EP1331400B1 - Pompe à canal latéral - Google Patents

Pompe à canal latéral Download PDF

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Publication number
EP1331400B1
EP1331400B1 EP20030001089 EP03001089A EP1331400B1 EP 1331400 B1 EP1331400 B1 EP 1331400B1 EP 20030001089 EP20030001089 EP 20030001089 EP 03001089 A EP03001089 A EP 03001089A EP 1331400 B1 EP1331400 B1 EP 1331400B1
Authority
EP
European Patent Office
Prior art keywords
channel
pump
pressure compensation
opening
pressure
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 - Fee Related
Application number
EP20030001089
Other languages
German (de)
English (en)
Other versions
EP1331400A3 (fr
EP1331400A2 (fr
Inventor
Dieter Bovensmann
Raimund Frielingsdorf
Alfred Kleinen
Stefan Kluth
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.)
TI Automotive Neuss GmbH
Original Assignee
TI Automotive Neuss 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 TI Automotive Neuss GmbH filed Critical TI Automotive Neuss GmbH
Publication of EP1331400A2 publication Critical patent/EP1331400A2/fr
Publication of EP1331400A3 publication Critical patent/EP1331400A3/fr
Application granted granted Critical
Publication of EP1331400B1 publication Critical patent/EP1331400B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F04D29/188—Rotors specially for regenerative pumps

Definitions

  • the invention relates to a single-stage side channel pump with two parallel pumping channels.
  • the side channel pump has an impeller with two mutually parallel half channels, which are provided on the two end faces of the impeller.
  • the two half-channels each have a plurality of blade walls, by which each half-channel is divided into the same number of pumping chambers.
  • the pump chambers of the two half-channels opposite a semi-annular, fixed half-channel is provided in each case, which is formed continuously in the circumferential direction.
  • the incoming liquid through an inlet is displaced by the pumping chambers of the impeller in a helical circulation flow which alternately passes through the respective impeller half-channel and the opposite fixed half-channel.
  • the pressure equalization opening in the channel partition wall extends over the entire length of the channel partition wall, so practically over the entire length of the pumping chamber.
  • the helical flow of the liquid in the pumping passage is greatly disturbed by the pressure equalizing port, thereby deteriorating the pumping power of the pump.
  • a fuel side channel pump is known, in which the channel partition wall also has pressure equalization openings.
  • the pressure equalization opening also extends over the entire length of the pumping chamber, so that the liquid flow is greatly disturbed.
  • a fuel side channel pump in which the pressure equalization opening on the leeward, that is arranged in the direction of rotation front half of the channel partition wall, whereby the gas transport and the pressure compensation are deteriorated.
  • the pressure compensation opening extends over approximately the entire radial width of the channel partition wall. Also, by extending over almost the entire width pressure equalization opening, the liquid flow is still significantly disturbed. However, the opening can not be further reduced because this would make the pressure equalization and in particular the gas transport too much worse.
  • the object of the invention is therefore to improve the pump power in a side channel pump with two parallel pumping channels and pressure equalization holes in the channel partition wall.
  • the pressure equalization opening is provided exclusively in the front half of the channel partition wall in the direction of rotation of the impeller, so that the rear half of the channel partition wall is free of openings.
  • the pressure equalization openings are therefore each in the leeward area of the channel partitions, but not in the windward area of the channel partitions.
  • the pressure equalization opening is in the range of relatively low pressure within the pumping chamber, but not in the region of high pressure within the pumping chamber.
  • the high pumping chamber pressure arises on the windward side of each blade wall and the adjacent opening-free area of the channel partition wall.
  • an opening-free bucket pocket is formed by which a high liquid delivery rate is ensured.
  • the opening length of the pressure compensation opening is less than 2/5 of the channel partition wall length.
  • the pressure compensation opening thus extends from the leeward side of a blade wall in the circumferential direction over a maximum of 2/5 of the entire channel partition wall length in the circumferential direction.
  • the blade walls are inclined at least 10 ° to the windward side, i. inclined in each case axially outward in the direction of rotation.
  • This will u.A. causes the pressure gradient in each pumping chamber to be increased in the circumferential direction, i. the pressure difference between the leeward side and the windward side within a pressure chamber is considerably increased. On the windward side there is a high pressure, while on the leeward side there is a low pressure.
  • the opening width of the pressure compensation opening is smaller than 2/5 of the channel partition wall width.
  • the opening area of the pressure compensation opening is preferably at most about 3/10 and in particular at most 1.5 / 10 of the area of a channel partition wall.
  • the pressure compensation opening is relatively small, so that the disturbances of the liquid flow within the pumping chamber are low.
  • the pressure equalization port is located directly adjacent to the leeward side of the front blade wall. This ensures that the pressure compensation opening is arranged in the region of the lowest pressure within each pumping chamber. The transition between the leeward side of a blade wall and the pressure equalization opening is step-free, so that only small flow disturbances occur.
  • the pressure compensation opening is arranged approximately in the radial center of the channel partition wall width.
  • the pressure equalization port is thus approximately in the range in which the liquid in the pumping chamber has approximately a radial flow direction, i. flows approximately radially outward.
  • the opening plane of the pressure compensation opening is thus approximately parallel to the flow direction of the liquid. This also ensures that the liquid flow experiences only relatively small disturbances and turbulences, but a pressure equalization and gas exchange remain ensured.
  • the blade walls may be formed free of openings, so that they close the entire half-channel cross-sectional area.
  • the side channel pump 10 shown for installation in motor vehicles, as used in particular for the promotion of fuel, but also of cleaning fluids and other liquids.
  • the side channel pump 10 is essentially constituted by a rotating impeller 12 and two stationary ones enclosing the impeller Housing halves 14,16 formed.
  • the impeller 12 is fixed by means of a coupling to a rotatable drive shaft 18, which is mounted with a roller bearing 20 and is driven by a drive motor 22.
  • the drive shaft can also be mounted with plain bearings.
  • a pump channel 24a, 24b is formed in each case, which extends approximately circular in the circumferential direction and is approximately circular in cross section.
  • Each pumping channel 24a, 24b is formed by a half channel 26a, 26b in the stationary housing halves 14, 16 and by a respectively opposite, rotating half channel 28a, 28b of the pump wheel 12.
  • the two respective opposite half-channels 28a, 28b of the impeller 12 are characterized by a plurality of the entire cross section of the half channels 28a, 28b obturating blade walls 30 in a plurality of pumping chambers 32 a, 32 b divided.
  • Both pumping channels 24a, 24b are each assigned an unillustrated liquid inlet and a liquid outlet, through which the liquid to be conveyed enters or is pumped out into the pumping channels 24a, 24b.
  • a pumping channel 24b associated with a vent hole 42 can escape through the gas bubbles that have formed in the liquid.
  • the pumping chambers 32a, 32b of the two pumping channels 24a, 24b are separated from each other by channel partitions 34, which lie in the radial center plane of the impeller 12.
  • Each channel partition wall 34 has, adjoining the circumferentially front blade wall 30, a pressure compensation opening 36, by means of which the two parallel pump chambers 32a, 32b are connected to one another.
  • the pressure compensation opening 36 is adjacent to the leeward side 38 of the respective blade wall 30, but not to the windward side 40 of the respective other blade wall 30 of the respective pumping chamber 32a, 32b.
  • the Pressure compensation opening 36 is arranged radially approximately in the middle of the respective pumping chamber 32a, 32b, as can be seen in FIG.
  • the opening length a of the pressure compensation opening 36 is about 1/4 of the channel separation wall length b, i. the length b of the channel partition wall 34 of a pumping chamber 32a, 32b in the circumferential direction, as shown in Fig. 3.
  • the opening width c of the pressure compensating opening 36 in the radial direction is about 1/3 of the channel partition wall width d, i. the radial extent of the channel partition.
  • the blade walls 30 are inclined by approximately an angle ⁇ of 20 ° to the windward side, as shown in Fig. 3.
  • the vent hole 42 is provided in the housing half 16, can escape through the gas bubbles in the pumped liquid from the pumping channel 24b.
  • the pumped liquid is sucked into the pumping channels 24a, 24b.
  • the liquid is set in a spiral movement within both pumping channels 24a, 24b.
  • a high acceleration of the liquid and thus a high pressure within the liquid are produced on the windward sides 40 of the blade walls 30.
  • any gas bubbles present in the liquid are driven in the direction of rotation away from the windward side 40 of the relevant blade wall 30 to the leeward side of the other blade wall 30 delimiting the pumping chamber 32a, 32b.
  • the pressure equalization port 36 is a constant pressure equalization between all parallel pumping chambers 32a, 32b.
  • the gas volume accumulated in both pumping chambers 32a, 32b emerges from the pumping channels 24a, 24b, the gas bubbles migrating from the ventless half channel 28a through the pressure equalizing opening 36.

Claims (7)

  1. Pompe à canaux latéraux présentant deux canaux de pompe (24a, 24b) parallèles, comportant
    une roue de pompe (12) comportant deux demi-canaux (28a, 28b) parallèles, séparés l'un de l'autre par une cloison de séparation de canaux (34), qui présentent chacun plusieurs chambres de pompe (32a, 32b) les unes derrière les autres dans la direction périphérique, qui sont formées et séparées les unes des autres par des parois d'aubes (30), dans laquelle
    les chambres de pompe (32a, 32b) des deux demi-canaux (28a, 28b) sont reliées les unes aux autres par des ouvertures d'équilibrage de pression (36) dans la cloison de séparation de canaux (34), un équilibrage de pression de la chambre de pompe (32a) de l'un des demi-canaux (28a) vers la chambre de pompe (32b) de l'autre demi-canal (28b) s'effectuant par les ouvertures d'équilibrage de pression,
    chaque ouverture d'équilibrage de pression (36) est prévue exclusivement dans la moitié avant de la cloison de séparation de canal (34) dans le sens de rotation, la moitié arrière de la cloison de séparation de canal étant réalisée sans ouverture, et
    la longueur d'ouverture (a) de l'ouverture d'équilibrage de pression (36) est inférieure aux 2/5 de la longueur de cloison de séparation de canaux (b),
    caractérisée en ce
    que les parois d'aubes (30) sont disposées de manière inclinée d'au moins 10° au côté lof (40).
  2. Pompe à canaux latéraux selon la revendication 1, caractérisée en ce que la largeur d'ouverture (c) de l'ouverture d'équilibrage de pression (36) est inférieure aux 2/5 de la largeur de cloison de séparation de canaux (d).
  3. Pompe à canaux latéraux selon la revendication 1 ou 2, caractérisée en ce que le rapport de la surface de la cloison de séparation de canaux (34) à la surface de l'ouverture d'équilibrage de pression (36) est inférieur à 0,3.
  4. Pompe à canaux latéraux selon l'une des revendications 1 à 3, caractérisée en ce que le rapport de la surface de la cloison de séparation de canaux (34) à la surface de l'ouverture d'équilibrage de pression (36) est d'environ 0,15.
  5. Pompe à canaux latéraux selon l'une des revendications 1 à 4, caractérisée en ce que l'ouverture d'équilibrage de pression (36) est disposée approximativement au milieu de la largeur de la cloison de séparation de canal (d).
  6. Pompe à canaux latéraux selon l'une des revendications 1 à 5, caractérisée en ce que l'ouverture d'équilibrage de pression (36) est disposée à proximité du côté aval (38) de la paroi d'aube (30) précédente.
  7. Pompe à canaux latéraux selon l'une des revendications 1 à 6, caractérisée en ce que les parois d'aubes sont réalisées sans ouverture et ferment la surface transversale totale de chaque demi-canal (28a, 28b).
EP20030001089 2002-01-23 2003-01-20 Pompe à canal latéral Expired - Fee Related EP1331400B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10202366 2002-01-23
DE2002102366 DE10202366A1 (de) 2002-01-23 2002-01-23 Seitenkanalpumpe

Publications (3)

Publication Number Publication Date
EP1331400A2 EP1331400A2 (fr) 2003-07-30
EP1331400A3 EP1331400A3 (fr) 2004-01-07
EP1331400B1 true EP1331400B1 (fr) 2006-03-29

Family

ID=7712798

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20030001089 Expired - Fee Related EP1331400B1 (fr) 2002-01-23 2003-01-20 Pompe à canal latéral

Country Status (3)

Country Link
EP (1) EP1331400B1 (fr)
DE (2) DE10202366A1 (fr)
ES (1) ES2256597T3 (fr)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3925396A1 (de) * 1989-08-01 1991-02-07 Swf Auto Electric Gmbh Kraftstoffoerderpumpe
DE19504079B4 (de) * 1995-02-08 2004-11-04 Robert Bosch Gmbh Strömungspumpe zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeugs
JPH08334097A (ja) * 1995-06-07 1996-12-17 Unisia Jecs Corp タービンポンプ
DE19643728A1 (de) * 1996-10-23 1998-04-30 Mannesmann Vdo Ag Förderpumpe
DE19903397B4 (de) * 1999-01-29 2005-02-03 Siemens Ag Laufrad
DE19906130A1 (de) * 1999-02-13 2000-08-17 Mannesmann Vdo Ag Förderpumpe
DE10026490A1 (de) * 2000-05-27 2001-11-29 Bosch Gmbh Robert Förderaggregat für Kraftstoff

Also Published As

Publication number Publication date
DE50302776D1 (de) 2006-05-18
DE10202366A1 (de) 2003-08-07
EP1331400A3 (fr) 2004-01-07
ES2256597T3 (es) 2006-07-16
EP1331400A2 (fr) 2003-07-30

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