EP3282124A1 - Pompe a liquides epais - Google Patents

Pompe a liquides epais Download PDF

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Publication number
EP3282124A1
EP3282124A1 EP16183666.3A EP16183666A EP3282124A1 EP 3282124 A1 EP3282124 A1 EP 3282124A1 EP 16183666 A EP16183666 A EP 16183666A EP 3282124 A1 EP3282124 A1 EP 3282124A1
Authority
EP
European Patent Office
Prior art keywords
delivery cylinder
valve
passage opening
pump according
forward movement
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.)
Granted
Application number
EP16183666.3A
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German (de)
English (en)
Other versions
EP3282124B1 (fr
Inventor
Felix Weber
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 Engineering GmbH
Original Assignee
Putzmeister Engineering GmbH
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Filing date
Publication date
Application filed by Putzmeister Engineering GmbH filed Critical Putzmeister Engineering GmbH
Priority to EP16183666.3A priority Critical patent/EP3282124B1/fr
Publication of EP3282124A1 publication Critical patent/EP3282124A1/fr
Application granted granted Critical
Publication of EP3282124B1 publication Critical patent/EP3282124B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0058—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control
    • 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
    • F04B7/0019—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers
    • 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
    • F04B7/0019—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers
    • F04B7/0026—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers and having an oscillating movement

Definitions

  • the invention relates to a slurry pump with a first delivery cylinder and a second delivery cylinder.
  • the slurry pump comprises a first inlet valve for introducing thick material into the first delivery cylinder and a second inlet valve for introducing thick material into the second delivery cylinder.
  • the slurry pump also includes an outlet valve to combine the flow rates of the first delivery cylinder and the second delivery cylinder, that is to lead to a common outlet.
  • Pumps of this type are used for conveying thick materials, such as fresh concrete or mortar.
  • the delivery cylinders suck the sludge in a backward motion out of a supply.
  • the intake valve associated with the intake valve is opened, so that the thick matter from the supply through the inlet valve can enter into the delivery cylinder.
  • the inlet valve associated with the delivery cylinder is closed, so that the thick material is conveyed in the direction of the pump outlet.
  • the outlet valve With the outlet valve, the flow rate of the first delivery cylinder and the flow rate of the second delivery cylinder are either locked or combined depending on the operating state.
  • the invention has for its object to introduce a slurry pump, which is constructed less expensive. Based on the cited prior art, the object is achieved with the features of claim 1. Advantageous embodiments are specified in the subclaims.
  • the outlet valve comprises a first passage opening for thick material conveyed by the first delivery cylinder and a second passage opening for thick material conveyed by the second delivery cylinder.
  • the outlet valve comprises a valve member, which closes the first passage opening in a first state, which closes the second passage opening in a second state and which closes neither the first passage opening nor the second passage opening in an intermediate state.
  • intermediate state is to be understood in a functional sense. It is possible, but not mandatory, that the valve member is also arranged spatially between the first passage opening and the second passage opening in the intermediate state.
  • the invention has recognized that it is possible to achieve the desired combination of the flow rates of the two delivery cylinders with only a single valve member. By the intermediate state in which closed neither of the two openings is, it is possible to realize substantially uniform transitions between the flow rates of the two delivery cylinders.
  • an axially movable piston may be accommodated in each of the delivery cylinders.
  • the pump may include a drive to drive axial forward and backward movement of the pistons in their respective delivery cylinders.
  • the thick matter can be sucked out of a supply with the backward movement. With the forward movement, the thick matter can be conveyed in the direction of an outlet of the pump.
  • Thick cloth is a generic term for media that are difficult to convey.
  • the thick matter may be, for example, a substance with coarse-grained constituents, a substance with aggressive constituents or the like.
  • the thick matter can also be a bulk material.
  • the thick material may be, for example, fresh concrete or mortar. Fresh concrete contains grains up to a size of more than 30 mm, binds, forms deposits in dead spaces and is therefore difficult to convey.
  • the thick matter pump according to the invention can be set up such that the inlet valves and the outlet valve are actuated to match the stroke of the delivery cylinders.
  • the first intake valve associated with the first delivery cylinder may be opened when the first delivery cylinder is in the backward movement.
  • the first intake valve may be closed when the first delivery cylinder is in the forward motion.
  • the first inlet valve can already be closed when the forward movement of the first delivery cylinder begins.
  • the first delivery cylinder after completion of the forward movement Make a slight backward movement before opening the first inlet valve again.
  • the second inlet valve and the second delivery cylinder can be matched accordingly.
  • the drive of the pump can be designed so that the backward movement of the delivery cylinder takes place within a shorter period of time than the forward movement.
  • the beginning of the forward movement of one piston may overlap with the end of the forward movement of the other piston. It is then promoted at any time by at least one of the two delivery cylinder material in the direction of the exhaust valve. This overlapping operation of the delivery cylinder forms the basis for being able to achieve a substantially continuous flow of the thick material.
  • the pressure buildup in the first delivery cylinder begins when the piston is in the forward motion and the associated first intake valve is closed.
  • a pressure In order to set the thick matter in motion, a pressure must be built up that corresponds to the pressure on the output side of the pump. Before the pressure is built up, there is a pressure difference across the valve member.
  • the outlet valve may be arranged such that the first delivery opening associated with the first delivery cylinder is still closed at the beginning of the forward movement of the first delivery cylinder.
  • the first passage opening may remain closed until the pressure built up with the first delivery cylinder substantially corresponds to the pressure on the output side of the pump, so that the valve member is only exposed to a small pressure difference.
  • the switching of the outlet valve, with which the passage opening is released can take place after the beginning of the pressure build-up, preferably after the pressure difference has dropped to less than 50%, more preferably to less than 20% of the initial value.
  • the self-energizing seal of the valve member can be relieved before the switching operation of the valve member. Without pressure difference, the material flow is also reduced, so that the wear of the valve member is lower, which is caused by passing during the switching operation of the valve member material passing.
  • the second delivery cylinder and the outlet valve can be matched accordingly.
  • the outlet valve is in the intermediate state, in which the thick matter can pass through both the first passage opening and through the second passage opening.
  • both the first passage opening and the second passage opening can be completely opened. It is then the entire cross-sectional area of the passage openings for the passage of thick matter available.
  • the thick material conveyed with the first delivery cylinder passes through the first passage opening of the discharge valve.
  • the material flow coming from the first delivery cylinder combines with the flow of material from the second delivery cylinder.
  • the second delivery cylinder is about to complete its forward movement at this stage.
  • the outlet valve With the next switching operation, the outlet valve is brought into a state in which the first passage opening is opened and the second passage opening is closed.
  • the first delivery cylinder Continue its forward movement, while the second delivery cylinder can go into the backward movement to suck more thick matter from the stock.
  • the switching operation can therefore take place before the backward movement of the second delivery cylinder begins. This is the case when the valve member of the exhaust valve is set in motion prior to the start of the backward movement. In particular, it is possible that the movement of the valve member is already completed before the start of the backward movement.
  • the pressure at which the thick stock in the supply usually corresponds to the ambient pressure which is substantially lower than the pressure which the delivery cylinders build up during the forward movement.
  • the switching action with which the second inlet valve is opened may take place when the pressure difference is below an initial pressure difference, preferably when the pressure difference has dropped to less than 50%, more preferably to less than 20% of the initial value.
  • the transition from the forward movement of the first delivery cylinder to the forward movement of the second delivery cylinder may be designed accordingly.
  • the forward movement of the conveyor cylinders can be done at a basic speed, while the other conveyor cylinder is in the backward movement.
  • the basic speed of the material flow is defined, which can provide the sludge pump according to the invention.
  • the speed may be reduced from the ground speed.
  • the two delivery cylinders can be coordinated with each other so that the velocities of the two forward movements in total correspond to the ground speed. This can be maintained in the direction of the pump outlet even in the overlapping phase, a substantially constant flow of material.
  • Vorhell theoryer Before the intake valves, a Vorhell varietyer may be arranged, from which the delivery cylinder suck the thick matter. In the Vorhell matterser can be refilled during operation of the slurry pump continuously thick matter, so that a sufficient amount is available from which the delivery cylinders can suck.
  • the path of the thick matter leads through passages of the inlet valves into the interior of the pump.
  • There are two separate paths the first of which is from the passage opening of the first inlet valve to the first conveyor cylinder extends and of which the second extends from the passage opening of the second inlet valve to the second delivery cylinder.
  • Each of the two inlet valves can be provided with its own valve member, via which the passage opening is released or closed. It is also possible a common valve member for the two intake valves. In all cases there may be three shift positions, wherein in a first shift position the first intake valve is open and the second intake valve is closed, wherein in a second shift position, the first intake valve is closed and the second intake valve is open, and wherein in a third shift position, both intake valves are closed ,
  • the valve member of the inlet valves may be a locking slide which is arranged in a first state in front of the passage opening and closes off the passage opening and which releases the passage opening in a second state. It can be provided, for example, a sliding mechanism or a rotating mechanism with which the gate valve between the two states.
  • the slurry pump may include a drive element that actively drives the shifts between the various states of the intake valves.
  • the mechanism may be formed as a sliding mechanism or as a rotating mechanism.
  • a drive element may be provided to actively switch the exhaust valve between the various states.
  • a passive actuation of the valve member of the exhaust valve In a passive operation changes the switching state of the exhaust valve depending on which delivery cylinder, a material flow is supplied to the outlet valve.
  • the outlet valve may be designed so that the valve member is arranged in the direction of the flow of material behind the passage openings. As a result, an applied over the valve member pressure difference can be used to enhance the sealing effect between the valve member and the passage opening.
  • the pump according to the invention may comprise a first operating mode and a second operating mode.
  • the first mode of operation may correspond to the previously described pumping mode, in which the thick matter is sucked from a Vorhell disposer and is conveyed via the outlet valve in the direction of a pump outlet.
  • the second operating mode can be configured as a suction operation, in which the material flow moves in the reverse direction.
  • suction mode for example, the pump may be operated to clean the exhaust valve or a line connected to the pump outlet, or to eliminate blockage in this area.
  • the interaction of the delivery cylinder with the valves in the reverse manner be matched. If a delivery cylinder in the backward movement, so the associated passage opening of the exhaust valve may be open, while the associated inlet valve is closed. During the forward movement of the delivery cylinder, the associated passage of the exhaust valve may be closed while the associated intake valve is open.
  • truck 14 On the back of a in Fig. 1 shown truck 14 is a slurry pump 15 is arranged in the form of a concrete pump.
  • the slurry pump 15 includes a prefill container 16 into which the concrete from a supply (not shown) is filled.
  • the sludge pump 15 sucks in the concrete from the prefill container and conveys the concrete through a connection pipe 17 which extends along a distribution boom 18.
  • the distribution boom 18 is mounted on a turntable 19 and can be folded over a plurality of joints, so that the end of the tube 17 can be brought into a spaced from the truck 14 position. In this position, the concrete is discharged from the connection pipe 17.
  • the slurry pump comprises according to Fig. 2 a first conveyor cylinder 21 and a second conveyor cylinder 22.
  • Each conveyor cylinder 21, 22 comprises a piston which sucks in a backward movement concrete from the Vorphilll essenceer 16 and conveys the concrete with a forward movement in the direction of an outlet 23 of the pump.
  • the first delivery cylinder 21 is associated with a first inlet valve 24.
  • the intake valve 24 is opened during the backward movement of the first delivery cylinder 21, so that the delivery cylinder 21 can suck in concrete from the Vorhell anyer 16.
  • the inlet valve 24 is closed during the forward movement of the first delivery cylinder 21, so that the concrete in the direction of the pump outlet 23 can be promoted.
  • the second delivery cylinder 22 is associated with a second inlet valve 25, the switching operations are matched to the backward and forward movements of the second delivery cylinder 22 accordingly.
  • the two delivery cylinders 21, 22 is associated with a common outlet valve 26.
  • the outlet valve 26 comprises a first passage opening 27 for concrete conveyed with the first delivery cylinder 21 and a second passage opening 28 for concrete conveyed with the second delivery cylinder 22.
  • a valve member 32 of the exhaust valve closes in a first switching state 29, the first passage opening 27 and leaves the second passage opening 28 open.
  • the outlet valve 26 closes the second passage opening 28 and leaves the first passage opening 27 open.
  • both passage openings 27, 28 are open.
  • the two conveyor cylinders 21, 22 are driven so that the backward movement takes place within a shorter period of time than the forward movement.
  • the beginning of the forward movement of the one delivery cylinder overlaps with the end of the forward movement of the other delivery cylinder. At any time, therefore, concrete is conveyed in the direction of the outlet valve 26 by at least one of the delivery cylinders 21, 22.
  • the valve member 32 of the exhaust valve 26 is actively switched by a drive between the various switching states. If the first delivery cylinder 21 in the forward movement and the second delivery cylinder 22 in the reverse movement, the exhaust valve 26 is in the switching state 30, in which only the coming of the first delivery cylinder 21 material flow can pass through the exhaust valve 26. If the second delivery cylinder 22 in the forward movement and the first delivery cylinder 21 in the reverse movement, the exhaust valve 26 is in the switching state 29, in which only the coming of the second delivery cylinder 20 material flow can pass through the exhaust valve 26. In the overlapping phase, in which both delivery cylinders 21, 22 are in the forward movement, the outlet valve 26 is in the intermediate state 31, in which the material flows from both delivery cylinders 21, 22 can pass through the outlet valve 26.
  • Both conveyor cylinders 21, 22 have a basic speed for the forward movement.
  • the basic speed of the forward movement is used, while the respective other conveyor cylinder 21, 22 in the backward movement.
  • the basic speed of the material flow is defined, which is promoted in this phase towards the pump outlet 23.
  • the speed is reduced from the ground speed such that the velocities of the two forward motions add up to the ground speed. In this way, a constant flow of material towards the pump outlet 23 is maintained even during the overlapping phase.
  • the Fig. 3 shows the sludge pump according to the invention in a perspective view.
  • the inlet valve 25 is in the open state, so that the associated inlet opening 45 of the pump is continuous and that with the second delivery cylinder 22 thick matter from the Vorhell anyer 16 can be sucked.
  • the first intake valve 24 is in the closed state.
  • the piston of the first delivery cylinder 21 is in the forward motion, the material flow moves through the first passage 27 of the slurry valve 26 and the interior of the valve housing 46 toward the pump outlet 23, see Fig. 4 ,
  • FIG. 5A the valve member 32 of the outlet valve 26 is switched so that it closes the passage opening 27 of the first delivery cylinder 21 and that it leaves open the passage opening 28 of the second delivery cylinder 22.
  • the inlet valve 25 of the second delivery cylinder 22 is closed, see Fig. 5B ,
  • the second delivery cylinder 22 is in the forward movement and conveys concrete through the passage opening 28 in the interior of the valve housing 46 and the pump outlet 23.
  • the inlet valve 24 of the first delivery cylinder 21 is opened, so that the first delivery cylinder 21 with a Backward movement through the inlet port 44 of the pump can suck concrete from the Vorphilll inherenter 16.
  • the backward movement of the first delivery cylinder 21 ends earlier than the forward movement of the second delivery cylinder 22 Fig. 6 the state is shown in which the forward movement of the first delivery cylinder 21 begins and the forward movement of the second delivery cylinder 22 is just before the end. Both inlet valves 24, 25 are closed.
  • the switching of the exhaust valve 26 in the intermediate state 31 begins after the first delivery cylinder 21 has already built up pressure in front of the passage opening 27, so that above the valve member 32 only a slight pressure difference is applied.
  • the outlet valve 26 is in the intermediate state 31, in which the valve member 32 leaves open both the first passage opening 27 and the second passage opening 28.
  • both delivery cylinders 21, 22 the speed of the forward movement is reduced, so that the delivery cylinder 21, 22 now jointly promote the amount of material that has previously promoted the second delivery cylinder 22 alone.
  • the intake valve 25 is opened, see Fig. 7 .
  • the second delivery cylinder 22 may already perform a first backward movement before opening the inlet valve 25.
  • the inlet valve 25 is opened, the second delivery cylinder 22 sucks concrete from the prefill container 16 with a backward movement through the inlet port 45 of the pump.
  • the first delivery cylinder 21 moves forward at its basic speed, so that the flow of material to the pump outlet 23 remains unchanged.
  • the exhaust valve 26 is actuated by a drive (not shown).
  • the drive acts on a shaft 33 of the valve member 32 and switches the valve member 32 between the various states.
  • FIGS. 9 and 10 show an embodiment in which the exhaust valve 26 is actuated passively.
  • the valve member 32 is rotatably mounted on a shaft which is arranged in the lower region of the valve member 32.
  • Fig. 10A is the exhaust valve 26 in a state in which the first passage opening 27 is closed and the second passage opening 28 is opened. If the slurry pump is in the pumping mode, this corresponds to a state in which the first delivery cylinder 21 in the backward movement and the second delivery cylinder 22 in the forward movement.
  • the outlet valve 26 shown in FIGS. 9 and 10 can also be actively actuated.
  • valve member 32 is moved by the flow of material into a middle position (intermediate state) in which both passage openings 27, 28 are free, see Fig. 10B , Ends the forward movement of the second delivery cylinder 21, the pressure decreases on this side of the valve member 32 and the valve member 32 is moved by the pressure difference in a position in which the second passage opening 27 is closed and the first passage opening 28 is free.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP16183666.3A 2016-08-11 2016-08-11 Pompe a liquides epais Active EP3282124B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16183666.3A EP3282124B1 (fr) 2016-08-11 2016-08-11 Pompe a liquides epais

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16183666.3A EP3282124B1 (fr) 2016-08-11 2016-08-11 Pompe a liquides epais

Publications (2)

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EP3282124A1 true EP3282124A1 (fr) 2018-02-14
EP3282124B1 EP3282124B1 (fr) 2023-08-02

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018126374A1 (de) 2018-10-23 2020-04-23 Schwing Gmbh Kontinuierlich fördernde Kolbenpumpe
WO2020120234A1 (fr) 2018-12-14 2020-06-18 Schwing Gmbh Pompe à piston et procédé pour faire fonctionner une pompe à piston
DE102018132309A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
DE102018132270A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
WO2020260443A1 (fr) 2019-06-27 2020-12-30 Putzmeister Engineering Gmbh Pompe à liquide épais et procédé de circulation d'un liquide épais

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653614A1 (de) * 1967-06-10 1971-08-19 Smith Bobbie Ray Schlammpumpe
DE2010112A1 (de) * 1970-03-04 1971-12-30 Putzmeister GmbH, Chur (Schweiz) Betonpumpe mit stoßfreier Förderung
US3659970A (en) * 1969-08-14 1972-05-02 Philip W Mcelroy Concrete pump
US4718826A (en) * 1985-12-23 1988-01-12 Simmer Richard C Mobile pumping apparatus for abrasive slurries
EP2387667B1 (fr) 2009-01-16 2013-03-20 Friedrich Schwing Procédé de transport de produits pâteux, et dispositif de pompage pour le transport de produits pâteux
CN103821688A (zh) * 2014-01-20 2014-05-28 三一汽车制造有限公司 一种泵送机构、泵送控制方法及混凝土泵送设备
US8827657B1 (en) 2014-01-15 2014-09-09 Francis Wayne Priddy Concrete pump system and method

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653614A1 (de) * 1967-06-10 1971-08-19 Smith Bobbie Ray Schlammpumpe
US3659970A (en) * 1969-08-14 1972-05-02 Philip W Mcelroy Concrete pump
DE2010112A1 (de) * 1970-03-04 1971-12-30 Putzmeister GmbH, Chur (Schweiz) Betonpumpe mit stoßfreier Förderung
US4718826A (en) * 1985-12-23 1988-01-12 Simmer Richard C Mobile pumping apparatus for abrasive slurries
EP2387667B1 (fr) 2009-01-16 2013-03-20 Friedrich Schwing Procédé de transport de produits pâteux, et dispositif de pompage pour le transport de produits pâteux
US8827657B1 (en) 2014-01-15 2014-09-09 Francis Wayne Priddy Concrete pump system and method
CN103821688A (zh) * 2014-01-20 2014-05-28 三一汽车制造有限公司 一种泵送机构、泵送控制方法及混凝土泵送设备

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018126374A1 (de) 2018-10-23 2020-04-23 Schwing Gmbh Kontinuierlich fördernde Kolbenpumpe
WO2020083605A1 (fr) 2018-10-23 2020-04-30 Schwing Gmbh Pompe à piston à transport continu
WO2020120234A1 (fr) 2018-12-14 2020-06-18 Schwing Gmbh Pompe à piston et procédé pour faire fonctionner une pompe à piston
DE102018132309A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
DE102018132270A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
US11891987B2 (en) 2018-12-14 2024-02-06 Schwing Gmbh Piston pump and method for operating a piston pump
WO2020260443A1 (fr) 2019-06-27 2020-12-30 Putzmeister Engineering Gmbh Pompe à liquide épais et procédé de circulation d'un liquide épais
DE102019117356A1 (de) * 2019-06-27 2020-12-31 Putzmeister Engineering Gmbh Dickstoffpumpe und Verfahren zum Fördern eines Dickstoffs

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