EP0857255B1 - Strömungspumpe - Google Patents
Strömungspumpe Download PDFInfo
- Publication number
- EP0857255B1 EP0857255B1 EP97922837A EP97922837A EP0857255B1 EP 0857255 B1 EP0857255 B1 EP 0857255B1 EP 97922837 A EP97922837 A EP 97922837A EP 97922837 A EP97922837 A EP 97922837A EP 0857255 B1 EP0857255 B1 EP 0857255B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- channel
- damping groove
- communication
- side channel
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid 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
-
- 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 flow pump, especially for delivering fuel from a Fuel tank of a motor vehicle, which in the preamble of Claim 1 defined genus.
- peripheral pump In a known two-flow flow pump of this type (DE 40 20 521 A1), there called peripheral pump, is from one side wall of the walls delimiting the pump chamber and the peripheral wall at a the pump outlet having intermediate housing and the other side wall one connected to an outlet nozzle Housing cover formed with pump inlet.
- the Pump or impeller arranged in the pump chamber is seated a molded on the housing cover and is rotatably with the output shaft of an electric motor connected, which is formed in an intermediate housing Depository is added. The sucks during operation Flow pump fuel on the intake manifold on and presses this into the interior of a via the pump outlet Enclosing electric motor and intermediate housing Pump housing. From there it is under pressure standing fuel over a at a pressure port of the Pump housing to be connected to the pressure line of the Internal combustion engine supplied.
- This known flow pump shows the geometrical Design of the outlet area of the side channel in the good noise behavior on both side walls.
- the flow pump according to the invention with the characteristic Features of claim 1 has the advantage that the of Flow pump still caused flow-induced Noises are further reduced.
- the Damping groove according to the invention which by their arrangement according to the invention in the region of the largest occurring amplitudes of the wall pressure vibrations with Impeller blade frequency, the wall alternating pressures significantly reduced what with a clear Noise reduction goes hand in hand.
- the flow pump seen in side view in FIG. 1, also called side channel pump, is used to pump Fuel from a fuel tank, not shown of a motor vehicle to a likewise not shown Internal combustion engine of the motor vehicle.
- the flow pump has a formed in a pump housing 10 Pump chamber 11 that of two radially extending, axially spaced side walls 12, 13 and one the side walls along their periphery with each other connecting peripheral wall 14 is limited (Fig. 1 and 2).
- the side wall 13 and the peripheral wall 14 are on one Intermediate housing 15 formed (Fig. 2 and 3), while the Side wall 12 on a suction or housing cover 16 (Fig. 4 and 5) which is formed with the intermediate housing 15 and / or the pump housing 10 is firmly connected.
- the Pump housing 10 overlaps the intermediate housing 15 and takes an electric motor not visible here inside on.
- the intermediate housing 15 there is also a side wall 13 axially penetrating pump outlet 17 is provided, the one Connection between the pump chamber 11 and the interior of the Manufactures pump housing 10, and the pump housing 10 is connected to a pressure port 18 on which the of the Flow pump delivered fuel exits.
- the Housing cover 16 has an intake port 19 for intake of the fuel from the fuel tank, which with a the pump inlet 33 penetrating the side wall 12 (FIG. 5) communicates.
- each side wall 12 13 has a side channel 20 or 21 educated.
- everyone Side channel 20, 21 runs concentrically to pump axis 22 and extends leaving one remaining Break bar 35 or 23 almost over the entire Circumference of the side wall 12 or 13.
- the interrupter web 35 is from the side channel start 201 and the side channel end 202 (Fig. 5), and according to the interrupter 23 from Side channel start 211 and side channel end 212 (FIG. 3) limited.
- the side channel start 201 of the side channel 20 in the side wall 12 on the housing cover 16 stands with the Pump inlet 33 (and this in turn with the intake manifold 19) and the side channel end 212 of the in the side wall 13 Intermediate housing 15 formed side channel 21 is available the pump outlet 17 in connection and this in turn the inside of the pump housing 10 with the pressure port 18.
- Impeller 24 arranged in the pump chamber 11 is a pump or coaxial to the pump axis 22 Impeller 24 arranged.
- the impeller 24 sits on the one hand on a bearing journal 25, which is coaxial on the side wall 12 protrudes into the pump chamber 11 and on the other hand rotatably on an output shaft 26 of the electric motor, the in a bearing bushing 27 coaxial to the pump axis 22 is stored.
- the bearing bush 27 is in a Sidewall 13 penetrating coaxial bore 28 in Pressed intermediate housing 15.
- the impeller 24 (Fig. 7) has a plurality of circumferentially from each other spaced impeller blades 29 at their from the Pump axis 22 opposite end by a circular Outer ring 30 are interconnected.
- the Impeller blades 29 each limit one between them Vane chamber 31, which is open in the axial direction.
- the Impeller blades 29 and the outer ring 30 are in one piece with the impeller 24, and the impeller blades 29 formed in that between on a common Distribution circuit arranged openings in the impeller 24 Web remain as impeller blades 29.
- the outer ring 30 is dimensioned so that between the circumferential outer surface 301 of the outer ring 30 and the peripheral wall 14 Radial gap 32 remains (Fig. 1). Sucks in operation Flow pump fuel through the intake 19 and presses the fuel through the pump outlet 17 into the Inside of the pump housing 10 and from there on Pressure port 18 to the internal combustion engine.
- curved damping groove 36 introduced (Fig. 5), the extends approximately across the side channel width. That in Fig. 5 side channel end of the side channel 20 identified by 202 has an approximately S-shaped curved contour, the middle part of the contour on the center line 37 of the Side channel 20 or parallel to it.
- the damping groove 36 is now such at the contour of the side channel end 202 along that the measured in the circumferential direction Distance dimension s between the center line 38 of the damping groove 36 and the contour of the side channel end 202 at each point the center line 38 is constant.
- the distance measure s is one to three times as large as that in Circumferential direction of the impeller 24 seen thickness ⁇ the Impeller blades 29.
- the shape of the damping groove 36 is there executed so that the outer and inner circular arc Boundary line of the damping groove 36 and the center line 38 the damping groove 36 the same center of curvature exhibit.
- the damping groove 36 has a semicircular cross section with the maximum groove depth t in the range of 0.1 - 1.5 mm, preferably between 0.2 mm and 0.5 mm.
- the maximum groove width b is one to three times that in Thickness ⁇ of the impeller blades 29 seen in the circumferential direction the impeller 24.
- damping groove 39 in the Side wall 13 of the intermediate housing 15 are introduced, here again in the interrupter 23 near the Side channel end 212 of the side channel 21.
- the pump outlet 17 opens here.
- the damping groove 39 is identical to the damping groove 36, so that the design information given there also apply here.
- the flow pump can the damping groove 36 in the side wall 12 of the housing cover 16 omitted, so that only - as described above - the Damping groove 36 in the side wall 13 of the intermediate housing 15 is available.
- the invention is not based on those described Embodiments limited. So the flow pump can also be executed with one flow, so that only in one Sidewall there is a side channel, the Side channel start with the pump inlet and its Side channel end is connected to the pump outlet.
- the side channel can be in the intermediate housing or in Housing cover are formed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
- Fig. 1
- eine Seitenansicht einer Strömungspumpe zum Fördern von Kraftstoff, teilweise geschnitten,
- Fig. 2
- einen Schnitt längs der Linie II-II in Fig. 3 eines Zwischengehäuses in der Strömungspumpe in Fig. 1
- Fig. 3
- eine Ansicht des Zwischengehäuses in Richtung Pfeil III in Fig. 2,
- Fig. 4
- einen Schnitt längs der Linie IV-IV in Fig. 5 eines Gehäusedeckels der Strömungspumpe in Fig. 1,
- Fig. 5
- eine Ansicht des Gehäusedeckels in Richtung Pfeil V in Fig. 4,
- Fig. 6
- einen Schnitt längs der Linie VI-VI in Fig. 5,
- Fig. 7
- eine Seitenansicht eines Laufrads der Strömungspumpe in Fig. 1.
Claims (11)
- Strömungspumpe, insbesondere zum Fördern von Kraftstoff aus einem Kraftstofftank eines Kraftfahrzeugs, mit einem in einem Pumpengehäuse (10) ausgebildeten Pumpenraum (11), der von zwei sich radial erstreckenden, voneinander beabstandeten Seitenwänden (20,21) und einer die Seitenwände (20,21) längs deren Peripherie miteinander verbindende Peripherwand (14) begrenzt ist, mit mindestens einem in einer der Seitenwände (12,13) angeordneten, zum Pumpenraum (11) hin offenen, nutartigen Seitenkanal (20,21), der konzentrisch zur Pumpenachse (22) mit einem zwischen Seitenkanalende (202,212) und Seitenkanalanfang (201,211), bezogen auf die Strömungsrichtung im Seitenkanal (20,21), verbleibenden Unterbrechersteg (35,23) verläuft, und mit einem im Pumpenraum (11) koaxial zur Pumpenachse (22) angeordneten, rotierenden Laufrad (24), das eine Vielzahl von in Umfangsrichtung voneinander beabstandeten, zwischen sich zumindest axial offene Schaufelkammern (31) begrenzenden, radialen Laufradschaufeln (29) aufweist, dadurch gekennzeichnet, daß im Unterbrechersteg (35) eine zum Pumpenraum (11) hin offene Dämpfungsnut (36) nahe dem Seitenkanalende (202) eingebracht ist, die sich über etwa die Seitenkanalbreite erstreckt.
- Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Dämpfungsnut (36) derart an der Kontur des Seitenkanalendes (202) entlanggeführt ist, daß das in Umfangsrichtung gemessene Abstandsmaß (s) zwischen der Mittellinie (38) der Dämpfungnut (36) und der Kontur des Seitenkanalendes (202) an jedem Punkt der Mittellinie (38) konstant ist.
- Pumpe nach Anspruch 2, dadurch gekennzeichnet, daß die beidseitig der Mittellinie (38) liegenden Begrenzungslinien der Dämpfungsnut (36) und die Mittellinie (38) den gleichen Krümmungsmittelpunkt aufweisen.
- Pumpe nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß das Abstandsmaß (s) das Ein- bis Dreifache der in Umfangsrichtung des Laufrads (24) gesehenen Dicke (δ) der Laufradschaufeln (29) des Laufrads (24) ist.
- Pumpe nach einem der Ansprüche 1 - 4, dadurch gekennzeichnet, daß die Dämpfungsnut (36) einen halbkreisförmigen Querschnitt aufweist.
- Pumpe nach einem der Ansprüche 1 - 5, dadurch gekennzeichnet, daß die maximale Nuttiefe (t) der Dämpfungsnut (36) im Bereich von 0,1 - 1,5mm, vorzugsweise zwischen 0,2 - 0,5mm, liegt.
- Pumpe nach einem der Ansprüche 1 - 6, dadurch gekennzeichnet, daß die maximale Nutbreite (b) der Dämpfungsnut (36) das Ein- bis Dreifache der in Umfangsrichtung gesehenen Dicke (δ) der Laufradschaufeln (29) des Laufrads (24) beträgt.
- Pumpe nach einem der Ansprüche 1 - 7, dadurch gekennzeichnet, daß in jeder Seitenwand (12,13) ein Seitenkanal (20,21) vorhanden ist und der Seitenkanalanfang (201) des einen Seitenkanals (20) mit einem Pumpeneingang (33) und das Seitenkanalende (212) des anderen Seitenkanals (21) mit einem Pumpenausgang (17) in Verbindung steht, und daß die Dämpfungsnut (36) im Unterbrechersteg (35) desjenigen Seitenkanals (20) angeordnet ist, dessen Seitenkanalanfang (201) mit dem Pumpeneingang (33) in Verbindung steht.
- Pumpe nach einem der Ansprüche 1 - 7, dadurch gekennzeichnet, daß in jeder Seitenwand (12,13) ein Seitenkanal (20,21) vorhanden ist und der Seitenkanalanfang (201) des einen Seitenkanals (20) mit einem Pumpeneingang (33) und das Seitenkanalende (212) des anderen Seitenkanals (21) mit einem Pumpenausgang (17) in Verbindung steht, und daß die Dämpfungsnut (39) im Unterbrechersteg (23) desjenigen Seitenkanals (21) angeordnet ist, dessen Seitenkanalende (212) mit dem Pumpenausgang (17) in Verbindung steht.
- Pumpe nach einem der Ansprüche 1 - 7, dadurch gekennzeichnet, daß in jeder Seitenwand (12,13) ein Seitenkanal (20,21) vorhanden ist und der Seicenkanalanfang (201) des einen Seitenkanals (20) mit einem Pumpeneingang (33) und das Seitenkanalende (212) des anderen Seitenkanals (21) mit einem Pumpenausgang (17) in Verbindung steht und daß im Unterbrechersteg (35,23) eines jeden Seitenkanals (20,21) eine gleichartige Dämpfungsnut (36,39) angeordnet ist.
- Pumpe nach einem der Ansprüche 1 - 10, dadurch gekennzeichnet, daß die eine Seitenwand (13) und die Peripherwand (14) an einem den Pumpenausgang (17) enthaltenden Zwischengehäuse (15) und die andere Seitenwand (12) an einem den Pumpeneingang (33) enthaltenden Gehäusedeckel (16) ausgebildet ist, der fest mit dem Zwischengehäuse (15) und/oder dem Pumpengehäuse (10) verbunden ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19634900 | 1996-08-29 | ||
DE19634900A DE19634900A1 (de) | 1996-08-29 | 1996-08-29 | Strömungspumpe |
PCT/DE1997/000760 WO1998009081A1 (de) | 1996-08-29 | 1997-04-15 | Strömungspumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0857255A1 EP0857255A1 (de) | 1998-08-12 |
EP0857255B1 true EP0857255B1 (de) | 2002-11-20 |
Family
ID=7804000
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97922837A Expired - Lifetime EP0857255B1 (de) | 1996-08-29 | 1997-04-15 | Strömungspumpe |
Country Status (8)
Country | Link |
---|---|
US (1) | US6017183A (de) |
EP (1) | EP0857255B1 (de) |
JP (1) | JP2000500210A (de) |
KR (1) | KR19990067133A (de) |
CN (1) | CN1197504A (de) |
BR (1) | BR9706636A (de) |
DE (2) | DE19634900A1 (de) |
WO (1) | WO1998009081A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3638818B2 (ja) * | 1999-05-20 | 2005-04-13 | 愛三工業株式会社 | ウエスコ型ポンプ |
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 |
US6669437B2 (en) * | 2001-10-04 | 2003-12-30 | Visteon Global Technologies, Inc. | Regenerative fuel pump with leakage prevent grooves |
US6890144B2 (en) | 2002-09-27 | 2005-05-10 | Visteon Global Technologies, Inc. | Low noise fuel pump design |
US7722311B2 (en) * | 2006-01-11 | 2010-05-25 | Borgwarner Inc. | Pressure and current reducing impeller |
DE102007018820A1 (de) * | 2007-04-20 | 2008-10-23 | Robert Bosch Gmbh | Förderaggregat |
KR20140021064A (ko) * | 2011-10-13 | 2014-02-19 | 미쓰비시덴키 가부시키가이샤 | 연료펌프 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3095820A (en) * | 1960-02-29 | 1963-07-02 | Mcculloch Corp | Reentry rotary fluid 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 |
DE9104728U1 (de) * | 1991-04-18 | 1992-08-20 | Robert Bosch Gmbh, 7000 Stuttgart, De | |
JP3107438B2 (ja) * | 1992-01-14 | 2000-11-06 | 三菱電機株式会社 | 電動燃料ポンプ |
DE4243544C2 (de) * | 1992-12-22 | 2003-04-17 | Bosch Gmbh Robert | Kraftstofförderpumpe |
JP3237360B2 (ja) * | 1993-02-04 | 2001-12-10 | 株式会社デンソー | 再生ポンプおよびそのケーシング |
DE4338677C2 (de) * | 1993-02-05 | 1999-07-29 | Mannesmann Vdo Ag | Pumpe zum Fördern von Fluid, insbesondere als Kraftstoff-Förderaggregat für Kraftfahrzeuge |
DE4318122C2 (de) * | 1993-06-01 | 2002-01-17 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeugs |
JP3463356B2 (ja) * | 1994-06-30 | 2003-11-05 | 株式会社デンソー | ウエスコポンプ |
DE4446537C2 (de) * | 1994-12-24 | 2002-11-07 | Bosch Gmbh Robert | Flüssigkeitspumpe |
-
1996
- 1996-08-29 DE DE19634900A patent/DE19634900A1/de not_active Withdrawn
-
1997
- 1997-04-15 WO PCT/DE1997/000760 patent/WO1998009081A1/de not_active Application Discontinuation
- 1997-04-15 US US08/983,595 patent/US6017183A/en not_active Expired - Fee Related
- 1997-04-15 BR BR9706636-2A patent/BR9706636A/pt not_active IP Right Cessation
- 1997-04-15 JP JP10511143A patent/JP2000500210A/ja active Pending
- 1997-04-15 EP EP97922837A patent/EP0857255B1/de not_active Expired - Lifetime
- 1997-04-15 KR KR1019980703079A patent/KR19990067133A/ko not_active Application Discontinuation
- 1997-04-15 CN CN97190860A patent/CN1197504A/zh active Pending
- 1997-04-15 DE DE59708770T patent/DE59708770D1/de not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE59708770D1 (de) | 2003-01-02 |
WO1998009081A1 (de) | 1998-03-05 |
DE19634900A1 (de) | 1998-03-05 |
EP0857255A1 (de) | 1998-08-12 |
KR19990067133A (ko) | 1999-08-16 |
JP2000500210A (ja) | 2000-01-11 |
US6017183A (en) | 2000-01-25 |
BR9706636A (pt) | 1999-09-14 |
CN1197504A (zh) | 1998-10-28 |
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