WO2012025422A2 - Pompe à membrane et procédé pour ajuster une telle pompe - Google Patents

Pompe à membrane et procédé pour ajuster une telle pompe Download PDF

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Publication number
WO2012025422A2
WO2012025422A2 PCT/EP2011/064044 EP2011064044W WO2012025422A2 WO 2012025422 A2 WO2012025422 A2 WO 2012025422A2 EP 2011064044 W EP2011064044 W EP 2011064044W WO 2012025422 A2 WO2012025422 A2 WO 2012025422A2
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
membrane
spring element
working fluid
hydraulic
Prior art date
Application number
PCT/EP2011/064044
Other languages
German (de)
English (en)
Other versions
WO2012025422A3 (fr
Inventor
Horst Fritsch
Original Assignee
Prominent Dosiertechnik 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 Prominent Dosiertechnik Gmbh filed Critical Prominent Dosiertechnik Gmbh
Priority to RU2013113175/06A priority Critical patent/RU2013113175A/ru
Priority to BR112013004111A priority patent/BR112013004111A2/pt
Priority to US13/818,114 priority patent/US20150004005A9/en
Priority to EP11745538.6A priority patent/EP2609331A2/fr
Priority to CN201180040470.5A priority patent/CN103210216B/zh
Priority to JP2013525246A priority patent/JP2013536363A/ja
Priority to CA2808373A priority patent/CA2808373C/fr
Priority to KR1020137006052A priority patent/KR20130137151A/ko
Publication of WO2012025422A2 publication Critical patent/WO2012025422A2/fr
Publication of WO2012025422A3 publication Critical patent/WO2012025422A3/fr

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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0081—Special features systems, control, safety measures
    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/033—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows having fluid drive
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • 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

Definitions

  • the present invention relates to a diaphragm pump and a method for adjusting a diaphragm pump.
  • Diaphragm pumps generally have a delivery chamber which is separated from a hydraulic chamber by a membrane, wherein the delivery chamber is in each case connected to a suction connection and a pressure connection.
  • the filled with working fluid hydraulic chamber can then be acted upon with a pulsating working fluid pressure.
  • the pulsating working fluid pressure causes a pulsating movement of the diaphragm, whereby the volume of the delivery chamber is periodically larger and smaller. This makes it possible, via the suction connection, which is connected to the delivery chamber with a corresponding check valve, to draw in the delivery medium when the volume of the delivery chamber is increased, and via the pressure connection, which is likewise connected to the delivery chamber by a corresponding non-return valve. Relieve under pressure when the volume of the pumping chamber is reduced.
  • a working fluid usually a hydraulic oil is used.
  • suitable liquids such as e.g. Water can be used with a water-soluble mineral additive.
  • the medium to be conveyed is separated from the drive, whereby on the one hand the drive from harmful influences of the pumped medium is shielded and on the other hand, the pumped medium from harmful influences of the drive, e.g. Contamination is shielded.
  • the pulsating working fluid pressure is often provided by means of a movable piston in contact with the working fluid.
  • the piston is reciprocated, for example, in a hollow cylindrical element, whereby the volume of the hydraulic space is reduced and increased, which leads to an increase and decrease in the pressure in the hydraulic chamber and in consequence to a movement of the membrane.
  • a small amount of the working fluid is lost by the narrow remaining gap between the piston on the one hand and hollow cylindrical element on the other hand, thereby gradually working - Amount of liquid is reduced in the hydraulic space. This has the consequence that the pressure stroke is no longer completely carried out by the membrane, since not enough working fluid for the pressure movement of the membrane is available.
  • DE 1 034 030 has already been proposed to connect the hydraulic chamber with the interposition of a valve, a so-called leak-relief valve, with a working fluid reservoir.
  • working fluid can be replenished in the hydraulic chamber through this leak-relief valve.
  • the leak-relief valve generally has a closing body which can be moved back and forth between a closed position in which the valve passage is closed and an open position in which the valve passage is open, for example in the form of a closing ball.
  • This closing body is biased in the closed position by means of a pressure element, for example a spring.
  • This pressure element is designed such that only when the pressure in the hydraulic chamber is less than a set pressure p L , the closing body moves in the direction of the open position.
  • the diaphragms are often provided with a spring element which is designed to exert a force on the diaphragm so that the membrane is biased in the direction of the hydraulic space.
  • the spring element supports the movement of the diaphragm in the direction of its suction stroke.
  • the requirement is placed on the diaphragm pumps that they survive over a predetermined period, usually 5000 to 10,000 operating hours, without maintenance and repair.
  • the diaphragm will move in the direction of pressure stroke of the piston movement with the result that before the piston has completed the pressure stroke, it comes to rest on the walls of the pumping chamber and to the the valve leading holes is perforated.
  • the leak-relief valve is dimensioned so that it only opens when the membrane comes to rest on the hydraulic-side dome at the end of the suction stroke. This creates a temporary negative pressure, whereby the spring-loaded leak-relief valve opens and the hydraulic chamber is exactly complemented by the lack of working fluid.
  • the risk of perforation of the membrane always arises when the leak-relief valve opens before the membrane has reached its hydraulic limit position. To avoid this, the pressure in the hydraulic chamber during the suction stroke may only be lower than the set pressure of the leak-relief valve when the diaphragm is against the calotte.
  • the force F acting on the membrane due to the pressure difference is proportional to the square of the diameter D of the membrane, at the same time the area subjected to bending and shear at the clamping edges of the membrane only increases in proportion to the diameter, the shear stress increases in proportion to the membrane diameter D, what then Especially in large diaphragm pumps to overuse the membrane and ultimately lead to a rupture of the membrane before the expiry of the predicted runtime.
  • the spring force F increases in proportion to D 2 , a pressure of at least 1 bar requires very strong and thus expensive springs for large diameters of the membrane. For example, with a membrane diameter of 100 mm, the spring force is 750 N, while with a membrane diameter of 400 mm, it is already 12000 N.
  • a diaphragm pump with a delivery chamber, a pressure and a suction port, wherein the pressure and suction ports are connected to the pumping chamber, a hydraulic chamber, wherein the pumping chamber and hydraulic chamber are separated from each other by a membrane, wherein the A hydraulic fluid space which can be filled with a working fluid can be acted upon by a pulsating working fluid pressure, whereby the diaphragm is moved between a first position, in which the delivery space has a smaller volume, and a second position, in which the delivery space has a larger volume, and the hydraulic space a leak relief valve is connected to a working fluid reservoir, the diaphragm having a spring element which is designed such that it exerts a first predetermined force on the diaphragm in the direction of the second position.
  • the spring element can be exchanged for another spring element, which is designed such that it exerts a second predetermined force on the membrane in the direction of the second position, or that the force exerted by the spring element on the membrane in the direction of the second position, is adjustable.
  • the spring force can be adapted to the existing conditions of use, such as the static pressure at the suction port. If, for example, the desired application ensures that the static pressure at the suction connection itself is already 1 bar and a suction valve which connects the suction connection to the delivery chamber is designed such that it opens at a pressure difference of more than 0.3 bar the pressure in the delivery chamber does not fall below 0.7 bar. Consequently, the spring element only has to exert a smaller force on the membrane, which in turn increases the life of the membrane. According to the invention thus the spring force of the spring element can be adapted to the local conditions.
  • the spring element can be demounted from the membrane.
  • the spring element can be exchanged without the membrane having to be replaced.
  • the membrane itself has corresponding elastic properties.
  • a hydraulic body and a membrane body are provided, between which the membrane is clamped, so that the hydraulic space in the hydraulic body and the delivery space in the membrane body is arranged, wherein the hydraulic body arranged in the direction of force of the spring element closable opening has, through which the spring element replaced or its spring constant can be adjusted.
  • the drive piston is arranged in the direction of force behind the spring element, so that an exchange or adjustment of the spring element is possible only by a very expensive disassembly of the pump.
  • the pulsating working fluid is supplied via a channel into the hydraulic chamber, wherein the channel is aligned at least in the region of its confluence with the hydraulic chamber such that it encloses an angle ⁇ with the force direction of the spring element. which is greater than 0 °, preferably greater than 45 °, more preferably greater than 70 ° and most preferably about 90 °.
  • the object mentioned at the outset is achieved in that the step is provided that the spring constant is selected or adjusted such that the pressure p F v applied to the working fluid by the spring element applies : p w > p A - p so where p A is the atmospheric pressure and pso is the static pressure at the suction port.
  • the pressure p F v de ra rt applied to the working fluid by the spring element is selected
  • the force applied by the spring element to the working fluid force can be chosen significantly smaller than is usually the case in the prior art, since the invention is considered for the first time that at the suction connection static pressure is applied, so that in the pumping chamber in the rule no lower pressure can be present.
  • the suction connection is connected via a check valve to the delivery chamber, which likewise has a corresponding spring element, so that the check valve opens only at a pressure difference Ap S v between the pressure at the suction connection and the pressure in the delivery chamber
  • the pressure p F v applied to the working fluid by the spring element is set such that: p A > p w > p A -p so + ⁇ 8 ⁇ .
  • the hydraulic chamber is connected to a working fluid reservoir via a leak-relief valve, the leak-relief valve having a closing body which can be moved back and forth between a closed position in which the valve passage is closed and an open position in which the valve passage is open Help a pressure element is held in the closed position, wherein the pressure element is designed such that when the pressure in the hydraulic chamber is smaller than a set pressure p L , the closing body moves in the direction of the open position.
  • the pressure element of the leak-relief valve and the spring element of the membrane is designed and arranged such that at any time the sum of the pressure p H in the hydraulic chamber and the applied by the spring element to the working fluid pressure p F v greater than the set pressure
  • the mass of the closing body is so large that the closing body at not more than 1 ms lasting pressure drop to 0 bar due to a pressure surge in the hydraulic space by not more than 0.2 mm, preferably not moved more than 0, 1 mm in the direction of the open position.
  • Figure 1 is a schematic sectional view of a diaphragm pump head according to the invention
  • Figure 2 is a schematic diagram of the pressure in the hydraulic chamber over time
  • FIG. 1 shows a detail of a diaphragm pump head in a sectional view.
  • the membrane pump has a membrane 1, which is clamped between a hydraulic body 23 and a membrane body 22.
  • the membrane divides the dome-shaped cavity in a delivery chamber 9 and a hydraulic chamber 8.
  • the membrane 1 is connected via a screw with a bolt which is pulled by means of a spring element 10 in the hydraulic body.
  • the spring element 10 exerts a force in the direction of the hydraulic chamber 8 on the membrane 1.
  • the delivery space 9 is connected to a suction port (not shown) and a pressure port (not shown) via respective valves.
  • the membrane 1 can be acted upon via the channel 24 with an oscillating hydraulic pressure. If the pressure in the channel 24 increases, the membrane 1 in FIG. 1 is moved to the left, i. the delivery chamber 9 is reduced. Any fluid that may be present is then expelled from the pressure port via the valve. Wrd then reduces the pressure in the channel 24, the spring element 10 will ensure that the membrane is pulled back into the hydraulic chamber. The pressure in the delivery chamber 9 will drop until it is less than the static pressure applied to the suction connection. Then, conveying medium is fed into the delivery chamber 9 via the suction connection.
  • pumped medium is therefore periodically drawn from the suction port and discharged via the pressure port at a higher pressure.
  • the membrane is held between the clamping edges 1 1, 12. Due to the spring element 10 may lead to a bulging of the membrane 1.
  • a leak-relief valve 6 is provided, via which the hydraulic chamber 8 is connected to a working fluid reservoir.
  • This leak-relief valve 6 has a small ball 16 which is pressed into a valve seat by means of a spring 17.
  • a set pressure p L is set.
  • an opening is provided in the hydraulic element 23, which can be closed by means of the cap 21. If the cap 21 is removed from the hydraulic body, then the spring element 10 can be accessed. As a result, the spring element can be easily replaced or readjusted to ensure that as little force as possible is applied to the membrane 1 via the spring element 10, but at the same time it is ensured that the leak-relief valve 6 opens only in case of need.
  • FIG. 2 graphically plots the pressure in the hydraulic chamber during the suction stroke over time. At the beginning of the suction stroke, the pressure in the hydraulic chamber corresponds approximately to the pressure with which the pump discharges the fluid from the pressure port. This pressure is significantly higher than the static pressure of the suction line. It is understood that the pressure in the hydraulic chamber is additionally determined by the return spring 10.
  • the suction stroke begins when the piston is moved back to generate the pulsating working fluid pressure. This initially leads to the fact that the pressure in the hydraulic chamber slowly reduced and since the pressure in the pumping chamber is greater, the membrane will move to the right, ie in the direction of the hydraulic chamber. The pressure in the delivery chamber will slowly drop until it reaches the static pressure at the suction port p S o. If the pressure drops even further, the corresponding non-return valve, which connects the delivery chamber to the suction port, will open and delivery medium will flow in via the suction port. In the moment in which the pressure in the delivery chamber thus reaches the static pressure at the suction port, there is an abrupt change in the velocity of the fluid in the suction line.
  • This Joukowsky shock in the delivery room leads to a pressure surge in the hydraulic room, since the two rooms are connected via the membrane. The result triggered high-frequency rapidly decaying pressure oscillation can be ignored for the following consideration at first.
  • the known diaphragm pumps are therefore equipped with corresponding return springs 10, which ensure that in all cases the pressure in the hydraulic chamber is greater than the set pressure. Since the pressure in the pumping chamber can not become less than zero and the pressure in the working fluid reservoir is typically below atmospheric pressure (1 bar), the springs are chosen so that they can even at the end of the suction stroke, i. when the spring has pulled the diaphragm to its point of reversal in the hydraulic chamber, it is greater than 1 bar. This ensures that even in the worst case, no unplanned opening of the leak-relief valve occurs.
  • the force applied to the membrane by the return spring 10 can be adjusted, since the diaphragm pumps are usually used in an environment in which a static pressure p S o is present at the suction connection which is greater than zero. Depending on which pressure is applied here, therefore, the spring force can be reduced to prevent the membrane is pulled unnecessarily strong by the spring element 10 in the hydraulic chamber. The lower the set force, the longer the life of the membrane. In addition, then the drive of the pump can also be reduced because he now has to work against a lower spring force of the spring element 10.
  • the energy consumption of the membrane pump can thus be significantly reduced. If, at a later time, the diaphragm pump is to be adapted to a different static pressure on the suction line, only the spring element 10 has to be adjusted or replaced by another one.
  • the pressure may fall below the set pressure p L , so that the leak-relief valve opens.
  • the set pressure p L can be significantly larger than p min be selected as long as p L is smaller than an average pressure P m in the hydraulic chamber.
  • the invention is based on the finding that the pressure surge occurs only during a very short time interval Ats ⁇ 1 millisecond.
  • the mass of the closing body is inventively chosen so large that such a pressure surge only leads to a stroke of less than 0.2 mm or preferably less than 0, 1 mm.
  • a corresponding leak-relief valve is shown in FIG.
  • This leak-relief valve has a closing body 16 accommodated in a valve body 18, which has a closing element 20 which, in the closed position, closes a bore in the valve body 18, so that the line to the working-fluid reservoir 19 is separated from the hydraulic space 8.
  • the closing body is biased by means of a spring element 17 in the closed position, which is shown in Figure 3.
  • the pressure of the working fluid in the working fluid reservoir and thus also the pressure in the conduit 19 remain substantially constant.
  • the closing body 16 is moved in the position shown in Figure 3 upwards, so that a connection between the conduit 19 and the hydraulic chamber 8 is opened.
  • the mass of the closing body must be at least 17.5 g to prevent movement of the closing body by more than 0.1 mm. If the mass of the closing body chosen so large, so even a pressure surge to 0 bar, the closing body does not move so far that a significant amount of working fluid leaking into the hydraulic chamber.
  • the described method can be improved even if one considers that the pressure surge generally does not lead to a pressure reduction to 0 bar, but only to a minimum pressure p min .
  • the difference p L - p m between the set pressure p L and the minimum pressure p min due to the surge can be used, whereby the mass can be further reduced.
  • the set pressure p L can be increased, whereby the spring 17 can be made weaker, which simplifies the handling of the pump.

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

Abstract

L'invention concerne une pompe à membrane comprenant une chambre de refoulement, un raccord de pression et un raccord d'aspiration, lesdits raccords de pression et d'aspiration étant reliés à la chambre de refoulement, une chambre hydraulique, la chambre de refoulement et la chambre hydraulique étant séparées l'une de l'autre par une membrane. La chambre hydraulique peut être remplie avec un fluide de travail et être sollicitée par une pression de liquide de travail pulsée, ce qui a pour effet de faire passer la membrane, d'une première position dans laquelle la chambre de refoulement présente un volume plus réduit, à une seconde position dans laquelle ladite chambre de refoulement présente un volume plus important. La chambre hydraulique est reliée à un réservoir de liquide de travail par l'intermédiaire d'une soupape de complément de remplissage en cas de fuites. La membrane comporte un élément ressort présentant une première constante de ressort, ledit élément ressort étant conçu de sorte à exercer une première force prédéterminée sur la membrane en direction de la seconde position. L'invention vise à mettre au point une pompe à membrane et un procédé pour ajuster une telle pompe, qui permettent de réduire voire de résoudre entièrement les problèmes évoqués. A cet effet, selon l'invention, l'élément ressort peut être remplacé par un autre élément ressort, conçu de manière à exercer une seconde force prédéterminée sur la membrane en direction de la seconde position ou bien la force que l'élément ressort exerce sur la membrane en direction de la seconde position peut être ajustée.
PCT/EP2011/064044 2010-08-26 2011-08-15 Pompe à membrane et procédé pour ajuster une telle pompe WO2012025422A2 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
RU2013113175/06A RU2013113175A (ru) 2010-08-26 2011-08-15 Мембранный насос и способ его регулировки
BR112013004111A BR112013004111A2 (pt) 2010-08-26 2011-08-15 bomba de diafragma e processo para regular uma bomba de diafragma
US13/818,114 US20150004005A9 (en) 2010-08-26 2011-08-15 Membrane Pump and Method for Adjusting Same
EP11745538.6A EP2609331A2 (fr) 2010-08-26 2011-08-15 Pompe à membrane et procédé pour ajuster une telle pompe
CN201180040470.5A CN103210216B (zh) 2010-08-26 2011-08-15 隔膜泵及其调节方法
JP2013525246A JP2013536363A (ja) 2010-08-26 2011-08-15 膜ポンプ及びその調節方法
CA2808373A CA2808373C (fr) 2010-08-26 2011-08-15 Pompe a membrane et procede pour ajuster une telle pompe
KR1020137006052A KR20130137151A (ko) 2010-08-26 2011-08-15 멤브레인 펌프 및 이의 조절방법

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010039831.4 2010-08-26
DE102010039831.4A DE102010039831B4 (de) 2010-08-26 2010-08-26 Membranpumpe sowie Verfahren zum Einstellen einer solchen

Publications (2)

Publication Number Publication Date
WO2012025422A2 true WO2012025422A2 (fr) 2012-03-01
WO2012025422A3 WO2012025422A3 (fr) 2012-07-19

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ID=44630436

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/064044 WO2012025422A2 (fr) 2010-08-26 2011-08-15 Pompe à membrane et procédé pour ajuster une telle pompe

Country Status (10)

Country Link
US (1) US20150004005A9 (fr)
EP (1) EP2609331A2 (fr)
JP (1) JP2013536363A (fr)
KR (1) KR20130137151A (fr)
CN (1) CN103210216B (fr)
BR (1) BR112013004111A2 (fr)
CA (1) CA2808373C (fr)
DE (1) DE102010039831B4 (fr)
RU (1) RU2013113175A (fr)
WO (1) WO2012025422A2 (fr)

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CN103821701B (zh) * 2014-02-19 2016-04-06 杭州大潮石化设备有限公司 一种液压隔膜往复泵内置式可控补油结构
DE102014109801A1 (de) * 2014-07-11 2016-01-14 Prominent Gmbh Membranpumpe mit reduzierter Leckageergänzung im Überlastfall
ITUB20151971A1 (it) * 2015-07-06 2017-01-06 Seko Spa Pompa a membrana
DE102021106765A1 (de) * 2021-03-19 2022-09-22 Prominent Gmbh Membranpumpe zur Förderung eines Fluids
CN114856979A (zh) * 2022-04-25 2022-08-05 上海大学 一种用于污水处理的小流量防沉积液动隔膜泵及系统

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EP1291524A2 (fr) 2001-09-07 2003-03-12 LEWA Herbert Ott GmbH + Co. Pompe à membrane hydraulique avec membrane précontrainte

Also Published As

Publication number Publication date
CA2808373A1 (fr) 2012-03-01
DE102010039831B4 (de) 2022-02-03
JP2013536363A (ja) 2013-09-19
US20140147292A1 (en) 2014-05-29
US20150004005A9 (en) 2015-01-01
RU2013113175A (ru) 2014-10-10
CN103210216B (zh) 2016-05-11
CA2808373C (fr) 2018-03-06
CN103210216A (zh) 2013-07-17
EP2609331A2 (fr) 2013-07-03
DE102010039831A1 (de) 2012-03-01
KR20130137151A (ko) 2013-12-16
WO2012025422A3 (fr) 2012-07-19
BR112013004111A2 (pt) 2016-06-28

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