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EP0449861B1 - Rotor de pompe centrifuge a vitesse specifique reduite - Google Patents

Rotor de pompe centrifuge a vitesse specifique reduite Download PDF

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Publication number
EP0449861B1
EP0449861B1 EP90900104A EP90900104A EP0449861B1 EP 0449861 B1 EP0449861 B1 EP 0449861B1 EP 90900104 A EP90900104 A EP 90900104A EP 90900104 A EP90900104 A EP 90900104A EP 0449861 B1 EP0449861 B1 EP 0449861B1
Authority
EP
European Patent Office
Prior art keywords
impeller
vane
centrifugal pump
ducts
pump impeller
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.)
Expired - Lifetime
Application number
EP90900104A
Other languages
German (de)
English (en)
Other versions
EP0449861A1 (fr
Inventor
Peter Hergt
Alexander Nicklas
Salvatore Scianna
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.)
KSB AG
Original Assignee
KSB AG
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 KSB AG filed Critical KSB AG
Priority to AT90900104T priority Critical patent/ATE89646T1/de
Publication of EP0449861A1 publication Critical patent/EP0449861A1/fr
Application granted granted Critical
Publication of EP0449861B1 publication Critical patent/EP0449861B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D29/2238—Special flow patterns
    • F04D29/2255—Special flow patterns flow-channels with a special cross-section contour, e.g. ejecting, throttling or diffusing effect
    • 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
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly

Definitions

  • the invention relates to a centrifugal pump impeller according to the preamble of the main claim.
  • impellers for centrifugal pumps which operate in the area of the lowest specific speed. These impellers have the feature that the actual blade channels are created by cutting tools, have a straight course and have a constant circular cross-section over their entire length. Compared to the known impellers with a diffuser-shaped blade channel, they have the advantage of being simple Manufacturability, but have the disadvantage of poor hydraulic efficiency.
  • the invention has for its object to provide an increase in the pressure coefficient and an improvement in efficiency in a centrifugal pump impeller for small flow rates and high delivery heights. This object is achieved in accordance with the characterizing part of the main claim.
  • the respective blade channels are cut obliquely. This enables the different inclination variations of the impeller cover disk and / or blade channels. This results in a gradual opening of the vane channels, on the basis of which a favorable influence on the liquid flowing within the vane channels is possible.
  • a further embodiment of the invention described in claim 5 provides that the distance between the impeller cover plate and the opposite housing wall is at most the difference between at the impeller outlet in Axial direction of measurable blade channel depth and an outward extension of the blade channel wall on the impeller outer diameter corresponds to the blade channel depth that can be determined.
  • the configurations described in claims 6 and 7 relate to the shape of the vane channel openings.
  • the opening of the vane channels which from the beginning widens continuously towards the outer diameter of the impeller, enables a smoothly occurring and slowly increasing impulse exchange towards the outlet.
  • the impeller (1) shown in Fig. 1 has a suction opening (2) through which the fastening means for connection to a pump shaft - not shown here - are also introduced.
  • the impeller cover disk (3) on the suction side has a smooth surface here and has an inclination which obliquely cuts the vane channels (5) in the region of the outer diameter of the impeller (4).
  • the blade channels (5) extend radially outward from the center of the impeller.
  • the shape of the impeller channels (5) selected here has a circular cross section; however, other cross-sectional shapes are also conceivable.
  • the blade channels (5) can be produced by bores made in the impeller from the outside. However, it is also possible to create the blade channel shapes using appropriate casting techniques.
  • each blade channel has an opening (6) that widens outwards.
  • the blade channel width (b) which can be measured directly there, is shown on the outside diameter. This is the blade channel width reduced by the inclined section.
  • the determinable blade channel width (b *) which corresponds to the uninfluenced blade channel width, results from the blade channel wall which is closest to the cover disk having the opening (6) through the opening (6) to the outside is extended. As shown in FIG. 4, the intersection (z) of this extension (x) with the cylindrical plane (y) of the impeller outer diameter forms a limit value, while the blade duct wall opposite this forms another limit that includes the determinable blade duct width (b *).
  • FIG. 2 shows a front view of the impeller (1), which can be seen how the blade channels run inside the impeller.
  • the impeller (1) shown here as an example has a number and shape of blade channels (5) which, at the impeller inlet (2) shown here, result in an overlap of the blade channels in the inlet.
  • the delivery rate can also be influenced by appropriate variation of the suction opening (2) forming the impeller inlet.
  • the openings (6) have a width (w) which is smaller than the maximum width of the blade channels (5).
  • the size of the width (w) can be influenced by a corresponding inclination of the blade channels or the cover disk.
  • Fig. 3 which corresponds to a section of III-III of Fig. 2, the course of the inclined blade channels (5) and the inclination of the impeller cover plates (3, 7) can be seen.
  • the blade channels and the impeller cover disks are inclined relative to planes (11, 12) that are perpendicular to the axis of rotation (8).
  • the alternating one blade channel is inclined to the suction-side cover plate (3) and the adjacent blade channel to the pressure-side cover plate (7).
  • a corresponding selection of the angle of inclination of the blade channels and / or the cover plate angle of inclination results in a cut of the blade channels in the impeller outlet area.
  • the right half of the figure also shows that the impeller on the suction side is opposite the housing wall (9) and on the pressure side the housing wall (10). Although these are parallel to the respective impeller cover, this is not a mandatory requirement. Different inclinations are also conceivable.
  • Fig. 4 From Fig. 4 it can be seen that in the area of the openings (6) between the impeller cover disc (3) and the suction-side housing wall (9) there is a distance (s) which is smaller than the difference (d) which can be measured on the impeller outer diameter (4) Blade channel width (b) and the determinable blade channel width (b *).
  • the distance (s) may at most correspond to the difference (d). A larger value would not produce the necessary effect.
  • the distance (s) used in the exemplary embodiment is smaller than the difference (d) shown.
  • the pump characteristic curve can be influenced in a simple manner in accordance with the selected distance (s).
  • the value (b *) can be determined by extending the blade duct wall provided with the opening (6) and closest to the housing towards the outside in the direction of the outer diameter of the impeller (4). Starting from the point of intersection (z) between the extension (x) and the cylindrical plane (y) of the outer diameter of the impeller, the blade channel width (b *) is determined into the blade channel. This can apply to both the suction and the pressure side of the impeller.
  • the distance (s) is always determined for one impeller side, i.e. on the suction or pressure side.
  • the distances (s) between the suction-side housing wall and the impeller cover plate or between the pressure-side housing wall and the impeller cover plate can have the same or different dimensions. If the open vane channels are only installed on one side of the impeller, then the distance (s) corresponds at most to the difference (d). If the open vane channels were attached on both sides, the distance (s) would be based on the dimensions prevailing on the respective impeller side.

Landscapes

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

Abstract

Un rotor de pompe centrifuge comprend des canaux (5) d'aubes qui présentent des ouvertures en forme de fentes (6) ménagées dans les disques de recouvrement (3, 7) du rotor, dans la région de son diamètre extérieur.

Claims (8)

  1. Roue de pompe centrifuge (1) de construction radiale et de vitesse de rotation spécifique faible dont les canaux entre les aubes (5) sont formés par des fentes ouvertes du côté de la chambre de flasque de la roue et traversant les disques de revêtement des flasques de la roue (3, 7), caractérisée en ce que les canaux entre les aubes (5) forment avec chacune des fentes (6) orientées vers la chambre de flasque de la roue des ouvertures orientées dans le sens radial par rapport à la partie externe de la roue, la longueur radiale de la partie fendue de l'ouverture orientée vers la flasque de roue étant égale ou inférieure à la moitié de la longueur du canal entre les aubes.
  2. Roue de pompe centrifuge selon la revendication 1 caractérisée en ce que les canaux entre les aubes (5) sont orientés perpendiculairement à l'axe de rotation (8) et en ce que la surface du disque de revêtement des flasques (3, 7) dont l'inclinaison forme un angle avec cet axe coupe obliquement les canaux entre les aubes (5) dans la zone de refoulement de la roue (1).
  3. Roue de pompe centrifuge selon la revendication 1 caractérisée en ce que les canaux entre les aubes (5) sont obliques par rapport à un plan radial de la roue et en ce que la surface des disques de revêtement des flasques coupe obliquement les canaux entre les aubes (5) dans la zone de refoulement de la roue (1).
  4. Roue de pompe centrifuge selon la revendication 1 caractérisée en ce que les canaux entre les aubes (5) et la surface du disque de revêtement des flasques (3, 7) sont inclinés l'un par rapport à l'autre.
  5. Roue de pompe centrifuge selon les revendications 1 à 4 caractérisée en ce que l'écart mesurable dans le sens de l'axe entre le disque de revêtement des flasques (3, 7) et la paroi du boîtier opposée (9, 10) correspond au plus à la différence (d) entre la largeur (b) du canal entre les aubes mesurable à la sortie de la roue dans le sens de l'axe et une largeur de canal entre les aubes (b*) pouvant être définie par une prolongation vers l'extérieur de la paroi du canal entre les aubes sur le diamètre externe de la roue (4).
  6. Roue de pompe centrifuge selon les revendications 1 à 5 caractérisée en ce que les ouvertures (6) des canaux entre les aubes placées dans la zone de refoulement de la roue (1) dans les disques de revêtement des flasques de la roue (3, 7) ont une forme qui s'élargit jusqu'au diamètre externe.
  7. Roue de pompe centrifuge selon les revendications 1 à 6 caractérisée en ce que les ouvertures (6) des canaux entre les aubes (5) qui s'élargissent dans le sens radial ont une largeur qui, au plus, correspond à la largeur du canal entre les aubes.
  8. Roue de pompe centrifuge selon une ou plusieurs des revendications 1 à 7 caractérisée en ce que les ouvertures (6) des canaux entre les aubes (5) s'élargissent dès le départ constamment jusqu'à atteindre le diamètre externe (4) de la roue.
EP90900104A 1988-12-23 1989-12-12 Rotor de pompe centrifuge a vitesse specifique reduite Expired - Lifetime EP0449861B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90900104T ATE89646T1 (de) 1988-12-23 1989-12-12 Kreiselpumpenlaufrad geringer spezifischer drehzahl.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3843428 1988-12-23
DE3843428A DE3843428C2 (de) 1988-12-23 1988-12-23 Kreiselpumpenlaufrad geringer spezifischer Drehzahl

Publications (2)

Publication Number Publication Date
EP0449861A1 EP0449861A1 (fr) 1991-10-09
EP0449861B1 true EP0449861B1 (fr) 1993-05-19

Family

ID=6369968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90900104A Expired - Lifetime EP0449861B1 (fr) 1988-12-23 1989-12-12 Rotor de pompe centrifuge a vitesse specifique reduite

Country Status (4)

Country Link
US (1) US5257910A (fr)
EP (1) EP0449861B1 (fr)
DE (2) DE3843428C2 (fr)
WO (1) WO1990007650A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5290236A (en) * 1991-09-25 1994-03-01 Baxter International Inc. Low priming volume centrifugal blood pump
DE102006040130A1 (de) * 2006-08-26 2008-02-28 Ksb Aktiengesellschaft Förderpumpe
DE102007020218A1 (de) * 2007-04-28 2008-10-30 Ksb Aktiengesellschaft Förderpumpe
US8221070B2 (en) * 2009-03-25 2012-07-17 Woodward, Inc. Centrifugal impeller with controlled force balance
PL216284B1 (pl) * 2010-03-22 2014-03-31 Fundacja Rozwoju Kardiochirurgii Im Prof Zbigniewa Religi Pompa odśrodkowa jednostrumieniowa
WO2014137206A1 (fr) * 2013-03-07 2014-09-12 Chaushevski Nikola Pompe à chambre rotative
KR102165728B1 (ko) * 2014-07-24 2020-10-14 닛산 가가쿠 가부시키가이샤 칼라필터 하층막 형성용 수지 조성물
US9777741B2 (en) 2014-11-20 2017-10-03 Baker Hughes Incorporated Nozzle-shaped slots in impeller vanes
JP6904622B1 (ja) * 2020-04-10 2021-07-21 セイコー化工機株式会社 磁気浮上式ポンプ
CN114483641B (zh) * 2022-02-15 2023-06-16 上海工业泵制造有限公司 一种叶轮及应用该叶轮的水泵

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA644854A (en) * 1962-07-17 Patay Pumps And Turbines Limited Rotary tube pumps, turbines and the like
NL102212C (fr) *
DE1249693B (fr) *
FR529613A (fr) * 1920-12-21 1921-12-02 Pompe centrifuge multitubulaire
US1986836A (en) * 1933-01-09 1935-01-08 Fairbanks Morse & Co Method of making centrifugal pumps
US2074650A (en) * 1934-01-24 1937-03-23 William S Holdaway Centrifugal pump
US1988875A (en) * 1934-03-19 1935-01-22 Saborio Carlos Wet vacuum pump and rotor therefor
GB575346A (en) * 1944-03-01 1946-02-14 Aluminium Plant & Vessel Co Improvements in or relating to centrifugal pumps
DE804064C (de) * 1944-03-01 1951-04-16 Apv Co Ltd Fluegelrad fuer Zentrifugalpumpen, insbesondere zum Foerdern von Milch
US2684062A (en) * 1950-11-18 1954-07-20 Rose David Centrifugal projector
US2956503A (en) * 1956-02-15 1960-10-18 Neidl Georg Rotary pumps, particularly for delivery of sewage, thick slurries and the like liquids
US3107625A (en) * 1961-09-01 1963-10-22 Walter E Amberg Centrifugal liquid pump
DE1453723A1 (de) * 1963-07-19 1969-07-31 Barske Ulrich Max Kreiselpumpe,insbesondere fuer kleine bis mittlere Foerderstroeme
SU620674A1 (ru) * 1976-09-21 1978-08-25 Предприятие П/Я Р-6603 Центробежное колесо
SU928080A1 (ru) * 1980-09-25 1982-05-15 Специальное Конструкторско-Технологическое Бюро Герметичных И Скважинных Насосов Рабочее колесо центробежного насоса
SU1052053A1 (ru) * 1982-04-29 1984-10-30 Uskov G I Центробежный насос
IT1187933B (it) * 1986-02-25 1987-12-23 Gilardini Spa Pompa rotativa per liquidi

Also Published As

Publication number Publication date
US5257910A (en) 1993-11-02
DE3843428A1 (de) 1990-07-05
WO1990007650A1 (fr) 1990-07-12
DE58904451D1 (de) 1993-06-24
EP0449861A1 (fr) 1991-10-09
DE3843428C2 (de) 1993-12-09

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