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WO2025165236A1 - Amortissement de pulsation de pompe - Google Patents

Amortissement de pulsation de pompe

Info

Publication number
WO2025165236A1
WO2025165236A1 PCT/NO2025/050009 NO2025050009W WO2025165236A1 WO 2025165236 A1 WO2025165236 A1 WO 2025165236A1 NO 2025050009 W NO2025050009 W NO 2025050009W WO 2025165236 A1 WO2025165236 A1 WO 2025165236A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
accumulator
working chamber
controlled valve
chamber
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.)
Pending
Application number
PCT/NO2025/050009
Other languages
English (en)
Inventor
Roman Jansen
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.)
Mhwirth GmbH
Mhwirth AS
Original Assignee
Mhwirth GmbH
Mhwirth AS
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 Mhwirth GmbH, Mhwirth AS filed Critical Mhwirth GmbH
Publication of WO2025165236A1 publication Critical patent/WO2025165236A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • 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
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive

Definitions

  • the present invention relates to pumps, particularly to heavy duty fluid pumps for large scale applications.
  • Reciprocating pumps are used in a variety of applications and for a wide range of purposes.
  • One such application is the conveyance of fluids in large-scale plants for earth drilling or mining.
  • Some examples of such pumps and their application are described in earlier patent publications US 2021/0231 113 A1 ; US 8,920,146 B2; US 2015/0260178 A1 ; WO 2020/193151 A1 ; and US 9,695,808 B2.
  • the type of pumps therein described are commonly used, for example, to pump mining slurry or drilling mud, i.e., fluid mixtures with demanding properties, for example, having solid particles suspended therein.
  • Such pumps for the applications mentioned above or other fields of use often have demanding operating conditions, which may include requirements for high output pressures or flow rates and the need to handle challenging media, for example, abrasive liquids and/or liquids containing solid particles.
  • Many such pumps are used in mobile or remote installations, for example at mining locations, and have high demands for operational reliability and low maintenance requirements.
  • pulsation damping in such pumping systems is known in different variants and are typically used in pipe systems in which pressure oscillations or pressure surges can arise, for example due to the operation of a pump, an actuator, or due to other flow influences.
  • pressure oscillations or pressure surges can arise, for example due to the operation of a pump, an actuator, or due to other flow influences.
  • irregular volume flows due to the oscillating movement of the pump pistons, irregular volume flows, as inherent to the functional principle, may arise at the intake and/or at the outlet of the pump.
  • Such irregular volume flows can lead to pressure pulsations, which have negative effects on the functionality of the pump and can lead to undesired oscillations in the adjacent pipe system.
  • pulsations In the intake part of the pump, these pulsations can cause cavitation, which on the one hand can lead to a reduction in the efficiency of the pump and on the other hand to damage to the pump.
  • Known pulsation dampers are usually arranged in inlet-side and/or outlet-side pipes of the pump and usually comprise a compensation or reservoir chamber that is filled with a compressible gas volume and is fluidically in operative connection with the fluid to be conveyed. Such dampers act in such a manner that a pressure increase is compensated by a compression of the gas volume located in the reservoir chamber. Since the gas has high compressibility compared to the pumped fluid, pressure pulsations can be reduced.
  • a pump for pumping mud or slurry comprising: a housing with a working chamber connected to a fluid inlet line and a fluid outlet line, a reciprocable pumping member operatively arranged in the working chamber, an accumulator fluidly connected to the working chamber via a damper conduit, a controlled valve arranged in the damper conduit.
  • a method for dampening of pressure fluctuations in a pump comprising: operating the pump to pump a mud or a slurry; providing one or more accumulators fluidly connected to a working chamber of the pump via one or more damper conduit(s); operating a controlled valve arranged in the damper conduit to selectively connect and disconnect the one or more accumulators to and from working chamber, and dampening, by the one or more accumulators, pressure fluctuations in the working chamber which have a frequency higher than a reciprocating speed of the pump.
  • Fig. 1 shows a piston diaphragm pump known from the prior art.
  • Fig. 2 shows a piston diaphragm pump according to an example.
  • Fig. 3 shows a piston diaphragm pump according to an example.
  • Fig. 4 shows a piston diaphragm pump according to an example.
  • Fig. 5 shows a piston diaphragm pump according to an example.
  • Fig. 6 shows a piston diaphragm pump according to an example.
  • Figs 7 and 8 illustrate a simulated pressure profile during operation of a pump with and without a damping arrangement.
  • Fig. 1 shows the basic structure of a piston diaphragm pump known from the prior art (see, for example, the abovementioned US 2021/0231 113 A1 and WO 2020/193151 A1 ).
  • the pump has a working chamber 2,4 arranged in a housing 5, inlet and outlet lines (pipes) 6,13 connected thereto, and a pump piston 1 operatively arranged in the housing 1 .
  • the piston diaphragm pump has a pump piston 1 (which can be a conventional piston or an equivalent drive element, such as a plunger), which is driven by a drive unit (not shown) in an oscillating motion and moves within a pump cylinder back and forth.
  • the drive unit may, for example, be a crank system.
  • the piston 1 displaces a volume of fluid in an intermediate fluid chamber 2, usually a hydraulic oil.
  • the intermediate fluid chamber 2 is delimited by the piston 1 , the pump housing 5 (which in this example includes the pump cylinder), and a flexible separation membrane 3,3a.
  • the intermediate fluid chamber 2 is operatively connected to a pump chamber 4, which contains a medium to be pumped 9,16.
  • the medium 9,16 may, for example, be a mud or a slurry.
  • the movement of the piston 1 thus causes a back- and-forth displacement of the separation membrane 3,3a, and thereby an increase or reduction in the volume of the pump chamber 4, wherein the separation membrane 3,3a move between its outer positions, indicated here by reference numerals 3 and 3a.
  • the end stroke position 3 illustrates the membrane at the end of a suction stroke / start of a discharge stroke
  • the end stroke position 3a (dashed) illustrates the membrane at the end of a discharge stroke / start of a suction stroke.
  • the pump may be a conventional piston pump and not a piston membrane pump as shown in Fig. 1 .
  • the membrane 3,3a is not used, the piston 1 operates directly on the medium 9,16, and the entire working chamber 2,4 makes up the pump chamber 4.
  • the medium 9,16 can be drawn into the pump chamber 4 from the inlet line 6, in which a suction valve 7 formed as a non-return valve is located.
  • the inlet line 6 of the pump additionally contains a reservoir 8, also called a pressure vessel, which is partly filled with the medium 9,16, i.e. a fluid to be conveyed, and in the upper part of which there is a gas 10 under pressure, for example compressed air.
  • the reservoir 8 is connected to a fluid source 11 .
  • the fluid source 11 may, for example, be a pit or a pipe supply of fluid to be pumped by the pump.
  • a feed pump (not shown) can be provided upstream the inlet line 6 to provide a suitable suction pressure in the inlet line 6.
  • the fill level in the reservoir 8 is regulated by the pressure of the gas 10.
  • the pressure of the gas 10 can be varied, for example via a control valve 12, in such a manner that a predetermined fill level in the reservoir 8 is regulated.
  • the reservoir 8 can be connected to a gas source via a pneumatic line and the control valve 12.
  • the pump chamber 4 is in this example connected to an additional reservoir 15 via the outlet line 13, in which a pressure valve 14 formed as a non-return valve is located.
  • a pressure valve 14 formed as a non-return valve is located.
  • the medium 9,16 to be pumped is likewise located in the lower part of the discharge-side reservoir 15, while a gas or air volume 17 that is under pressure is located thereabove.
  • the fill level of the reservoir 15 can be regulated via a control valve 18 and a gas source that is connected thereto. The volume flow generated by the pump can then be supplied to the intended receiver via a discharge line 19.
  • the pump comprises a damper conduit 37 connected to the intermediate fluid chamber 2.
  • the damper conduit 37 fluidly connects the intermediate fluid chamber 2 with an accumulator 44, via a throttle 43.
  • the accumulator 44 has two chambers: a first chamber 45 which is fluidly connected with the damper conduit 37 (via the throttle 43), and a second chamber 46 which comprises a compressible medium such as air or nitrogen.
  • the compressible medium will be assumed to be a gas
  • the fluid in the chamber 45 will be assumed to be an oil of the same type as in the intermediate chamber 2.
  • the chambers 45 and 46 are separated by a flexible membrane 47, however this is optional and accumulators without such separation membranes may alternatively be used.
  • the accumulator 44 may, for example, be a bladder accumulator.
  • the damper conduit 37 and accumulator 44 are in this example separate from the inlet and outlet lines 6,13.
  • the accumulator 44 is fluidly connected to the intermediate fluid chamber 3 via the housing 5.
  • the amount of gas in the second chamber 46 may be chosen such that pressure characteristics and dynamic response of the accumulator 44 during the suction and/or discharge stroke of the pump are suitable for damping out pressure fluctuations efficiently. Particularly, this may include choosing the amount of gas so that the gas pressure relates to the suction pressure and/or the discharge pressure of the pump, optionally also to the properties of the throttle 43 and the intermediate fluid, such that the accumulator 44 obtains good pulsation-dampening properties. Selecting the properties of these elements will be a routine design matter when the operating conditions of the pump is known.
  • Pulsation effects may occur both during the suction stroke and the delivery stroke of the pump. As will be known to the skilled reader, the suction stroke and the discharge stroke may be carried out at significantly different pressures.
  • An additional hydraulic accumulator 39 may, for better performance, be connected to the damper conduit 37.
  • the additional accumulator 39 is fluidly connected to the intermediate chamber via the damper conduit 37 and, in this example, a second throttle 38.
  • the additional accumulator 39 has a gas chamber 41 and oil chamber 40 separated by a flexible membrane 42, similarly as the arrangement of accumulator 44.
  • the gas volume in chamber 41 and the gas volume in chamber 46 can in this example be chosen so that accumulator 44 provides efficient dampening of pressure fluctuations during the discharge stroke of the pump, and the accumulator 39 provides efficient dampening of pressure fluctuations during the suction stroke.
  • the size of the accumulators 44,39, the flow resistance of the throttles 43,38 (if used), and other design variables may also be configured according to the expected operating conditions of the pump, e.g. the expected pressure levels, the type of fluid to be pumped, the fluid used in the intermediate chamber 2, etc.
  • One or both of the throttles 38,43 may have adjustable flow resistance in order that the flow resistance can be varied, for example if the pump is required to operate under varying external operating conditions.
  • such pressure pulsations may only be prevalent (to a problematic degree) during either the suction stroke or the discharge stroke.
  • a solution with only one accumulator may be sufficient.
  • one accumulator can be designed such as to provide satisfactory dampening of pulsation during both the suction and discharge strokes.
  • Fig. 2 illustrates a pump similarly as described above.
  • a controlled valve 48,49 is arranged in the damper conduit 37, such that the controlled valve 48,49 regulates the fluid connection between the respective accumulator 39,44 and the working chamber 2,4.
  • the illustrated pump is a piston membrane pump and the damper conduit 37 is connected to the intermediate fluid chamber 2.
  • Each controlled valve 48,49 has an open position in which fluid communication between the working chamber 2,4 and the accumulators 39,44 is permitted, and a closed position in which fluid communication between the working chamber 2,4 and the accumulators 39,44 is prevented.
  • the first controlled valve 48 is configured to permit fluid communication between the working chamber 2,4 and the first accumulator 39 during a pump suction stroke and prevent fluid communication between the working chamber 2,4 and the first accumulator 39 during a pump discharge stroke.
  • the second controlled valve 49 is configured to permit fluid communication between the working chamber 2,4 and the second accumulator 44 during the pump discharge stroke and prevent fluid communication between the working chamber 2,4 and the second accumulator 44 during the pump suction stroke.
  • the first accumulator 39 is configured to dampen pressure fluctuations at a first pressure level corresponding to a design intake (suction) pressure for the pump
  • the second accumulator 44 is configured to dampen pressure fluctuations at a second pressure level corresponding to a design discharge pressure for the pump.
  • Figs 7 and 8 illustrate a simulated sequence of several pump cycles having no pulsation damping (Fig. 7) compared to the pump having a pulsation damping system as described above active (Fig. 8).
  • the plots illustrate the pressure in the working chamber 2,4 against time.
  • the first pressure level i.e. the design suction (intake) pressure
  • the second pressure level i.e. the design discharge pressure
  • PD design discharge pressure
  • the damper conduit 37 may comprise a throttle 38,43 to enhance the damping effect.
  • the controlled valve(s) 48,49 may have a throttle incorporated therein, for example by means of a restriction in the flow area through the valve(s) being incorporated in the valve design.
  • the controlled valve(s) 48,49 may be operated via an external controller.
  • the valve timing may, for example, be set based on a measured piston position or crank position.
  • the controlled valves, here indicated with reference numerals 50,53 are configured to open and close in response to a pressure in the damper conduit 37, the working chamber 2,4 and/or the intermediate chamber 2.
  • the pressure in the working chamber 2,4 and the damper conduit 37 is used to achieve the desired switching behavior via hydraulically pilot-controlled valves.
  • the accumulators 39,44 can be connected to or sealed off from the intermediate fluid chamber 2 via the hydraulically pilot-controlled valves 50 and 53.
  • the necessary switching pressure can, for example, be regulated via pressure control valves 56,57 and an associated pressure generating unit 58 or equivalent supply.
  • the pressure control valve 57 determines at what pressure the accumulator 44 is connected to the working chamber 2,4 via valve 53 in order to reduce the pulsations during the pump delivery stroke. When the pressure drops below the set pressure of the pressure control valve 57 at the end of the delivery stroke, valve 53 closes and the accumulator 44 is decoupled from the working chamber 2,4.
  • valve 50 switches to the open position and connects the working chamber 2,4 the accumulator 39, so that pulsation damping is provided during the suction stroke of the pump.
  • valve 50 closes again and decouples the accumulator 39 from the working chamber 2,4.
  • an electronic controller 62 can be operatively connected to the controlled valves 50,53 and configured to control the operation of the controlled valves 50,53 in response to a measured pressure in the damper conduit 37 and/or the working chamber 2,4. This may allow adjustment of the switching points of the two valves 50 and 53 to the requirements of the pump or to changing suction and delivery pressures. The switching points may also be set dynamically.
  • Fig. 5 illustrates electrically pilot-controlled pressure control valves 59 and 60 for this purpose.
  • the pressure in the working chamber 2,4 or damper conduit 37 may be determined via a pressure sensor 61 and processed by an electronic control unit (PLC) as part of the electronic controller 62, so that the electronic controller 62 can send electrical control signals to the electrical pressure control valves 59 and 60.
  • PLC electronice control unit
  • the switching points of the valves 50 and 53 can be adjusted so that one accumulator 39,44 is connected and active during the suction stroke and the other bladder accumulator 39,44 is connected and active during the delivery stroke.
  • the suction and delivery pressure can each be sensed via a separate pressure sensor, which is connected, for example, to the fluid inlet line 6 or to the fluid outlet line 13.
  • the accumulator(s) 39,44 may comprise a gas-filled chamber 41 ,46 and an oil-filled chamber 40,45 separated by a displacement body 42, 47, 42’, 47’.
  • the displacement body 42, 47, 42’, 47’ may be provided as a displaceable wall or as a displaceable diaphragm or membrane.
  • the displacement body may be a displaceable piston 42’, 47’ arranged in a cylinder.
  • the gas-filled chamber(s) 41 ,46 may be fluidly connected to a separate gas source, illustrated as 72,73 in Fig. 6 but also applicable to the examples shown in Figs 1 -5, via a control valve 70,71 so as to regulate a gas pressure prevailing in the gas-filled chamber 41 ,46.
  • the pulsation damping setup described above may advantageously be combined with a reservoir (8,15) arranged in at least one of the fluid inlet line 6 or in the fluid outlet line 13.
  • the teaching provided herein can provide more flexibility in the choice of accumulator(s) design in a pulsation damping system for a pump, and/or longer operational lifetime of the accumulator(s).
  • a need for the accumulator(s) 39,44 to handle dynamics and large variations in fluid pressure is reduced.
  • problems associated with excessive wear of a flexible membrane 42,47 or a piston 42’47’ can be reduced, in that the volume changes in the accumulator(s) 39,44 are reduced. In this manner, repeated excessive stretching of a membrane 42,47, or “bottoming out” of a piston 42’, 47’, can be prevented.
  • Solutions described herein may, for example, be particularly suitable for pumps which convey fluids having solids content or fluids whose characteristics vary or are challenging to predict.
  • fluids may include drilling muds, slurries, or discharge water from mining operations.
  • valves 7,14 are usually passive one-way valves, however may optionally be of a different type, for example actively controlled valves.
  • a pump according to the examples and embodiments described herein may also be implemented without one or both reservoirs 8,15.
  • the examples described here relate to a piston membrane pump
  • the examples and embodiments described herein may also be implemented as a regular piston pump, in which the piston 1 operates directly on the medium 9,16, and the entire working chamber 2,4 makes up the pump chamber 4.
  • the piston 1 may have a diameter larger than 300 mm, for example, larger than 400 mm, for example, larger than 500 mm, for example, larger than 600 mm.
  • the membrane 3,3a may have a diameter larger than 500 mm, for example, larger than 600 mm, for example, larger than 750 mm, for example, larger than 1000 mm, and/or an area larger than 0.2 m 2 , for example, larger than 0.5 m 2 .
  • the pump may have a design output of more than 250 kW, for example, more than 500 kW, for example, more than 1000 kW pumping power.
  • the pump may be a pump for pumping mining slurry.
  • the maximum design outlet pressure of the pump may, for example, be more than 30 bar (3000 kPa), for example, more than 75 bar (7500 kPa), for example, more than 100 bar (10,000 kPa).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe pour pomper de la boue ou une suspension comprenant : un boîtier (5) avec une chambre de travail (2, 4) raccordée à des conduites d'entrée (6) et de sortie (6, 13) de fluide, un élément de pompage à mouvement alternatif (1), un accumulateur (39, 44) en communication fluidique avec la chambre de travail (2, 4) par l'intermédiaire d'un conduit amortisseur (37), une vanne commandée (48, 49, 50, 53) disposée dans le conduit amortisseur (37). L'invention concerne en outre un procédé d'amortissement de fluctuations de pression dans une pompe, consistant à : actionner la pompe pour pomper une boue ou une suspension ; fournir un ou plusieurs accumulateurs (39, 44) en communication fluidique avec une chambre de travail (2, 4) de la pompe ; actionner une vanne commandée (48, 49, 50, 53) pour raccorder et isoler le ou les accumulateurs (39, 44) vers et depuis la chambre de travail (2, 4), et amortir les fluctuations de pression dans la chambre de travail (2, 4) qui ont une fréquence supérieure à une vitesse de va-et-vient de la pompe.
PCT/NO2025/050009 2024-02-04 2025-01-21 Amortissement de pulsation de pompe Pending WO2025165236A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20240099 2024-02-04
NO20240099 2024-02-04

Publications (1)

Publication Number Publication Date
WO2025165236A1 true WO2025165236A1 (fr) 2025-08-07

Family

ID=94478450

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NO2025/050009 Pending WO2025165236A1 (fr) 2024-02-04 2025-01-21 Amortissement de pulsation de pompe

Country Status (1)

Country Link
WO (1) WO2025165236A1 (fr)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB204695A (en) * 1922-09-19 1923-12-20 Henri Corblin Improvements in diaphragm compressors
US8920146B2 (en) 2005-04-12 2014-12-30 Mhwirth Gmbh Pump system
US20150260178A1 (en) 2012-10-10 2015-09-17 Mhwirth Gmbh Piston membrane pump
EP3059458A1 (fr) * 2015-02-23 2016-08-24 Reinhard Gruber Procede et dispositif destines au fonctionnement d'une installation a haute pression hydraulique
US9695808B2 (en) 2011-09-30 2017-07-04 Mhwirth Gmbh Positive displacement pump and operating method thereof
WO2018091306A1 (fr) * 2016-11-15 2018-05-24 Mhwirth Gmbh Procédé permettant de faire fonctionner une pompe à piston et pompe à piston
DE102018110847A1 (de) * 2018-05-07 2019-11-07 Mhwirth Gmbh Pulsationsdämpfungssystem
WO2020193151A1 (fr) 2019-03-25 2020-10-01 Mhwirth Gmbh Pompe et système et procédés associés
US20210231113A1 (en) 2018-05-07 2021-07-29 Mhwirth Gmbh Pulsation damping system

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB204695A (en) * 1922-09-19 1923-12-20 Henri Corblin Improvements in diaphragm compressors
US8920146B2 (en) 2005-04-12 2014-12-30 Mhwirth Gmbh Pump system
US9695808B2 (en) 2011-09-30 2017-07-04 Mhwirth Gmbh Positive displacement pump and operating method thereof
US20150260178A1 (en) 2012-10-10 2015-09-17 Mhwirth Gmbh Piston membrane pump
EP3059458A1 (fr) * 2015-02-23 2016-08-24 Reinhard Gruber Procede et dispositif destines au fonctionnement d'une installation a haute pression hydraulique
WO2018091306A1 (fr) * 2016-11-15 2018-05-24 Mhwirth Gmbh Procédé permettant de faire fonctionner une pompe à piston et pompe à piston
DE102018110847A1 (de) * 2018-05-07 2019-11-07 Mhwirth Gmbh Pulsationsdämpfungssystem
US20210231113A1 (en) 2018-05-07 2021-07-29 Mhwirth Gmbh Pulsation damping system
WO2020193151A1 (fr) 2019-03-25 2020-10-01 Mhwirth Gmbh Pompe et système et procédés associés

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