EP1811184B1 - Roue pour une unité de pompage et unité de pompage correspondante - Google Patents

Roue pour une unité de pompage et unité de pompage correspondante Download PDF

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Publication number
EP1811184B1
EP1811184B1 EP05028030A EP05028030A EP1811184B1 EP 1811184 B1 EP1811184 B1 EP 1811184B1 EP 05028030 A EP05028030 A EP 05028030A EP 05028030 A EP05028030 A EP 05028030A EP 1811184 B1 EP1811184 B1 EP 1811184B1
Authority
EP
European Patent Office
Prior art keywords
impeller
blade
gap
impeller according
cover disks
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.)
Not-in-force
Application number
EP05028030A
Other languages
German (de)
English (en)
Other versions
EP1811184A1 (fr
Inventor
Lasse Ilves
Heikki Yli-Korpela
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.)
Grundfos Management AS
Original Assignee
Grundfos Management 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 Grundfos Management AS filed Critical Grundfos Management AS
Priority to EP05028030A priority Critical patent/EP1811184B1/fr
Priority to AT05028030T priority patent/ATE385290T1/de
Priority to DE502005002739T priority patent/DE502005002739D1/de
Priority to CN2006800464917A priority patent/CN101326372B/zh
Priority to PCT/EP2006/011990 priority patent/WO2007079890A1/fr
Priority to US12/158,462 priority patent/US8251663B2/en
Publication of EP1811184A1 publication Critical patent/EP1811184A1/fr
Application granted granted Critical
Publication of EP1811184B1 publication Critical patent/EP1811184B1/fr
Not-in-force 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2288—Rotors specially for centrifugal pumps with special measures for comminuting, mixing or separating

Definitions

  • the invention relates to an impeller for a pump unit, in particular for a sewage pump unit, and a pump unit with such an impeller.
  • the impeller according to the invention for a pump unit is provided in particular for a sewage pump unit.
  • the impeller is closed, d. H. it has two in the axial direction, d. H. in the direction of the axis of rotation, spaced apart cover disks, between which at least one blade is arranged to form a flow channel for conveying the fluid.
  • the two cover plates are firmly connected to each other via at least one connecting element, so that they are held at a defined distance from each other.
  • the at least one blade extends from an inner diameter, d. H. from a central region of the impeller located in the circumference of the axis of rotation to an outer diameter of the impeller.
  • the blade thus extends in a known manner in the impeller in the radial direction from the inside to the outside, wherein it may have a curvature to improve the flow guidance.
  • the blade serves to convey the fluid and forms a flow channel leading outwards to the circumference of the impeller, in which the fluid is accelerated during rotation of the impeller.
  • the blade is designed such that it has a continuous gap.
  • This gap extends from the inner diameter, ie the edge facing the axis of rotation, to the edge located on the outer diameter, ie the edge of the blade facing the outer circumference of the impeller.
  • the gap thus extends along the blade from the inner region of the impeller to the outside.
  • the arrangement of this gap has the advantage that long-fiber contaminants, which in conventional wheels on the inner edge, d. H. would remain stuck on the inner diameter edge of the blade, here are conveyed through the gap with the fluid to the outer ⁇ enrise of the impeller. That is, the contaminants do not stick to the edge of the blade, but can move through the gap through the blade to the outer periphery of the impeller where they are washed away with the fluid flow delivered by the impeller. In this way, the risk of impurities settling in the impeller is significantly reduced. In addition, the efficiency of such an impeller is greater than an open impeller.
  • the described blade is connected to only one of the two cover plates. That is, in the axial direction, the blade extends from one of the two shrouds, and the continuous gap is formed between the free longitudinal edge of the blade, which extends from inside to outside, and the adjacent second shroud.
  • the blade can be integrally formed with the first cover plate, with which it is connected.
  • the gap is arranged so that the blade is divided into two blade parts, each of which is connected to only one of the two cover plates. That is, on the two cover plates substantially opposite blade parts are formed, which extend from the cover plate, with which they are connected to the other cover plate.
  • the blades are arranged or have an axial length, which is selected so that the two blade parts do not touch with their free longitudinal edges, ie the extending from the inner diameter to the outer diameter of the impeller longitudinal edges. Between these two longitudinal edges of the continuous gap is then formed, which extends from the inner diameter to the outer diameter of the impeller through the entire blade, so that impurities can be discharged through this gap to the outer periphery of the impeller.
  • the two blade parts are preferably arranged offset from each other in the region of the gap in the circumferential direction of the impeller. This means that the free longitudinal edges of the two blade parts are not exactly opposite each other but offset in the circumferential direction to each other, so that between the two blade parts in the circumferential direction, a gap is formed, which extends continuously from the inner to the outer diameter of the blade. That is, the free longitudinal edges of the blades are spaced apart in the circumferential direction.
  • the blade parts are formed so long in the axial direction that they overlap each other in the axial direction in the region of the gap.
  • the blade parts ie at least the blade parts facing the gap, are offset relative to one another in the circumferential direction, so that the free ends of the blade parts can overlap one another by overlapping.
  • the overlap in the axial direction it is achieved that there is no distance between the facing blade parts in the axial direction, so that only one gap is created between the blade parts whose width extends in the circumferential direction. That is, the blade parts are spaced apart in the circumferential direction in the region of their free longitudinal edges. Because there is no axial clearance between the blade parts, free flow of the fluid through the gap upon rotation of the impeller is prevented so that the efficiency loss due to the gap is minimized.
  • the overlap of the blade parts is formed so that the overlap in the course of the blade from the inner to the outer diameter of the impeller changes and in particular decreases. In this way, it is possible to improve the continuity of the gap for impurities from the inner diameter to the outer diameter, so that impurities which have once entered the gap at the inner diameter, are reliably conveyed out of the gap on the outer periphery of the impeller and not get stuck in the gap.
  • the gap may also be formed so that it widens in the course of the blade from the inner to outer diameter of the impeller.
  • the gap can expand, in particular in the circumferential direction. This embodiment also ensures that the contaminants which have entered the gap are reliably conveyed out of the gap and do not settle there.
  • the impeller is formed so that a plurality of the previously described, having a continuous gap blades are arranged between the two cover plates.
  • an impeller is provided with multiple flow channels, which offers a higher efficiency compared to the impellers with only one flow channel. Due to the design of the blades with the through-going gap, which extends from the inner edge of the blade to the outer edge of the blade, that is, from the edge on the inner diameter to the edge on the outer diameter, it can be ensured at the same time that long-fiber contaminants not at the Suction mouth of the pump facing inner edges of the blades can catch. These impurities would rather, enter the nip and conveyed by the fluid flow to the outer periphery of the impeller.
  • the connecting element between the two cover disks is preferably designed as a continuous blade connecting the two cover disks with each other. That is, this blade has no gap and is formed according to the blades in conventional covered wheels. The blade establishes the firm connection between the two cover discs. In this way, the connecting element also supports the pumping action of the impeller.
  • the cover plates are connected to each other only via a single continuous blade. Accordingly, all other blades of the impeller are formed as described above with a continuous gap. In this way, the risk that impurities settle in the impeller, largely reduced, since only a single blade has a continuous edge located on the inner diameter at which impurities could accumulate. For all other blades such impurities can not settle because they would be discharged through the gap during rotation of the impeller to the outside.
  • the gap in the blade or the gaps in the plurality of blades preferably extend in the direction of flow of a fluid to be conveyed by the rotor wheel. In this way it is achieved that impurities which have entered the gap can be conveyed in the direction of movement of the fluid to the outer diameter of the impeller. That is, the fluid flow can entrain contaminants in the gap and convey it outward.
  • the impeller is particularly preferably designed as a, preferably one-piece, casting made of metal or plastic.
  • wheels made of cast metal are preferably used because they have a high strength and the risk of damage to the impeller by impurities is relatively low.
  • castings made of metal or plastic can also be formed as complex cast wheels.
  • the impeller made of sheet metal, in particular stainless steel sheet.
  • the blades or the blade parts are preferably angled in cross-section L-shaped and welded to one of the legs on one of the cover plates. The fact that one of the legs lies flat against the cover disc, a firm connection of the blades or blade parts can be achieved with the cover plate, even if they are connected only at one axial end with a cover plate.
  • the edge of the blade located at the inner diameter of the impeller ie, the inner edge of the blade, is preferably formed as a guide to the entrance of the gap, so that long-fiber contaminants are guided from the edge into the gap.
  • the inner edge of the blade can in particular be chamfered or rounded, wherein the bevel or rounding runs to the gap or the entrance of the gap at the inner diameter.
  • the invention further relates to a pump unit with an impeller according to the foregoing description. That is, the pump unit with the above-described impeller is used as a waste water pump. Wastewater pumps usually promote contaminated fluid, so that in this case the impeller described above has particular advantages, since the risk that settle impurities on the impeller is significantly reduced by the impeller according to the invention.
  • the impeller has two cover disks 2 and 4, of which the cover disk 4 has a central inlet opening 6. Through the inlet opening 6, the fluid to be delivered is sucked in on rotation of the impeller about the axis of rotation X.
  • a first blade 8 is arranged, which is formed continuously and the cover plates 2 and 4 firmly connected to each other, so that they are held in the direction of the longitudinal axis X at a defined distance.
  • the blade 8 ensures that the cover plate 4 rotates together with the cover plate 2 about the longitudinal axis X.
  • the drive shaft for the impeller engages the central opening 10 in the cover plate 2, so that the drive torque is transmitted to the cover plate 2 and from this via the blade 8 on the cover plate 4th
  • the impeller still has a split-shaped blade, which is formed from two blade parts 12 and 14.
  • the blade part 12 is firmly connected to the cover plate 2 and the blade part 14 fixed to the cover plate 4.
  • the blade portion 12 is integrally formed with the cover plate 2 and the blade portion 14 integral with the cover plate 4.
  • the entire impeller is integrally formed from cast metal.
  • the blade parts 12 and 14 are arranged relative to one another such that a gap 16 is formed between them.
  • the gap 16 is formed in such a way that the longitudinal edges 18 and 20 of the blade parts 12 and 14 are offset from each other in the circumferential direction, so that in a, here curved, plane, which runs obliquely to the axis of rotation X, the gap 16 is formed.
  • the blade parts 12 and 14 overlap one another such that the free longitudinal edge 18 of the blade part 12 is located closer to the cover plate 4 than the free longitudinal edge 20 of the blade part 14. That is, in the axial direction X is no gap between the blade parts 12 and 14th formed so that in a plane transverse to the longitudinal axis X, the fluid can not flow directly through the gap 16.
  • the lower cover plate 2 is formed on its side facing the cover plate 4 conical or conical. Accordingly, the cover plate 2 facing inside of the cover plate 4 is conical.
  • a flow channel 20 is formed between the blade 8 and the blade formed from the blade parts 12 and 14, which leads from the inlet opening 6 to the outer periphery of the impeller. That is, in the flow channel 20 is a flow guide from the axial inlet at the opening 6 to a radial outlet on the outer circumference of the impeller.
  • the gap 16 between the blade parts 12 and 14 extends along this flow channel 20 in the direction of flow of the fluid approximately in the middle of the blade formed by the blade parts 12 and 14.
  • the gap 16 extends from the inner edges 22 and 24 of the blade parts 12 and 14 facing the inner diameter of the blade wheel to the outer edges 26 and 28 of the blade parts 12 and 14 located at a further outer diameter, in particular at the outer periphery of the rotor.
  • the inner edges 22 and 24 are chamfered so that they are inclined to the entrance of the gap 16 on the inner diameter of the impeller. In this way, long-fiber contaminants, which stick to the inner edges 22 and 24 upon rotation of the impeller, are guided in the gap 16. That is, the edges 22 and 24 are arranged so that they are not normal to the circumferential direction but obliquely aligned with the circumferential direction. Preferably, the edges in the transition region to the longitudinal edges 16 and 18 are also rounded, so that long-fiber contaminants easily slip into the gap 16 and can slide over the longitudinal edges 16 and 18 to the outer periphery of the impeller. Since the gap 16 extends in the flow direction of the fluid to be conveyed, the impurities in the gap are entrained by the fluid and conveyed to the outside.
  • the gap 16 is formed so as to widen toward the outer circumference, i. H. has at its edges facing the edges 26 and 28 a greater width than at the edges 22 and 24 facing the inlet region. This ensures that contaminants that have entered the gap do not settle there and are conveyed safely to the outside.
  • the impeller described is particularly suitable for use in a sewage pump through which contaminated fluid is conveyed.
  • the impeller in the pump may be preceded by a cutting unit.
  • the impeller is also particularly suitable for a single-stage pump. Downstream of the impeller in the flow direction is preferably a spiral housing, which deflects the radially emerging from the impeller fluid to a discharge nozzle of the pump, which may extend in particular in the axial direction or parallel to the axis of rotation X.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Claims (15)

  1. Roue mobile pour une unité de pompage, en particulier pour une unité de pompage des eaux usées, comprenant deux flasques de recouvrement (2, 4) espacés l'un de l'autre en direction axiale (X), qui sont reliés l'un à l'autre par l'intermédiaire d'au moins un élément de jonction (8), et au moins une aube (12, 14) qui est disposée entre les deux flasques de recouvrement (2, 4) et qui s'étend d'un diamètre intérieur de la roue mobile à un diamètre extérieur de la roue mobile,
    caractérisée en ce que
    l'aube (12, 14) présente une fente (16) continue, qui s'étend de l'arête (22, 24), située à hauteur du diamètre intérieur, de l'aube (12, 14) jusqu'à l'arête (26, 28), située à hauteur du diamètre extérieur, de l'aube (12, 14).
  2. Roue mobile selon la revendication 1, caractérisée en ce que l'aube (12, 14) n'est reliée qu'à l'un des deux flasques de recouvrement (2, 4).
  3. Roue mobile selon la revendication 1 ou 2, caractérisée en ce que la fente (16) divise l'aube en deux parties d'aube (12, 14), dont chacune n'est reliée qu'à l'un des deux flasques de recouvrement (2, 4).
  4. Roue mobile selon la revendication 3, caractérisée en ce que les deux parties d'aube (12, 14) sont disposées en décalage l'une par rapport à l'autre, dans la région de la fente (16), suivant la direction circonférentielle de la roue mobile.
  5. Roue mobile selon la revendication 4, caractérisée en ce que les deux parties d'aube (12, 14) sont, dans la direction axiale (X), dotées d'une longueur telle, qu'elles se chevauchent l'une l'autre en direction axiale (X), dans la région de la fente (16).
  6. Roue mobile selon la revendication 5, caractérisée en ce que le chevauchement des parties d'aube (12, 14) se modifie et, en particulier, diminue dans le sens d'extension de l'aube du diamètre intérieur vers le diamètre extérieur de la roue mobile.
  7. Roue mobile selon l'une des revendications précédentes, caractérisée en ce que la fente (16) s'élargit dans le sens d'extension de l'aube (12, 14) du diamètre intérieur vers le diamètre extérieur de la roue mobile.
  8. Roue mobile selon l'une des revendications précédentes, caractérisée en ce que plusieurs aubes (12, 14) présentant une fente (16) continue, sont disposées entre les deux flasques de recouvrement (2, 4).
  9. Roue mobile selon l'une des revendications précédentes, caractérisée en ce que l'élément de jonction est réalisé sous forme d'une aube continue (8), reliant l'un à l'autre les deux flasques de recouvrement (2, 4).
  10. Roue mobile selon la revendication 9, caractérisée en ce que les deux flasques de recouvrement (2, 4) ne sont reliés l'un à l'autre que par une aube continue (8) unique.
  11. Roue mobile selon l'une des revendications précédentes, caractérisée en ce que la fente (16) dans l'aube (12, 14) s'étend dans la direction d'écoulement d'un fluide devant être transporté par la roue mobile.
  12. Roue mobile selon l'une des revendications précédentes, caractérisée en ce qu'elle est réalisée sous forme d'une pièce moulée en métal ou en matière plastique, de préférence monobloc.
  13. Roue mobile selon l'une des revendications 1 à 11, caractérisée en ce que la roue mobile est réalisée en tôle, en particulier en tôle d'acier inoxydable, les aubes ou les parties d'aube (12, 14) étant coudées, de préférence sous forme d'un L en coupe transversale, et étant soudées, avec une branche, à l'un des flasques de recouvrement (2, 4).
  14. Roue mobile selon l'une des revendications précédentes, caractérisée en ce que l'arête (22, 24) de l'aube (12, 14), située à hauteur du diamètre intérieur de la roue mobile, est conçue comme un guide en direction de l'entrée de la fente (16), de sorte que des impuretés à longues fibres sont conduites dans la fente (16) par l'arête (22, 24).
  15. Unité de pompage comprenant une roue mobile selon l'une des revendications précédentes, caractérisée en ce qu'elle est conçue comme une pompe à eaux usées.
EP05028030A 2005-12-21 2005-12-21 Roue pour une unité de pompage et unité de pompage correspondante Not-in-force EP1811184B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP05028030A EP1811184B1 (fr) 2005-12-21 2005-12-21 Roue pour une unité de pompage et unité de pompage correspondante
AT05028030T ATE385290T1 (de) 2005-12-21 2005-12-21 Laufrad für ein pumpenaggregat und zugehöriges pumpenaggregat
DE502005002739T DE502005002739D1 (de) 2005-12-21 2005-12-21 Laufrad für ein Pumpenaggregat und zugehöriges Pumpenaggregat
CN2006800464917A CN101326372B (zh) 2005-12-21 2006-12-13 用于泵装置的叶轮和相关的泵装置
PCT/EP2006/011990 WO2007079890A1 (fr) 2005-12-21 2006-12-13 Roue a aubes pour ensemble de pompe et ensemble de pompe associe
US12/158,462 US8251663B2 (en) 2005-12-21 2006-12-13 Impeller for a pump unit and associated pump unit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05028030A EP1811184B1 (fr) 2005-12-21 2005-12-21 Roue pour une unité de pompage et unité de pompage correspondante

Publications (2)

Publication Number Publication Date
EP1811184A1 EP1811184A1 (fr) 2007-07-25
EP1811184B1 true EP1811184B1 (fr) 2008-01-30

Family

ID=36274079

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05028030A Not-in-force EP1811184B1 (fr) 2005-12-21 2005-12-21 Roue pour une unité de pompage et unité de pompage correspondante

Country Status (6)

Country Link
US (1) US8251663B2 (fr)
EP (1) EP1811184B1 (fr)
CN (1) CN101326372B (fr)
AT (1) ATE385290T1 (fr)
DE (1) DE502005002739D1 (fr)
WO (1) WO2007079890A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2188532B1 (fr) * 2007-08-16 2011-10-12 Frideco AG Roue à aubes de pompe et pompe comprenant une telle roue à aubes de pompe
WO2013082717A1 (fr) 2011-12-06 2013-06-13 Bachellier Carl Roy Appareil à roue à ailettes amélioré et procédé de dispersion perfectionné
US9206820B2 (en) * 2012-06-11 2015-12-08 Aerojet Rocketdyne, Inc. Inducer with cavitation instability controls to reduce vibrations and radial loads
DK2908012T3 (en) 2014-01-24 2019-04-01 Mcfinn Tech Radial impeller and centrifugal pump housing
WO2015160850A1 (fr) * 2014-04-14 2015-10-22 Enevor Inc. Roue à aubes conique et ses applications
US20160186758A1 (en) * 2014-08-06 2016-06-30 Flow Control Llc. Impeller with axially curving vane extensions to prevent airlock
CN104806561B (zh) * 2014-10-15 2017-02-15 湖南山水节能科技股份有限公司 一种带加宽叶轮出口调节装置的可调泵
CN104806564B (zh) * 2014-10-15 2017-02-15 湖南山水节能科技股份有限公司 一种带减窄叶轮出口调节装置的可调泵
US10480524B2 (en) * 2016-11-23 2019-11-19 Eddy Pump Corporation Eddy pump impeller
USD951301S1 (en) * 2019-04-03 2022-05-10 Eugene Juanatas Hoehn Centrifugal impeller assembly
CN114076121A (zh) * 2021-03-15 2022-02-22 中交疏浚技术装备国家工程研究中心有限公司 一种将导叶应用于离心式泥泵以实现抗磨的新方法

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Publication number Priority date Publication date Assignee Title
DE2442446A1 (de) * 1974-09-05 1976-03-18 Lederle Pumpen & Maschf Pumpe zum foerdern von wasser und abwasser
DE3608229A1 (de) * 1986-03-12 1987-09-17 Klein Schanzlin & Becker Ag Laufschaufel fuer eine axialkreiselpumpe
US6220819B1 (en) * 2000-01-12 2001-04-24 Industrial Technology Research Institute Centrifugal pump impeller
DE10012181C2 (de) * 2000-03-13 2002-05-16 Ritz Pumpenfabrik Gmbh & Co Kg Kreiselpumpe mit Noppen-Laufrad und Noppen-Laufrad hierfür
US6506023B1 (en) * 2000-09-05 2003-01-14 Industrial Technology Research Institute Integrally formed stamping sheet-metal blades having 3D structure
DE10050108A1 (de) * 2000-10-09 2002-06-06 Allweiler Ag Laufrad für eine Kreiselpumpe
US7241114B2 (en) * 2002-10-30 2007-07-10 Siemens Ag Rotor for a centrifugal pump

Also Published As

Publication number Publication date
WO2007079890A1 (fr) 2007-07-19
DE502005002739D1 (de) 2008-03-20
US20090169374A1 (en) 2009-07-02
CN101326372A (zh) 2008-12-17
CN101326372B (zh) 2011-06-22
US8251663B2 (en) 2012-08-28
ATE385290T1 (de) 2008-02-15
EP1811184A1 (fr) 2007-07-25

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