WO2014111082A1 - Rotor pour pompes à vis sans fin et/ou à vis excentrée ainsi que pompes à vis sans fin ou à vis excentrée - Google Patents

Rotor pour pompes à vis sans fin et/ou à vis excentrée ainsi que pompes à vis sans fin ou à vis excentrée Download PDF

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Publication number
WO2014111082A1
WO2014111082A1 PCT/DE2014/000015 DE2014000015W WO2014111082A1 WO 2014111082 A1 WO2014111082 A1 WO 2014111082A1 DE 2014000015 W DE2014000015 W DE 2014000015W WO 2014111082 A1 WO2014111082 A1 WO 2014111082A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
region
screw
helical
length
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.)
Ceased
Application number
PCT/DE2014/000015
Other languages
German (de)
English (en)
Inventor
Thomas Streubel
Johann Kreidl
Reinhard Denk
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.)
Netzsch Pumpen and Systeme GmbH
Original Assignee
Netzsch Pumpen and Systeme 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 Netzsch Pumpen and Systeme GmbH filed Critical Netzsch Pumpen and Systeme GmbH
Priority to CN201480005167.5A priority Critical patent/CN104937270B/zh
Priority to BR112015016607A priority patent/BR112015016607A2/pt
Publication of WO2014111082A1 publication Critical patent/WO2014111082A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the present invention relates to a rotor for screw and / or
  • Eccentric screw pumps are pumps for pumping a large number of media, in particular viscous, highly viscous and abrasive media such as sludges, liquid manure, crude oil and fats.
  • the driven, coiled rotor rolls in the stator.
  • This is a housing with a spiral-shaped inside.
  • the rotor performs with its figure axis an eccentric rotation about the stator.
  • the outer screw, i. the stator has the form of a double thread, while the rotor screw is only catchy.
  • the rotor is usually made of a highly abrasion resistant material such as
  • Example steel The stator, however, consists of an elastic material, for example rubber. Due to the special shape of rotor and stator between the rotor and stator sealed cavities, which move axially upon rotation of the rotor and promote the medium. The shape of the cavities is constant, so that the fluid is not crushed. With suitable interpretation can with
  • Housing medium causes.
  • a helical spiral screw is incorporated in the inner wall of the pump housing.
  • the rotor is a cylinder or similar. formed and has a plurality of sealing elements in the area of the helical formation of the housing. A transport material located between the sealing elements is conveyed by rotation of the rotor in the axial direction.
  • DE10 2010 021 592 A1 describes a method for producing the rotor of a
  • the rotor is integrally formed in a known manner and includes a worm gear and a drive head. The process creates a smooth surface of the screw helix without machining grooves or the like. so that the risk of damage to the existing of an elastic material
  • the screw body consists of a hardening interspersed with fillers casting resin.
  • the worm body may be partially hollow to save material and reduce weight.
  • Eccentric screw pumps with a ceramic Totormantel which consists of at least two rotor shell items and is inexpensive to produce.
  • EP 2 532 833 A1 describes a conveyor element for an eccentric screw pump with a first screw thread for providing a first delivery volume and a second screw thread for providing a second delivery volume.
  • the object of the invention is a rotor for a screw pump or
  • the invention relates to a rotor for screw and / or
  • Eccentric screw pumps which includes a rotor head for mounting the rotor to a drive and a rotor body.
  • the rotor has a rotor overall length.
  • the rotor consists of at least two rotor areas, in particular a first rotor portion, the rotor head and a first portion of the
  • Rotor worm comprises and at least a second Rotor Schemet.
  • the rotor head comprising the first rotor portion is made of a solid material and the at least one adjoining second rotor portion is formed as a hollow body.
  • the rotor is made hollow to a large extent.
  • the first rotor region comprises about 5 - 40% of
  • Rotor length and the remaining rotor area, consisting of at least a second rotor area, comprises about 60% - 95% of the rotor length.
  • Embodiment are made of solid material about 30% to 1/3 of the rotor length and the remaining 2/3 to 70% of the rotor length are formed as a hollow body. According to another embodiment, about 10% of the rotor length is made of solid material and the remaining 90% are formed as a hollow body.
  • the solid material is in the region of the receptacle for the drive, i. in the area of the rotor head, because the rotor in this area has the greatest loads due to the rotatory
  • the rotors comprising the rotor head and the rotor screw are manufactured in one piece, for example, turned in one piece, cast, etc., and then provided in regions with a hollow interior.
  • a one-piece rotor is made of a solid material and then hollowed out in the second rotor region by introducing a central bore along the rotor longitudinal axis over the second region of the rotor length. The drilling takes place via the rotor head opposite the free end of the rotor. The hole opening can then be used with an end plate or similar. be closed to prevent the cargo gets into the hollow interior and deposited there.
  • the bore has a first diameter in a second region, which adjoins the first region encompassing the rotor head, and in a third end, the rotor head
  • opposite region has a second diameter, wherein the first diameter is smaller than the second diameter.
  • the third terminal area is thus made lighter than the middle second area and the terminal first area made in solid material.
  • the first rotor region comprising the rotor head and the first portion of the rotor screw and the at least one second rotor portion made individually and then connected together.
  • the areas can each be manufactured as turned components, components made of cast iron, components made of precision casting or by forming.
  • the first rotor area is manufactured by means of a different manufacturing method than the at least one second rotor area.
  • the first region is a solid material rotating part and the second rotor region is a cast component having a hollow inner region already formed during production.
  • the rotor consists of three areas, wherein the first area comprising the rotor head and the middle area are manufactured as a common part and the third terminal area is manufactured individually and fastened to the free end of the middle area.
  • the rotor part comprising the first and middle regions is cast in the piece, for example. Subsequently, the central area is drilled out from the free end, so that in this area a hollow body is formed.
  • a terminal, third area for example, a
  • the two rotor parts can be materially connected to one another, glued together, screwed together, etc.
  • the connection can be both detachable and non-detachable.
  • the first and at least a second rotor region consist of different materials.
  • the first rotor region should be made of a material which is particularly suitable for sufficiently absorbing the forces acting on the rotor head.
  • Embodiment is provided that the first rotor portion and an adjacent central rotor portion made of a first material, wherein the first rotor portion is made of the material as a solid material and wherein the central rotor portion, for example, by a bore along the rotor longitudinal axis or due to manufacturing an inner cavity ,
  • the terminal rotor portion is made of another, preferably lighter, material and also has an inner cavity. The two rotor parts are fastened together by suitable means.
  • different rotor areas are designed for different temperature levels.
  • the rotor has at least one diameter orthogonal to the rotor longitudinal axis.
  • the rotor includes at least a first rotor portion having a first diameter and a second rotor portion having a second diameter, wherein the first and second diameters are unequal.
  • the different diameters of the rotor serve for temperature compensation in the stator elastomer.
  • the diameter of the rotor is reduced continuously or stepwise from the suction side to the pressure side. Due to the increasing pressure within the pump, the friction of the conveyed material on the rotor and stator increases and thus also the temperature in the pump. Since the rotor and the stator made of different materials with different coefficients of expansion, for example, the stator is made of rubber and the rotor made of steel, etc., they expand
  • the rotor diameter is reduced continuously or stepwise. According to one embodiment of the invention, the
  • Suction side designed for an average temperature of the conveyed material of approx. 40 ° C +/- 10 ° C.
  • the reduction of the rotor diameter is preferably carried out stepwise and may be in an area of the pressure side, in particular in the region of the outlet flange, for example, for a temperature of the conveyed material of about 100 ° C +/- 10 ° C, designed.
  • the conveyed material cools during conveyance by the screw and / or eccentric screw pump, so that the temperature of the conveyed goods on the suction side is higher than on the pressure side.
  • the at least one second rotor region of the rotor may comprise a central rotor region adjoining the first rotor region and having a first outer circumferential surface and a terminal third rotor region having a first rotor surface second outer circumferential surface exist. It can be provided in particular that the design of the screw flights on the outer circumferential surface respectively
  • the outer circumferential surface of the central rotor region can have a helical helix of a first pitch and a first mean pitch of the helixes relative to one another.
  • the terminal third rotor region may have a helical or helical helix of a second pitch and a second mean pitch of the helix relative to one another. This gives you different sized in the two areas
  • Feed chambers Such an embodiment can be advantageously used in particular in the promotion of multi-phase mixtures. With an enlargement of the
  • Delivery chambers in the region of the free end of the rotor can also counteract a possible temperature development (as already described above) in these stator regions, and thus an improvement in the efficiency can be achieved.
  • the pitch and / or the pitch of the helixes are changed in a range between 1% to 5%, preferably in a range between 2% and 4%.
  • the invention further relates to a screw or eccentric screw pump for conveying transported goods with a rotor having a helical or helically coiled outer circumferential surface.
  • the rotor is arranged in a housing with a spiral-shaped or helically wound inner circumferential surface.
  • the rotor has the features already described above, in particular the rotor consists of at least two rotor regions, wherein the rotor head comprising the first rotor portion is made of solid material and wherein the at least one second rotor portion is formed as a hollow body. According to one embodiment, it is provided that the rotor has at least two
  • Rotor regions having differently designed outer circumferential surface comprises and that the stator comprises at least two corresponding areas with correspondingly differently shaped inner circumferential surfaces.
  • the rotor can thus be made much lighter than rotors made of solid material. This results especially in pumps with long lengths, especially with a rotor length of several meters, great ease of assembly and during operation.
  • Examples of long-length pumps are pumps used in harbors where the rotor-stator delivery chambers are so large that live fish can be pumped from a trawler into the factory. without them getting hurt.
  • Breakout force is the force needed to overcome stiction and initiate the transition to sliding friction, ie the minimum force needed to move the rotor of the pump from static to dynamic.
  • the breakaway forces of a partially hollow rotor are substantially lower than in a rotor made of solid material.
  • the drive energy required for operating the pump is also significantly lower. But even with smaller pumps, the partially hollow running rotor can be used advantageously. For example, in pumps that are used to promote fruit yoghurt, the rotor weight should not be too large, otherwise the fruit can be squeezed and no more than whole fruit in the yogurt cups or similar. reach.
  • Figures 2 show various views of a further embodiment of a rotor according to the invention.
  • FIG. 3 shows a further embodiment of a rotor according to the invention. Identical or equivalent elements of the invention will be identical
  • Rotor longitudinal axis X and comprises a rotor head 2, which serves for attachment to a drive, and a rotor screw 3, which forms in connection with the stator (not shown), the conveying chambers for the transported goods.
  • the rotor 1 according to the invention comprises a first region I, which is formed of solid material and a second region II, which is formed as a hollow body.
  • the rotor has a total rotor length LG, which is composed of the sum of the lengths Li and Ln of the two regions I and II, or which is composed of the sum of the lengths L2 and L3 of the
  • the first region I comprises the rotor head 2 and is preferably formed significantly shorter than the second region II, i. Li ⁇ Ln.
  • the rotor head 2 and an adjoining subregion 5 of the rotor worm 3 are formed from solid material 10, while the remaining region of the rotor worm 3 forms the second region II, which is formed as a hollow body 12 with a hollow interior region 13 ,
  • the hollow inner region 13 is surrounded by a rotor shell 14, which has an outer circumferential surface 16, which is formed as a helical contour.
  • the first region I for example, as a solid cast steel body o.a. made while the second area II with hollow inner area 3 made extra and attached to the first area I.
  • Inner region 13 is at the free end of the second rotor portion II by a
  • End cover 18 closed. This prevents goods to be transported from entering the hollow inner region 13 of the rotor 1, 1a and contaminating it. Deposits in the hollow interior region 13 could lead to an imbalance of the rotor 1, 1 a, which would adversely affect the rotational behavior of the rotor 1, 1 a.
  • FIGS. 1B and 1C show embodiments of a rotor 1b, 1c, in which the first region I * with the length Li * essentially comprises only the rotor head 2 of the length L2, while the second region II * with the length Ln * substantially only the rotor screw 3 of length L3 comprises.
  • the length Li * of the first region I * and the length L2 of the rotor head 2 is about 10% of the total length LG of the rotor 1b, 1 c.
  • FIGS. 1B and 1C only the rotor head 2 of solid material 10 is thus formed, while the rotor worm 3 is completely formed as a hollow body 12.
  • the rotor screw 3b in Figure 1 B is a helical Rotor casing 14 with helically formed outer circumferential surface 16, for example, made of steel or other suitable material and with the
  • Solid material 10 existing rotor head 2 connected.
  • a rotor 1 made of solid material 10 is produced for the rotor 1c according to FIG. 1C. From the free end 4 of the rotor screw 3, this is drilled out to the rotor head 2 and thus a hollow inner region 13 is formed, so that the rotor screw 3 c is now a hollow body 12. The hole at the free end 4 is with a
  • Rotor heads 2 i. about 10% of the total rotor length LG formed as a solid material.
  • Rotor worm 3 correspond, however, are designed as a hollow body. As a result, the rotor 1 b, 1 c according to the invention is much lighter. This causes a facilitated
  • FIGS. 2 show different representations of a further embodiment of a rotor 1d according to the invention.
  • the second hollow inner region 11d which essentially comprises the rotor screw 3 is subdivided once again into a central partial region 3-1 and a terminal partial region 3-2.
  • the rotor worm has a rotor longitudinal axis X and a mean diameter D.
  • the region of the rotor screw 3, which comprises the first region I and the central portion 3-1, is manufactured, for example, as a solid casting and provided with a bore along the rotor longitudinal axis X, the hollow inner region 13-1 of the middle
  • Subarea 3-1 forms.
  • the terminal portion 3-2 is made as a separate hollow part and connected at the free end 4-1 of the portion 3-1 cohesively, positively or non-positively with this.
  • the rotor 1 can be made of one part.
  • a first bore having a first diameter is introduced from the free end opposite the rotor head 2, which bore extends largely along the rotor worm to the rotor head 2.
  • the bore is extended from the free end through a second bore with a larger diameter, wherein the second bore extends only over the terminal portion 3-2.
  • the ratio between hollow interior 13 and rotor shell 14 is greater in both cases in the terminal area 3-2 than in the central area 3-1.
  • the terminal portion 3-2 relatively comprises a larger inner cavity 3-2 than the middle portion 3-1, ie, the terminal portion 3-2 is made lighter than the middle portion 3-1.
  • the free end of the terminal portion 3-2 can in turn be closed with an end cover 18.
  • FIG. 3 shows a further embodiment of a rotor 1e according to the invention, which is largely comparable to the rotor 1d of that described in FIG.
  • Embodiment is.
  • the second region is hollow
  • Inner region 13 which essentially comprises the rotor screw 3, also once again divided into a central portion 3-1 and a terminal portion 3-2.
  • the region of the rotor worm 3, which comprises the first region I and the middle subregion 3-1, is manufactured, for example, as a solid casting and provided with a bore along the rotor longitudinal axis X, which forms the hollow inner region of the central subregion 3-1 (cf. also Figure 2A).
  • the terminal portion 3-2 is made as a separate hollow part and connected at the free end 4-1 of the portion 3-1 cohesively, positively or non-positively with this.
  • the rotor has a first diameter Di and in the partial area 3-2 the rotor has a second diameter D2.
  • the second diameter D2 is smaller than the first diameter Di.
  • the configuration of the worm windings 17 on the outer circumferential surface 18 in the subregions 3-1, 3-2 is in each case designed differently.
  • the outer circumferential surface 18-1 of the central rotor region 3-1 has a helical or helical helix 17-1 of a first pitch and a first mean pitch A1 of the helixes relative to one another.
  • the terminal third rotor portion 3-2 has a helical or helical helix 17-2 a second pitch and a second average distance A2 of the helices to each other.
  • the transition region between the central rotor region 3-1 and the third rotor region 3-2 has a so-called transitional distance Aü and thus again forms a different sized delivery chamber.

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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)

Abstract

L'invention concerne un rotor (1) destiné à des pompes à vis sans fin et à vis excentrée. Ledit rotor comprend une tête de rotor (2), destinée à être fixée à un dispositif d'entraînement, et une vis sans fin (3), ledit rotor (1) présentant une longueur totale (LG) donnée. Selon l'invention, le rotor (1) est constitué de deux parties de rotor (I, II) ou plus. La première partie de rotor (I) comprend la tête de rotor (2) et un premier tronçon (5) de la vis sans fin (3), et est formée d'un matériau plein. La ou les autres parties de rotor (II) sont conformées sous forme de corps creux présentant une partie interne creuse (13).
PCT/DE2014/000015 2013-01-17 2014-01-15 Rotor pour pompes à vis sans fin et/ou à vis excentrée ainsi que pompes à vis sans fin ou à vis excentrée Ceased WO2014111082A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201480005167.5A CN104937270B (zh) 2013-01-17 2014-01-15 用于蜗杆泵和/或偏心蜗杆泵的转子以及蜗杆泵或偏心蜗杆泵
BR112015016607A BR112015016607A2 (pt) 2013-01-17 2014-01-15 rotor para bombas helicoidais e/ou bombas helicoidais excêntricas e bomba helicoidal ou helicoidal excêntrica

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013100451.2 2013-01-17
DE102013100451.2A DE102013100451B4 (de) 2013-01-17 2013-01-17 Rotor für Schnecken- und / oder Exzenterschneckenpumpen und Schnecken- oder Exzenterschneckenpumpe

Publications (1)

Publication Number Publication Date
WO2014111082A1 true WO2014111082A1 (fr) 2014-07-24

Family

ID=50158992

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2014/000015 Ceased WO2014111082A1 (fr) 2013-01-17 2014-01-15 Rotor pour pompes à vis sans fin et/ou à vis excentrée ainsi que pompes à vis sans fin ou à vis excentrée

Country Status (4)

Country Link
CN (1) CN104937270B (fr)
BR (1) BR112015016607A2 (fr)
DE (1) DE102013100451B4 (fr)
WO (1) WO2014111082A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017186494A1 (fr) * 2016-04-28 2017-11-02 BSH Hausgeräte GmbH Accouplement à barrettes ressort et rotor pour une pompe de dosage d'un appareil électroménager
US12152588B1 (en) 2023-05-26 2024-11-26 Grant Prideco, Inc. Free-mold stator for a progressing cavity pump
US20250347208A1 (en) * 2024-05-09 2025-11-13 Schlumberger Technology Corporation Pump having hollow rotor disposed in stator

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106685152B (zh) * 2015-11-10 2019-03-12 耐驰（兰州）泵业有限公司 制造用于偏心螺杆泵的可液压调整的定子的方法
CN117780636B (zh) * 2024-02-26 2024-05-03 东营华来智能科技有限公司 一种应用于单螺杆油气混输泵的比例定量液体反馈器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1703828A1 (de) * 1968-07-17 1971-12-16 Sigma Lutin Spindel,insbesondere von Einspindelpumpen,Herstellungsverfahren und Vorrichtung zur Durchfuehrung des Verfahrens
DE2211786A1 (de) 1972-03-11 1973-09-13 Hermann Kraemer Foerdervorrichtung, insbesondere foerderpumpe
DE2707901A1 (de) 1977-02-24 1978-08-31 Allweiler Ag Exzenterschnecke fuer exzenterschneckenpumpen und verfahren zu ihrer herstellung
DE19925106A1 (de) 1998-06-05 1999-12-09 Netzsch Mohnopumpen Gmbh Rotor für Schnecken- und Exzenterschneckenpumpen
DE102010021592A1 (de) 2010-05-26 2011-12-01 Vautid Gmbh Verfahren zur Herstellung des Rotors einer Exzenterschneckenpumpe
EP2532833A1 (fr) 2011-06-10 2012-12-12 ViscoTec Pumpen-u. Dosiertechnik GmbH Elément de transport pour une pompe à vis sans fin excentrique et pompe à vis sans fin excentrique

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE361451B (fr) 1971-03-26 1973-11-05 Akerlund & Rausing Ab
CN2700606Y (zh) * 2003-12-03 2005-05-18 扬振平 地面驱动无杆采油螺杆泵
CN1690436A (zh) * 2004-04-22 2005-11-02 高元芳 螺杆泵及其生产方法
CN2869388Y (zh) * 2005-10-19 2007-02-14 大庆油田有限责任公司 采油等壁厚定子螺杆泵

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1703828A1 (de) * 1968-07-17 1971-12-16 Sigma Lutin Spindel,insbesondere von Einspindelpumpen,Herstellungsverfahren und Vorrichtung zur Durchfuehrung des Verfahrens
DE2211786A1 (de) 1972-03-11 1973-09-13 Hermann Kraemer Foerdervorrichtung, insbesondere foerderpumpe
DE2707901A1 (de) 1977-02-24 1978-08-31 Allweiler Ag Exzenterschnecke fuer exzenterschneckenpumpen und verfahren zu ihrer herstellung
DE19925106A1 (de) 1998-06-05 1999-12-09 Netzsch Mohnopumpen Gmbh Rotor für Schnecken- und Exzenterschneckenpumpen
DE102010021592A1 (de) 2010-05-26 2011-12-01 Vautid Gmbh Verfahren zur Herstellung des Rotors einer Exzenterschneckenpumpe
EP2532833A1 (fr) 2011-06-10 2012-12-12 ViscoTec Pumpen-u. Dosiertechnik GmbH Elément de transport pour une pompe à vis sans fin excentrique et pompe à vis sans fin excentrique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017186494A1 (fr) * 2016-04-28 2017-11-02 BSH Hausgeräte GmbH Accouplement à barrettes ressort et rotor pour une pompe de dosage d'un appareil électroménager
US12152588B1 (en) 2023-05-26 2024-11-26 Grant Prideco, Inc. Free-mold stator for a progressing cavity pump
US20250347208A1 (en) * 2024-05-09 2025-11-13 Schlumberger Technology Corporation Pump having hollow rotor disposed in stator
US12560061B2 (en) * 2024-05-09 2026-02-24 Schlumberger Technology Corporation Pump having hollow rotor disposed in stator

Also Published As

Publication number Publication date
DE102013100451A1 (de) 2014-07-17
CN104937270A (zh) 2015-09-23
DE102013100451B4 (de) 2016-04-07
CN104937270B (zh) 2017-05-03
BR112015016607A2 (pt) 2017-07-11

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