WO1997040275A1 - Pompe tourbillonnaire - Google Patents

Pompe tourbillonnaire Download PDF

Info

Publication number
WO1997040275A1
WO1997040275A1 PCT/EP1997/001735 EP9701735W WO9740275A1 WO 1997040275 A1 WO1997040275 A1 WO 1997040275A1 EP 9701735 W EP9701735 W EP 9701735W WO 9740275 A1 WO9740275 A1 WO 9740275A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
blades
peripheral pump
pump according
chambers
Prior art date
Application number
PCT/EP1997/001735
Other languages
German (de)
English (en)
Inventor
Christoph Schmidt
Thomas Werner
Original Assignee
Mannsmann Vdo 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 Mannsmann Vdo Ag filed Critical Mannsmann Vdo Ag
Priority to AU25098/97A priority Critical patent/AU2509897A/en
Priority to DE59705556T priority patent/DE59705556D1/de
Priority to EP97916453A priority patent/EP0894198B1/fr
Publication of WO1997040275A1 publication Critical patent/WO1997040275A1/fr

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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/34—Balancing of radial or axial forces on regenerative rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/35—Reducing friction between regenerative impeller discs and casing walls

Definitions

  • the invention relates to a peripheral pump with an impeller rotating in a pump housing, which faces the pump housing at a short distance with its end faces to limit a sealing gap and has several depressions in this area and has at least one ring of vanes for conveying liquid.
  • Peripheral pumps of this type are frequently used to deliver fuel in a fuel tank of a motor vehicle and are therefore known.
  • the impeller often has a ring of blades in the radially outer region of its end faces.
  • the blades move in ring channels formed by the pump housing and generate circulation flows running transversely to the direction of movement of the blades.
  • the ring channels have an inlet channel and an outlet channel. An overflow of the liquid from the outlet channel to the inlet channel is prevented by a sill which interrupts the circulation flow.
  • the depressions in the impeller are filled with leakage fluid and thus form pressure pockets of an axial plain bearing, which connect to the delivery chambers via the sealing gaps between the impeller and the pump housing. are bound.
  • the invention is based on the problem of designing a peripheral pump of the type mentioned at the outset in such a way that it has the lowest possible friction losses even with high axial forces and thus a high delivery rate.
  • connection of two opposite recesses enables the liquid to be exchanged from one end of the impeller to the other.
  • the impeller thus floats in operation on a liquid film which reliably prevents contact of the impeller on the pump housing during the operation of the peripheral pump according to the invention.
  • leakage liquid is drawn in through the sealing gaps and through the connection between the depressions, as a result of which the liquid film in the sealing gaps is constantly renewed. This significantly reduces the friction losses in the peripheral pump and ensures a high delivery rate.
  • the depressions could be arranged in a radially outer region of the impeller as seen from the blades.
  • the impeller has a high peripheral speed, whereby the axial forces are absorbed when the peripheral pump starts.
  • the peripheral pump is particularly space-saving if, according to an advantageous development of the invention, the depressions are arranged in the radially inner region of the impeller as seen from the blades.
  • the depressions Due to a high volume, the depressions have very good emergency running properties with a short-term absence of the liquid to be conveyed, if the depressions are trough-shaped in accordance with another advantageous development of the invention.
  • the depressions are easy to produce if, according to another advantageous development of the invention, they are pocket-shaped in a tangential section through the impeller.
  • a peripheral pump is frequently used, in which a ring of blades for conveying a liquid from an inlet channel to an outlet channel is incorporated in each of the end faces of the impeller, and with ring channels incorporated into the pump housing on both sides in the area of the blades, which with Vane chambers between the vanes form opposing delivery chambers, the vanes, seen in the direction of rotation, rise from the central region of the impeller to the front sides.
  • the delivery pressure can be increased simply by creating a connection for overflowing the liquid in the region of two opposing blade chambers of the blades and by connecting the inlet channel to one delivery chamber and the outlet channel to the other delivery chamber is.
  • the peripheral pump flows axially through a first delivery chamber and a second delivery chamber and each has only a single inlet channel and a single outlet channel.
  • the peripheral pump can therefore be mounted, for example, in a fuel tank with particularly little effort.
  • the impeller has no central web separating the delivery chambers, so that the peripheral pump is particularly narrow.
  • the peripheral pump according to the invention has a particularly high delivery volume, since the vane chambers are not constricted with guide elements. The friction losses within the circulation flow during a transition from the first delivery chamber to the second delivery chamber are kept particularly small by connecting their delivery chambers.
  • the liquid can thus flow from the first delivery chamber into the second delivery chamber almost without disturbing the circulation flow, which leads to a particularly high delivery pressure and to a particularly high efficiency of the peripheral pump according to the invention.
  • the slight disturbance of the circulation flow has an advantageous effect particularly in the case of hot liquids with a high vapor pressure, since these tend to form vapor bubbles which reduce the delivery pressure and cause cavitation damage to the impeller when the circulation flow is disturbed.
  • the liquid to be pumped is hardly heated thanks to the low friction losses. If the delivery chambers in the area of the vane chambers have a circular cross section, the friction losses are particularly low.
  • the impact losses when the circulation flow enters the blade chambers can be kept to a minimum if, according to another advantageous development of the invention, the blades, viewed in the running direction of the impeller, are at an angle of 5 to 45 ° to the surface normal of the end faces of the impeller rise from the central area of the impeller to the respective end face.
  • the peripheral pump according to the invention already reaches a particularly high delivery pressure at a low rotational speed of the impeller if, according to another advantageous development of the invention, the blades, viewed in the running direction of the impeller, through an angle of 10 to 20 ° to the surface normal of the end faces of the impeller from the central region of the Rise the impeller towards the respective end face.
  • a lance-shaped circulation flow directed in the direction of rotation of the impeller can be generated very easily if, according to another advantageous development of the invention, the blades are seen as parabolic from the central region of the impeller to the end faces in the direction of the impeller increase.
  • the liquid flows particularly easily from the first conveying chamber into the second conveying chamber when the connection created by the overlapping of the conveying chambers is expanded outwards and / or inwards in the radial direction of the impeller according to another advantageous development of the invention. This also leads to an increase in the maximum achievable delivery pressure.
  • the ratio of the speed of the liquid normal to the direction of circulation and the average speed in the direction of circulation to one another is decisive for the stability of the circulation flow and thus for the maximum delivery pressure that can be generated with the peripheral pump.
  • This ratio is only dependent on the ratio of the mean diameter of the ring of the blades to the radius of the delivery chambers at a predetermined operating point of a peripheral pump, in which the circular delivery chambers are divided approximately in half between the blade chambers and the ring channels.
  • a high delivery pressure is achieved according to another advantageous development of the invention simply by the ratio of the mean diameter of the ring of the blades to the radius of the delivery chamber being greater than 7 and less than 99 is selected.
  • Tests have led to a particularly high delivery pressure if the ratio of the mean diameter of the ring of the blades to the radius of the delivery chamber is chosen to be greater than 15 and less than 30 according to another advantageous development of the invention. According to another advantageous further development of the invention, disturbances arising from a tearing off of the circulation flow after leaving the blade chambers are simply avoided by the edges of the blades protruding into the feed chambers being rounded off or having a chamfer.
  • the radius or the chamfer only has to be present on the blades at the edges at which the circulation flow touches the blades.
  • the blades then have a particularly simple design if the radius or the chamfer, viewed in the running direction of the impeller, is arranged on the edge of the front of the blades in a radially outer region and on the edge of the rear in a radially inner region.
  • the interference-reducing effect of the radii or the width of the bevels depends essentially on the dimensions of the blades. For example, large blades need correspondingly large radii or chamfers. According to another advantageous development of the invention, the liquid circulates in the delivery chambers with particularly little interference if the radius or the width of the chamfer corresponds to at least 1/70 the height of the blades.
  • the impeller can be produced inexpensively if, according to another advantageous development of the invention, it is made of plastic by injection molding. Furthermore, the impeller made of plastic has a particularly low weight, as a result of which the peripheral pump very quickly reaches its maximum delivery rate after a start.
  • FIG. 1 shows a longitudinal section through a peripheral pump according to the invention
  • FIG. 1 shows a longitudinal section of a peripheral pump according to the invention with a pump housing 1, in which an impeller 2 is rotatably arranged.
  • a ring 5 of blades 6, 6a, 6b are incorporated in each of its two end faces 3, 4.
  • the impeller 2 is fixed in its center on a drive shaft 7 in a rotationally fixed manner.
  • the pump housing 1 has an annular channel 8, 9 in the area of the blades 6, 6a, 6b on both sides.
  • the annular channels 8, 9 together with blade chambers 10, 10a, 10b shown in FIG. 2 form between the blades 6, 6a, 6b delivery chambers 11, 12, each of which has a circular cross section.
  • the delivery chambers 11, 12 are each divided in half between the vane chambers 10, 10a, 10b and the ring channels 8, 9 and have a connection 13 to one another which is produced by an overlap of their circular cross sections. By means of this connection 13, liquid can be separated from the flow from one delivery chamber 11 into the other delivery chamber 12.
  • the impeller 2 In its radially outer region and on its end faces 3, 4, the impeller 2 is opposite the pump housing 1 by a small distance. This creates a sealing gap 14 which runs around the impeller 2 and seals the conveying chambers 11, 12.
  • FIG. 2 shows a tangential section through the peripheral pump according to the invention from FIG. 1 along the line II-II.
  • the pump housing 1 has an inlet channel 18 and an outlet channel 19, which are separated from one another by a sill 20 arranged on both sides of the impeller 2.
  • the sill 20 interrupts the circulation flows of the liquid to be delivered which are generated in the delivery chambers 11, 12.
  • the inlet channel 18 is connected to the first delivery chamber 11 directly behind the rocker 20. Seen in the direction of circulation, directly in front of the sill 20, the second delivery chamber 12 opens into the outlet channel 19.
  • the blades 6, 6a, 6b are arranged symmetrically in the impeller 2 and rise from an axially central region of the impeller 2 to the end faces 3, 4 of the impeller 2 by an angle ⁇ .
  • the angle ⁇ shown here is approximately 15 °.
  • FIG. 3 shows a tangential section of the depressions 15, 16 of the impeller 2 along the line III-III from FIG. 1.
  • the depressions 15, 16 are machined into the impeller 2 in the form of a pocket and connected to one another at their center via the channel 17.

Landscapes

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

Abstract

L'invention concerne une pompe périphérique comportant une roue mobile (2) tournant dans un carter (1), dans laquelle les pertes par friction sont diminuées par des cavités (15, 16) pratiquées dans les faces (3, 4) de la roue mobile (2) et reliées mutuellement par un canal (7). Une fuite de faible quantité du liquide à refouler est aspirée par des fentes d'étanchéité (14) situées entre les faces (3, 4) de la roue mobile (2) et le carter (1) de la pompe, par l'intermédiaire du canal (17). La roue mobile (2) flotte de ce fait constamment sur une pellicule de liquide.
PCT/EP1997/001735 1996-04-18 1997-04-08 Pompe tourbillonnaire WO1997040275A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU25098/97A AU2509897A (en) 1996-04-18 1997-04-08 Peripheral pump
DE59705556T DE59705556D1 (en) 1996-04-18 1997-04-08 Peripheralpumpe
EP97916453A EP0894198B1 (fr) 1996-04-18 1997-04-08 Pompe tourbillonnaire

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19615323A DE19615323A1 (de) 1996-04-18 1996-04-18 Peripheralpumpe
DE19615323.9 1996-04-18

Publications (1)

Publication Number Publication Date
WO1997040275A1 true WO1997040275A1 (fr) 1997-10-30

Family

ID=7791642

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1997/001735 WO1997040275A1 (fr) 1996-04-18 1997-04-08 Pompe tourbillonnaire

Country Status (5)

Country Link
EP (1) EP0894198B1 (fr)
AU (1) AU2509897A (fr)
DE (2) DE19615323A1 (fr)
ES (1) ES2169373T3 (fr)
WO (1) WO1997040275A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2351324A (en) * 1999-06-23 2000-12-27 Ford Motor Co Regenerative pump impeller

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3800128B2 (ja) 2001-07-31 2006-07-26 株式会社デンソー インペラ及びタービン式燃料ポンプ
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
DE102017215731A1 (de) * 2017-09-07 2019-03-07 Robert Bosch Gmbh Seitenkanalverdichter für ein Brennstoffzellensystem zur Förderung und/oder Verdichtung von einem gasförmigen Medium

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1689579A (en) * 1921-08-24 1928-10-30 Arthur W Burks Rotary pump
DE3708336A1 (de) * 1987-03-14 1988-09-22 Bosch Gmbh Robert Laufrad zum foerdern eines mediums
US4854830A (en) * 1987-05-01 1989-08-08 Aisan Kogyo Kabushiki Kaisha Motor-driven fuel pump
US4872806A (en) * 1987-05-15 1989-10-10 Aisan Kogyo Kabushiki Kaisha Centrifugal pump of vortex-flow type
DE8911302U1 (fr) * 1989-09-22 1991-01-31 Robert Bosch Gmbh, 7000 Stuttgart, De
WO1992000457A1 (fr) * 1990-06-28 1992-01-09 Robert Bosch Gmbh Pompe tourbillonnaire servant en particulier a alimenter un moteur a combustion interne d'un vehicule a moteur avec un carburant contenu dans un reservoir
US5409357A (en) * 1993-12-06 1995-04-25 Ford Motor Company Impeller for electric automotive fuel pump
DE19504079A1 (de) * 1995-02-08 1996-08-14 Bosch Gmbh Robert Strömungspumpe zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeuges

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1333505A (en) * 1919-03-14 1920-03-09 Herbert J Passmore Planting attachment for cultivators
US3399626A (en) * 1966-08-23 1968-09-03 Lucas Industries Ltd Liquid displacement pumps

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1689579A (en) * 1921-08-24 1928-10-30 Arthur W Burks Rotary pump
DE3708336A1 (de) * 1987-03-14 1988-09-22 Bosch Gmbh Robert Laufrad zum foerdern eines mediums
US4854830A (en) * 1987-05-01 1989-08-08 Aisan Kogyo Kabushiki Kaisha Motor-driven fuel pump
US4872806A (en) * 1987-05-15 1989-10-10 Aisan Kogyo Kabushiki Kaisha Centrifugal pump of vortex-flow type
DE8911302U1 (fr) * 1989-09-22 1991-01-31 Robert Bosch Gmbh, 7000 Stuttgart, De
WO1992000457A1 (fr) * 1990-06-28 1992-01-09 Robert Bosch Gmbh Pompe tourbillonnaire servant en particulier a alimenter un moteur a combustion interne d'un vehicule a moteur avec un carburant contenu dans un reservoir
US5409357A (en) * 1993-12-06 1995-04-25 Ford Motor Company Impeller for electric automotive fuel pump
DE19504079A1 (de) * 1995-02-08 1996-08-14 Bosch Gmbh Robert Strömungspumpe zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeuges

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
TONN E: "ZUR BERECHNUNG VON PERIPHERALPUMPEN", KONSTRUKTION, vol. 44, no. 2, 1 February 1992 (1992-02-01), pages 64 - 70, XP000306468 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2351324A (en) * 1999-06-23 2000-12-27 Ford Motor Co Regenerative pump impeller
US6296439B1 (en) 1999-06-23 2001-10-02 Visteon Global Technologies, Inc. Regenerative turbine pump impeller
GB2351324B (en) * 1999-06-23 2004-01-21 Ford Motor Co Regenerative turbine pump impeller

Also Published As

Publication number Publication date
EP0894198A1 (fr) 1999-02-03
DE19615323A1 (de) 1997-10-23
AU2509897A (en) 1997-11-12
EP0894198B1 (fr) 2001-11-28
ES2169373T3 (es) 2002-07-01
DE59705556D1 (en) 2002-01-10

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