WO1996024769A1 - Strömungspumpe zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs - Google Patents
Strömungspumpe zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs Download PDFInfo
- Publication number
- WO1996024769A1 WO1996024769A1 PCT/DE1996/000024 DE9600024W WO9624769A1 WO 1996024769 A1 WO1996024769 A1 WO 1996024769A1 DE 9600024 W DE9600024 W DE 9600024W WO 9624769 A1 WO9624769 A1 WO 9624769A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- impeller
- rotation
- axis
- flow pump
- vanes
- Prior art date
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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP8523873A JPH09511812A (ja) | 1995-02-08 | 1996-01-10 | 自動車の燃料貯え容器から内燃機関に燃料を圧送するフィードポンプ |
BR9605117A BR9605117A (pt) | 1995-02-08 | 1996-01-10 | Bomba de fluxo para o transporte de combustível de um reservatório para o motor de combustão interna de um automóvel |
EP96900265A EP0774077B2 (de) | 1995-02-08 | 1996-01-10 | Strömungspumpe zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs |
US08/700,504 US5807068A (en) | 1995-02-08 | 1996-01-10 | Flow pump for feeding fuel from a supply container to internal combustion engine of a motor vehicle |
DE59605787T DE59605787D1 (de) | 1995-02-08 | 1996-01-10 | Strömungspumpe zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19504079A DE19504079B4 (de) | 1995-02-08 | 1995-02-08 | Strömungspumpe zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeugs |
DE19504079.1 | 1995-02-08 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996024769A1 true WO1996024769A1 (de) | 1996-08-15 |
Family
ID=7753421
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1996/000024 WO1996024769A1 (de) | 1995-02-08 | 1996-01-10 | Strömungspumpe zum fördern von kraftstoff aus einem vorratsbehälter zur brennkraftmaschine eines kraftfahrzeugs |
Country Status (8)
Country | Link |
---|---|
US (1) | US5807068A (de) |
EP (1) | EP0774077B2 (de) |
JP (1) | JPH09511812A (de) |
KR (1) | KR100382681B1 (de) |
CN (1) | CN1071420C (de) |
BR (1) | BR9605117A (de) |
DE (2) | DE19504079B4 (de) |
WO (1) | WO1996024769A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2320524A (en) * | 1996-10-16 | 1998-06-24 | Ford Motor Co | Impeller for a regenerative turbine fuel pump |
US6113363A (en) * | 1999-02-17 | 2000-09-05 | Walbro Corporation | Turbine fuel pump |
US6425733B1 (en) | 2000-09-11 | 2002-07-30 | Walbro Corporation | Turbine fuel pump |
Families Citing this family (30)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19615323A1 (de) * | 1996-04-18 | 1997-10-23 | Vdo Schindling | Peripheralpumpe |
DE19615322A1 (de) * | 1996-04-18 | 1997-10-23 | Vdo Schindling | Peripheralpumpe |
DE19719609A1 (de) * | 1997-05-09 | 1998-11-12 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeuges |
KR100317013B1 (ko) | 1997-08-07 | 2001-12-24 | 이토 히로미 | 전동식 연료 펌프의 임펠러 |
DE19757580A1 (de) | 1997-12-23 | 1999-07-01 | Bosch Gmbh Robert | Seitenkanalpumpe mit Seitenkanal im Ansaugdeckel zur Vermeidung verlustbehafteter Wirbelstrukturen |
JP3756337B2 (ja) | 1999-02-09 | 2006-03-15 | 愛三工業株式会社 | 流体ポンプ |
DE19912314C2 (de) * | 1999-03-19 | 2002-10-10 | Siemens Ag | Förderpumpe |
US6296439B1 (en) * | 1999-06-23 | 2001-10-02 | Visteon Global Technologies, Inc. | Regenerative turbine pump impeller |
US6299406B1 (en) * | 2000-03-13 | 2001-10-09 | Ford Global Technologies, Inc. | High efficiency and low noise fuel pump impeller |
DE10013908A1 (de) * | 2000-03-21 | 2001-09-27 | Mannesmann Vdo Ag | Förderpumpe |
US6527506B2 (en) * | 2000-03-28 | 2003-03-04 | Delphi Technologies, Inc. | Pump section for fuel pump |
US6439833B1 (en) * | 2000-08-31 | 2002-08-27 | Delphi Technologies, Inc. | V-blade impeller design for a regenerative turbine |
US6533538B2 (en) * | 2000-12-07 | 2003-03-18 | Delphi Technologies, Inc. | Impeller for fuel pump |
JP4827319B2 (ja) | 2001-05-09 | 2011-11-30 | 株式会社ミツバ | 液体ポンプのインペラ |
JP2003193991A (ja) | 2001-12-25 | 2003-07-09 | Aisan Ind Co Ltd | 燃料ポンプ |
JP3964200B2 (ja) * | 2001-12-26 | 2007-08-22 | 愛三工業株式会社 | 燃料ポンプ |
DE10202366A1 (de) * | 2002-01-23 | 2003-08-07 | Pierburg Gmbh | Seitenkanalpumpe |
US7037066B2 (en) * | 2002-06-18 | 2006-05-02 | Ti Group Automotive Systems, L.L.C. | Turbine fuel pump impeller |
US6932562B2 (en) * | 2002-06-18 | 2005-08-23 | Ti Group Automotive Systems, L.L.C. | Single stage, dual channel turbine fuel pump |
JP4692009B2 (ja) * | 2004-04-07 | 2011-06-01 | 株式会社デンソー | 燃料ポンプ用インペラおよびそれを用いた燃料ポンプ |
JP2006022727A (ja) * | 2004-07-08 | 2006-01-26 | Aisan Ind Co Ltd | 燃料噴射弁 |
JP4252507B2 (ja) * | 2004-07-09 | 2009-04-08 | 愛三工業株式会社 | 燃料ポンプ |
JP4912090B2 (ja) | 2006-08-30 | 2012-04-04 | 愛三工業株式会社 | インペラ及びインペラを用いた燃料ポンプ |
GB2477178B (en) * | 2010-02-18 | 2012-01-11 | Quail Res And Design Ltd | Improved Pump |
US9249806B2 (en) | 2011-02-04 | 2016-02-02 | Ti Group Automotive Systems, L.L.C. | Impeller and fluid pump |
DE102013220668A1 (de) * | 2013-10-14 | 2015-04-16 | Continental Automotive Gmbh | Laufrad für eine insbesondere als Seitenkanalgebläse ausgebildete Seitenkanal-Strömungsmaschine |
DE102013220717B4 (de) * | 2013-10-14 | 2016-04-07 | Continental Automotive Gmbh | Pumpe |
KR101888056B1 (ko) * | 2014-11-03 | 2018-08-13 | 주식회사 코아비스 | 다단 연료펌프 |
DE102017215731A1 (de) * | 2017-09-07 | 2019-03-07 | Robert Bosch Gmbh | Seitenkanalverdichter für ein Brennstoffzellensystem zur Förderung und/oder Verdichtung von einem gasförmigen Medium |
US12000411B2 (en) | 2022-01-07 | 2024-06-04 | Phinia Delphi Luxembourg Sarl | Fluid pump impeller including blades extending from a hub to an outer ring and having a draft angle between adjacent blades that varies between the hub and the outer ring |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1689579A (en) * | 1921-08-24 | 1928-10-30 | Arthur W Burks | Rotary pump |
US1973669A (en) * | 1931-01-12 | 1934-09-11 | Spoor Willem Lodewijk Joost | Rotary pump |
DE1403575A1 (de) * | 1961-02-22 | 1968-11-28 | Mcculloch Corp | Wiedereintritts-Rotations-Stroemungsmittelpumpe |
DE3327922A1 (de) * | 1983-08-03 | 1985-02-14 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstofffoerderaggregat |
WO1992000457A1 (de) * | 1990-06-28 | 1992-01-09 | Robert Bosch Gmbh | Peripheralpumpe, insbesondere zum fördern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1689570A (en) * | 1922-11-18 | 1928-10-30 | Rubber Latex Res Corp | Process of making reenforced hard rubber |
US2042499A (en) * | 1933-09-15 | 1936-06-02 | Roots Connersville Blower Corp | Rotary pump |
US2217211A (en) * | 1937-09-11 | 1940-10-08 | Roots Connersville Blower Corp | Rotary pump |
US3095820A (en) * | 1960-02-29 | 1963-07-02 | Mcculloch Corp | Reentry rotary fluid pump |
US3951567A (en) * | 1971-12-18 | 1976-04-20 | Ulrich Rohs | Side channel compressor |
US3917431A (en) * | 1973-09-18 | 1975-11-04 | Dresser Ind | Multi-stage regenerative fluid pump |
SU578497A1 (ru) * | 1975-09-29 | 1977-10-30 | Московское Ордена Ленина И Ордена Трудового Красного Знамени Высшее Техническое Училище Им.Н.Э.Баумана | Рабочее колесо вихревой машины |
DE3509374A1 (de) * | 1985-03-15 | 1986-09-25 | Robert Bosch Gmbh, 7000 Stuttgart | Einrichtung zum foerdern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges |
US5265996A (en) * | 1992-03-10 | 1993-11-30 | Sundstrand Corporation | Regenerative pump with improved suction |
-
1995
- 1995-02-08 DE DE19504079A patent/DE19504079B4/de not_active Expired - Fee Related
-
1996
- 1996-01-10 CN CN96190011A patent/CN1071420C/zh not_active Expired - Fee Related
- 1996-01-10 KR KR1019960705575A patent/KR100382681B1/ko not_active IP Right Cessation
- 1996-01-10 JP JP8523873A patent/JPH09511812A/ja not_active Abandoned
- 1996-01-10 US US08/700,504 patent/US5807068A/en not_active Expired - Fee Related
- 1996-01-10 WO PCT/DE1996/000024 patent/WO1996024769A1/de active IP Right Grant
- 1996-01-10 BR BR9605117A patent/BR9605117A/pt not_active IP Right Cessation
- 1996-01-10 EP EP96900265A patent/EP0774077B2/de not_active Expired - Lifetime
- 1996-01-10 DE DE59605787T patent/DE59605787D1/de not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1689579A (en) * | 1921-08-24 | 1928-10-30 | Arthur W Burks | Rotary pump |
US1973669A (en) * | 1931-01-12 | 1934-09-11 | Spoor Willem Lodewijk Joost | Rotary pump |
DE1403575A1 (de) * | 1961-02-22 | 1968-11-28 | Mcculloch Corp | Wiedereintritts-Rotations-Stroemungsmittelpumpe |
DE3327922A1 (de) * | 1983-08-03 | 1985-02-14 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstofffoerderaggregat |
WO1992000457A1 (de) * | 1990-06-28 | 1992-01-09 | Robert Bosch Gmbh | Peripheralpumpe, insbesondere zum fördern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2320524A (en) * | 1996-10-16 | 1998-06-24 | Ford Motor Co | Impeller for a regenerative turbine fuel pump |
GB2320524B (en) * | 1996-10-16 | 2000-10-25 | Ford Motor Co | Impeller for a regenerative turbine fuel pump |
US6113363A (en) * | 1999-02-17 | 2000-09-05 | Walbro Corporation | Turbine fuel pump |
US6425733B1 (en) | 2000-09-11 | 2002-07-30 | Walbro Corporation | Turbine fuel pump |
Also Published As
Publication number | Publication date |
---|---|
KR970702436A (ko) | 1997-05-13 |
KR100382681B1 (ko) | 2003-08-21 |
DE19504079B4 (de) | 2004-11-04 |
JPH09511812A (ja) | 1997-11-25 |
CN1145659A (zh) | 1997-03-19 |
BR9605117A (pt) | 1997-10-07 |
EP0774077B2 (de) | 2006-04-05 |
DE19504079A1 (de) | 1996-08-14 |
CN1071420C (zh) | 2001-09-19 |
US5807068A (en) | 1998-09-15 |
EP0774077A1 (de) | 1997-05-21 |
EP0774077B1 (de) | 2000-08-23 |
DE59605787D1 (de) | 2000-09-28 |
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