EP2404061B1 - Exzenterschneckenpumpe - Google Patents

Exzenterschneckenpumpe Download PDF

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Publication number
EP2404061B1
EP2404061B1 EP10711641.0A EP10711641A EP2404061B1 EP 2404061 B1 EP2404061 B1 EP 2404061B1 EP 10711641 A EP10711641 A EP 10711641A EP 2404061 B1 EP2404061 B1 EP 2404061B1
Authority
EP
European Patent Office
Prior art keywords
rotor
eccentric screw
screw pump
stator
section
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.)
Revoked
Application number
EP10711641.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2404061A2 (de
Inventor
Ralf Daunheimer
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
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Application filed by Individual filed Critical Individual
Priority to PL10711641T priority Critical patent/PL2404061T3/pl
Publication of EP2404061A2 publication Critical patent/EP2404061A2/de
Application granted granted Critical
Publication of EP2404061B1 publication Critical patent/EP2404061B1/de
Revoked 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • F04C2250/201—Geometry of the rotor conical shape

Definitions

  • the invention relates to an eccentric screw pump, in particular for pumping thick, highly viscous and abrasive media, with a longitudinal direction L, at least having a conical, helically wound, at least single-start rotor with a pitch h, with at least one eccentricity e and at least one cross section d, the is rotatably arranged in a single or multi-turn conical stator, in which a plurality of chambers, each with a volume, are formed between the rotor and the stator, which are used to convey the medium and in which the chambers between the stator and the rotor are delimited by a sealing line D. are.
  • the invention further relates to an eccentric screw pump, in particular for pumping thick, highly viscous and abrasive media, with a longitudinal direction L, at least having a step-shaped, helically wound, at least single-start rotor with a pitch h, with at least one eccentricity e and at least one cross section d, which is rotatably arranged in a single or multi-turn staircase-shaped stator.
  • Eccentric screw pumps are sufficiently known from the prior art.
  • B. in the DE 633 784 a Eccentric screw pump described in which two helical elements lie one inside the other and in which the outer element has one more screw thread or tooth than the inner element and in which the gradients of the screw turns of the two elements behave like the number of threads or teeth, but are constant, may be increasing or decreasing, at least three cooperating helical elements are provided, of which the middle one tooth more than the inside and one tooth less than the outside.
  • an eccentric screw pump with a conical screw shaft and a housing insert is known, which is characterized in that the eccentric screw shaft has a round, cylindrical basic cross-section and a conically increasing conical outer diameter, and that the conically wound inner hollow screw with twice the pitch of the eccentric screw shaft, a conical, hypocycloid Rolling of the eccentric worm on the inner surface of the conical, winding hollow worm causes.
  • the U.S. 1,892,217 A discloses progressing cavity pumps, including those with a conically shaped rotor.
  • This prior art proposes the use of gears with which the rotor and stator are aligned with one another in a manner not described in detail so that they are just not in contact, in order to avoid wear.
  • the disclosure must be understood to mean that this occurs only once when the pump is started up.
  • the eccentric screw pump according to the invention is characterized in that the volumes of each individual chamber between the stator and rotor are of the same size.
  • This embodiment of an eccentric screw pump according to the invention makes it possible for the pump to always have the maximum possible delivery rate. If there are any signs of wear, B. the rotor shaft or the stator can be moved in the longitudinal direction so that the chamber volume is the same again and the pumping performance of the eccentric screw pump is optimal.
  • the cross section d of the rotor decreases in the longitudinal direction of the rotor. Via the decrease in the cross section, e.g. the chamber volume is kept constant when the eccentricity changes.
  • the pitch h of the rotor decreases with a decreasing cross section d of the rotor and that the rotor has a decreasing cross section d in the longitudinal direction L. It is also possible that the eccentricity e of the rotor increases or decreases in the longitudinal direction L and that the cross section d of the rotor decreases or increases. Furthermore, the eccentric screw pump according to the invention can be designed such that the eccentricity of the rotor increases or decreases in the longitudinal direction and the pitch h of the rotor increases or decreases in the longitudinal direction.
  • the eccentricity of the rotor increases or decreases in the longitudinal direction L
  • the pitch h of the rotor increases or decreases in the longitudinal direction L
  • the rotor has a decreasing or increasing cross-section d in the longitudinal direction.
  • eccentric screw pumps for the most diverse areas of application, namely areas of application in which thick, highly viscous and / or abrasive media have to be transported.
  • the rotor can have a coating, e.g. B. with chrome, with a ceramic material or other materials.
  • the stator and / or rotor can consist of an elastomer or a solid.
  • the appropriate material for the stator and / or rotor depending on the intended area of use for the eccentric screw pump according to the invention.
  • the stator can also advantageously have an annular or tubular stator casing made of a different material.
  • This stator casing can be used to protect the stator and thus to increase the service life of the eccentric screw pump.
  • the stator casing is conical in shape.
  • the stator has a uniform plastic wall thickness.
  • Fig. 1 shows a rotor 1 of an eccentric screw pump according to the invention in longitudinal section.
  • the rotor 1 has a pitch h and an eccentricity e 1 at the beginning of the rotor 1 and an eccentricity e n at the end of the rotor 1.
  • the eccentricity of the rotor 1 increases so that the dimension e n is greater than the dimension e 1 .
  • Figure 1b the view A: A is shown on the beginning end of the rotor 1.
  • the rotor 1 has a cross section d 1 and the eccentricity e 1 which can also be seen in this view.
  • Figure 1c shows view B: B Fig.
  • Fig. 2 shows the stator 2 of an eccentric screw pump according to the invention.
  • the rotor 1 described above can be made Fig. 1a are introduced and in this way forms the eccentric screw pump according to the invention, which is characterized in that the individual volumes that are available for the transport of the medium are of the same size in the longitudinal direction L of the rotor.
  • the conicity of the stator and the rotor that fits into it can be clearly seen. Due to the conicity of the stator 2 and rotor 1 and the corresponding setting of the pitch, cross section and / or eccentricity, it is possible to keep the individual volumes of the chambers in the eccentric screw pump according to the invention constant.
  • FIGS. 3a, 3b and 3c show a further embodiment of a rotor 1 which can be introduced into an eccentric screw pump according to the invention.
  • the rotor 1 At its beginning (view A: A) the rotor 1 has a cross section d 1 which is larger than the cross section of the rotor 1 at its end (view B: B), which is marked with the dimension d 2 .
  • a decrease in the cross section of the rotor can be seen along the longitudinal direction L of the rotor 1, which results in the rotor 1 having a conical shape.
  • the eccentricity e of the rotor begins at the beginning of the rotor 1 (position A) with a size e 1 and ends at position B with a maximum value e n .
  • the eccentricity e thus increases in the longitudinal direction of the rotor 1, that is to say from the larger cross section to the smaller cross section d.
  • the respective views A: A and B: B are shown, which enable the top view of the end or the beginning of the rotor 1.
  • the Figure 3b it can be seen that the eccentricity e 1 at the beginning of the rotor 1, at the point A with the cross section d 1, is significantly less than the eccentricity e n, which is located in FIG Figure 3c which shows a view (view B: B) of the rotor end.
  • FIG Figure 3c shows a view (view B: B) of the rotor end.
  • the cross section d 2 is also smaller than the cross section d 1 .
  • an eccentric screw pump 100 according to the invention is shown, which has a rotor 1 and a stator 2.
  • Different chamber volumes V 3 , V 4 , V 5 ... V n of the chambers 3, 4, 5 ... n can be seen between the rotor 1 and the stator 2, which according to the invention are all the same size.
  • the same size of the volumes just listed results from the fact that both the rotor 1 has a predetermined Conicity and an eccentricity, pitch and / or cross section of the rotor 1 adapted to it, which is surrounded by the correspondingly shaped stator 2.
  • a sealing line D is formed between the stator 2 and the rotor 1, along which the necessary pressure is built up that is necessary to circulate the abrasive, highly viscous medium to be transported under pressure through the eccentric screw pump 100.
  • this sealing line migrates essentially spirally along the longitudinal direction L in the direction of the outlet of the eccentric screw pump 100 according to the invention and moves the medium to be transported in the direction of the pump outlet.
  • the medium to be transported which is located within the volumes, is moved in the direction of the outlet of the eccentric screw pump 100 according to the invention.
  • the drive of the eccentric screw pump 100 according to the invention can, for. B. via an electric motor which is arranged at the end (position A) of the eccentric screw pump according to the invention, which has the cross section d 1 and rotates the rotor 1 at this point.
  • Figure 4a It can also be seen that the cross-section d 1 at the beginning of the rotor 1 is larger than the cross-section d 2 at the end of the rotor 1. This is associated with the fact that the eccentricity of the eccentric screw pump 100 according to the invention at the beginning, i.e. in the area of the entry into the eccentric screw pump (position A) is less than towards the end (position B), that is to say towards the outlet end of the medium of the eccentric screw pump 100.
  • the eccentricity at the inlet of the eccentric screw pump (position A) is marked with e 1 and the eccentricity at the outlet (position B) of the eccentric screw pump 100 according to the invention is marked with e n .
  • the views of the input area and the end area of the eccentric screw pump 100 according to the invention, which are shown in FIGS Figures 4b and 4c also clearly show once again that the eccentricity increases in the longitudinal direction L of the eccentric screw pump 100 according to the invention or in the longitudinal direction L of the rotor 1, so that e 1 is smaller than e n .
  • the Figures 5a to 5c show a further possible embodiment of the eccentric screw pump 100 according to the invention, which differs from that in FIGS Figures 4a to 4c
  • the eccentric screw pump 100 shown differs in that the cross section d 1 of the rotor 1 in the longitudinal direction L of the rotor 1 is not changed.
  • the pitch h of the rotor or stator in the longitudinal direction L of the eccentric screw pump according to the invention was changed.
  • the slope h decreases in the longitudinal direction L of the eccentric screw pump 100 according to the invention.
  • the Figure 5b and 5c show the views along the line A: A and B: B, respectively Figure 5a , namely the views of the inlet end and the outlet end of this embodiment of the Eccentric screw pump 100 according to the invention. It can be seen that the eccentricity e 1 at the inlet end of the eccentric screw pump is greater than the eccentricity e n in the outlet area.
  • a further embodiment of the eccentric screw pump 100 according to the invention is also shown, which differs from that shown in FIGS Figures 4a to 4c
  • the eccentric screw pump shown differs in that, in this embodiment, both the cross section and the pitch of the rotor or the stator have been changed.
  • FIGs 7a to 7c Another variant of the eccentric screw pump according to the invention is shown in which both the eccentricity, the cross section and the pitch of the rotor or the stator have been changed, the individual volumes V 3 , V 4 , V 5 being kept constant.
  • the slope h decreases in the longitudinal direction L of the eccentric screw pump according to the invention.
  • the change in terms of the cross section of the rotor 1 and the eccentricity e show Figures 7b and 7c .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP10711641.0A 2009-03-02 2010-03-02 Exzenterschneckenpumpe Revoked EP2404061B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10711641T PL2404061T3 (pl) 2009-03-02 2010-03-02 Mimośrodowa pompa śrubowa

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202009002823U DE202009002823U1 (de) 2009-03-02 2009-03-02 Exzenterschneckenpumpe
PCT/EP2010/052597 WO2010100134A2 (de) 2009-03-02 2010-03-02 Exzenterschneckenpumpe

Publications (2)

Publication Number Publication Date
EP2404061A2 EP2404061A2 (de) 2012-01-11
EP2404061B1 true EP2404061B1 (de) 2020-11-11

Family

ID=40911653

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10711641.0A Revoked EP2404061B1 (de) 2009-03-02 2010-03-02 Exzenterschneckenpumpe

Country Status (10)

Country Link
US (1) US9109595B2 (da)
EP (1) EP2404061B1 (da)
CA (1) CA2754139C (da)
DE (1) DE202009002823U1 (da)
DK (1) DK2404061T3 (da)
ES (1) ES2846680T3 (da)
PL (1) PL2404061T3 (da)
PT (1) PT2404061T (da)
RU (1) RU2535795C2 (da)
WO (1) WO2010100134A2 (da)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202009002823U1 (de) 2009-03-02 2009-07-30 Daunheimer, Ralf Exzenterschneckenpumpe
EP2532833B1 (de) 2011-06-10 2015-07-29 ViscoTec Pumpen-u. Dosiertechnik GmbH Förderelement für eine Exzenterschneckenpumpe und Exzenterschneckenpumpe
DE202011110637U1 (de) 2011-06-10 2015-07-02 Viscotec Pumpen- U. Dosiertechnik Gmbh Exzenterschneckenpumpe
CN103775334B (zh) * 2014-02-13 2016-01-13 北京工业大学 一种锥螺杆-衬套副
DE102014117483A1 (de) 2014-04-14 2015-10-15 Erich Netzsch Gmbh & Co. Holding Kg Verstellbare Pumpeinheit für eine Verdrängerpumpe
JP5802914B1 (ja) 2014-11-14 2015-11-04 兵神装備株式会社 流動体搬送装置
CA2970680A1 (en) * 2014-12-23 2016-06-30 Schlumberger Canada Limited Design and method to improve downhole motor durability
CA3026754A1 (en) 2016-06-10 2017-12-14 Activate Artificial Lift Inc. Progressing cavity pump and methods of operation
CN106640627B (zh) * 2016-12-30 2018-10-19 北京工业大学 一种等过流面积的锥螺杆-衬套副
DE102017100715A1 (de) 2017-01-16 2018-07-19 Hugo Vogelsang Maschinenbau Gmbh Regelung der Spaltgeometrie in einer Exzenterschneckenpumpe
BE1025347B1 (nl) * 2017-06-28 2019-02-05 Atlas Copco Airpower Naamloze Vennootschap Cilindrisch symmetrische volumetrische machine
US11035338B2 (en) 2017-11-16 2021-06-15 Weatherford Technology Holdings, Llc Load balanced power section of progressing cavity device
DE202018104142U1 (de) * 2018-07-18 2019-10-22 Vogelsang Gmbh & Co. Kg Rotor für eine Exzenterschneckenpumpe
WO2020185749A1 (en) * 2019-03-11 2020-09-17 National Oilwell Varco, L.P. Progressing cavity devices and assemblies for coupling multiple stages of progressing cavity devices
WO2020232231A1 (en) * 2019-05-14 2020-11-19 Schlumberger Technology Corporation Mud motor or progressive cavity pump with varying pitch and taper
DE112020004079T5 (de) 2019-08-29 2022-05-19 Heishin Ltd. Einachsige exzenterschneckenpumpe
CA3114159A1 (en) 2020-04-02 2021-10-02 Abaco Drilling Technologies Llc Tapered stators in positive displacement motors remediating effects of rotor tilt
US11421533B2 (en) 2020-04-02 2022-08-23 Abaco Drilling Technologies Llc Tapered stators in positive displacement motors remediating effects of rotor tilt
US11859632B2 (en) 2020-11-04 2024-01-02 John Lloyd Bowman Boundary-layer pump and method of use
US12092128B2 (en) 2020-11-04 2024-09-17 John Lloyd Bowman Boundary-layer pump and method of use
DE102021131427A1 (de) 2021-11-30 2023-06-01 Vogelsang Gmbh & Co. Kg Exzenterschneckenpumpe mit Arbeitszustellung und Ruhezustellung sowie Verfahren zum Steuern der Exzenterschneckenpumpe
DE202022107205U1 (de) 2022-12-23 2024-04-22 Vogelsang Gmbh & Co. Kg Exzenterschneckenpumpe mit gekapselter Statorauskleidung

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US2553548A (en) 1945-08-14 1951-05-22 Henry D Canazzi Rotary internal-combustion engine of the helical piston type
US2957427A (en) 1956-12-28 1960-10-25 Walter J O'connor Self-regulating pumping mechanism
US3139035A (en) 1960-10-24 1964-06-30 Walter J O'connor Cavity pump mechanism
US3208391A (en) 1963-04-23 1965-09-28 Flygts Pumpar Ab Screw pump
DE2632716A1 (de) 1976-07-21 1978-01-26 Martin Theodor Melchior Fluessigkeitspumpe, insbesondere fuer gips-anwurfgeraete
DE2736590A1 (de) 1977-08-13 1979-02-22 Hartmut Kowalzik Exzenterschneckenpumpe mit konischer schneckenwelle und gehaeuse-einsatz
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US5358390A (en) 1992-11-11 1994-10-25 Jaeger Arnold Eccentric screw pump
US5722820A (en) 1996-05-28 1998-03-03 Robbins & Myers, Inc. Progressing cavity pump having less compressive fit near the discharge
US6354824B1 (en) 2000-03-09 2002-03-12 Kudu Industries, Inc. Ceramic hardfacing for progressing cavity pump rotors
US6457958B1 (en) 2001-03-27 2002-10-01 Weatherford/Lamb, Inc. Self compensating adjustable fit progressing cavity pump for oil-well applications with varying temperatures
DE10345597A1 (de) 2003-09-29 2005-05-12 Verschleis Technik Dr Ing Hans Förderschnecke für eine Exzenterschneckenpumpe
DE202005008989U1 (de) 2005-06-07 2005-08-11 Seepex Gmbh + Co Kg Exzenterschneckenpumpe
EP1813812A1 (de) 2006-01-26 2007-08-01 Grundfos Management A/S Exzenterschneckenpumpe
WO2008000505A1 (en) 2006-06-30 2008-01-03 Grundfos Management A/S Moineau pump
EP1988288A1 (en) 2007-05-04 2008-11-05 Grundfos Management A/S Moineau pump
DE202009002823U1 (de) 2009-03-02 2009-07-30 Daunheimer, Ralf Exzenterschneckenpumpe

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Publication number Priority date Publication date Assignee Title
US1892217A (en) 1930-05-13 1932-12-27 Moineau Rene Joseph Louis Gear mechanism
US2553548A (en) 1945-08-14 1951-05-22 Henry D Canazzi Rotary internal-combustion engine of the helical piston type
US2957427A (en) 1956-12-28 1960-10-25 Walter J O'connor Self-regulating pumping mechanism
US3139035A (en) 1960-10-24 1964-06-30 Walter J O'connor Cavity pump mechanism
US3208391A (en) 1963-04-23 1965-09-28 Flygts Pumpar Ab Screw pump
DE2632716A1 (de) 1976-07-21 1978-01-26 Martin Theodor Melchior Fluessigkeitspumpe, insbesondere fuer gips-anwurfgeraete
DE2632716C2 (da) 1976-07-21 1989-03-09 Martin Theodor 6639 Rehlingen De Melchior
DE2736590A1 (de) 1977-08-13 1979-02-22 Hartmut Kowalzik Exzenterschneckenpumpe mit konischer schneckenwelle und gehaeuse-einsatz
DE3442977A1 (de) 1984-11-24 1986-05-28 Verschleiß-Technik Dr.-Ing. Hans Wahl GmbH & Co, 7302 Ostfildern Schneckenpumpe sowie verfahren und vorrichtung zu ihrer herstellung
US5358390A (en) 1992-11-11 1994-10-25 Jaeger Arnold Eccentric screw pump
US5722820A (en) 1996-05-28 1998-03-03 Robbins & Myers, Inc. Progressing cavity pump having less compressive fit near the discharge
US6354824B1 (en) 2000-03-09 2002-03-12 Kudu Industries, Inc. Ceramic hardfacing for progressing cavity pump rotors
US6457958B1 (en) 2001-03-27 2002-10-01 Weatherford/Lamb, Inc. Self compensating adjustable fit progressing cavity pump for oil-well applications with varying temperatures
DE10345597A1 (de) 2003-09-29 2005-05-12 Verschleis Technik Dr Ing Hans Förderschnecke für eine Exzenterschneckenpumpe
DE202005008989U1 (de) 2005-06-07 2005-08-11 Seepex Gmbh + Co Kg Exzenterschneckenpumpe
EP1813812A1 (de) 2006-01-26 2007-08-01 Grundfos Management A/S Exzenterschneckenpumpe
WO2008000505A1 (en) 2006-06-30 2008-01-03 Grundfos Management A/S Moineau pump
EP1988288A1 (en) 2007-05-04 2008-11-05 Grundfos Management A/S Moineau pump
DE202009002823U1 (de) 2009-03-02 2009-07-30 Daunheimer, Ralf Exzenterschneckenpumpe
WO2010100134A2 (de) 2009-03-02 2010-09-10 Ralf Daunheimer Exzenterschneckenpumpe

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WO2010100134A3 (de) 2010-12-29
RU2535795C2 (ru) 2014-12-20
ES2846680T3 (es) 2021-07-28
US9109595B2 (en) 2015-08-18
CA2754139C (en) 2018-07-24
PL2404061T3 (pl) 2021-06-28
WO2010100134A2 (de) 2010-09-10
DK2404061T3 (da) 2021-02-08
EP2404061A2 (de) 2012-01-11
DE202009002823U1 (de) 2009-07-30
RU2011139951A (ru) 2013-04-10
US20110305589A1 (en) 2011-12-15
CA2754139A1 (en) 2010-09-10
PT2404061T (pt) 2021-01-29

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