EP0772743B1 - Pompe a liquide - Google Patents

Pompe a liquide Download PDF

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Publication number
EP0772743B1
EP0772743B1 EP96900268A EP96900268A EP0772743B1 EP 0772743 B1 EP0772743 B1 EP 0772743B1 EP 96900268 A EP96900268 A EP 96900268A EP 96900268 A EP96900268 A EP 96900268A EP 0772743 B1 EP0772743 B1 EP 0772743B1
Authority
EP
European Patent Office
Prior art keywords
delivery channel
pump impeller
rotation
edge section
inner edge
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
Application number
EP96900268A
Other languages
German (de)
English (en)
Other versions
EP0772743A1 (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

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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-5,310,308.
  • This liquid pump is used to deliver fuel and has a pump impeller with vanes which is driven in rotation.
  • the pump impeller is arranged in a pump chamber which is delimited by a wall part in the direction of the axis of rotation of the pump impeller.
  • a suction opening is formed in one wall part and an outlet opening is formed in the other wall part.
  • a delivery channel is formed which extends in the circumferential direction from the suction opening to the outlet opening. The suction opening opens into the conveyor channel beginning of the one wall part and the outlet opening opens into the conveyor channel end of the other wall part.
  • the outlet opening has a conveying channel, into which it opens, which delimits the direction of rotation of the pump impeller Opening wall that ends on the end face of the wall part facing the pump impeller in an edge that is rounded. This opening wall also extends 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 favorable flow in the region of the outlet opening and the liquid pump has a higher delivery pressure and a higher efficiency compared to the known liquid pump having.
  • FIG. 1 shows a section of a liquid pump in a longitudinal section
  • FIG. 2 shows a section of a cross section through the liquid pump along the line II-II in FIG. 1 in the region of the outlet opening
  • FIG. 3 shows a section of a cross section through the liquid pump along the line III-III in FIG. 1 at the end of the delivery channel
  • FIG. 4 a section of 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, to convey 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 with a spacing from one another over the circumference of the pump impeller 10 arranged wings 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 conveyor channel 29 is also formed opposite the wing rim 12 of the pump impeller 10, into which an outlet opening 30 opens at the end of the latter.
  • the delivery channels 25 and 29 are arranged approximately congruently and extend in the direction of rotation 11 of the pump impeller 10 from the suction opening 26 to the outlet opening 30.
  • the delivery channels 25 and 29 are in the area between the suction opening 26 and the outlet opening 30 through an interrupter 32 and 33 respectively separated from each other.
  • the conveying 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 delimited radially inwards to the axis of rotation 16 of the pump impeller 10 by an inner edge 34 and outwards 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.
  • the outlet opening 30 extends 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, namely in the direction of rotation 11 of the pump impeller 10 from the end face 28 of the intermediate housing 20 the outer surface 39 out.
  • 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 designated 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 a 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 conveying channel 29 to its central region 36 and which is opposite an imaginary radial arrangement which is shown in dash-dot lines in FIG. 2 and with 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 ⁇ is included referred to the central region 36 of the conveyor channel 29 as the center.
  • the inner edge section 42a can be slightly curved, in particular when viewed in the direction of rotation 11, it has a convex curve, and the transition from the inner edge 34 of the conveying 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 resulting 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 occurs at an early stage is led out of the pump and thus a re-entry into the spaces between the vanes 12 of the impeller 10 is prevented.
  • the mass flow fraction 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 has an outer edge section 42b starting from the central region 36 of the conveying channel 29 to the outer edge 35 thereof.
  • the outer edge section 42b extends further in the direction of rotation 11 of the pump impeller 10 than the imaginary straight radial extension of the inner edge section 42a, so that the conveying channel 29 has an extension 44 on its outer edge 35 which extends further in the direction of rotation 11 relative to its inner edge 34 .
  • 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 straight extension of the inner edge section 42a. The distance s corresponds approximately to half to the full width b of the delivery channel 29.
  • the width b of the delivery channel 29 in front of the area of the outlet opening 30 is used as a basis.
  • the outer edge section 42b is curved, preferably with a course in the form of a mirror-inverted S viewed in the direction of rotation 11, and runs out towards the outer edge 35 of the conveying 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 delimited radially inwards to the axis of rotation 16 of the pump impeller 10 by an inner edge 46 and outwards 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 forms the transition from the delivery channel 25 to the interrupter 32.
  • the wall 50 extends from the bottom of the conveying channel 25 to the end face 24 of the suction cover 19 inclined in the direction of rotation 11.
  • the edge 52 When viewed in the radial direction with respect to the axis of rotation 16, the edge 52 has an inner section 52a which extends from the inner edge 46 of the conveying channel 25 to its central region 48 and which is opposite an imaginary radial arrangement which is shown in dash-dot lines in FIG. 3 and with 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 designed to be slightly curved, 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 liquid conveyed, so that here the overflow to the outlet opening 30 in the intermediate housing 20 is initiated as early as possible.
  • the edge 52 When viewed in the radial direction with respect to the axis of rotation 16, the edge 52 has an outer edge section 52b starting from the central region 48 of the conveying channel 25 to the outer edge 47 thereof.
  • the outer edge section 52b extends further in the direction of rotation 11 of the pump impeller 10 than the imaginary straight radial extension of the inner edge section 52a, so that the delivery channel 25 has an extension 54 on its outer edge 47 which extends further in the direction of rotation 11 than 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 in the case of an imaginary straight extension of the inner edge section 52a.
  • 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 towards the outer edge 47 of the conveying channel 25 approximately radially with respect to the axis of rotation 16.
  • the extension 54 of the conveyor channel 25 is approximately in cross section semicircular.
  • the wall 50 is arranged inclined in such a way that it extends in the central region 48 of the conveying channel 25 in the direction of rotation 11 over an area which extends approximately half to the entire width b of the conveying 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 offset from one another in the circumferential direction with respect to the axis of rotation 16 of the pump impeller 10 arranged. Relative to the axis of rotation 16 of the pump impeller 10, 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 delivery channels 25 and 29 is approximately 5 to 15 °.
  • the start of the delivery channel 29 is, viewed in the direction of the axis of rotation 16 of the pump impeller 10, approximately coincident with the start of the delivery channel 25, into which the suction opening 24 opens.
  • the above-described configuration of the end region of the delivery channel 25 in the intake 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 intake cover 19 to vibrate.
  • the liquid pump During the operation of the liquid pump, it sucks fuel through the suction opening 26 in the suction cover 19, which fuel is conveyed in the delivery channels 25 and 29. At the end of 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)

Claims (12)

  1. Pompe à liquide, en particulier pour transférer du carburant, comprenant une roue à aubes de pompe (10) pourvue d'ailettes (12), entraînée en rotation, qui est disposée dans une chambre de pompe (17) délimitée dans la direction de son axe de rotation (16) par respectivement une partie de paroi (19, 20), une ouverture d'admission (26) dans l'une des parties de paroi, la partie (19) et une ouverture de sortie (30) dans l'autre partie de paroi (20), respectivement des canaux de transfert (25, 29), de forme annulaire, disposés dans les faces frontales (24, 28) des parties de paroi (19, 20), qui sont tournées vers la roue à aubes (10) de la pompe, canaux de transfert (25, 29) qui s'étendent de l'ouverture d'aspiration (26) jusqu'à l'ouverture de sortie (30), l'ouverture d'aspiration (26) débouchant dans le début du canal de transfert de l'une des parties de paroi (19) et l'ouverture de sortie (30) débouchant dans la zone de l'extrémité du canal de transfert de l'autre partie de paroi (20), et l'ouverture de sortie (30) présentant une paroi (40) qui délimite le canal de transfert (29), dans lequel celle-ci débouche, dans le sens de rotation (11) de la roue à aubes (10) de la pompe, paroi (40) qui se termine sur la face frontale (28), qui est tournée vers la roue à aubes (10) de la pompe par une arête (42),
    caractérisée en ce que
    l'arête (42), vu dans le sens radial par rapport à l'axe de rotation (16) de la roue à aubes (10) de la pompe, présente une section intérieure d'arête (42a), qui, en partant d'un bord intérieur (34), qui délimite le canal de transfert (29) radialement en direction de l'axe de rotation (34), s'étend en direction d'une zone centrale (36) du canal de transfert (29), vu dans le sens radial par rapport à l'axe de rotation (16), de façon inclinée par rapport à un dispositif radial imaginaire (42') dans le sens de rotation (11) de la roue à aubes (10) de la pompe.
  2. Pompe à liquide selon la revendication 1,
    caractérisée en ce que
    la section intérieure d'arête (42a) s'étend en étant inclinée d'un angle (β) de environ 20° à 50°, de préférence environ 30° à 40°, par rapport à l'agencement radial imaginaire avec la zone centrale (36) du canal de transfert (29) comme centre.
  3. Pompe à liquide selon la revendication 1 ou 2,
    caractérisée en ce que
    l'arête (42) présente en partant de la zone centrale (36) du canal de transfert (29), vu dans le sens radial par rapport à l'axe de rotation (16) de la roue à aubes (10) de la pompe, vers le bord extérieur (35) qui délimite le canal de transfert (29) radialement vers l'extérieur, une section d'arête extérieure (42b), qui va plus loin dans le sens de rotation (11) de la roue à aubes (10) de la pompe par rapport au prolongement radial rectiligne, imaginaire de la section d'arête (42a) intérieure.
  4. Pompe à liquide selon la revendication 3,
    caractérisée en ce que
    la section d'arête extérieure (42b) s'étend par rapport au prolongement radial rectiligne, imaginaire de la section d'arête (42a) intérieure sur le bord extérieur (35) du canal de transfert (29) d'environ la moitié jusqu'à la totalité de la largeur (b) du canal de transfert (29) dans le sens de rotation (11) de la roue à aubes (10) de la pompe.
  5. Pompe à liquide selon l'une des revendications précédentes,
    caractérisée en ce que
    la paroi (40), qui délimite l'ouverture de sortie (30) dans le sens de rotation (11) de la roue à aubes (10) de la pompe, s'étend de façon inclinée par rapport à la face frontale (28), qui est tournée vers la roue à aubes (10) de la pompe, de la partie de la paroi (20) dans le sens de rotation (11) en s'écartant de la face frontale (28).
  6. Pompe à liquide selon la revendication 5,
    caractérisée en ce que
    la paroi (40) s'étend de façon inclinée sous un angle (α) d'environ 20 à 40° par rapport à la face frontale (28) de la partie de paroi (20).
  7. Pompe à liquide selon l'une des revendications précédentes,
    caractérisée en ce que
    la section transversale d'écoulement effectif de l'ouverture de sortie (30) s'agrandit d'au maximum 20% ou est sensiblement constante en partant du canal de transfert (29) jusqu'à son embouchure sur la face frontale (39) de la partie de paroi (20) qui est tournée à l'opposé de la roue à aubes (10) de la pompe.
  8. Pompe à liquide selon l'une des revendications précédentes,
    caractérisée en ce que
    - le canal de transfert (25), dans le commencement duquel débouche l'ouverture d'aspiration (26), est délimité à son extrémité dans le sens de rotation (11) de la roue à aubes (10) de la pompe par une paroi (50), qui se termine sur la face frontale (24) de la partie de paroi (19) qui est tournée vers la roue à aubes (10) de la pompe par une arête (52),
    - l'arête (52) présente, vu dans le sens radial par rapport à l'axe de rotation (16) de la roue à aubes (10) de la pompe, une section d'arête intérieure (52a), qui en partant d'un bord intérieur (46) qui délimite le canal de transfert (25) radialement en direction de l'axe de rotation (16), s'étend en direction d'une zone centrale (48) du canal de transfert (25), vu dans le sens radial par rapport à l'axe de rotation (16), de façon inclinée par rapport à un agencement radial imaginaire (52') dans le sens de rotation (11) de la roue à aubes (10) de la pompe.
  9. Pompe à liquide selon la revendication 8,
    caractérisée en ce que
    la section d'arête intérieure (52a) s'étend de façon inclinée sous un angle (γ) de environ 20° à 50°, environ de préférence 30° à 40°, par rapport à un dispositif radial imaginaire avec la zone centrale (48) du canal de transfert (25) comme centre.
  10. Pompe à liquide selon la revendication 8 ou 9,
    caractérisée en ce que
    l'arête (52) en partant de la zone centrale (48) du canal de transfert (25), vu dans le sens radial par rapport à l'axe de rotation (16) de la roue à aubes (10) de la pompe, vers le bord extérieur (47) qui délimite radialement vers l'extérieur le canal de transfert (25), présente une section extérieure d'arête (52b), qui s'étend davantage dans le sens de rotation (11) de la roue à aubes (10) de la pompe, par rapport au prolongement radial, rectiligne, imaginaire de la section d'arête intérieure (52a).
  11. Pompe à liquide selon la revendication 10,,
    caractérisée en ce que
    la section d'arête extérieure (52b) s'étend par rapport au prolongement radial, rectiligne, imaginaire de la section d'arête intérieure (52a) sur le bord extérieur (47) du canal de transfert (25) d'environ la moitié jusqu'à la totalité de la largeur (d) du canal de transfert (25) dans le sens de rotation (11) de la roue à aubes (10) de la pompe.
  12. Pompe à liquide selon l'une des revendications 8 à 11,
    caractérisée en ce que
    dans la zone centrale (36, 48)des canaux de transfert (29, 25), vu dans le sens radial par rapport à l'axe de rotation (16), l'arête (42) du canal de transfert (29), dans lequel débouche l'ouverture de sortie (30), est disposée dans le sens de rotation (11) de la roue à aubes (10) de la pompe tournée d'un angle (ϕ) environ de 5° à 15° vers l'arête (52) du canal de transfert (25), dans lequel débouche l'ouverture d'aspiration (26).
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
DE19504564A DE19504564A1 (de) 1995-02-11 1995-02-11 Flüssigkeitspumpe
DE19504564 1995-02-11
PCT/DE1996/000028 WO1996024770A1 (fr) 1995-02-11 1996-01-11 Pompe a liquide

Publications (2)

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

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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

Also Published As

Publication number Publication date
US5785490A (en) 1998-07-28
KR970702437A (ko) 1997-05-13
JP3734506B2 (ja) 2006-01-11
DE19504564A1 (de) 1996-08-14
KR100382682B1 (ko) 2003-10-04
WO1996024770A1 (fr) 1996-08-15
BR9605306A (pt) 1997-10-07
EP0772743A1 (fr) 1997-05-14
CN1071421C (zh) 2001-09-19
CN1146795A (zh) 1997-04-02
DE59604876D1 (de) 2000-05-11
JPH09512323A (ja) 1997-12-09

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