WO1998017916A1 - Förderpumpe - Google Patents
Förderpumpe Download PDFInfo
- Publication number
- WO1998017916A1 WO1998017916A1 PCT/EP1997/005403 EP9705403W WO9817916A1 WO 1998017916 A1 WO1998017916 A1 WO 1998017916A1 EP 9705403 W EP9705403 W EP 9705403W WO 9817916 A1 WO9817916 A1 WO 9817916A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- channel
- feed pump
- area
- pump according
- delivery chamber
- 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
Definitions
- the invention relates to a feed pump with a driven impeller rotating in a pump housing, which has at least one end face of a ring of vane chambers delimiting guide vanes and with at least one partially annular channel arranged in the area of the guide vanes in the pump housing, which channel with the vane chambers is used for conveying forms a liquid from an inlet channel to an outlet channel provided delivery chamber and has a compression region with a tapering cross-section over a limited angular range.
- Such delivery pumps are known as peripheral or side channel pumps and are often used to deliver fuel from a fuel tank to an internal combustion engine of a motor vehicle.
- the guide vanes in the delivery chamber generate a circulation flow which runs transversely to the direction of movement of the guide vanes.
- the compression area serves to increase the pressure in the delivery chamber.
- gas bubbles present in the hot fuel from vaporous fuel are to condense in the liquid fuel by exceeding the vapor pressure. This is important, for example, for a warm start of the motor vehicle, since the temperature of the fuel is particularly high here and gas bubbles are therefore very often sucked in through the inlet duct.
- Cold fuel which usually contains no gas bubbles, should also be reliably pumped with the feed pump.
- the compression area is located directly on the inlet channel adjoining area of the partially annular channel.
- the fuel flows from the inlet duct directly into the compression area and generates swirls there.
- these eddies have areas with high and low pressures and thus prevent the gas bubbles from dissolving reliably.
- there is a risk of cavitation in this feed pump in particular on the wall of the partially annular channel in the compression area. In the long run, this cavitation leads to destruction of the wall of the partially annular channel and to a reduced delivery capacity of the delivery pump.
- a further feed pump has become known, in which the region of the partially annular duct adjoining the inlet duct initially has a first region with a constant cross section. At the end of this area, a degassing hole is machined into the pump housing at the radially inner end of the partially annular channel. Then the cross section of the part-ring-shaped channel is abruptly reduced in order to be guided with a constant cross section to the area of the outlet channel. The gas bubbles are not condensed in the fuel, but should be removed through the degassing hole. Since the circulation flow is already formed in the first area, the gas bubbles are entrained by the fuel and form a foam with the liquid fuel.
- the invention is based on the problem of designing a feed pump of the type mentioned at the outset in such a way that gas bubbles present in the fuel are condensed particularly reliably and that, if possible, no cavitation occurs in the region of the partially annular channel.
- This problem is solved according to the invention in that the partially annular channel between the inlet channel and the compression area has a calming area with a constant cross section.
- the fuel sucked in through the inlet channel first reaches the calming region, in which eddies introduced into the delivery chamber can dissipate through the inlet channel. After the turbulence has subsided, the fuel, together with the gas bubbles, reaches the compression region in which the gas bubbles reliably condense in the fuel when their vapor pressure is exceeded. Since the swirling of the fuel is first removed in the calming area, the risk of cavitation in the wall of the partially annular channel is kept as low as possible and a constant delivery rate of the delivery pump is ensured.
- the invention is also particularly suitable for a feed pump in which delivery chambers are arranged on both sides of the impeller, which have a connection for overflowing the liquid from one delivery chamber into the other delivery chamber, the inlet channel into one delivery chamber and the other delivery chamber into the outlet channel flows.
- a feed pump is often used to achieve a high delivery rate with particularly small dimensions.
- the feed pump has a particularly high delivery rate for cold and warm fuel if the part-annular channel of the delivery chamber opening into the outlet channel has a continuous movement in the direction of movement of the guide vanes, essentially over the same angular range as the calming range of the partially ring-shaped one Channel of the other delivery chamber extending cross-sectional expansion.
- the swirling of the fuel flowing in through the inlet channel subsides particularly reliably if the calming region extends over an angular region of approximately 50 °.
- the gas bubbles in the fuel condense particularly reliably in the fuel if the compression range extends over an angular range of approximately 70 °.
- the flow guide vane could be designed as a component to be inserted separately into the inlet duct.
- the feed pump consists of a particularly few components which can be manufactured inexpensively if the flow guide vane is manufactured in one piece with the pump housing and is arranged on the side of the inlet duct facing away from the partially annular duct.
- the cross-sectional enlargement of the partially annular channel leading to the outlet channel could be produced, for example, by a continuous depression with a constant width of the partially annular channel.
- a circulation flow forms particularly quickly in this part-ring-shaped channel if the cross-sectional expansion of the part-ring-shaped channel leading to the outlet channel is produced by widening the part-ring-shaped channel. As a result, the delivery rate of the feed pump is additionally increased.
- the delivery capacity of the feed pump can be further increased if the cross-sectional widening is produced by a radially inner boundary of the part-ring-shaped channel, which is directed inward in the direction of flow, with a simultaneous continuous depression.
- the circulation flow first forms in the radially outer region of the guide vanes, where the pressure is greatest anyway due to the centrifugal forces generated by the guide vanes.
- FIG. 1 shows a longitudinal section through a feed pump according to the invention
- FIG. 2 shows a tangential section through the feed pump from FIG. 1 along the line II-II,
- FIG. 3 shows a sectional view through the feed pump along the line III-III from FIG. 1,
- Figure 4 is a sectional view through the feed pump along the line IV - IV of Figure 1.
- FIG. 1 shows a longitudinal section of a feed pump according to the invention, designed as a side channel pump, with a pump housing 1.
- An impeller 2 is rotatably arranged in the pump housing 1.
- a ring 5 of guide vanes 6, 6a, 6b are incorporated in each of its two end faces 3, 4.
- the impeller 2 is fixed in its center on a drive shaft 7 in a rotationally fixed manner.
- the pump housing 1 has The area of the guide vanes 6, 6a, 6b on each side has a partially annular channel 8, 9.
- the conveying chambers 11, 12 have a connection 13 to one another which is produced by an overlap of the semicircular cross sections of the vane chambers 10, 10a, 10b. Through this connection 13, liquid can flow from one delivery chamber 11 into the other delivery chamber 12 with almost no swirling.
- the impeller 2 faces the pump housing 1 with a small distance. This creates a sealing gap 14 which runs around the impeller 2 and seals the delivery chambers 11, 12.
- a plurality of mutually opposite depressions 15, 16 are machined in the end faces 3, 4.
- Two opposite depressions 15, 16 are connected to one another by a channel 17.
- a small amount of leakage of the liquid to be delivered reaches the recesses 15, 16 through the sealing gap 14 between the impeller 2 and the pump housing 1.
- the recesses 15, 16 form axial sliding bearings for the impeller 2.
- FIG. 2 shows a tangential section through the feed pump according to the invention from FIG. 1 along the line II-II.
- the pump housing 1 has an inlet channel 18 and an outlet channel 19, which are separated from one another by a sill 20 arranged on both sides of the impeller 2.
- the sill 20 interrupts the circulation flows of the liquid to be delivered which are generated in the delivery chambers 11, 12.
- the one lasskanal 18 opens into a delivery chamber 11, while the other delivery chamber 12 opens into the outlet channel 19.
- a flow guide vane 25 is arranged in the inlet channel 18 and is made in one piece with the pump housing 1.
- 19 opening delivery chamber 12 has, seen in the flow direction, a cross-sectional widening 26 on the inlet side, which extends over the same angular range as the calming area 21 of the other part-ring-shaped channel 8.
- a cross-sectional widening 26 is followed by a conveying area 27 with a constant cross-section.
- FIG. 3 shows, in a sectional illustration along the line III-III from FIG. 1, the partially annular channel 8, into which the inlet channel 18 opens.
- the inlet duct 18 is half covered by the flow guide vane 25.
- the calming region 21 of the partially annular channel 8 extends approximately over an angular range of 50 °, to which the compression region 22 adjoins approximately over an angular range of 70 °.
- the pump housing 1 is penetrated by a vent hole 28. This vent hole 28 is mainly used to vent the feed pump when filling for the first time.
- FIG. 4 shows the partially annular channel 9 opening into the outlet channel 19. It can clearly be seen that the radially outer boundary of the partially annular channel 9 has a constant radius over the entire angular range. The cross-sectional widening 26 at the beginning of the partially annular channel 9 is generated by the radially inner boundary.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
- Jet Pumps And Other Pumps (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP97910403A EP0934466B1 (de) | 1996-10-23 | 1997-10-01 | Förderpumpe |
DE59707441T DE59707441D1 (de) | 1996-10-23 | 1997-10-01 | Förderpumpe |
BR9713271-3A BR9713271A (pt) | 1996-10-23 | 1997-10-01 | Bomba de alimentação |
US09/284,562 US6152687A (en) | 1996-10-23 | 1997-10-01 | Feed pump |
HK00101390A HK1022508A1 (en) | 1996-10-23 | 2000-03-03 | Feed pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19643728A DE19643728A1 (de) | 1996-10-23 | 1996-10-23 | Förderpumpe |
DE19643728.8 | 1996-10-23 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998017916A1 true WO1998017916A1 (de) | 1998-04-30 |
Family
ID=7809549
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1997/005403 WO1998017916A1 (de) | 1996-10-23 | 1997-10-01 | Förderpumpe |
Country Status (9)
Country | Link |
---|---|
US (1) | US6152687A (de) |
EP (1) | EP0934466B1 (de) |
KR (1) | KR20000049235A (de) |
CN (1) | CN1082629C (de) |
BR (1) | BR9713271A (de) |
DE (2) | DE19643728A1 (de) |
ES (1) | ES2177951T3 (de) |
HK (1) | HK1022508A1 (de) |
WO (1) | WO1998017916A1 (de) |
Families Citing this family (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19744037C1 (de) * | 1997-10-06 | 1999-06-02 | Mannesmann Vdo Ag | Förderpumpe |
DE19941786B4 (de) * | 1999-09-02 | 2008-11-20 | Continental Automotive Gmbh | Förderpumpe |
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 |
US6533538B2 (en) * | 2000-12-07 | 2003-03-18 | Delphi Technologies, Inc. | Impeller for fuel pump |
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 |
US6688844B2 (en) * | 2001-10-29 | 2004-02-10 | Visteon Global Technologies, Inc. | Automotive fuel pump impeller |
US6655909B2 (en) | 2001-11-30 | 2003-12-02 | Visteon Global Technologies, Inc. | High flow fuel pump |
DE10202366A1 (de) * | 2002-01-23 | 2003-08-07 | Pierburg Gmbh | Seitenkanalpumpe |
US6932562B2 (en) * | 2002-06-18 | 2005-08-23 | Ti Group Automotive Systems, L.L.C. | Single stage, dual channel turbine fuel pump |
US7037066B2 (en) | 2002-06-18 | 2006-05-02 | Ti Group Automotive Systems, L.L.C. | Turbine fuel pump impeller |
JP4310426B2 (ja) * | 2002-07-25 | 2009-08-12 | 米原技研有限会社 | 加圧遠心ポンプの気体の混入構造 |
US6767181B2 (en) * | 2002-10-10 | 2004-07-27 | Visteon Global Technologies, Inc. | Fuel pump |
US6984099B2 (en) * | 2003-05-06 | 2006-01-10 | Visteon Global Technologies, Inc. | Fuel pump impeller |
US20040258545A1 (en) * | 2003-06-23 | 2004-12-23 | Dequan Yu | Fuel pump channel |
JP2005016312A (ja) | 2003-06-23 | 2005-01-20 | Aisan Ind Co Ltd | 燃料ポンプ |
KR100590169B1 (ko) * | 2004-04-13 | 2006-06-19 | 주식회사 캐프스 | 자동차용 연료펌프의 임펠러구조 |
JP4252507B2 (ja) * | 2004-07-09 | 2009-04-08 | 愛三工業株式会社 | 燃料ポンプ |
JP4672420B2 (ja) * | 2005-04-08 | 2011-04-20 | 愛三工業株式会社 | 燃料ポンプ |
DE102007003555B4 (de) * | 2006-08-04 | 2016-11-10 | Continental Automotive Gmbh | Förderpumpe mit Filter |
DE102010004379A1 (de) | 2009-12-16 | 2011-06-22 | Continental Automotive GmbH, 30165 | Kraftstoffpumpe |
US9249806B2 (en) | 2011-02-04 | 2016-02-02 | Ti Group Automotive Systems, L.L.C. | Impeller and fluid pump |
KR101349689B1 (ko) * | 2011-12-19 | 2014-01-13 | 자동차부품연구원 | 베인 펌프 및 이를 갖는 자동차 |
WO2014186839A1 (en) * | 2013-05-20 | 2014-11-27 | Vilo Niumeitolu | Shock absorber generator |
WO2015178425A1 (ja) * | 2014-05-21 | 2015-11-26 | エウレカ・ラボ株式会社 | ミル機能と羽根せん断機能との一体型微細化装置 |
US20170023022A1 (en) * | 2015-07-20 | 2017-01-26 | Delphi Technologies, Inc. | Fluid pump |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4591311A (en) * | 1983-10-05 | 1986-05-27 | Nippondenso Co., Ltd. | Fuel pump for an automotive vehicle having a vapor discharge port |
DE4036309A1 (de) * | 1989-11-17 | 1991-05-23 | Mitsubishi Electric Corp | Umfangfluss-brennstoffpumpe |
GB2263503A (en) * | 1992-01-22 | 1993-07-28 | Nippon Denso Co | Inlet configuration of a fuel pump. |
US5284417A (en) * | 1993-06-07 | 1994-02-08 | Ford Motor Company | Automotive fuel pump with regenerative turbine and long curved vapor channel |
DE4343078A1 (de) * | 1993-12-16 | 1995-06-22 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine |
US5551835A (en) * | 1995-12-01 | 1996-09-03 | Ford Motor Company | Automotive fuel pump housing |
DE19607573A1 (de) * | 1995-04-07 | 1996-10-10 | Walbro Corp | Kraftstoffpumpe und Verfahren zu ihrer Herstellung |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN2068609U (zh) * | 1990-03-19 | 1991-01-02 | 陆守余 | 液环式氯气泵 |
DE4446537C2 (de) * | 1994-12-24 | 2002-11-07 | Bosch Gmbh Robert | Flüssigkeitspumpe |
-
1996
- 1996-10-23 DE DE19643728A patent/DE19643728A1/de not_active Ceased
-
1997
- 1997-10-01 WO PCT/EP1997/005403 patent/WO1998017916A1/de not_active Application Discontinuation
- 1997-10-01 EP EP97910403A patent/EP0934466B1/de not_active Expired - Lifetime
- 1997-10-01 KR KR1019990703339A patent/KR20000049235A/ko not_active Application Discontinuation
- 1997-10-01 BR BR9713271-3A patent/BR9713271A/pt active Search and Examination
- 1997-10-01 ES ES97910403T patent/ES2177951T3/es not_active Expired - Lifetime
- 1997-10-01 CN CN97198972A patent/CN1082629C/zh not_active Expired - Fee Related
- 1997-10-01 US US09/284,562 patent/US6152687A/en not_active Expired - Lifetime
- 1997-10-01 DE DE59707441T patent/DE59707441D1/de not_active Expired - Lifetime
-
2000
- 2000-03-03 HK HK00101390A patent/HK1022508A1/xx not_active IP Right Cessation
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4591311A (en) * | 1983-10-05 | 1986-05-27 | Nippondenso Co., Ltd. | Fuel pump for an automotive vehicle having a vapor discharge port |
DE4036309A1 (de) * | 1989-11-17 | 1991-05-23 | Mitsubishi Electric Corp | Umfangfluss-brennstoffpumpe |
GB2263503A (en) * | 1992-01-22 | 1993-07-28 | Nippon Denso Co | Inlet configuration of a fuel pump. |
US5284417A (en) * | 1993-06-07 | 1994-02-08 | Ford Motor Company | Automotive fuel pump with regenerative turbine and long curved vapor channel |
DE4343078A1 (de) * | 1993-12-16 | 1995-06-22 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine |
DE19607573A1 (de) * | 1995-04-07 | 1996-10-10 | Walbro Corp | Kraftstoffpumpe und Verfahren zu ihrer Herstellung |
US5551835A (en) * | 1995-12-01 | 1996-09-03 | Ford Motor Company | Automotive fuel pump housing |
Non-Patent Citations (1)
Title |
---|
TONN E: "ZUR BERECHNUNG VON PERIPHERALPUMPEN", KONSTRUKTION, vol. 44, no. 2, 1 February 1992 (1992-02-01), pages 64 - 70, XP000306468 * |
Also Published As
Publication number | Publication date |
---|---|
DE19643728A1 (de) | 1998-04-30 |
BR9713271A (pt) | 2000-03-28 |
EP0934466B1 (de) | 2002-06-05 |
US6152687A (en) | 2000-11-28 |
HK1022508A1 (en) | 2000-08-11 |
CN1234097A (zh) | 1999-11-03 |
EP0934466A1 (de) | 1999-08-11 |
KR20000049235A (ko) | 2000-07-25 |
DE59707441D1 (de) | 2002-07-11 |
CN1082629C (zh) | 2002-04-10 |
ES2177951T3 (es) | 2002-12-16 |
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