EP0772743A1 - Pompe a liquide - Google Patents

Pompe a liquide

Info

Publication number
EP0772743A1
EP0772743A1 EP96900268A EP96900268A EP0772743A1 EP 0772743 A1 EP0772743 A1 EP 0772743A1 EP 96900268 A EP96900268 A EP 96900268A EP 96900268 A EP96900268 A EP 96900268A EP 0772743 A1 EP0772743 A1 EP 0772743A1
Authority
EP
European Patent Office
Prior art keywords
rotation
pump impeller
channel
respect
axis
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
Application number
EP96900268A
Other languages
German (de)
English (en)
Other versions
EP0772743B1 (fr
Inventor
Klaus Dobler
Michael Huebel
Willi Strohl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0772743A1 publication Critical patent/EP0772743A1/fr
Application granted granted Critical
Publication of EP0772743B1 publication Critical patent/EP0772743B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • 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
    • F04D5/007—Details of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet
    • F05B2250/503—Inlet or outlet of regenerative pumps

Definitions

  • the invention relates to a liquid pump according to the preamble of claim 1.
  • Such a liquid pump is known from US Pat. No. 5,310,308.
  • This liquid pump serves to deliver fuel and has a pump impeller which is provided with vanes and is driven in rotation.
  • the pump impeller is arranged in a pump chamber which is delimited in the direction of the axis of rotation of the pump run by a wall part in each case.
  • a sucking opening is formed in one wall part and an outlet opening is formed in the other wall part.
  • a conveying channel extending in the circumferential direction from the sucking opening to the outlet opening is formed in the end faces of the two wall parts facing the pump impeller.
  • the sucking opening opens into the beginning of the conveying channel of one wall part and the outlet opening opens into the end of the conveying channel of the other wall part.
  • the outlet opening has a feed channel into which it opens in the direction of rotation of the pump impeller. bordering opening wall, which ends at the end face of the wall part facing the pump impeller in an edge which is rounded. This opening wall also runs approximately perpendicular to the end face of the wall part facing the pump impeller.
  • the liquid pump according to the invention with the features according to claim 1 has the advantage that the inclined arrangement of the inner portion of the edge of the outlet opening achieves a more favorable flow pattern in the area of the outlet opening and the liquid pump has a higher flow rate than the known liquid pump ⁇ pressure and has a higher efficiency.
  • FIG. 1 shows a section of a liquid pump in a longitudinal section
  • FIG. 2 shows a section through the liquid pump along the line II-II in FIG. 1 in the area of the outlet opening
  • FIG. 3 shows a section through the liquid pump along the line III-III in FIG. 1 at the end of the conveyor channel
  • FIG. 4 in detail the liquid pump in a cylinder jacket section along the line IV-IV in FIG. 2 and FIG. 3.
  • a liquid pump shown in FIGS. 1 to 4 which is used in particular for conveying fuel from a storage tank to the internal combustion engine of a motor vehicle, has a pump impeller 10, which, starting from its two end faces, has a ring each with a distance from one another over the top Has circumference of the pump impeller 10 arranged vanes 12 or blades.
  • the wings 12 can be connected to one another at their radially outer ends via a ring 13.
  • the pump impeller 10 is driven, for example, by an electric motor, not shown, via a shaft 14 rotating around an axis 16.
  • the pump impeller 10 is arranged in a pump chamber 17 which is delimited in the direction of the axis of rotation 16 of the pump impeller 10 by a wall part 19 and 20, respectively.
  • the pump chamber 17 is through a limited cylindrical wall part 22, which can be arranged as a separate ring between the two wall parts 19 and 20 or as shown in Figure 1 is integrally formed with one of the wall parts 19 or 20.
  • the wall part 20 arranged towards the drive motor is designed as an intermediate housing and the other wall part 19 is designed as an intake cover.
  • the shaft 14 driving the pump impeller 10 projects through the intermediate housing 20 into the pump chamber 17.
  • annular delivery channel 25 is formed, which lies opposite the wing rim 12 of the pump impeller 10 and in the beginning of which a suction opening 26 opens which is open to the outside of the liquid pump.
  • annular delivery channel 29 is likewise formed opposite the wing ring 12 of the pump impeller 10, into which an outlet opening 30 opens at the end of the latter.
  • the conveying channels 25 and 29 are arranged approximately congruently and extend in the direction of rotation 11 of the pump impeller 10 from the infant opening 26 to the outlet opening 30.
  • the conveying channels 25 and 29 are in the area between the infant opening 26 and the outlet opening 30 through an interrupter 32 and 33 separated from each other.
  • the conveyor channels 25 and 29 are approximately semicircular in cross section.
  • FIG. 2 shows an enlarged cross section through the liquid pump, in which the intermediate housing 20 can be seen, with the delivery channel 29 formed therein.
  • the delivery channel 29 is radially inward to the axis of rotation 16 of the pump impeller 10 through an inner edge 34 bounded and outwardly by an outer edge 35.
  • the central region of the conveying channel 29 in the radial direction with respect to the axis of rotation 16 is indicated by its center line 36. As shown in FIG.
  • the outlet opening 30 runs in a channel-like manner from the delivery channel 29 to the outer surface 39 of the intermediate housing 20, the outlet opening 30 being arranged inclined with respect to the axis of rotation 16 of the pump impeller 10, specifically in the direction of rotation 11 of the pump impeller 10 from the End face 28 of the intermediate housing 20 towards its outer surface 39.
  • the wall 40 delimiting the outlet opening 30 in the direction of rotation 11 is inclined at an angle ⁇ of approximately 20 to 40 ° to the end face 28 of the intermediate housing 20 facing the pump impeller 10.
  • the wall 40 can taper to the end face 28 or, as shown in FIG. 4, the transition from the wall 40 to the end face 28 can also be rounded.
  • the outlet opening 30 is designed in such a way that its effective flow cross-section downstream remains constant between the points labeled A and B in FIG. 4 or only increases slightly, that is to say by no more than about 20%.
  • the wall 41 delimiting the outlet opening 30 counter to the direction of rotation 11 is arranged inclined at approximately the same angle ⁇ as the wall 40.
  • the outlet opening 30 is approximately circular in cross section.
  • the wall 40 delimiting the outlet opening 30 in the direction of rotation 11 runs out on the end face 28 of the intermediate housing 20 facing the pump impeller 10 in an edge 42 which forms the transition from the delivery channel 29 to the interrupter 33.
  • the edge 42 has an inner edge section 42a which extends from the inner edge 34 of the conveyor channel 29 to its central region 36 and which is opposite an imaginary radial arrangement, which is shown in dash-dot lines in FIG drawn in and designated 42 ', is inclined in the direction of rotation 11 of the pump impeller 10.
  • the inner edge section 42a is arranged at an angle ⁇ of approximately 20 to 50 °, in particular of approximately 30 to 40 ° in the direction of rotation 11, inclined to the radial arrangement.
  • the angle ß is included referred to the central region 36 of the conveyor channel 29 as the center.
  • the inner edge section 42a can, as shown in FIG. 2, be slightly curved, in particular when viewed in the direction of rotation 11, convexly curved, and the transition from the inner edge 34 of the conveyor channel 29 to the edge section 42a is rounded.
  • the inner edge section 42a is thus approximately normal, that is to say perpendicular to the resultant path lines of the flow of the liquid conveyed by the liquid pump, which are indicated in FIG. 2 by arrows 43, so that the flow of the liquid in the inner section of the conveying channel 29 is led out of the pump at an early stage and thus a re-entry into the spaces between the vanes 12 of the impeller 10 is prevented.
  • the mass flow portion of the circulating liquid in the interrupter area 32, 33 is significantly reduced, which leads to significantly lower pressure surges in the interrupter area 32, 33, since less kinetic energy of the circulation flow has to be reduced in the interrupter area. This is associated with a significant reduction in noise.
  • the edge 42 When viewed in the radial direction with respect to the axis of rotation 16, the edge 42 has an outer edge starting from the central region 36 of the conveying channel 29 towards its outer edge 35
  • the outer edge section 42b runs further than the imaginary straight radial extension of the inner edge section 42a drawn in with a broken line, in the direction of rotation 11 of the pump impeller 10, so that the delivery channel 29 on its outer edge 35 continues to rotate relative to its inner edge 34 Direction 11 extending extension 44.
  • the outer edge section 42b extends on the outer edge 35 of the conveying channel 29 in the direction of rotation 11 by a distance s than in the case of an imaginary rectilinear extension of the inner edge section 42a.
  • the distance s corresponds approximately to half to the entire width b of the conveyor channel 29.
  • the width b of the conveyor channel 29 in front of the area of the outlet opening 30 is taken as a basis.
  • the outer edge section 42b is curved, preferably with a course in the form of a mirror-inverted S when viewed in the direction of rotation 11, and runs toward the outer edge 35 of the conveyor channel 29 approximately radially with respect to the axis of rotation 16.
  • FIG. 3 shows an enlarged cross section through the liquid pump, in which the suction cover 19 can be seen, with the delivery channel 25 formed therein.
  • the delivery channel 25 is radially inward to the axis of rotation 16 of the pump impeller 10 through an inlet inner edge 46 and to the outside by an outer edge 47.
  • the central region of the conveying channel 25 in the radial direction with respect to the axis of rotation 16 is indicated by the center line 48 thereof.
  • the delivery channel 25 is delimited at its end in the direction of rotation 11 of the pump impeller 10 by a wall 50, which ends at the end face 24 of the suction cover 19 facing the pump impeller 10 in an edge 52 which marks the transition from the delivery channel 25 to the Interrupter 32 forms.
  • the wall 50 extends from the base of the conveying channel 25 to the end face 24 of the suction cover 19 in the direction of rotation 11.
  • the edge 52 has an inner section 52a which extends from the inner edge 46 of the conveyor channel 25 to its central region 48 and which is opposite an imaginary radial arrangement which is shown in FIG dash-dotted line and designated 52 ', is inclined in the direction of rotation 11 of the pump impeller 10.
  • the inner edge section 52a is at an angle ⁇ of approximately 20 to 50 °, in particular approximately 30 to 40 ° in the direction of rotation 11 arranged inclined to the radial arrangement.
  • the angle ⁇ is related to the central region 48 of the delivery channel 25 as the center.
  • the inner edge section 52a can be of slightly curved design, in particular when viewed in the direction of rotation 11, it has a convex curve, and the transition from the inner edge 46 of the conveying channel 25 to the edge section 52a is rounded.
  • the inner edge section 52a on the suction cover 19 is thus, like the inner edge section 42a on the intermediate housing 20, also arranged approximately normal to the resulting path lines of the conveyed liquid, so that here the overflow to the outlet opening 30 in the intermediate housing 20 is initiated as early as possible.
  • the edge 52 has an outer edge section 52b, starting from the central region 48 of the conveying channel 25 towards its outer edge 47.
  • the outer edge section 52b runs in relation to the imaginary straight radial extension of the inner one drawn in with a broken line
  • Edge section 52a further in the direction of rotation 11 of the pump impeller 10, so that the delivery channel 25 has on its outer edge 47 an extension 54 which extends further in the direction of rotation 11 relative to its inner edge 46.
  • the outer edge section 52b extends in the direction of rotation 11 on the outer edge 47 of the conveying channel 25 by a distance 1 than when the inner edge section 52a is thought to be linearly extended.
  • the distance 1 corresponds approximately to half to the full width d of the conveyor channel 25.
  • the width b of the conveyor channel 25 is used as a basis in front of its end region.
  • the outer edge section 52b is curved, preferably with an approximately s-shaped course when viewed in the direction of rotation 11, and runs approximately radially with respect to the axis of rotation 16 toward the outer edge 47 of the conveyor channel 25.
  • the extension 54 of the conveyor channel 25 is approximately in cross section 96/24770 PCI7DE96 / ⁇ 0028
  • the wall 50 is arranged inclined in such a way that it extends in the central area 48 of the conveyor channel 25 in the direction of rotation 11 over an area which extends approximately half to the entire width b of the conveyor channel 25.
  • the edge 42, which forms the transition of the delivery channel 29 to the interrupter 33 on the intermediate housing 20 and the edge 52, which forms the transition of the delivery channel 25 to the interrupter 32 on the suction cover 19, are preferably in the circumferential direction with respect to the axis of rotation 16 of the pump impeller 10 arranged offset to each other.
  • the edge 42 on the intermediate housing 20 is arranged in the direction of rotation 11 by an angle ⁇ after the edge 52 on the suction cover 19.
  • the angle ⁇ in the central region 36 or 48 of the conveyor channels 25 and 29 is approximately 5 to 15 °.
  • the beginning of the conveying channel 29, viewed in the direction of the axis of rotation 16 of the pump impeller 10, is arranged approximately congruently with the beginning of the conveying channel 25, into which the feeding opening 24 opens.
  • the above-described design of the end region of the conveying channel 25 in the suction cover 19 also reduces the noise generated by the liquid pump during its operation, since the favorable flow guidance in particular does not excite or only slightly excite the suction cover 19 becomes.
  • the liquid pump sucks fuel through the suction opening 26 in the suction cover 19, which fuel is conveyed in the delivery channels 25 and 29.
  • the fuel flows out through the outlet opening 30 under increased pressure, flowing through the drive motor (not shown) and reaching the internal combustion engine via lines (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

La présente invention concerne une pompe à liquide qui possède une roue pourvue d'ailettes et entraînée en rotation, logée dans une chambre de pompe limitée, dans la direction de l'axe de rotation (16) de la roue, par une cloison (20) de chaque côté. Dans chacune des cloisons (20), un conduit de refoulement (29) annulaire est tourné vers la roue, et un orifice de sortie (30) débouche dans un conduit de refoulement (29). Dans le sens de rotation (11) de la roue de pompe (10), l'orifice de sortie (30) est limité par une paroi (40) qui se termine, sur la face de la paroi (20), par une arête (42). Cette arête (42) présente une partie intérieure (42a) qui, par rapport à une disposition radiale imaginaire (42') autour de l'axe de rotation (16), est inclinée dans le sens de rotation (11). La partie intérieure de l'arête (42a) se raccorde à une partie extérieure de l'arête (42b) qui, par rapport à un prolongement imaginaire rectiligne de la partie intérieure de l'arête (42b), s'étend plus loin dans le sens de rotation (11). Grâce à ce mode de réalisation, on obtient une amélioration de l'écoulement, hors du conduit de refoulement (29), à travers l'orifice de sortie (30).
EP96900268A 1995-02-11 1996-01-11 Pompe a liquide Expired - Lifetime EP0772743B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19504564 1995-02-11
DE19504564A DE19504564A1 (de) 1995-02-11 1995-02-11 Flüssigkeitspumpe
PCT/DE1996/000028 WO1996024770A1 (fr) 1995-02-11 1996-01-11 Pompe a liquide

Publications (2)

Publication Number Publication Date
EP0772743A1 true EP0772743A1 (fr) 1997-05-14
EP0772743B1 EP0772743B1 (fr) 2000-04-05

Family

ID=7753711

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900268A Expired - Lifetime EP0772743B1 (fr) 1995-02-11 1996-01-11 Pompe a liquide

Country Status (8)

Country Link
US (1) US5785490A (fr)
EP (1) EP0772743B1 (fr)
JP (1) JP3734506B2 (fr)
KR (1) KR100382682B1 (fr)
CN (1) CN1071421C (fr)
BR (1) BR9605306A (fr)
DE (2) DE19504564A1 (fr)
WO (1) WO1996024770A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19615322A1 (de) 1996-04-18 1997-10-23 Vdo Schindling Peripheralpumpe
JP3638818B2 (ja) 1999-05-20 2005-04-13 愛三工業株式会社 ウエスコ型ポンプ
DE19927789A1 (de) 1999-06-18 2000-12-21 Bosch Gmbh Robert Flüssigkeitspumpe, insbesondere zum Fördern von Kraftstoff
DE10245619B4 (de) * 2002-09-11 2004-08-26 Fresenius Medical Care Deutschland Gmbh Verfahren zur Blutrückgabe aus einer Blutbehandlungsvorrichtung und Vorrichtung zur Durchführung des Verfahrens
JP4396750B2 (ja) * 2007-09-14 2010-01-13 株式会社デンソー 燃料ポンプ
US9249806B2 (en) * 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
DE102012222336B4 (de) * 2012-12-05 2018-02-08 Continental Automotive Gmbh Strömungsmaschine
US10167770B1 (en) * 2017-09-12 2019-01-01 Paragon Technology, Inc. Automotive water pump spacer with volute extension
DE102020205531A1 (de) * 2020-04-30 2021-11-04 Mahle International Gmbh Seitenkanalverdichter zum Verdichten von Gas

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Publication number Priority date Publication date Assignee Title
DE1026174B (de) * 1955-10-12 1958-03-13 Geraetebau G M B H Deutsche Selbstansaugende Kreiselpumpe
US3356033A (en) * 1965-10-22 1967-12-05 Ford Motor Co Centrifugal fluid pump
US3459130A (en) * 1967-02-28 1969-08-05 Lucas Industries Ltd Liquid displacement pumps
AT316313B (de) * 1972-04-18 1974-07-10 Diosgyoeri Gepgyar Schleuderpumpe
JPS5724493A (en) * 1980-07-21 1982-02-09 Hitachi Ltd Vortex flow blower
US4508492A (en) * 1981-12-11 1985-04-02 Nippondenso Co., Ltd. Motor driven fuel pump
ATE29698T1 (de) * 1982-04-28 1987-10-15 Ase Uk Ltd Verstellbare fahrzeugsicherheitsgurtbefestigung.
JPH0642489A (ja) * 1992-04-04 1994-02-15 Miura Kenkyusho:Kk ウェスコポンプの騒音低減構造
US5273394A (en) * 1992-09-24 1993-12-28 General Motors Corporation Turbine pump
US5401143A (en) * 1993-06-07 1995-03-28 Ford Motor Company Multi-stage automotive fuel pump having angeled fuel transfer passage
DE4446537C2 (de) * 1994-12-24 2002-11-07 Bosch Gmbh Robert Flüssigkeitspumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9624770A1 *

Also Published As

Publication number Publication date
DE59604876D1 (de) 2000-05-11
CN1146795A (zh) 1997-04-02
JP3734506B2 (ja) 2006-01-11
KR100382682B1 (ko) 2003-10-04
CN1071421C (zh) 2001-09-19
US5785490A (en) 1998-07-28
KR970702437A (ko) 1997-05-13
EP0772743B1 (fr) 2000-04-05
WO1996024770A1 (fr) 1996-08-15
JPH09512323A (ja) 1997-12-09
BR9605306A (pt) 1997-10-07
DE19504564A1 (de) 1996-08-14

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