EP0114932B1 - Roue à canal pour une pompe centrifuge - Google Patents

Roue à canal pour une pompe centrifuge Download PDF

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Publication number
EP0114932B1
EP0114932B1 EP83109755A EP83109755A EP0114932B1 EP 0114932 B1 EP0114932 B1 EP 0114932B1 EP 83109755 A EP83109755 A EP 83109755A EP 83109755 A EP83109755 A EP 83109755A EP 0114932 B1 EP0114932 B1 EP 0114932B1
Authority
EP
European Patent Office
Prior art keywords
impeller
vane
edge
rotary pump
pump according
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
Application number
EP83109755A
Other languages
German (de)
English (en)
Other versions
EP0114932A1 (fr
Inventor
Martin Stähle
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
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
Priority claimed from CH750582A external-priority patent/CH660511A5/de
Priority claimed from CH212183A external-priority patent/CH662864A5/de
Application filed by Individual filed Critical Individual
Publication of EP0114932A1 publication Critical patent/EP0114932A1/fr
Application granted granted Critical
Publication of EP0114932B1 publication Critical patent/EP0114932B1/fr
Expired 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
    • F04D29/225—Channel wheels, e.g. one blade or one flow channel

Definitions

  • the invention relates to a centrifugal pump with a single-bladed impeller of open design, in particular for conveying viscous media, the outlet end of the bladed brushing a housing wall penetrated by the impeller axis, and the pressure-side blade flank in front of the housing wall ending in a front edge running between the tip edge of the blade and the impeller hub .
  • the present invention aims to provide a centrifugal pump of the type mentioned, in which the housing wall and the front edge cooperate in such a way that perfect delivery of viscous media is also possible.
  • the centrifugal pump according to the invention is characterized in that the housing wall is a straight truncated cone, the front edge of the impeller blade flank on the pressure side impinging the truncated cone wall with play extending from the blade outlet tip over a circumferential angle of at least 20 ° to a point where it ends in the impeller hub.
  • the end edge can be designed as a sharp shear edge which interacts with a counter-shear edge of the housing wall.
  • the relevant angles namely cone angle of the housing wall, flank angle of the blade and circumferential angle of the blade front edge, counter edge angle on the housing and shear edge angle on the blade, can vary within relatively large ranges.
  • the housing wall cone angle and the flank angle of the blade can be between 5 ° and 70 °, and the front edge circumferential angle between 20 ° and 360 ° or more.
  • the counter shear edge angle and the shear edge angle can each be between 5 ° and 90 °, but together should not be 180 °.
  • the single-bladed impeller has a conical hub 1, the axis la of which is mounted in the housing 2 in a manner not shown, passing through the pressure-side housing wall 3.
  • the housing wall 3 forms a straight truncated cone and is brushed with a small clearance 4 by the blade 5, the end edge of which is designated by 6.
  • the angle of inclination of the housing wall 3 to the radial plane is called the cone angle below.
  • the radially inner edge 9 of this cutout forms a stationary shear edge, the pitch angle of which is designated 8.
  • the blade flank 7 runs out at point 7a into the front edge 8 of the blade 5;
  • the blade front edge 8 ends in the hub 1.
  • the blade front edge 8 forming the pressure-side boundary of the blade flank 7 and covering the truncated cone housing wall 3 extends over a circumferential angle ⁇ up to the blade tip 8a , in which the blade end edge 6 runs out via a step 6a.
  • the condition here is that the two angles 8 and y together must not be 180 °, because only then does a real shear effect occur while the cut parts are pushed away at the same time.
  • the flank angle c which causes a fiber loop coming onto the flank 7 to slide towards the pressure side and must therefore be at least about 5 °, is expediently between about 15 ° and 40 °; an angle e of 30 ° has proven to be particularly suitable.
  • circumferential angle ⁇ of the blade front edge (between tip 8a and point 7a) can assume virtually any value between approximately 20 ° and 360 °.
  • circumferential angles ⁇ between 90 ° and 270 ° have been found to be particularly advantageous.
  • a longer fibrous part no longer needs to slide along the blade end edge 6 with its always relatively weak slope to the blade tip 6a in order to reach the area of the interacting shear edges 8, 9; rather, the fibrous part will slide off directly on the pressure-side flank 7 against the point 7a of the smallest radial distance of the blade front edge 8 and cut over this counter-shear edge 9 on the housing wall while slipping over this point 7a; Even if several passes or revolutions of the impeller are required to completely cut the fibrous part, this happens considerably faster than if the complete slipping of the fibrous part along the blade end edge 6 would have to be waited for.
  • the impeller of the centrifugal pump shown in FIGS. 6-10 has a conical hub 21 with a blade 25, whose axis 33 passes through the pressure-side housing wall 23, which is designed as a truncated cone.
  • the housing wall 23, which has a cone angle between 5 ° and 70 °, is coated with a small clearance 24 by the end edge 28 of the pressure-side blade flank 27. This end edge 28 extends from the blade outlet tip 35, into which the end edge 26 ends, spirally over a relatively large distance to a point 31 at which it ends in the hub 21, which has a relatively small radius r.
  • a relatively large area of the housing wall 23 is exposed over a relatively large arc v, which is expediently between 30 ° and 90 °, between the blade outlet tip 35 and the aforementioned hub location 31.
  • the exposure of the housing wall by reducing the impeller hub radius r can go so far that it can still be responsible for the strength conditions for the power transmission from the drive shaft 33 through the impeller hub to the blade.
  • the width b of the uncovered part of the rear housing wall which becomes visible between the pressure-side flank 27 and the suction-side flank 39 in the impeller delivery channel, decreases the more it extends against the impeller inlet part. This reduction in the width b in the direction of the impeller inlet takes place for reasons of the strength and stability of the blade end part.
  • the exposed part of the housing wall in the impeller conveying channel will have an arc v calculated from the impeller end edge tip 35 of e.g. Have at least 20 °, certain impeller shapes can allow an arc of up to 180 °. This means that the end edge 28 can extend over a circumferential angle between 360 ° and 540 °.
  • An outlet opening 36 is provided in the housing wall 23 in the vicinity of the drive shaft, so that gases can escape which are carried in the conveying medium and which separate out against the impeller rotation center and reach the housing wall center through the uncovering of the impeller.
  • impeller hub 21 and the housing wall 23 form a labyrinth between the exposure of the impeller rear side and the interior 37 between the hub and the rear wall, where the outlet opening 36 is located, so that no co-conveyed solid parts get into the outlet opening.
  • the labyrinth structure is interrupted at least on the housing wall side (in FIG. 9 also on the hub side) by means of a transverse groove 38, so that a self-cleaning effect occurs.

Landscapes

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

Claims (10)

1. Pompe centrifuge comprenant une roue à une aube de construction ouverte destinée en particulier au refoulement de fluides visqueux, l'extrémité d'évacuation de l'aube (5, 25) balayant avec un jeu une paroi du boîtier (3, 23) traversée par l'axe de la roue (1a, 33), et le flanc de l'aube (7, 27) côté refoulement se terminant devant la paroi du boîtier (3, 23) par un bord d'attaque (8, 28) se prolongeant entre la pointe de sortie de l'aube (8a, 35) et le moyeu de la roue à aubes (1, 21), caractérisée en ce que la paroi du boîtier (3, 23) est un cône droit tronqué, le bord d'attaque (8, 28) du flanc de l'aube de la roue côté refoulement (7, 27) qui balaye avec du jeu (4, 24) la paroi du cône tronqué, s'étendant de la pointe de sortie de l'aube (8a, 35) sur un angle inscrit (11) d'au moins 20° jusqu'à un endroit (7a, 31) où il se termine dans le moyeu de la roue à aubes (1, 21);
2. Pompe centrifuge selon la revendication 1, caractérisée en ce que le bord d'attaque (28) du flanc de l'aube de la roue côté refoulement (27) s'étend entre la pointe de sortie (35) et la position extrême (31) du moyeu (21) sur un angle inscrit d'au moins 380° et de 540° au plus.
3. Pompe centrifuge selon la revendication 2, caractérisée en ce que la partie de la paroi de boîtier (23) libérée entre le flanc de l'aube (27) côté refoulement et le flanc de l'aube (39) côté aspiration gràce au long bord d'attaque (28) s'étend sur un arc (v) d'au moins 30° entre la pointe de l'arête de la roue à aubes (35) et la position du moyeu (31) déjà citée.
4. Pompe centrifuge selon l'ume des revendications 1 à 3, caractérisée en ce que la paroi du boîtier (23) est munie à proximité de l'arbre d'entraînement d'une ouverture d'échappement (36) destinée aux gaz comtenus dans le fluide à refouler.
5. Pompe centrifuge selon l'une des revendicatioms 1 à 4, caractérisée en ce que le moyeu de la roue à aubes (21) et la paroi du boîtier (23) forment entre la surface de la paroi libérée et l'espace intérieur situé entre le moyeu et la paroi arrière et ventilé par une ouverture d'échappement (3e), un labyrinthe qui empêche que des morceaux solides ne sortent par cette ouverture d'échappement.
6. Pompe centrifuge selon la revendication 5, caractérisée en ce que le labyrinthe est interrompu au moins du côté de la paroi par une rainure transversale (38).
7. Pompe centrifuge selon la revendication 1, en particulier destinée à refouler des matières solides à fibres longues en suspension, caractérisée en ce que le bord d'attaque est réalisé sous la forme d'une arête coupante qui interagit avec ume contre-arête coupante (9) de la paroi du boîtier.
8. Pompe centrifuge selon la revendication 7, caractérisée en ce que l'angle d'inclinaison (e) du flanc de l'aube (7) cêté refoulement et l'angle du cône (4) de la paroi du boîtier (3) sont chacun compris entre au moins 5° et 70° au plus et de préférence entre 15° et 40°, tandis que l'angle inscrit (η) du bord d'attaque de l'aube (8) situé entre la pointe de l'aube (8a) et une position près de l'axe (7a) de ce bord est compris entre 90° et 270°.
9. Pompe centrifuge selon la revendication 8, caractérisée en ce que la somme des angles aigus d'inclinaison (y, 8) du bord d'attaque de l'aube (8) et de la contre-arête coupante (9) reste inférieure à 180°.
10. Pompe centrifuge selon la revendication 9, caractérisée en ce que l'arête extrême de l'aube (6) comporte directement devant la pointe de l'aube (8a) côté refoulement un seuil (6a) empêchant les morceaux de matière fibreuse de glisser facilement le long de l'arête extrême.
EP83109755A 1982-12-22 1983-09-29 Roue à canal pour une pompe centrifuge Expired EP0114932B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH750582A CH660511A5 (en) 1982-12-22 1982-12-22 Centrifugal pump having a single-blade impeller
CH7505/82 1982-12-22
CH212183A CH662864A5 (en) 1983-04-20 1983-04-20 Centrifugal pump having an open-type single-blade impeller
CH2121/83 1983-04-20

Publications (2)

Publication Number Publication Date
EP0114932A1 EP0114932A1 (fr) 1984-08-08
EP0114932B1 true EP0114932B1 (fr) 1986-09-03

Family

ID=25689566

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83109755A Expired EP0114932B1 (fr) 1982-12-22 1983-09-29 Roue à canal pour une pompe centrifuge

Country Status (8)

Country Link
US (1) US4540334A (fr)
EP (1) EP0114932B1 (fr)
BR (1) BR8306883A (fr)
CA (1) CA1214687A (fr)
DE (1) DE3365881D1 (fr)
DK (1) DK154907C (fr)
ES (1) ES528338A0 (fr)
FI (1) FI72577C (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2118712C1 (ru) * 1993-07-16 1998-09-10 Штеле Мартин Центробежный насос

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4778336A (en) * 1987-07-09 1988-10-18 Weil Pump Company Cutter pump subassembly
IL122889A (en) * 1995-07-10 2001-03-19 Harman Jayden David Rotor for use with a fluid flow generator or reactor
AU694679B2 (en) * 1995-07-10 1998-07-23 Jayden David Harman A rotor
US5997242A (en) * 1996-12-02 1999-12-07 Alden Research Laboratory, Inc. Hydraulic turbine
SE520416C2 (sv) * 1997-11-18 2003-07-08 Flygt Ab Itt Pumphjul
CA2405497C (fr) 1999-11-25 2009-01-27 Jayden David Harman Rotor a lame unique ou multilames
AUPR982502A0 (en) * 2002-01-03 2002-01-31 Pax Fluid Systems Inc. A heat exchanger
AUPR982302A0 (en) 2002-01-03 2002-01-31 Pax Fluid Systems Inc. A fluid flow controller
DE03726967T1 (de) * 2002-01-03 2005-05-04 Pax Scient Inc Wirbelringerzeuger
AU2003903386A0 (en) * 2003-07-02 2003-07-17 Pax Scientific, Inc Fluid flow control device
CN1875193A (zh) * 2003-11-04 2006-12-06 百思科技公司 流体循环系统
KR20070012357A (ko) * 2004-01-30 2007-01-25 팍스 싸이언티픽 인코퍼레이션 원심 팬, 펌프 또는 터빈용 하우징
CN1985093A (zh) * 2004-01-30 2007-06-20 百思科技公司 用于离心通风机、泵或涡轮机的机罩
JP2006132417A (ja) * 2004-11-05 2006-05-25 Toshiba Tec Corp ポンプ
USD570996S1 (en) 2006-09-25 2008-06-10 Pax Scientific, Inc. Rotor
WO2008042251A2 (fr) 2006-09-29 2008-04-10 Pax Streamline, Inc. Ventilateur hélicoïdal
USD570999S1 (en) 2006-11-22 2008-06-10 Pax Scientific, Inc. Rotor
US20090308472A1 (en) * 2008-06-15 2009-12-17 Jayden David Harman Swirl Inducer
US8506236B2 (en) * 2009-08-03 2013-08-13 Ebara International Corporation Counter rotation inducer housing
WO2011017372A1 (fr) * 2009-08-03 2011-02-10 Ebara International Corporation Inducteur à étages multiples pour pompes centrifuges
US8550771B2 (en) * 2009-08-03 2013-10-08 Ebara International Corporation Inducer for centrifugal pump
US9968810B2 (en) * 2010-02-19 2018-05-15 Leonard E. Doten Bucket supported polymer gel emulsion preparation system
WO2013120049A1 (fr) 2012-02-10 2013-08-15 Randy Dixon Pompe à lobes avec lames racleuses
CN102536835B (zh) * 2012-03-21 2014-04-09 江苏大学 固液两相流螺旋离心泵
US10273970B2 (en) * 2016-01-27 2019-04-30 John A. Kozel Construction of articles of manufacture of fiber reinforced structural composites
DE102017213507A1 (de) * 2017-08-03 2019-02-07 KSB SE & Co. KGaA Laufrad für Abwasserpumpe
CN110425178A (zh) * 2019-06-27 2019-11-08 山西天海给排水设备有限公司 一种高效无堵塞螺旋离心泵叶轮的几何参数的设计算法

Citations (1)

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Publication number Priority date Publication date Assignee Title
DE2855385B1 (de) * 1978-08-31 1979-11-22 Martin Staehle Kreiselpumpe mit Einschaufel-Laufrad zur Foerderung von langfaserigen aufgeschwemmten Feststoffen

Family Cites Families (5)

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Publication number Priority date Publication date Assignee Title
US1959710A (en) * 1931-09-21 1934-05-22 Chicago Pump Co Pump
US2202790A (en) * 1938-02-23 1940-05-28 Allis Chalmers Mfg Co Waste paper stock pump
US2845870A (en) * 1955-04-22 1958-08-05 Borg Warner Fuel booster pump
US3028140A (en) * 1957-06-17 1962-04-03 James R Lage Rotary fluid flow machine having rotor vanes constructed according to three dimensional calculations
DE1528890A1 (de) * 1965-08-14 1970-01-29 August Wuebker & Soehne Ohg Ma Vertikalpumpe fuer Jauchegruben

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2855385B1 (de) * 1978-08-31 1979-11-22 Martin Staehle Kreiselpumpe mit Einschaufel-Laufrad zur Foerderung von langfaserigen aufgeschwemmten Feststoffen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2118712C1 (ru) * 1993-07-16 1998-09-10 Штеле Мартин Центробежный насос

Also Published As

Publication number Publication date
FI72577B (fi) 1987-02-27
US4540334A (en) 1985-09-10
ES8501851A1 (es) 1984-12-01
CA1214687A (fr) 1986-12-02
FI834352A0 (fi) 1983-11-28
DK154907C (da) 1989-06-12
DK582683D0 (da) 1983-12-16
EP0114932A1 (fr) 1984-08-08
ES528338A0 (es) 1984-12-01
FI834352L (fi) 1984-06-23
DK582683A (da) 1984-06-23
DK154907B (da) 1989-01-02
DE3365881D1 (en) 1986-10-09
BR8306883A (pt) 1984-07-31
FI72577C (fi) 1987-06-08

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