matter that would transport the screw conveyor 30 in the ideal case, if at the feed channel 1 1 to the two-cylinder piston pump 20 would be no back pressure, derive.
  • the screw conveyor 30 is dimensioned so that the theoretically possible throughput at the maximum speed of the screw conveyor is about 50-100% higher than the maximum pumping power to be provided by the two-cylinder piston pump 20. This ensures that the screw conveyor can always provide a sufficient amount of thick matter in the feed channel 1 1 available.
  • the two-cylinder piston pump 20 has position sensors 26 a, b on the exhaust-valve valve drives 12 e, f and delivery-piston end-position sensors 14 a, b whose signals are processed by the control device 40.
  • the delivery piston end position sensors 14a, b for the electrohydraulic switching (EHU) of the two-cylinder piston pump 20 initially have the function of early detection of an approach of the delivery pistons 24a, b to the rear region of the delivery cylinders 27a, b. Based on these sensor signals, the control device 40 reduces the power of the two-cylinder piston pump 20 via the hydraulic pump 43b, with the delivery pistons 24a, b initially maintaining their direction of movement.
  • Switching devices not shown here on the delivery cylinders 24a, b, controlled by the hydraulic control block 44, ensure that the direction of movement of the delivery cylinders 24a, b is switched when the delivery pistons 24a, b arrive at the rear end of the delivery cylinders 27a, b.
  • the delivery piston end position sensors 14a, b, the position sensors 26a, b and the filling degree determining means 41 which is a part of the electronic control device 40, the degree of filling, and thus the effective delivery, the Two-cylinder piston pump 20 is determined, as will be explained in more detail in connection with the further drawings.
  • the control unit 40 is also connected to an input unit 42, in which, inter alia, a desired flow rate F so n and a desired filling degree W so n can be entered for the two-cylinder piston pump 20.
  • the two-cylinder piston pump 20 shown in FIG. 2 has hydraulic cylinders 28a, b with pistons 22a, b and piston rods 23a, b, which drive the delivery pistons 24a, b of the delivery cylinders 27a, b of the two-cylinder piston pump 20.
  • the piston rods 23a, b pass through a water box 13, which supplies water to the rear side of the delivery pistons 24a, b for cooling, lubricating and cleaning purposes. Since both delivery pistons 24a, b work in parallel, virtually the water level in the water tank 13 does not change, since the water during the movement of the piston 24a, b is constantly pushed back and forth between them.
  • two sensors 14a, b are arranged, which detect when one of the delivery pistons 24a, b has almost reached its rear end position during the aspiration of the thick material.
  • two Saugventilgeophen 25a, b with inlet openings 1 1 1 a, b are shown, which are connected to the supply channel 1 1, not shown, brought up from above.
  • the Saugventilgeophen 25a, b are open to the delivery cylinders 27a, b, so that the delivery piston 24a, b can suck the thick matter through the feed ports 1 1 a, b in their intake stroke.
  • the suction valve housings 25a, b each have outlet openings 12a, b which can be opened and closed by means of outlet valve plates 12c, d and outlet valve actuators 12e, f.
  • the Auslasstellerventilantriebe 12e, f are, for example, hydraulic actuators (hydraulic cylinders) which are controlled by the hydraulic control block 44.
  • To the Outlet valve actuators 12e, f are the aforementioned position sensors 26a, b which detect the position (or approach) of pistons 12g, h of the exhaust actuator valves 12e, f.
  • FIG. 3 shows a side view of a thick matter pump 10 according to the invention with the feed unit 30, which has already been described in more detail in connection with FIG.
  • the delivery cylinder 27b shown below in FIG. 2, of the two-cylinder piston pump 20 with the delivery piston 24b is located in the intake stroke. That is, the delivery piston 24b moves to the right and sucks the fed from the screw conveyor 30 via the feed channel 1 1 thick material in the delivery cylinder 27b, while the Einlasstellerventil 1 1 d open and the Auslasstellerventil 12d is closed.
  • Fig. 4 the beginning of the filling degree measurement for a cylinder of the two-cylinder piston pump 20 is shown.
  • the delivery piston 24b is in its end position detected by the delivery piston end position sensor 14b.
  • the aspirated thick matter is shown here in dashed lines and fills part of the delivery piston 27b and the Saugventilgephases 25b.
  • the air cylinder 28b now begins to push the delivery piston 24b to the left via the piston rod 22b while the respective intake ports 11b, 12b are closed both by the outlet valve plate 12d and by the inlet valve plate 11d.
  • the inlet opening 1 1 b is held closed by the pressure of the inlet valve actuator 1 1 f, while the outlet opening 12 b is deflected via the outlet valve disk 12 d by the backpressure of the thick material D already pumped into the outlet 21 (shown by the two arrows pointing to the right in the pressure valve housing 25 c ) is pressed against the outlet opening 12b.
  • the control electronics detect at which point practically only thick matter but no appreciable air volume is present in the delivery cylinder 27b and the suction valve housing 25b and the actual delivery process begins.
  • the delivery piston 24b now conveys the thick matter into the outlet 21 through the outlet opening 12b, as shown in FIG. 6, until the delivery piston 24b has reached its left-hand end position.
  • the delivery piston 24a (see Fig. 2), not shown here, moves the pumping unit in the intake operation to the right until it comes into the region of the delivery piston end position sensor 14a, whereby the beginning of the flow rate measurement on the second pumping unit is triggered.
  • the filling degree determining means 41 may be made of the total time required for the delivery piston 24b for a pumping operation and the time required from the beginning of the pumping stroke for the pre-compression until triggering of the position sensor 26b, the actual degree of filling F of the two-cylinder is the piston pump 20 determine.
  • Filling degree determining means 41 which uses the data of these sensors for the degree of filling determination, a measuring device for determining the degree of filling. Alone by increasing the speed of the delivery cylinder of the two-cylinder piston pump 20, a proportional increase in the flow rate F of the slurry pump 10 can not be achieved in the rule because the degree of filling W of the two-cylinder piston pump 20 is usually lower, if the power or speed of the screw conveyor 30 is not readjusted. In order to comply with the degree of filling W of the two-cylinder piston pump 20 with a change in the target flow rate F so n according to the present invention, the drive 31 of the screw conveyor 30 is controlled so that the target filling degree F so n is maintained.
  • the screw conveyor When starting up the thick matter pump 10, in which a certain target flow rate F so n at a certain, tailored to the thick material to be pumped desired filling degree W so n is to be achieved, the screw conveyor will start with a defined excess power. That is, for example, if a target flow rate F is desired so n of 50m 3 / h, which corresponds, for example, half the capacity of the thick matter pump, the drive 31 of the screw conveyor 30 is initially driven so that they the delivery cylinders 27 a, b of the two-cylinder Piston pump 20 initially a volume of 60m 3 / h (calculated without back pressure) supplies, although the screw conveyor 30 would theoretically be able to promote significantly more thick material in the feed channel 1 1 when starting.
  • the two-cylinder piston pump 20 requires a certain starting time or a certain number of pumping strokes until a constant degree of filling W is set in the delivery cylinders 27a, b. Therefore, it does not make sense to determine the degree of filling from the first pumping stroke after start-up of the two-cylinder piston pump 20 and readjust the rotational speed of the screw conveyor 20, as might result in strong speed jumps and overshoot in the rules.
  • the degree of filling W ist of the two-cylinder piston pump 20 is preferably determined only after a preset number of pump strokes and the drive 31 of the screw conveyor 30 then adjusted accordingly to obtain the preset target filling degree F so n.
  • the number of pump strokes until the regulation of the screw conveyor 30 is effective is usefully limited, for example, between two and six pump strokes, in order to avoid in the operation of the system not meaningful presets by the operator.
  • a practical lower target filling level can be, for example, 70%.
  • the Nachregel for the adjustment of the drive power is also adjustable.
  • a gain factor KP
  • Kl which influences the control speed
  • Kl reset time
  • the Nachregel Anthony can be adapted to the thick material to be pumped.
  • it may be appropriate for a thin liquid thick set a rather low control speed to prevent overshoot of the control and to specify a higher control speed for viscous thickers in order to achieve a rapid change in the degree of filling.
  • the delivery rate F of the two-cylinder piston pump 20 is shown with a continuous line from bottom left to top right.
  • the screw conveyor 30 always works with a slightly higher theoretical throughput to ensure sufficient pressure of the thick material in the feed channel 1 1, so that the two-cylinder piston pump 20 does not suck in too much air and the target filling degree F so n can be met.
  • the speed of the screw conveyor 30 can be varied via the drive 31 from the control device 40 via the hydraulic pump 43c so that it is slowly controlled up or down along the vertical arrows shown on the left, for example, until the set filling degree Wsoii of the two-cylinder Piston pump 20 is reached.
  • a power surplus of about 20% in the screw conveyor (feed unit) 30 is set to the pre-set degree of filling W so n (this could be 80%, for example) to comply.
  • the sludge pump 10 quickly reaches the new desired operating conditions even with changed setpoint specifications without, for example, the power of the screw conveyor 30 having to be readjusted for an unnecessarily long time.
  • the slurry pump and the associated sensors can be constructed very differently and deviating from this description, without departing from the idea of the invention.
  • the end position sensors 14a, b as be constructed mechanical, inductive or capacitive switch.
  • the measurement of the position of the delivery piston can also be made possible by known path measuring systems, eg magnetorestrictive position sensors.
  • the invention shown here could be used for two-cylinder piston pumps, whose pistons do not work counterparallel, but are controlled individually, which, controlled accordingly, leads to a more continuous Dickstoff handstrom at the outlet 21.
  • the sensors 26a, b may, as shown here, be attached to the hydraulic cylinders of the exhaust actuator valves, but for example also directly detect the position of the exhaust valve disks 12c, d.
  • a pressure difference measurement between the Saugventilgephinen 25a, b and the pressure valve housing 25c for the filling degree determination could be made.

Abstract

L'invention concerne une pompe (10) pour liquide épais comprenant : une unité de transport (20) comportant un volume de pompage (V), un conduit d'amenée (11) servant à aspirer le liquide épais et une sortie (21) ; un dispositif de commande (40) qui détermine un degré de remplissage (Wist) de l'unité de transport (20) au moyen d'un dispositif de mesure (14a, b ; 26a, b ; 41) et qui définit à partir du volume de pompage (V) de l'unité de transport (20) et du degré de remplissage (Wist) déterminé la quantité transportée réelle (Fist) de l'unité de transport (20) ; une unité d'amenée (30) comportant un entraînement (31) qui amène le liquide épais à l'unité de transport (20) par le biais du conduit d'amenée (11), le dispositif de commande (40) commandant l'entraînement (31) de l'unité d'amenée (30) en fonction du degré de remplissage (Wist) de l'unité de transport (20); et une unité d'entrée (42), l'unité d'entrée (42) permettant de régler une quantité transportée cible (Wsoll) et un degré de remplissage cible (Fsoll) de l'unité de transport (20) et le dispositif de commande (40) commandant l'entraînement (31) de l'unité d'amenée (30) de sorte que la unité de transport (20) observe le degré de remplissage cible (Fsoll) lorsque la quantité transportée cible (Wsoll) est modifiée. Le dispositif de commande (40) détermine la puissance de l'entraînement (31) de l'unité d'amenée qui est nécessaire au degré de remplissage cible (Fsoll) (30), il détermine à partir du rapport entre la quantité transportée réelle (Fist) de l'unité de transport (20) et la puissance déterminée de l'unité d'amenée (30) une puissance excédentaire de l'entraînement (31) de l'unité d'amenée (30), et il transmet la puissance excédentaire déterminée aux nouvelles quantités transportées cibles (Fsoll) pour l'entraînement (31) de l'unité d'amenée (30).
PCT/EP2014/073638 2013-11-07 2014-11-04 Pompe pour liquide épais et unité d'amenée WO2015067584A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013018606.4 2013-11-07
DE102013018606.4A DE102013018606B4 (de) 2013-11-07 2013-11-07 1 - Dickstoffpumpe mit Fördereinheit und Zuführeinheit

Publications (1)

Publication Number Publication Date
WO2015067584A1 true WO2015067584A1 (fr) 2015-05-14

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WO (1) WO2015067584A1 (fr)

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DE102016005945A1 (de) * 2016-05-17 2017-11-23 Dürr Systems Ag Beschichtungsmittelpumpe
DE102018208121A1 (de) * 2018-05-23 2019-11-28 Putzmeister Engineering Gmbh System zur Erfassung und zur Lösung einer teilweisen oder vollständigen Dickstoffverstopfung in einer Dickstoffförderleitung
DE102018208125A1 (de) * 2018-05-23 2019-11-28 Putzmeister Engineering Gmbh System zur Vermeidung einer Dickstoffverstopfung in einer Dickstoffförderleitung beim Anpumpen von Dickstoff in der Dickstoffförderleitung
DE102021202325A1 (de) 2021-03-10 2022-09-15 Putzmeister Engineering Gmbh Verfahren zum Betreiben einer Bau- und/oder Dickstoffpumpe zum Fördern von Bau- und/oder Dickstoff und Bau- und/oder Dickstoffpumpe zum Fördern von Bau- und/oder Dickstoff

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US5336052A (en) * 1993-04-28 1994-08-09 Abel Pumpen Gmbh & Co. Kg Viscous material pump
EP0562398B1 (fr) 1992-03-21 1996-06-26 Schwing GmbH Pompe pour matières épaisses

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DE4206576B4 (de) 1992-03-02 2005-08-04 Putzmeister Ag Verfahren und Anordnung zur Bestimmung der Fördermenge oder des Förderstroms von mittels einer Kolbendickstoffpumpe transportiertem Fördergut
US5839883A (en) 1996-05-22 1998-11-24 Schwing America, Inc. System and method for controlling a materials handling system
US8376716B2 (en) * 2009-04-10 2013-02-19 Schwing Bioset, Inc. Multi-pump sequencing

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Publication number Priority date Publication date Assignee Title
DE2052583A1 (de) * 1970-10-27 1972-05-04 Bors, Heinz J., Campione (Schweiz) Vorrichtung zum Fördern dickflüssiger Stoffe, insbesondere Beton, Mörtel und dgl
EP0562398B1 (fr) 1992-03-21 1996-06-26 Schwing GmbH Pompe pour matières épaisses
US5336052A (en) * 1993-04-28 1994-08-09 Abel Pumpen Gmbh & Co. Kg Viscous material pump

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DE102013018606A1 (de) 2015-05-07

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