EP0774077A1 - Pompe a circulation destinee a amener du carburant d'un reservoir au moteur a combustion interne d'un vehicule - Google Patents

Pompe a circulation destinee a amener du carburant d'un reservoir au moteur a combustion interne d'un vehicule

Info

Publication number
EP0774077A1
EP0774077A1 EP96900265A EP96900265A EP0774077A1 EP 0774077 A1 EP0774077 A1 EP 0774077A1 EP 96900265 A EP96900265 A EP 96900265A EP 96900265 A EP96900265 A EP 96900265A EP 0774077 A1 EP0774077 A1 EP 0774077A1
Authority
EP
European Patent Office
Prior art keywords
impeller
rotation
axis
flow pump
vanes
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.)
Granted
Application number
EP96900265A
Other languages
German (de)
English (en)
Other versions
EP0774077B1 (fr
EP0774077B2 (fr
Inventor
Klaus Dobler
Michael Huebel
Willi Strohl
Jochen Rose
Bernhard Blaettel
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7753421&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0774077(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0774077A1 publication Critical patent/EP0774077A1/fr
Publication of EP0774077B1 publication Critical patent/EP0774077B1/fr
Application granted granted Critical
Publication of EP0774077B2 publication Critical patent/EP0774077B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for regenerative pumps

Definitions

  • Strain pump for conveying fuel from a reservoir to the internal combustion engine of a motor vehicle
  • the invention relates to a flow pump for delivering fuel from a reservoir to the internal combustion engine of a motor vehicle according to the preamble of claim 1.
  • Such a flow pump is known from DE 33 27 922 AI.
  • This flow pump has an impeller rotating in a pump chamber, which has on each of its two axially directed end faces a ring of vanes arranged at a distance from one another in the circumferential direction, between which there are gaps.
  • the wings interact with a ring-shaped delivery channel for delivering fuel.
  • the blades are flat and when looking at the impeller radially to its axis of rotation, the blades run parallel to the axis of rotation of the impeller.
  • a circulation flow is formed between the blades and the delivery channel, through which the energy is transported from the impeller to the flow.
  • the fuel occurs in the
  • the flow pump according to the invention with the features according to claim 1 has the advantage that the achievable delivery pressure and efficiency are increased. This can be attributed to the improved flow conditions due to the arrangement of the vanes leading on the end face of the impeller in the direction of rotation of the impeller, since this causes the fuel delivered to flow into the intermediate spaces approximately parallel to the vanes. This prevents the flow from tearing off at the rear of the blades pointing in the opposite direction to the direction of rotation of the impeller and the associated vortex formation, which in turn avoids shock losses in the flow and increases the circulation flow required for the energy transport between the blades of the impeller and the Funding channel is responsible.
  • FIG. 1 shows a flow pump for conveying fuel from a reservoir to the internal combustion engine of a motor vehicle in a simplified representation
  • FIG. 2 in an enlarged representation a section of the flow pump designated by II in FIG. 1 according to a first
  • FIG. 3 the impeller of the flow pump of FIG. 2 viewed in a cross section perpendicular to its axis of rotation
  • FIG. 4 the impeller of the flow pump in a section along line IV-IV in FIG. 3
  • FIG. 5 the section of the flow pump designated II in FIG. 1 6
  • the impeller of the flow pump of FIG. 5 viewed in a cross section perpendicular to its axis of rotation
  • FIG. 7 the impeller of the flow pump in a section along line VII-VII in FIG. 6, FIG.
  • Embodiment viewed in a side view in the direction of its axis of rotation and Figure 12 shows the impeller in a section along line XII-XII in Figure 11.
  • FIG. 1 shows a simplified representation of an assembly 10 which, in a common housing 12, comprises a flow pump 14 and a drive motor 15 for the flow pump 14.
  • the unit 10 is in a fuel tank 16 Arranged motor vehicle and the flow pump 14 draws fuel from the reservoir 16 during operation of the unit 10 and delivers this via a pressure line 17 to the engine 18 of the motor vehicle.
  • the flow pump 14 has an impeller 22 rotating in a pump chamber 20, the pump chamber 20 being delimited in the direction of the axis of rotation 24 of the impeller 22 by a chamber wall 25, 26 in each case.
  • the flow pump 14 is shown in sections according to a first exemplary embodiment and is designed as a so-called peripheral side channel pump.
  • the impeller 22 has on its two axially, that is, in the direction of its axis of rotation 24, end faces 28, 29 each a ring of vanes 30 arranged at a distance from one another in the circumferential direction of the impeller 22.
  • Groove-like spaces 31 are provided between the wings 30 and the wings 30 are essentially flat.
  • the bottom of the groove-like gaps 31 is rounded in the longitudinal sections containing the axis of rotation 24, viewed through the impeller 22, for example in the form of a circular section.
  • the vanes 30 extend in the radial direction with respect to the axis of rotation 24 of the impeller 22 from a radially inner end 30a to a radially outer end 30b on the outer circumference of the impeller 22. In the direction of the axis of rotation 24 of the impeller 22, the vanes 30 extend from one the wing rings of the two end faces 28, 29 approximately in the middle of the axial width of the impeller 22 separating web 33 to the end faces 28, 29 of the impeller 22.
  • the wing rings of the impeller 22 interact with an annular delivery channel 34 formed in the pump chamber 20 for delivering fuel.
  • a suction opening 35 opens into the delivery channel 34 and a pressure opening 36 opens into the end.
  • the fuel to be delivered flows through the Suction opening 35 into the delivery channel 34 and flows out of this under increased pressure through the pressure opening 36.
  • the conveying channel 34 extends in the radial direction with respect to the axis of rotation 24 of the impeller 22, starting from the radially inner ends 30a of the blades 30 and beyond their radially outer ends 30b. In the direction of the axis of rotation 24 of the impeller 22, the conveying channel 34 extends beyond the end faces 28, 29 of the impeller 22.
  • the conveying channel 34 is thus arranged laterally next to the vanes 30 in the direction of the axis of rotation 24 of the impeller 22 and also extends * over the outer circumference of the impeller 22.
  • the vanes 30, as is clear in FIG. 4, are arranged obliquely in such a way that, starting from the web 33, they lead to the respective end face 28, 29 at which the vanes 30 end, in the direction of rotation 21 of the impeller 22.
  • This means that the blades 30 are not arranged parallel to the axis of rotation 24 of the impeller 22, that is to say at right angles to the respective end face 28, 29, but rather include an angle ⁇ directed in the direction of rotation 21 of the impeller 22 with the axis of rotation 24.
  • the angle ⁇ is between 25 ° and 60 °, preferably between 30 ° and 55 °.
  • FIGS. 5 to 7 show the flow pump 14 according to a second exemplary embodiment and designed as a so-called side channel pump.
  • the impeller 122 has on each of its two axially directed end faces 128, 129 a ring of vanes 130 which are arranged at a distance from one another in the circumferential direction of the impeller 122 and between which groove-like gaps 131 are present.
  • the wings 130 of the two end faces 128, 129 of the impeller 122 are separated from one another when viewed by a web 133 in the direction of the axis of rotation 24 of the impeller 122 and are connected to one another at their radially outer ends 130b by a closed ring 140.
  • the web 133 can be continuous in the radial direction with respect to the axis of rotation 24 of the impeller 122, so that the two end faces 128, 129 of the impeller 122 are completely separated from one another, or the web 133 can end in the radial direction in front of the ring 140, so that between the web 133 and ring 140 in the area of the spaces 131 each have an opening 142 through which the two end faces 128, 129 of the impeller 122 are connected to one another.
  • annular conveying channel 144 or 145 is formed, the conveying channels 144, 145 being formed opposite the respective rim of the wings 130 in the end faces 128, 129 of the impeller 122.
  • Delivery channel 144 opens at the beginning of the suction opening 135 and the other delivery channel 145 opens at the end of the pressure opening 136.
  • the two delivery channels 144, 145 have no connection to one another over the outer circumference of the impeller 122, that is to say over the outer circumference of the ring 140.
  • the vanes 130 are arranged obliquely in accordance with FIG. 7 such that, starting from the web 133, they lead to the respective end face 128, 129 at which the vanes 130 end, in the direction of rotation 21 of the impeller 122.
  • This means that the wings 130 are not parallel are arranged to the axis of rotation 24 of the impeller 122, but instead form with the axis of rotation 24 an angle .alpha.
  • the angle ⁇ is between 25 ° and 60 °, preferably between 30 ° and 55 °.
  • FIGS. 8 and 9 show the impeller 222 of the flow pump 14 according to a third exemplary embodiment.
  • the flow pump 14 is designed as a side channel pump and the two delivery channels shown in FIG. 5 are present, the vane ring on one end face of the impeller 222 interacting with a delivery channel.
  • the impeller 222 has on its two axially directed end faces 228, 229 in each case a ring of vanes 230 arranged at a distance from one another in the circumferential direction, between each of which there are groove-like spaces 231, the base of which is rounded, for example in the form of a circular section.
  • the wings 230 are connected to one another at their radially outer ends 230b via a ring 240.
  • the edges 232 of the vanes 230 with which they end on the respective end face 228, 229 of the impeller are not arranged radially with respect to the axis of rotation 24 of the impeller 222, but the edges 232 rush to the radially outer ones Ends 230b of the blades 230 ahead of their arrangement at the radially inner ends 230a of the blades 230 in the circumferential direction 21 of the impeller 222.
  • the edges 232 of the blades 230 on the respective end face 228, 229 of the impeller 222 extend straight from the radially inner ends 230a of the blades 230 to the radially outer ends 230b of the blades 230.
  • the edges 232 are inclined at an angle ⁇ in the circumferential direction 21 of the impeller 222.
  • the angle ⁇ is between 20 ° and 45 °, preferably between 25 ° and 40 °.
  • the vanes 230 are also arranged at an incline such that, starting from the web 233 separating the vanes 230 of the two end faces 228, 229 from one another, towards the respective front side 228, 229 at which the vanes 230 end, in the circumferential direction 21 lead the impeller 222.
  • This means that the vanes 230 are not arranged parallel to the axis of rotation 24 of the impeller 222, but instead form an angle ⁇ directed in the direction of rotation 21 of the impeller 222 with the axis of rotation 24.
  • the angle ⁇ is not constant over the course of the wings 230 starting from their radially inner end 230a to their radially outer end 230b.
  • the vanes 230 on the respective end face 228, 229 of the impeller 222 with the axis of rotation 24 form an angle ⁇ E directed in the circumferential direction 21 of the impeller 222, which is between 25 ° and 50 °, in particular between 30 ° and 45 ° is.
  • the angle ⁇ E is preferably approximately 37 °.
  • the vanes 230 on the respective end face 228, 229 of the impeller 222 with the axis of rotation 24 form an angle ⁇ A directed in the circumferential direction 21 of the impeller 222, which is between 45 ° and 70 °, in particular between 50 ° and 65 °.
  • the angle ⁇ A is preferably approximately 60 °. Starting from the radially inner ends 230a of the vanes 230, the angle ⁇ increases linearly towards their radially outer ends 230b. This increase in the angle ⁇ starting from the radially inner ends 230a of the vanes 230 to their radially outer ends 230b results in the above-described arrangement of the edges 232 of the vanes 230 in the circumferential direction 21 of the impeller 222 by the angle ⁇
  • the inner ends of web 233 arranged in the cross section of the vanes 230 run perpendicular to the axis of rotation 24 of the impeller 222 approximately radially with respect to the axis of rotation 24, and are therefore not inclined as on their edge 232 located on the end face.
  • the above-described configuration of the vanes 230 with the angle ⁇ increasing from their radially inner ends 230a to their radially outer ends 230b further increases the delivery pressure and the efficiency of the flow pump.
  • FIG. 10 shows a variant of the impeller 322
  • the impeller 322 is essentially of the same design as in the third exemplary embodiment, but the edge 332 with which the vanes 330 end on the end face of the impeller 322 does not run in a straight line but is curved.
  • the edge 332 is arranged approximately radially with respect to the axis of rotation 24 of the impeller 322 and the edge 332 runs continuously to the radially outer ends 330b of the vanes 330 in the circumferential direction 21 of the impeller 322.
  • the Angle ⁇ which the vanes 330 enclose with the axis of rotation 24 of the impeller 322 is greater starting from the radially inner ends 330a of the vanes 330 to their radially outer ends 330b.
  • the increase in the size of the angle ⁇ does not take place linearly as in the third exemplary embodiment, but rather increases towards the radially outer ends 330b of the wings 330.
  • the vanes 330 run approximately radially in cross section perpendicular to the axis of rotation 24 of the impeller 322 with respect to the axis of rotation 24, are therefore not curved as on their edge 332 lying on the end face.
  • FIGS. 11 and 12 show the impeller 422 of the flow pump 14 according to a fourth exemplary embodiment.
  • the flow pump 14 is designed as a peripheral side channel pump and has a delivery channel as shown in the first exemplary embodiment in FIG. 2.
  • the impeller 422 has on each of its two axially directed end faces 428, 429 a ring of vanes 430 which are arranged at a distance from one another in the circumferential direction and between which there are intermediate spaces 431.
  • the vanes 430 extend in the radial direction with respect to the axis of rotation 24 of the impeller 422 from a radially inner end 430a to a radially outer end 430b on the outer circumference of the impeller 422
  • the axis of rotation 24 of the impeller 422 extends from a web 433 which separates the wing rings of the two end faces 428,429 approximately in the middle of the axial width of the impeller 422 from one web 433 to the end faces 428,429 of the impeller 422.
  • the wings 430 are as in the case of the above
  • the described embodiments are arranged so as to be inclined so that, starting from the web 433, they lead to the respective end face 428, 429 at which the vanes 430 end in the circumferential direction 21 of the impeller 422.
  • vanes 430 are not arranged parallel to the axis of rotation 24 of the impeller 422, but instead enclose an angle ⁇ directed in the direction of rotation 21 of the impeller 422 with the axis of rotation 24.
  • the angle ⁇ is between 25 ° and 50 °, in particular between 30 ° and 45 °.
  • the angle ⁇ is preferably approximately 37 °.
  • the angle ⁇ is approximately constant over the radial extension of the vanes 430, that is to say between the radially inner ends 430a and the radially outer ends 430b thereof.
  • the radially outer ends 430b of the vanes 430 rush toward their radially inner ends 430a Direction of rotation 21 of the impeller 422 ahead.
  • the blades 430 run in the direction of the axis of rotation 24 of the impeller 422, viewed between their radially inner ends 430a and their radially outer ends 430b, but can also run in a straight line in another embodiment.
  • the vanes 430 initially run approximately radially with respect to the axis of rotation 24 of the impeller 422 and towards their radially outer ends 430b the curvature, that is to say the deviation from the radial arrangement, increases.
  • the vanes 430 In the area of their radially outer ends 430b, the vanes 430 enclose an angle ⁇ directed in the circumferential direction 21 with a line 450 which is radial to the axis of rotation 24 of the impeller 422 and which is laid through the radially outer ends 430b of the vanes 430.
  • the angle ⁇ is between 30 ° and 60 °, in particular between 40 ° and 55 °.
  • the angle ⁇ is preferably approximately 45 °.
  • vanes 430 are necessary because, in the case of a peripheral side channel pump, the fuel to be delivered, like in the case of a side channel pump, in the region of the radially inner ends 430a of the vanes 430, enters the spaces 431, but exits them radially outward.
  • the vanes 430 are also curved in the direction of rotation 21 in the region of their inner ends arranged on the web 433, as well as on the end faces 428, 429 of the impeller 422.

Landscapes

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

Abstract

La pompe à circulation selon l'invention possède une roue (22) qui tourne dans une chambre de pompe et est pourvue, sur chacune de ses faces (28, 29) orientées axialement, d'une couronne d'ailettes (30) séparées par des espaces intercalaires (31), ladite roue agissant conjointement avec un conduit de refoulement (34) correspondant aux ailettes (30), pour pomper le carburant. Les ailettes (30), vues dans la direction radiale par rapport à l'axe de rotation (24) de la roue (22), sont disposées en biais, par rapport à l'axe de rotation (24), de telle façon qu'elles avancent vers la face (28, 29) de la roue (22) dans le sens de rotation (21) de la roue (22). Un angle (α), compris entre 25 et 70° et dirigé dans le sens de rotation (21) de la roue (22), est formé par les ailettes (30) et l'axe de rotation (24). Cette position oblique des ailettes (30) produit, par rapport à une position parallèle à l'axe de rotation (24), une amélioration de la pénétration du carburant refoulé dans les espaces intercalaires (31) séparant les ailettes (30), ce qui donne une augmentation de la pression de refoulement et une amélioration du rendement de la pompe à circulation.
EP96900265A 1995-02-08 1996-01-10 Pompe a circulation destinee a amener du carburant d'un reservoir au moteur a combustion interne d'un vehicule Expired - Lifetime EP0774077B2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19504079 1995-02-08
DE19504079A DE19504079B4 (de) 1995-02-08 1995-02-08 Strömungspumpe zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeugs
PCT/DE1996/000024 WO1996024769A1 (fr) 1995-02-08 1996-01-10 Pompe a circulation destinee a amener du carburant d'un reservoir au moteur a combustion interne d'un vehicule

Publications (3)

Publication Number Publication Date
EP0774077A1 true EP0774077A1 (fr) 1997-05-21
EP0774077B1 EP0774077B1 (fr) 2000-08-23
EP0774077B2 EP0774077B2 (fr) 2006-04-05

Family

ID=7753421

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900265A Expired - Lifetime EP0774077B2 (fr) 1995-02-08 1996-01-10 Pompe a circulation destinee a amener du carburant d'un reservoir au moteur a combustion interne d'un vehicule

Country Status (8)

Country Link
US (1) US5807068A (fr)
EP (1) EP0774077B2 (fr)
JP (1) JPH09511812A (fr)
KR (1) KR100382681B1 (fr)
CN (1) CN1071420C (fr)
BR (1) BR9605117A (fr)
DE (2) DE19504079B4 (fr)
WO (1) WO1996024769A1 (fr)

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JP3756337B2 (ja) 1999-02-09 2006-03-15 愛三工業株式会社 流体ポンプ
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Also Published As

Publication number Publication date
DE19504079A1 (de) 1996-08-14
KR970702436A (ko) 1997-05-13
WO1996024769A1 (fr) 1996-08-15
JPH09511812A (ja) 1997-11-25
BR9605117A (pt) 1997-10-07
CN1071420C (zh) 2001-09-19
DE59605787D1 (de) 2000-09-28
EP0774077B1 (fr) 2000-08-23
DE19504079B4 (de) 2004-11-04
EP0774077B2 (fr) 2006-04-05
US5807068A (en) 1998-09-15
CN1145659A (zh) 1997-03-19
KR100382681B1 (ko) 2003-08-21

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