EP0842366B1 - Unite pour le transport de carburant depuis un reservoir jusqu'au moteur a combustion interne d'un vehicule automobile - Google Patents

Unite pour le transport de carburant depuis un reservoir jusqu'au moteur a combustion interne d'un vehicule automobile Download PDF

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Publication number
EP0842366B1
EP0842366B1 EP97914145A EP97914145A EP0842366B1 EP 0842366 B1 EP0842366 B1 EP 0842366B1 EP 97914145 A EP97914145 A EP 97914145A EP 97914145 A EP97914145 A EP 97914145A EP 0842366 B1 EP0842366 B1 EP 0842366B1
Authority
EP
European Patent Office
Prior art keywords
impeller
unit according
vanes
flow duct
ring
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 - Lifetime
Application number
EP97914145A
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German (de)
English (en)
Other versions
EP0842366A1 (fr
Inventor
Klaus Neidhard
Michael HÜBEL
Willi Strohl
Jochen Rose
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0842366A1 publication Critical patent/EP0842366A1/fr
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Publication of EP0842366B1 publication Critical patent/EP0842366B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • 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
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/005—Regenerative pumps of multistage type the stages being radially offset
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/048—Arrangements for driving regenerative pumps, i.e. side-channel 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

Definitions

  • the invention is based on a unit for conveying Fuel from a reservoir to the internal combustion engine of a motor vehicle according to the preamble of claim 1.
  • Such an assembly is known from DE 40 20 521 A1.
  • This unit has a flow pump Feed pump on, rotating by a drive part driven impeller rotates in a pump chamber.
  • the Pump chamber is in the direction of the axis of rotation of the impeller through two opposite end walls and in radial direction with respect to the axis of rotation Ring wall limited.
  • the impeller instructs on its circumference a wreath of wings on both ends on.
  • the wing is at the height of the two end walls one over part of the circumference around the axis of rotation of the impeller extending groove arranged with the wings of the impeller each form a delivery channel.
  • the Delivery channels lead from an inlet opening at one end to an outlet opening at their other end.
  • the impeller has one of its vanes radially outward pointing outer ring connecting ends. It has been shown that this Execution of the unit due to convection due to the entry of dirt particles Axial gaps in between the end faces of the impeller and the end walls not to exclude the space between the outer ring of the impeller and the ring wall is. This is due to the fact that in the conveying channels in the direction of rotation of the impeller a pressure build-up occurs and thus there is a higher pressure than in that Space between the outer ring of the impeller and the ring wall, so that a leakage amount flows from the delivery channels into the annulus. An entry of dirt particles in this space can lead to increased wear of the unit and should therefore be avoided.
  • An aggregate for conveying fuel with an impeller that is in on its outer ring one lateral surface has a second ring of wings, is from G 92 18 042 Ul known.
  • the wings in the lateral surface form a flow channel together with the ring wall, in which pressure builds up.
  • GB 21 34 598 A shows a unit for conveying fuel with a two-stage Flow pump with a radially inner and a radially outer flow channel, the radially inner with the radially outer flow channel connected in series and therefore both flow channels are passed through in succession.
  • the unit according to the invention for delivering fuel from a storage container to the internal combustion engine of a motor vehicle has the advantage that the at least one outer flow channel in the space between the outer ring of the Impeller and the ring wall in the direction of rotation of the impeller also build up pressure takes place and thus a pressure difference between the at least one flow channel and the delivery channels are avoided or at least reduced and thus the leakage amount avoided or at least reduced between the delivery channels and the annular space is.
  • the pressure build-up in at least one flow channel takes place approximately accordingly the pressure build-up in the delivery channels. Furthermore, an entry of Dirt particles in this room are reduced.
  • Aggregate specified Through the training according to each of claims 2 and 3 is achieved that in at least one flow channel a pressure build-up approximately corresponding the pressure builds up in the delivery channels. By training according to claim 5 the pressure build-up in at least one flow channel can be influenced.
  • FIG. 1 shows an aggregate for conveying of fuel with a flow pump in an axial longitudinal section
  • FIG. 2 in detail the flow pump in an enlarged view according to a first embodiment in an axial longitudinal section
  • Figure 3 shows the flow pump in one Cross-section along lines III-III in Figure 2
  • Figure 4 detail of the flow pump in a modified version in cross section
  • FIG Flow pump in a further modified embodiment Figure 6 shows the flow pump excerpts in a longitudinal section according to a second embodiment
  • Figure 7 shows the flow pump in a cross section along line VII-VII in Figure 6
  • Figure 8 shows the flow pump in cross section in a modified version
  • Figure 9 shows the flow pump in sections in a longitudinal section according to a third exemplary embodiment
  • FIG. 10 shows the flow pump in a cross section along line X-X in Figure 9.
  • FIG. 1 An assembly shown in simplified form in FIG. 1 is used to deliver fuel a not shown Internal combustion engine of a motor vehicle.
  • the Fuel delivery unit has a flow pump 10, whose impeller 12 by an electric drive motor 14 is driven in rotation. During the operation of the The fuel delivery unit sucks the flow pump 10 Fuel through a suction nozzle 16 and presses it via a pump outlet 18 in a more detailed below explained wall in a room 20 in which the drive motor 14 is arranged. From there, the fuel is over a pressure port 22 and a not shown Fuel line supplied to the internal combustion engine.
  • the flow pump 10 is enlarged in FIGS. 2 to 10 shown.
  • the impeller 12 of the flow pump 10 runs in a pump chamber 24 um, which in the direction of the axis of rotation 13 of the impeller 12 through a respective end wall 26 and 28 is limited and in the radial direction with respect to Axis of rotation 13 is limited by an annular wall 30.
  • the End wall 26 can be a cover of the Form fuel delivery unit, on which the intake manifold 16th is arranged.
  • the other end wall 28 can be a partition to form space 20 and the pump outlet 18 in the form of a Have outlet opening.
  • the impeller 12 has on his Circumference on each of its two faces spaced apart, radially outward upright wings 32.
  • the wings 32 are thereby formed that around on a common pitch circle the axis of rotation 13 arranged openings 34 webs remain, which the openings 34 in the circumferential direction of the Limit impeller 12.
  • the wings 32 are radial at their outer ends by a closed outer ring 36 connected with each other.
  • FIG Figure 3 shows a partially annular around the Axis of rotation 13 of the impeller 12 at the level of the wing 32 of Impeller 12 extending groove 38 arranged at the in Direction of rotation 11 of the impeller 12 considered the beginning connected to the suction port 16 inlet opening 40.
  • the groove 38 is in a circumferential area 41 in the circumferential direction 11 of the impeller 12 viewed between its end and hers Interrupted beginning.
  • the end wall 28 is also a mirror image of the end wall 26 one is partially annular around the axis of rotation 13 of the impeller 12 groove 42 extending at the level of the blades 32 of the impeller 12 arranged, in the direction of rotation 11 of the impeller 12th viewed end of the pump outlet 18 leads away.
  • the groove 42 is also in a circumferential area in the circumferential direction 11 the impeller 12 viewed between its end and hers Interrupted beginning.
  • the grooves 38 and 42 form together with the wings 32 of these end faces facing the Impeller 12 each have a feed channel 44 in which at Operation of the fuel delivery unit fuel from the Inlet opening 40 is conveyed to outlet opening 18.
  • the Flow pump 10 is thus a side channel pump formed because the conveyor channels 44 only laterally next to the Impeller 12 are formed and not on the Extend the outer circumference of the impeller 12.
  • Embodiment of the flow pump 10 has the impeller 12 on its outer ring 36 in its end walls 26, 28 facing end faces each have a wreath of in Wings 50 spaced apart from one another in the circumferential direction.
  • the Wing 50 are at their radially outer ends over a further, the impeller 12 radially outwardly delimiting ring 51 connected to each other.
  • the wings 50 can Minimization of fluid mechanical energy losses in Direction of rotation 11 of the impeller 12 with its radially outer Run ahead of ends, preferably about 25 ° to 50 °.
  • German patent application 1 95 04 079 the content of which belongs to the content of the present application should.
  • the end walls 26, 28 each have one partially ring-shaped around the axis of rotation 13 of the impeller 12 at height the wing 50 extends groove 52 or 54.
  • the grooves 52 or 54 extend at least approximately over the same scope as that forming the delivery channels 44 Grooves 38 and 42 of the end walls 26, 28, wherein the grooves 52 or 54 also over a slightly smaller or larger one Perimeter can extend as the grooves 38 and 42.
  • Die outer grooves 52, 54 are over from the inner grooves 38, 42 part of its circumference by webs 56 of the end walls 26, 28 Cut.
  • the outer grooves 52, 54 form with the wings 50 of these end faces of the outer ring 36 of the Impeller 12 each have an outer flow channel 58. In the outer flow channels 58 is intended to operate the Fuel delivery unit to build up pressure at least approximately the pressure build-up in the delivery channels 44 equivalent.
  • the outer flow channels 58 are each radial within these arranged delivery channels 44 over connected part of its scope. It can be provided be that the outer flow channels 58 forming Grooves 52,54 in the area of their in the circumferential direction 11 of Impeller 12 considered in the beginning and / or in the area of their viewed in the direction of rotation 11 with the end Delivery channels 44 connected to forming inner grooves 38,42 are. As shown in Figure 4, this connection can be done by one or more recesses which interrupt the webs 56 60 done.
  • both at the beginning and at End of the outer grooves 52, 54 connect to the inner Grooves 38.42 available so that at the beginning and at the end of the outer flow channels 58 approximately the same pressure conditions adjust like at the beginning and at the end of the inner Delivery channels 44.
  • the connection of the outer Grooves 52, 54 with the inner grooves 38, 42 as in FIG. 3 also shown in a medium circumferential area between their beginning and end also over one or more the webs 56 interrupting recesses 60 take place. The width, depth and position of the recesses 60 is so determines that there are favorable flow conditions between the grooves and there is a pressure equalization between sets this.
  • the outer flow channels 58 are in peripheral regions 62 between their in the direction of rotation 11 of the impeller 12 considered ends and beginnings interrupted or at least narrows.
  • the circumferential areas 62 correspond to essentially the peripheral regions 41, in which the inner Grooves 38,42 are interrupted, but can also be something be larger or slightly smaller than this.
  • the embodiment shown in FIG. 3 are the outer grooves 52, 54 between their in the direction of rotation 11 of the impeller 12 considered ends and beginnings in the peripheral regions 62 completely interrupted.
  • Figure 4 modified version are the grooves 52,54 in the Circumferential area 62 narrows.
  • the grooves run 52.54 in Circumferential area 62 radially offset from the rest Circumference, for example radially further, so that none or only a slight overlap with the wings 50 of the Outer ring 36 of the impeller 12 is present and accordingly the flow channels 58 interrupted or at least narrowed are.
  • the wings 50 of the outer ring 36 of the impeller 36 form together with the grooves 52, 54 another flow pump, which is also a side channel pump because the Flow channels 58 only to the side of the impeller 12 are arranged and no connection via the ring 51 on Have the outer circumference of the impeller 12.
  • the flow pump is not like the known one multi-stage feed pumps of the first, inner feed pump downstream, but promotes, so to speak, parallel to this from the same inlet opening 40 to the same outlet opening 18.
  • the vanes 50 arranged on the outer ring 36 of the impeller 12 When operating the fuel delivery unit is also carried out by the vanes 50 arranged on the outer ring 36 of the impeller 12 a delivery of fuel in the flow channels 58.
  • the amount of fuel delivered, the dependency of the amount of fuel delivered from the speed of the impeller 12 and the course of the pressure build-up over the scope of the Flow channels 58 can be formed by the formation of the wing 50 and the grooves 52, 54 and the formation of the interruption or narrowing of the flow channels 58 are influenced, so that through appropriate training a desired Flow rate and a desired pressure build-up can be achieved can.
  • the flow pump 10 is according to one shown second embodiment.
  • the End walls 26, 28 each have one partially ring-shaped around the axis of rotation 13 of the impeller 12 at height the wing 70 extending groove 72 or 74.
  • the grooves 72 or 74 extend approximately over the same Scope like that of the delivery channels 44 with grooves 38 or 42 of the end walls 26, 28, but can also over a slightly smaller or a slightly larger scope than these extend.
  • peripheral region 41 is interrupted or at least their width and / or depth be reduced. Additionally or alternatively, the radial gap 76 in the peripheral region 41 can be reduced, such as this with a modified shown in Figure 7 Execution is the case. A reduction in the gap 76 can radially inward through one of the annular wall 30 protruding projection 77 can be achieved.
  • the connection can be as with first embodiment at the beginning and / or at the end of Flow channel 78 or in an intermediate Circumferential area.
  • For connecting the flow channel 78 with the conveying channels 44 are one or more Recesses 79 are provided in the intermediate walls 26, 28.
  • the through the wings 70 of the outer ring 36 of the impeller 12 and the second feed pump formed in the flow channel 78 a combined side channel and peripheral pump, because the flow channel 78 both laterally next to the outer ring 36 of the impeller 12 and extends over its outer circumference.
  • the wing 70 of the impeller 12, the dimensions of the Flow channel 78 and the interruption or narrowing the flow channel 78 are coordinated such that in the flow channel 78 in the circumferential direction of the impeller 12 a pressure build-up approximately corresponding to the pressure build-up in the Delivery channels 44 and a predetermined fuel delivery rate results.
  • the flow pump 10 is shown in FIG shown a third embodiment. It points the impeller 12 also has a ring on its outer ring 36 of vanes 90 spaced apart in the circumferential direction that protrude radially outward from the outer ring 36.
  • the Wings 90 can extend across the entire width of the impeller 12 or it can extend to the two End faces of the outer ring 36 of the impeller 12 each Wreath of wings 90 may be arranged. Between the radial outer ends of the wings 90 and the annular wall 30 remains a radial gap 92 which together with the wings 90 of the Outer ring 36 of the impeller 12 has a flow channel 94 forms.
  • the flow channel 94 in turn extends approximately over the same scope as the inner delivery channels 44, but also about a slightly larger or something extend smaller circumference than the inner delivery channels 44. Between its in the direction of rotation 11 of the impeller 12 considered end and its beginning is the flow channel 94 approximately in the same peripheral region 41 as the inner grooves 38 or 42 interrupted or at least narrowed. The Interruption or narrowing of the flow channel 94 can take place by the radial gap 92 more or less strong is reduced by what is radially from the annular wall 30 protrusion 96 protruding inwards.
  • the end wall 28 is shown with the groove 42, wherein the end wall 26 with the groove 38 is a mirror image is.
  • the exemplary embodiment is the flow channel 94 with the inner conveyor channels 44 connected.
  • the connection can be made in Area of the impeller 12 in the circumferential direction 11 considered start and / or end of the flow channel 94 take place or in an arranged between them Peripheral region.
  • the connection of the flow channel 94 with the inner delivery channels 44 can be the same as in the first two Embodiments through one or more recesses 98 in the end walls 26, 28.
  • the wing 90 of the Impeller 12 the dimensions of the flow channel 94 and the interruption or narrowing of the flow channel 94 can be coordinated so that in Flow channel 94 in the circumferential direction of the impeller 12 Pressure build-up approximately according to the pressure build-up in the Delivery channels 44 and a predetermined fuel delivery rate results.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (13)

  1. Unité de transfert de carburant à partir d'un réservoir vers un moteur à combustion interne d'un véhicule automobile, comportant une pompe de transfert (10) en forme de pompe à liquide, dont le rotor (12) entraíné en rotation par un moyen d'entraínement (14) tourne dans une chambre de pompe (24) délimitée en direction de l'axe de rotation (13) du rotor (12) par deux parois frontales (26, 28) opposées l'une à l'autre et dans la direction radiale par rapport à l'axe de rotation (13) du rotation (12), par une paroi annulaire (30), dans laquelle
    le rotor (12) présente, à sa périphérie, au niveau de ses deux faces frontales, chaque fois une couronne d'ailettes (32) écartées dans la direction périphérique et dirigées radialement vers l'extérieur, et dans les deux parois frontales (26, 28), à la hauteur des ailettes (32) à chaque fois une rainure (38, 42) s'étend sous la forme d'une partie d'anneau autour de l'axe de rotation (13) du rotor (12), et forme avec les ailettes (32) du rotor (12) chaque fois un canal de transfert (44) conduisant dans le sens de rotation du rotor (12) d'un orifice d'entrée (40) à son début jusqu'à un orifice de sortie (18) à son extrémité, et
    le rotor (12) présente un anneau extérieur (36) reliant l'extrémité radiale extérieure des ailettes (32), l'anneau extérieur (36) du rotor (12) comportant une autre couronne d'ailettes (50, 70, 90) dirigées radialement vers l'extérieur et écartées dans la direction périphérique, ces ailettes formant avec les parois frontales (26, 28) et/ou la paroi annulaire (30) au moins un canal d'écoulement (58, 78, 94) s'étendant au moins suivant une forme d'une partie d'anneau autour de l'axe de rotation (13) du rotor (12), canal dans lequel s'établit une augmentation de pression dans la direction de rotation du rotor (12),
    caractérisée en ce que
    au moins un canal d'écoulement (58, 78, 94) est relié sur une partie de sa périphérie aux canaux de transfert (44) de façon à y établir une augmentation de pression correspondant sensiblement à celle dans les canaux de transfert (44).
  2. Unité selon la revendication 1,
    caractérisée en ce qu'
    au moins le canal d'écoulement (58, 78, 94) est relié aux canaux de transfert (44) dans la zone de son début et/ou de son extrémité dans le sens de rotation (11) du rotor (12).
  3. Unité selon la revendication 1,
    caractérisée en ce qu'
    au moins le canal d'écoulement (58, 78, 94) est relié aux canaux de transfert (44) dans une zone périphérique entre son début et son extrémité dans le sens de rotation (11) du rotor (12).
  4. Unité selon une des revendications précédentes,
    caractérisée en ce qu'
    au moins le canal d'écoulement (58, 78, 94) est Interrompu ou rétréci dans une zone périphérique (62) entre son extrémité et son début lorsqu'on considère le sens de rotation (11) du rotor (12).
  5. Unité selon la revendication 4,
    caractérisée en ce que
    les canaux de transfert (44) sont interrompus ou au moins rétrécis. également entre leur extrémité et leur début selon le sens de rotation (11) du rotor (12), dans une zone périphérique (41, 43) qui correspond au moins en partie avec la zone périphérique (62) dans laquelle au moins un canal d'écoulement (58, 78, 94) est Interrompu ou rétréci.
  6. Unité selon l'une des revendications précédentes,
    caractérisée en ce qu'
    un unique canal d'écoulement (94) est formé à la périphérie extérieure du rotor (12) entre les parois frontales (26, 28) et la paroi annulaire (30).
  7. Unité selon l'une des revendications 1 à 5,
    caractérisée en ce que
    les ailettes (50) de l'anneau extérieur (36) du rotor (12) sont reliées au niveau de leurs extrémités radiales extérieures par un autre anneau fermé (51) et
    dans les deux parois frontales (26, 28), au niveau des ailettes (50) on a à chaque fois une rainure (52, 54) s'étendant au moins sous la forme d'une partie d'anneau autour de l'axe de relation (13) du rotor (12), ces rainures formant chaque fois un canal d'écoulement latéral (58) avec les ailettes (50).
  8. Unité selon la revendication,
    caractérisée en ce que
    l'interruption ou le rétrécissement des canaux d'écoulement (58) est réalisée par une interruption ou au moins un rétrécissement des rainures (52, 54).
  9. Unité selon la revendication 7,
    caractérisée en ce que
    l'interruption ou au moins le rétrécissement des canaux d'écoulement (58) est obtenu par un décalage radial des rainures (52, 54) par rapport aux ailettes (50) de façon que celles-ci ne chevauchent pas les ailettes (50) ou ne les chevauchent que de manière réduite.
  10. Unité selon les revendications 4 ou 5 et 6,
    caractérisée en ce que
    l'interruption ou du moins le rétrécissement du canal d'écoulement (94) est formé par au moins une partie en saillie (96) radialement en saillie vers l'intérieur par rapport à la paroi annulaire (30).
  11. Unité selon la revendication 4 ou 5,
    caractérisée en ce que
    le canal d'écoulement (78) s'étend à la fois latéralement à côté de l'anneau extérieur (36) du rotor (12) et sur sa périphérie extérieure.
  12. Unité selon la revendication 11,
    caractérisée en ce que
    l'interruption ou du moins le rétrécissement du canal d'écoulement (78) est obtenu par une interruption ou au moins un rétrécissement de la partie s'étendant sur la périphérie extérieure de l'anneau extérieur (36) du rotor (12) par une saillie (77) dirigée radialement vers l'intérieur à partir de la parol annulaire (36).
  13. Unité selon la revendication 11 ou 12,
    caractérisée en ce que
    l'interruption ou au moins le rétrécissement du canal d'écoulement (78) est obtenu par une interruption ou au moins un rétrécissement de sa partie qui s'étend latéralement à côté de l'anneau extérieur (36) du rotor (12), par son interruption on au moins son rétrécissement.
EP97914145A 1996-06-05 1997-02-13 Unite pour le transport de carburant depuis un reservoir jusqu'au moteur a combustion interne d'un vehicule automobile Expired - Lifetime EP0842366B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19622560A DE19622560A1 (de) 1996-06-05 1996-06-05 Aggregat zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeugs
DE19622560 1996-06-05
PCT/DE1997/000272 WO1997046809A1 (fr) 1996-06-05 1997-02-13 Unite pour le transport de carburant depuis un reservoir jusqu'au moteur a combustion interne d'un vehicule automobile

Publications (2)

Publication Number Publication Date
EP0842366A1 EP0842366A1 (fr) 1998-05-20
EP0842366B1 true EP0842366B1 (fr) 2003-05-07

Family

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EP97914145A Expired - Lifetime EP0842366B1 (fr) 1996-06-05 1997-02-13 Unite pour le transport de carburant depuis un reservoir jusqu'au moteur a combustion interne d'un vehicule automobile

Country Status (8)

Country Link
US (1) US6152686A (fr)
EP (1) EP0842366B1 (fr)
JP (1) JPH11510875A (fr)
KR (1) KR19990036157A (fr)
CN (1) CN1118635C (fr)
BR (1) BR9702277A (fr)
DE (2) DE19622560A1 (fr)
WO (1) WO1997046809A1 (fr)

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DE102004052439A1 (de) 2004-10-28 2006-05-04 Siemens Ag Kraftstoffpumpe und Kraftstoffversorgungsanlage für eine Brennkraftmaschine eines Kraftfahrzeuges mit einer Kraftstoffpumpe
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DE3303352A1 (de) * 1983-02-02 1984-08-02 Robert Bosch Gmbh, 7000 Stuttgart Aggregat zum foerdern von kraftstoff, vorzugsweise aus einem vorratstank zur brennkraftmaschine, insbesondere eines kraftfahrzeuges
ES2055894T3 (es) * 1989-04-07 1994-09-01 Ciba Geigy Ag Concentrados de sustancias activas pesticidas y su preparacion.
US4948344A (en) * 1989-10-17 1990-08-14 Sundstrand Corporation Controlled vortex regenerative pump
DE4020521A1 (de) * 1990-06-28 1992-01-02 Bosch Gmbh Robert Peripheralpumpe, insbesondere zum foerdern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges
DE9218042U1 (de) * 1992-12-19 1993-06-09 Pierburg GmbH, 4040 Neuss Brennstoffpumpe
DE4336090C2 (de) * 1993-10-22 2001-10-04 Bosch Gmbh Robert Aggregat zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeuges
DE4411627A1 (de) * 1994-04-02 1995-10-05 Bosch Gmbh Robert Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeuges
US5413457A (en) * 1994-07-14 1995-05-09 Walbro Corporation Two stage lateral channel-regenerative turbine pump with vapor release

Also Published As

Publication number Publication date
EP0842366A1 (fr) 1998-05-20
WO1997046809A1 (fr) 1997-12-11
KR19990036157A (ko) 1999-05-25
CN1118635C (zh) 2003-08-20
DE19622560A1 (de) 1997-12-11
BR9702277A (pt) 1999-07-20
DE59710028D1 (de) 2003-06-12
CN1189879A (zh) 1998-08-05
US6152686A (en) 2000-11-28
JPH11510875A (ja) 1999-09-21

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