EP1029180A1 - Pompe a canal lateral et flux circonferentiel - Google Patents

Pompe a canal lateral et flux circonferentiel

Info

Publication number
EP1029180A1
EP1029180A1 EP97950152A EP97950152A EP1029180A1 EP 1029180 A1 EP1029180 A1 EP 1029180A1 EP 97950152 A EP97950152 A EP 97950152A EP 97950152 A EP97950152 A EP 97950152A EP 1029180 A1 EP1029180 A1 EP 1029180A1
Authority
EP
European Patent Office
Prior art keywords
side channel
impeller
face
area
edge
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.)
Withdrawn
Application number
EP97950152A
Other languages
German (de)
English (en)
Inventor
Peter Fandrey
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.)
Sterling Fluid Systems Germany GmbH
Sterling Fluid Systems GmbH
Original Assignee
Sterling Fluid Systems Germany GmbH
Sterling Fluid Systems 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 Sterling Fluid Systems Germany GmbH, Sterling Fluid Systems GmbH filed Critical Sterling Fluid Systems Germany GmbH
Publication of EP1029180A1 publication Critical patent/EP1029180A1/fr
Withdrawn legal-status Critical Current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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/007—Details of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet
    • F05B2250/503—Inlet or outlet of regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise

Definitions

  • the invention relates to a side channel centrifugal pump with a housing forming a side channel, the surface of which, adjacent to the side channel, forms an end face adjacent to the impeller except for a narrow gap, the
  • transition edge from the side channel to the end face is rounded in those areas in which it deviates from the circumferential direction, and with an impeller, the wings of which have a predetermined web width in the circumferential direction in the end plane of the impeller.
  • the invention has for its object to reduce the tendency to cavitation and noise in a pump of the type mentioned. It achieves this through the features of claim 1 and preferably those of the subclaims.
  • the invention is based on the knowledge that cavitation and noise generation are to be expected not only at those points where the flow velocity of the medium being conveyed is particularly high, but also at other transition edges. It is also based on the knowledge that a rounding only promises an optimal effect if its radius of curvature is matched to the wing speed and the web width of the wing.
  • the wing speed is to be understood as its peripheral speed at the point in question in each case.
  • the web width is to be understood as the width of the impeller in the circumferential direction in the end plane of the impeller. The greater the wing speed and the web width, the greater the rounding should be.
  • the effect of the rounding is that when the end of the wing reaches the end of the end face and the beginning of the side channel, it does not suddenly enter quasi-still liquid there, but already in the area of the rounding Flow around the wing edges is built up, which brings about a pressure equalization and reduces the shock. This preparatory flow is all the more violent, the higher the relative speed of the wing to the edge of the housing and the shorter the rounding. It was also found that the smaller the web width of the wing, the cheaper it is. The invention teaches for the first time the consideration of this interdependency and the use of a certain minimum value of the quotient of edge radius and web width for a given wing speed.
  • this circumferential length including the rounding sections is at least 2.5 wing divisions. Furthermore, it has proven to be expedient that the depth of the side channel increases shortly before its end.
  • Fig. 1 is a plan view of a housing part that forms the side channel
  • Fig. 2 shows a section along line AB of Fig. 1
  • Fig. 3 shows a cylindrical section along line CD of Fig. 1
  • Fig. 4-6 shows enlarged details of the in Fig. 2 and 3 areas designated IV-VI.
  • Side channel 1 is expanded.
  • the side channel 1 is delimited radially on the inside by the edge 2 and on the outside by the edge 3. It begins at point 4 at the same angular point at which the suction opening 5 begins radially further inwards at point 6, the outline of which is indicated by dash-dotted lines in FIG. It is located in the other housing part, not shown in the drawing.
  • the side channel widens under a correspondingly oblique course of its inner edge 7 until it reaches its final cross section approximately 60-90 ° after its start, which can be seen in FIG. 2 above. It keeps it up to the pressure opening 8 through which the medium exits the side channel.
  • the pressure opening is limited by the side boundaries 11, 12, by the side channel bottom 10 and by the edge 9 (FIG. 3).
  • the housing part shown Radially inside the inner boundary edge 2, outside the outer boundary edge 3 and between the start edge 7 and the end edge 9 of the side channel, the housing part shown forms a flat end face, which in the assembled pump is adjacent to the impeller (blade 16 in FIG. 3) is and includes a small sealing gap with its end face 13.
  • the apex region 14 between the end edge 9 and the start edge 7 of the side channel also belongs to this end face.
  • the blades 16 of the impeller located in this area each have the task of sealing the pressure difference between the end (pressure opening 8) and the beginning 4 of the side channel 1 in close cooperation with this surface 14.
  • the wings 16 indicated in cross-section sweep with their web 17 at a short distance over the surface 14 until they reach the edge 7 and enter the more or less stationary medium at this point.
  • the associated shock is reduced according to the invention by rounding the edge 17 according to radius 15, this radius corresponding to the design rule according to the invention. Its minimum value is 0.25 [sec / m] times the wing circumferential speed [m / sec] times the web width in the circumferential direction [mm].
  • the factor is preferably between 0.4 and 0.6. It should not be greater than 1, because otherwise the curve becomes so large that it disadvantageously reduces the effective length of the side channel.
  • the length of the curvature cannot namely be increased at the expense of the circumferential length of the apex 14, which is determined by the distance between the edge 9 and the beginning 4 of the side channel, because the mentioned seal must be effective in this area.
  • the edge 9 on the side facing the impeller is also rounded, as can be seen from FIG.
  • the circumferential distance between the point furthest back in the circumferential direction of the edge 9 and the start 4 of the side channel corresponds to at least 2.5 wing divisions.
  • the bottom of the side channel 1 lowers a little in the area 18 shortly before the pressure opening 8 in order to make it possible for the free cross section between the edges 9, 10, 11, 12 which delimit the pressure opening not to decrease is lower than in the remaining part of the side channel 1.
  • the lowering 18 begins shortly before the pressure opening, namely at a distance from it which is of the order of magnitude of the height or width of the side channel.

Landscapes

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

Abstract

L'invention concerne une pompe à canal latéral et flux circonférentiel dotée d'un carter formant un canal latéral (1). La surface du carter, adjacente au canal latéral, constitue une face frontale (13) avoisinant la roue-hélice. Le bord de transition (2, 3, 7) entre le canal latéral (1) et la face frontale (13) est arrondi dans les zones où il s'écarte de la direction circonférentielle. Les ailettes (16) de la roue-hélice ont dans le plan frontal une largeur d'âme prédéterminée dans le sens circonférentiel. Selon l'invention, le rayon (15) du bord de transition (7) est supérieur à 0,25 (sec/m) fois le produit Largeur d'âme x Vitesse des ailettes, là où les ailettes (16) de la roue-hélice quittent la zone de la face frontale (13, 14) pour mordre sur la zone du canal latéral (1). Cela permet de réduire l'inclinaison de cavitation et le bruit.
EP97950152A 1997-11-10 1997-11-10 Pompe a canal lateral et flux circonferentiel Withdrawn EP1029180A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP1997/006236 WO1999024719A1 (fr) 1997-11-10 1997-11-10 Pompe a canal lateral et flux circonferentiel

Publications (1)

Publication Number Publication Date
EP1029180A1 true EP1029180A1 (fr) 2000-08-23

Family

ID=8166791

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97950152A Withdrawn EP1029180A1 (fr) 1997-11-10 1997-11-10 Pompe a canal lateral et flux circonferentiel

Country Status (6)

Country Link
US (1) US6296440B1 (fr)
EP (1) EP1029180A1 (fr)
AU (1) AU738340B2 (fr)
CA (1) CA2306051A1 (fr)
CZ (1) CZ20001268A3 (fr)
WO (1) WO1999024719A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6173699B1 (en) * 1999-02-04 2001-01-16 Caterpillar Inc. Hydraulically-actuated fuel injector with electronically actuated spill valve
US6984099B2 (en) * 2003-05-06 2006-01-10 Visteon Global Technologies, Inc. Fuel pump impeller
US20040258545A1 (en) * 2003-06-23 2004-12-23 Dequan Yu Fuel pump channel
DE102006046827A1 (de) * 2006-10-02 2008-04-03 Robert Bosch Gmbh Förderaggregat

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1196016B (de) 1962-11-13 1965-07-01 Bmw Triebwerkbau Ges M B H Kraftstoffbehaelteranlage fuer Brennkraft-maschinen, insbesondere fuer Gasturbinen
GB1281842A (en) 1970-02-18 1972-07-19 Leyland Gas Turbines Ltd Gas turbine engines
DE3644356A1 (de) 1986-12-24 1988-07-07 Elsbett L Schmierung und kuehlung der turbinenwelle von abgasturboaufladern
JPH02103194U (fr) 1989-01-31 1990-08-16
JP2757646B2 (ja) * 1992-01-22 1998-05-25 株式会社デンソー 燃料ポンプ
US5401147A (en) * 1993-09-07 1995-03-28 Ford Motor Company Automotive fuel pump with convergent flow channel
DE4343078B4 (de) * 1993-12-16 2007-09-13 Robert Bosch Gmbh Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine
DE19531902A1 (de) * 1995-08-30 1997-03-06 Sihi Gmbh & Co Kg Seitenkanalpumpe insbesondere für höhere Drehzahlen
US6126387A (en) * 1996-08-26 2000-10-03 Aisan Kogyo Kabushiki Kaisha Fuel pump having low operating noise
DE19649529A1 (de) * 1996-11-29 1998-06-04 Duerr Dental Gmbh Co Kg Seitenkanalmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9924719A1 *

Also Published As

Publication number Publication date
CA2306051A1 (fr) 1999-05-20
WO1999024719A1 (fr) 1999-05-20
CZ20001268A3 (cs) 2001-12-12
US6296440B1 (en) 2001-10-02
AU5320398A (en) 1999-05-31
AU738340B2 (en) 2001-09-13

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