EP0842366B1 - Aggregat zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs - Google Patents
Aggregat zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs Download PDFInfo
- 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
Links
Images
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.
Landscapes
- 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)
Description
Claims (13)
- Aggregat zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeugs mit einer als Strömungspumpe ausgebildeten Förderpumpe (10), deren von einem Antriebsteil (14) rotierend angetriebenes Laufrad (12) in einer Pumpenkammer (24) umläuft, die in Richtung der Drehachse (13) des Laufrads (12) durch zwei einander gegenüberliegende Stirnwände (26,28) und in radialer Richtung bezüglich der Drehachse (13) des Laufrads (12) durch eine Ringwand (30) begrenzt ist, wobei das Laufrad (12) an seinem Umfang an seinen beiden Stirnseiten jeweils einen Kranz von in Umfangsrichtung zueinander beabstandeten, radial auswärts gerichteten Flügeln (32) aufweist und wobei in den beiden Stirnwänden (26,28) in Höhe der Flügel (32) jeweils eine sich teilringförmig um die Drehachse (13) des Laufrads (12) erstreckende Nut (38,42) angeordnet ist, die mit den Flügeln (32) des Laufrads (12) jeweils einen Förderkanal (44) bilden, die in Umlaufrichtung (11) des Laufrads (12) betrachtet von einer Einlassöffnung (40) an ihrem Anfang zu einer Auslassöffnung (18)an ihrem Ende führen, und wobei das Laufrad (12) einen dessen Flügel (32) an deren radial äußeren Enden verbindenden Außenring (36) aufweist, und wobei am Außenring (36) des Laufrads (12) ein weiterer Kranz von in Umfangsrichtung zueinander beabstandeten, radial auswärts gerichteten Flügeln (50;70;90) angeordnet ist, die zusammen mit den Stirnwänden (26,28) und/oder mit der Ringwand (30) wenigstens einen sich zumindest teilringförmig um die Drehachse (13) des Laufrads (12) erstreckenden Strömungskanal (58;78;94) bilden, in dem in Umlaufrichtung (11) des Laufrads (12) ein Druckaufbau erfolgt, dadurch gekennzeichnet, dass der wenigstens eine Strömungskanal (58;78;94) über einen Teil seines Umfangs mit den Förderkanälen (44) verbunden ist, so dass in diesem ein Druckaufbau etwa entsprechend dem Druckaufbau in den Förderkanälen (44) erfolgt.
- Aggregat nach Anspruch 1, dadurch gekennzeichnet, daß der wenigstens eine Strömungskanal (56;78;94) im Bereich seines in Umlaufrichtung (11) des Laufrads (12) betrachteten Anfangs und/oder seines Endes mit den Förderkanälen (44) verbunden ist.
- Aggregat nach Anspruch 1, dadurch gekennzeichnet, daß der wenigstens eine Strömungskanal (58;78;94) in einem zwischen dessen in Umlaufrichtung (11) des Laufrads (12) betrachteten Anfang und Ende angeordeten Umfangsbereich mit den Förderkanälen (44) verbunden ist.
- Aggregat nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der wenigstens eine Strömungskanal (58;78;94) in einem Umfangsbereich (62) zwischen dessen in Umlaufrichtung (11) des Laufrads (12) betrachtetem Ende und Anfang unterbrochen oder zumindest verengt ist.
- Aggregat nach Anspruch 4, dadurch gekennzeichnet, daß die Förderkanäle (44) in einem sich zumindest teilweise mit dem Umfangsbereich (62), in dem der wenigstens eine Strömungskanal (58; 78; 94) unterbrochen oder zumindest verengt ist, deckenden Umfangsbereich (41,43) ebenfalls zwischen deren in Umlaufrichtung (11) des Laufrads (12) betrachteten Enden und Anfängen unterbrochen oder zumindest verengt sind.
- Aggregat nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß ein einziger Strömungskanal (94) über den Außenumfang des Laufrads (12) zwischen den Stirnwänden (26,28) und der Ringwand (30) gebildet ist.
- Aggregat nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Flügel (50) des Außenrings (36) des Laufrads (12) an ihren radial äußeren Enden durch einen weiteren geschlossenen Ring (51) miteinander verbunden sind und daß in den beiden Stirnwänden (26,28) in Höhe der Flügel (50) jeweils eine zumindest teilringförmig um die Drehachse (13) des Laufrads (12) verlaufende Nut (52,54) angeordnet ist, die zusammen mit den Flügeln (50) jeweils einen seitlichen Strömungskanal (58) bilden.
- Aggregat nach Anspruch 7, dadurch gekennzeichnet, daß die Unterbrechung oder zumindest Verengung der Strömungskanäle (58) durch eine Unterbrechung oder zumindest Verengung der Nuten (52,54) erzeugt ist.
- Aggregat nach Anspruch 7, dadurch gekennzeichnet, daß die Unterbrechung oder zumindest Verengung der Strömungskanäle (58) durch einen radialen Versatz der Nuten (52,54) zu den Flügeln (50) erzeugt ist, so daß diese sich nicht oder gegenüber ihrem übrigen Umfang geringer mit den Flügeln (50) überdecken.
- Aggregat nach Anspruch 4 oder 5 und 6, dadurch gekennzeichnet, daß die Unterbrechung oder zumindest Verengung des Strömungskanals (94) durch wenigstens einen von der Ringwand (30) radial nach innen abstehenden Vorsprung (96) erzeugt ist.
- Aggregat nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß sich der Strömungkanal (78) sowohl seitlich neben dem Außenring (36) des Laufrads (12) als auch über dessen Außenumfang erstreckt.
- Aggregat nach Anspruch 11, dadurch gekennzeichnet, daß die Unterbrechung oder zumindest Verengung des Strömungskanals (78) durch eine Unterbrechung oder zumindest Verengung von dessen sich über den Außenumfang des Außenrings (36) des Laufrads (12) erstreckenden Anteil durch einen von der Ringwand (36) radial nach innen abstehenden Vorsprung (77) erzeugt ist.
- Aggregat nach Anspruch 11 oder 12, dadurch gekennzeichnet, daß die Unterbrechung oder zumindest Verengung des Strömungskanals (78) durch eine Unterbrechung oder zumindest Verengung von dessen sich seitlich neben dem Außenring (36) des Laufrads (12) erstreckenden Anteil durch dessen Unterbrechung oder zumindest Verengung erzeugt ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19622560 | 1996-06-05 | ||
DE19622560A DE19622560A1 (de) | 1996-06-05 | 1996-06-05 | Aggregat zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeugs |
PCT/DE1997/000272 WO1997046809A1 (de) | 1996-06-05 | 1997-02-13 | Aggregat zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0842366A1 EP0842366A1 (de) | 1998-05-20 |
EP0842366B1 true EP0842366B1 (de) | 2003-05-07 |
Family
ID=7796219
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97914145A Expired - Lifetime EP0842366B1 (de) | 1996-06-05 | 1997-02-13 | Aggregat zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs |
Country Status (8)
Country | Link |
---|---|
US (1) | US6152686A (de) |
EP (1) | EP0842366B1 (de) |
JP (1) | JPH11510875A (de) |
KR (1) | KR19990036157A (de) |
CN (1) | CN1118635C (de) |
BR (1) | BR9702277A (de) |
DE (2) | DE19622560A1 (de) |
WO (1) | WO1997046809A1 (de) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19719609A1 (de) * | 1997-05-09 | 1998-11-12 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeuges |
FR2768191B1 (fr) * | 1997-09-08 | 2004-11-26 | Marwal Systems | Pompe turbine notamment pour reservoir de carburant de vehicule automobile |
FR2768193B1 (fr) * | 1997-09-08 | 2004-11-26 | Marwal Systems | Pompe turbine notamment pour reservoir de carburant de vehicule automobile perfectionnee pour presenter un rendement ameliore |
FR2768192B1 (fr) * | 1997-09-08 | 2004-01-23 | Marwal Systems | Pompe turbine a rendement ameliore notamment pour reservoir de carburant de vehicule automobile |
DE19949615C2 (de) * | 1998-10-14 | 2002-08-08 | Ford Motor Co | Schaufelradpumpe vom Seitenkanaltyp zum Fördern von Kraftstoff |
ES2194667T3 (es) * | 1999-11-23 | 2003-12-01 | Siemens Ag | Bomba para carburante. |
US6527505B2 (en) * | 2000-12-11 | 2003-03-04 | Visteon Global Technologies, Inc. | Regenerative fuel pump flow chamber |
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 |
US6932562B2 (en) * | 2002-06-18 | 2005-08-23 | Ti Group Automotive Systems, L.L.C. | Single stage, dual channel turbine fuel pump |
US6890144B2 (en) | 2002-09-27 | 2005-05-10 | Visteon Global Technologies, Inc. | Low noise fuel pump design |
DE102004052439A1 (de) | 2004-10-28 | 2006-05-04 | Siemens Ag | Kraftstoffpumpe und Kraftstoffversorgungsanlage für eine Brennkraftmaschine eines Kraftfahrzeuges mit einer Kraftstoffpumpe |
US20080056886A1 (en) * | 2006-08-31 | 2008-03-06 | Varian, S.P.A. | Vacuum pumps with improved pumping channel cross sections |
DE102007026533A1 (de) * | 2007-06-08 | 2008-12-11 | Continental Automotive Gmbh | Kraftstoffpumpe |
DE102007038144A1 (de) * | 2007-08-13 | 2009-02-19 | Continental Automotive Gmbh | Seitenkanalpumpe zur Förderung von Kraftstoff in einem Kraftfahrzeug |
US20230011740A1 (en) * | 2021-07-07 | 2023-01-12 | Eaton Intelligent Power Limited | Regenerative pump and methods |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3560104A (en) * | 1969-02-28 | 1971-02-02 | Abas Beaucan Neale | Two-stage,vortex-type centrifugal compressor or pump |
JPS58222997A (ja) * | 1982-06-21 | 1983-12-24 | Nippon Denso Co Ltd | ポンプ装置 |
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 |
DE59006174D1 (de) * | 1989-04-07 | 1994-07-28 | Ciba Geigy Ag | Pestizide Wirkstoffkonzentrate und ihre Herstellung. |
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 |
-
1996
- 1996-06-05 DE DE19622560A patent/DE19622560A1/de not_active Ceased
-
1997
- 1997-02-13 DE DE59710028T patent/DE59710028D1/de not_active Expired - Fee Related
- 1997-02-13 KR KR1019980700825A patent/KR19990036157A/ko not_active Application Discontinuation
- 1997-02-13 BR BR9702277A patent/BR9702277A/pt not_active IP Right Cessation
- 1997-02-13 CN CN97190446A patent/CN1118635C/zh not_active Expired - Fee Related
- 1997-02-13 JP JP10500068A patent/JPH11510875A/ja active Pending
- 1997-02-13 EP EP97914145A patent/EP0842366B1/de not_active Expired - Lifetime
- 1997-02-13 US US08/983,623 patent/US6152686A/en not_active Expired - Fee Related
- 1997-02-13 WO PCT/DE1997/000272 patent/WO1997046809A1/de not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
US6152686A (en) | 2000-11-28 |
JPH11510875A (ja) | 1999-09-21 |
DE19622560A1 (de) | 1997-12-11 |
DE59710028D1 (de) | 2003-06-12 |
EP0842366A1 (de) | 1998-05-20 |
WO1997046809A1 (de) | 1997-12-11 |
BR9702277A (pt) | 1999-07-20 |
CN1118635C (zh) | 2003-08-20 |
KR19990036157A (ko) | 1999-05-25 |
CN1189879A (zh) | 1998-08-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0774077B2 (de) | Strömungspumpe zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs | |
EP0842366B1 (de) | Aggregat zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs | |
EP0536159B1 (de) | Aggregat zum fördern von kraftstoff vom vorratstank zur brennkraftmaschine eines kraftfahrzeuges | |
EP1828611B1 (de) | Flügelzellenpumpe | |
DE4318122C2 (de) | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeugs | |
EP1828609B1 (de) | Flügelzellenpumpe | |
DE19719609A1 (de) | Aggregat zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeuges | |
DE3235427A1 (de) | Fluegelpumpe | |
DE19634734A1 (de) | Strömungspumpe | |
DE102005047175A1 (de) | Flügelzellenpumpe | |
EP1103723B1 (de) | Kraftstoffpumpe | |
DE102004014457B4 (de) | Kraftstoffpumpe | |
DE3117743C2 (de) | Ölpumpe | |
DE19528181A1 (de) | Peripheralpumpe, insbesondere zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeuges | |
DE3801306A1 (de) | Fluegelzellenverdichter | |
DE4326505A1 (de) | Peripheralpumpe, insbesondere zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeugs | |
DE3644150C2 (de) | Kraftstoffeinspritzpumpe für Brennkraftmaschinen | |
DE10054590B4 (de) | Kraftstoffpumpe | |
DE19902626C2 (de) | Seitenkanalgebläse | |
WO2002093014A1 (de) | Strömungspumpe, insbesondere zum fördern von kraftstoff aus einem vorratsbehälter zu einer brennkraftmaschine eines kraftfahrzeugs | |
AT407427B (de) | Kraftstoffeinspritzpumpe für brennkraftmaschinen | |
DE19652420A1 (de) | Stromregelanordnung für eine hydraulische Fördereinrichtung | |
WO1998004825A1 (de) | Kraftstoffeinspritzpumpe für brennkraftmaschinen | |
DE19749484A1 (de) | Stromregelanordnung für eine hydraulische Fördereinrichtung | |
DE10216549A1 (de) | Pumpe |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR IT |
|
17P | Request for examination filed |
Effective date: 19980612 |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
17Q | First examination report despatched |
Effective date: 20020807 |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Designated state(s): DE FR IT |
|
REF | Corresponds to: |
Ref document number: 59710028 Country of ref document: DE Date of ref document: 20030612 Kind code of ref document: P |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20040210 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20040901 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20041029 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050213 |