EP1187991A1 - Förderpumpe - Google Patents
FörderpumpeInfo
- Publication number
- EP1187991A1 EP1187991A1 EP01907576A EP01907576A EP1187991A1 EP 1187991 A1 EP1187991 A1 EP 1187991A1 EP 01907576 A EP01907576 A EP 01907576A EP 01907576 A EP01907576 A EP 01907576A EP 1187991 A1 EP1187991 A1 EP 1187991A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- shaft
- feed pump
- pump according
- housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 claims description 3
- 239000002828 fuel tank Substances 0.000 claims description 2
- 239000007788 liquid Substances 0.000 claims description 2
- 238000005406 washing Methods 0.000 claims description 2
- 238000007789 sealing Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
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
- F04D29/18—Rotors
-
- 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
- the invention relates to a feed pump, in particular for delivering fuel from a fuel tank of a motor vehicle or for delivering washing liquid from a windshield washer system, with an impeller which is arranged in a rotationally fixed manner on a driven shaft and with a housing which faces a subarea of the impeller at a short distance.
- Such feed pumps are usually designed as peripheral pumps or side channel pumps and are known from practice.
- the housing usually has two housing parts with a recess for the impeller.
- a particularly small sealing gap is arranged in the radially outer regions of the impeller adjacent to guide vanes between the impeller and the housing parts.
- an axial sliding bearing is usually arranged in the sealing gap.
- a disadvantage of the known feed pump is that positional tolerances and the angle of inclination of the shaft relative to the housing lead to the impeller grinding on the housing. However, this grinding creates strong noises and also reduces the efficiency of the feed pump.
- the invention is based on the problem of designing a feed pump of the type mentioned at the outset in such a way that it has a particularly low noise level and the highest possible efficiency.
- the impeller has means for the mobility of its outer edge with respect to the shaft in the pivoting direction about an axis arranged transversely to the shaft and / or with respect to its radially inner region in the axial direction.
- the radially outer region of the impeller in the housing can tilt by a predetermined amount or it can tilt slightly move.
- the position can be adjusted in the housing, for example by the forces of the thrust bearing of the impeller. This reliably prevents the impeller from rubbing against the housing. Noise is kept particularly low thanks to the invention. Due to the constant sealing gap in the area adjacent to the guide vanes, the feed pump according to the invention has a particularly high efficiency.
- rattling noises can be kept particularly low if the impeller has a depression surrounding the shaft in its area adjacent to the shaft.
- the connection of the impeller to the shaft can be limited to the intended dimensions at an intended height of the impeller. With a very small play of the impeller against the shaft, these dimensions are decisive for the intended swiveling of the impeller.
- Another advantage of this design is that the impeller cannot grind against the housing in the region of the depression.
- the depression could be arranged on an end face of the impeller. To further reduce the noise development of the feed pump according to the invention, however, it is helpful if a depression is arranged in each of the two end faces of the impeller.
- a play between the shaft and the impeller can be kept particularly low if the impeller can be swiveled according to another advantageous development of the invention if the impeller is designed to be elastic, at least in its radially inner region. In the best case, the impeller can be pressed onto the shaft.
- the elastic design of the radially inner region enables simple swiveling and axial mobility of the radially outer edge of the impeller.
- the elastic region of the impeller could be produced, for example, by the impeller having an insert made of an elastic material in this region. According to another advantageous development of the invention, however, the elastic region of the impeller is particularly economical if the impeller has a groove which is arranged concentrically to the shaft.
- feed pumps in one direction of rotation of the impeller have a much higher efficiency than in the opposite direction of rotation.
- a planned high efficiency of the feed pump can be ensured particularly easily if the shaft and / or the impeller have means for their correct arrangement. With this design, the impeller cannot be rotated on the shaft, so that its direction of rotation is reliably determined.
- the means for the correct arrangement of the impeller are structurally particularly simple if the impeller has a projection arranged near one of its end faces for engaging in a shoulder-like recess of the shaft designed corresponding to the projection and if the shaft is axially immovable is held relative to the housing.
- the housing can only be installed if the impeller is fixed in the correct position on the shaft.
- the means for correctly arranging the impeller require a particularly low structural outlay if the shaft has two non-parallel and / or different flats on its lateral surface for a form-fitting connection in the direction of rotation with a correspondingly shaped recess of the impeller ,
- FIG. 2 shows a sectional view through the feed pump according to the invention from FIG. 1 along the line II-II,
- FIG. 3 shows a longitudinal section through a further embodiment of the feed pump according to the invention
- FIG. 4 shows a sectional view through the feed pump according to the invention from FIG. 3 along the line IV-IV,
- FIG 5 shows a longitudinal section through a further embodiment of the feed pump according to the invention.
- FIG. 1 shows a sectional view through a feed pump according to the invention, designed as a side channel pump, with an impeller 2 rotatable in a housing 1.
- the impeller 2 is arranged on a driven shaft 3 in a rotationally fixed and slightly axially displaceable manner.
- the shaft 3 can for example be designed as a motor shaft of an electric motor, not shown.
- the housing 1 has two housing parts 5, 6, which are kept at a distance by means of a ring 4, and a sheet-metal strip 7 rolled on the edges of the housing parts 5, 6 for prestressing them against the ring 4.
- an inlet channel 8 is arranged, while the other housing part 5 has an outlet channel 9.
- the inlet channel 8 and the outlet channel 9 are each connected to partially annular channels 10, 11.
- the impeller 2 has vane chambers 14, 15 delimited by guide vanes 12, 13 in the region of the partially annular channels 10, 11. In this region, the housing 1 faces the impeller 2 to form sealing gaps at a particularly small distance. In the end faces of the impeller 2 there are opposing pockets 16 of axial slide bearings 17, which are interconnected with channels 18. When the impeller 2 rotates in the housing 1, fuel or windshield washer fluid, for example, can be conveyed from the inlet duct 8 through the impeller 2 to the outlet duct 9.
- the feed pump can of course also be designed as a peripheral pump, in which the rotor blades 12, 13 are arranged on the circumference of the impeller 2.
- the impeller 2 In its radially inner region, the impeller 2 has a recess 19, 20 in each of the two end faces. These recesses 19, 20 limit the dimensions with which the impeller 2 is connected to the shaft 3 and, in conjunction with a slight play of the impeller 2, enable on the shaft 3 a slight tilting of the impeller 2 about an axis running perpendicular to the plane of the drawing. As a result, the impeller 2 can adapt to the dimensions of the housing 1 in its radially outer region, which has the blade chambers 14, 15. This adaptation is also improved in that the impeller 2 is made slightly elastic in its radially inner region by the recesses 19, 20. The position of the radially outer region of the impeller 2 is set by the forces of the axial slide bearing 17 and thus grinding of the impeller 2 on the housing parts 5, 6 is prevented.
- Figure 2 shows in a sectional view through the feed pump of Figure 1 along the line II - II that the shaft 3 for rotationally fixed connection to the impeller 2 has two flats 21, 22 on its outer surface.
- the impeller 2 has a recess 23 designed in accordance with the shaft 3.
- the flats 21, 22 run at an angle of ⁇ 180 ° to one another and therefore not parallel. As a result, the impeller 2 can only be mounted on the shaft 3 in the intended direction of rotation and thus in the correct position.
- the flats 21, 22 also have different dimensions.
- FIG. 3 shows a further embodiment of the feed pump, in which a housing 24 is axially immovably connected to an electric motor 25 provided for driving it.
- a shaft 27 which is positively connected to an impeller 26 in the direction of rotation has a shoulder-like recess 28 for receiving a projection 29 of the impeller 26.
- Housing 24 of the feed pump is axially immovably connected to an electric motor 25.
- the impeller 26 can be mounted in the housing 24 only in the position shown and thus in the direction of rotation provided.
- the impeller 26 has a recess 30 in the region of the shaft 27.
- the dimensions of the recess 30 in the impeller 26 limit the dimensions of the connection of the impeller 26 to the shaft 27 to an intended dimension.
- the radially outer region of the impeller 26 can thereby tilt slightly relative to the shaft 27 and thus adapt to tolerances of the housing. Due to the radial dimensions of the depression 30, an intended elasticity of the radially inner region of the impeller 26 can be ensured.
- Figure 4 shows in a sectional view along the line IV - IV through the feed pump of Figure 3 that the shoulder-like recess 28 of the shaft 27 has a flat 31 for non-rotatable connection with a correspondingly shaped recess 32 of the impeller 26.
- FIG. 5 shows a further embodiment of the feed pump in a sectional view. This differs from that of FIG. 1 primarily in that an impeller 33 has two grooves 35, 36 arranged concentrically with the shaft 34. These grooves 35, 36 produce an elasticity in the radially inner region of the impeller 33 and therefore allow a slight axial mobility and a pivotability of its radially outer region about an axis arranged perpendicular to the plane of the drawing. The impeller 33 can therefore be attached to the shaft 34 without play.
Landscapes
- 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
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10019909A DE10019909A1 (de) | 2000-04-20 | 2000-04-20 | Förderpumpe |
DE10019909 | 2000-04-20 | ||
PCT/EP2001/002421 WO2001081768A1 (de) | 2000-04-20 | 2001-03-03 | Förderpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1187991A1 true EP1187991A1 (de) | 2002-03-20 |
EP1187991B1 EP1187991B1 (de) | 2007-01-24 |
Family
ID=7639658
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01907576A Expired - Lifetime EP1187991B1 (de) | 2000-04-20 | 2001-03-03 | Förderpumpe |
Country Status (10)
Country | Link |
---|---|
US (1) | US6503049B2 (de) |
EP (1) | EP1187991B1 (de) |
JP (1) | JP2003532010A (de) |
KR (1) | KR20020026191A (de) |
CN (1) | CN1366585A (de) |
AU (1) | AU3550301A (de) |
BR (1) | BR0106079A (de) |
DE (2) | DE10019909A1 (de) |
ES (1) | ES2276766T3 (de) |
WO (1) | WO2001081768A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
JP4271501B2 (ja) * | 2003-06-06 | 2009-06-03 | 愛三工業株式会社 | 燃料ポンプ |
US9249806B2 (en) | 2011-02-04 | 2016-02-02 | Ti Group Automotive Systems, L.L.C. | Impeller and fluid pump |
JP6135593B2 (ja) * | 2013-09-24 | 2017-05-31 | 株式会社デンソー | 燃料ポンプ |
CN107461362A (zh) * | 2017-09-30 | 2017-12-12 | 江苏大学镇江流体工程装备技术研究院 | 一种开式侧流道泵水力设计方法 |
CN108386388B (zh) * | 2018-02-26 | 2022-05-13 | 江苏大学镇江流体工程装备技术研究院 | 一种相同流量扬程可选的超低比转速泵及设计方法 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2080272A (en) * | 1934-11-07 | 1937-05-11 | Mcilvaine Burner Corp | Control valve for oil burners |
US2604852A (en) * | 1948-05-03 | 1952-07-29 | Fairbanks Morse & Co | Pump impeller |
DE2023834A1 (de) * | 1970-05-15 | 1971-11-25 | Siemen & Hinsch Gmbh | Flügelradbefestigung bei Kreiselpumpen |
GB2036179B (en) * | 1978-11-28 | 1983-03-23 | Compair Ind Ltd | Regenerative rotodynamic compressors and pumps |
JPS5853200B2 (ja) * | 1981-03-12 | 1983-11-28 | 株式会社デンソー | 電動式燃料ポンプ装置 |
JPH0531279Y2 (de) * | 1988-05-25 | 1993-08-11 | ||
DE4123089C2 (de) * | 1991-07-12 | 1998-02-19 | Mannesmann Vdo Ag | Kraftstoff-Förderaggregat |
US5409357A (en) * | 1993-12-06 | 1995-04-25 | Ford Motor Company | Impeller for electric automotive fuel pump |
-
2000
- 2000-04-20 DE DE10019909A patent/DE10019909A1/de not_active Withdrawn
-
2001
- 2001-03-03 BR BR0106079-1A patent/BR0106079A/pt not_active Application Discontinuation
- 2001-03-03 WO PCT/EP2001/002421 patent/WO2001081768A1/de active IP Right Grant
- 2001-03-03 EP EP01907576A patent/EP1187991B1/de not_active Expired - Lifetime
- 2001-03-03 ES ES01907576T patent/ES2276766T3/es not_active Expired - Lifetime
- 2001-03-03 AU AU35503/01A patent/AU3550301A/en not_active Abandoned
- 2001-03-03 KR KR1020017016316A patent/KR20020026191A/ko not_active Application Discontinuation
- 2001-03-03 JP JP2001578825A patent/JP2003532010A/ja not_active Withdrawn
- 2001-03-03 DE DE50111939T patent/DE50111939D1/de not_active Expired - Lifetime
- 2001-03-03 CN CN01800980A patent/CN1366585A/zh active Pending
- 2001-04-20 US US09/839,895 patent/US6503049B2/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO0181768A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN1366585A (zh) | 2002-08-28 |
WO2001081768A1 (de) | 2001-11-01 |
JP2003532010A (ja) | 2003-10-28 |
US6503049B2 (en) | 2003-01-07 |
DE10019909A1 (de) | 2001-10-25 |
AU3550301A (en) | 2001-11-07 |
BR0106079A (pt) | 2002-03-05 |
KR20020026191A (ko) | 2002-04-06 |
DE50111939D1 (de) | 2007-03-15 |
EP1187991B1 (de) | 2007-01-24 |
ES2276766T3 (es) | 2007-07-01 |
US20020012584A1 (en) | 2002-01-31 |
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