EP0735271A2 - Seitenkanalbrennstoffpumpe für Kraftfahrzeug - Google Patents

Seitenkanalbrennstoffpumpe für Kraftfahrzeug Download PDF

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Publication number
EP0735271A2
EP0735271A2 EP96200851A EP96200851A EP0735271A2 EP 0735271 A2 EP0735271 A2 EP 0735271A2 EP 96200851 A EP96200851 A EP 96200851A EP 96200851 A EP96200851 A EP 96200851A EP 0735271 A2 EP0735271 A2 EP 0735271A2
Authority
EP
European Patent Office
Prior art keywords
pump
rotor
fuel
spiral form
cavities
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
EP96200851A
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English (en)
French (fr)
Other versions
EP0735271B1 (de
EP0735271A3 (de
Inventor
Libero Magini
Marco Badami
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.)
Bitron SpA
Original Assignee
Bitron SpA
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
Priority claimed from IT95MI000652A external-priority patent/IT1275712B1/it
Priority claimed from ITMI960032 external-priority patent/IT1281608B1/it
Application filed by Bitron SpA filed Critical Bitron SpA
Publication of EP0735271A2 publication Critical patent/EP0735271A2/de
Publication of EP0735271A3 publication Critical patent/EP0735271A3/de
Application granted granted Critical
Publication of EP0735271B1 publication Critical patent/EP0735271B1/de
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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/048—Arrangements for driving regenerative pumps, i.e. side-channel 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
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/005—Regenerative pumps of multistage type the stages being radially offset

Definitions

  • This invention relates to a pump of peripheral type for feeding fuel to injection-fed internal combustion vehicle engines.
  • the engine efficiency is negatively influenced, as often the engine is fed with a fuel quantity greater than the optimum value.
  • pumps are usually used, positioned in the tank. Sometimes they are integrated into the fuel level measurement system or located along the line conveying the fuel from the tank to the engine.
  • These pumps driven by an electric motor, are either positive displacement pumps of roller or lobe type, or pumps of the type generally known as peripheral.
  • peripheral pumps could be increased with regard both to the achievable head and to the available capacity for a fixed head required by the customer.
  • An object of the present invention is to provide an at least two-stage peripheral pump for motor vehicles offering better performance than the known art, both in terms of the achievable head and in terms of the pump fuel capacity for equal operating variables.
  • a further object of the present invention is to provide a peripheral fuel pump for motor vehicles which is of small dimensions but of good hydraulic performance in terms of capacity, pressure and efficiency, compared with peripheral pumps of the known art.
  • a further object of the present invention is to provide a peripheral fuel pump for motor vehicles of simple, low-cost construction without the need to use complicated or costly techniques.
  • a two-stage pump for fuel feed to an injection-fed internal combustion engine is described, the pump being inserted into a vehicle fuel tank and comprising a hollow pump body provided with a fuel intake aperture and a fuel delivery aperture, and containing a rotor in the form of a disc provided with blading.
  • the pump body consists of two parts joined together and comprises, in its inner surfaces, opposing channel recesses of compound spiral form respectively facing at least two pluralities of pocket cavities provided in each of the two faces of the rotor to receive the fuel.
  • the two faces of the rotor are connected together by at least one passage provided within the rotor, the pocket cavities defining at least two pump stages, which are connected together by an intermediate portion of said channel recesses of compound spiral form.
  • the rotor is hence shaped to comprise two separate pressurization regions. The combined action of these two stages provides the pump head, ie the pressure rise undergone by the fuel to enable it to be injected into the engine.
  • Said rotor also comprises a central passage enabling the fuel to be distributed over both the rotor faces and form two different zones of action.
  • those surfaces of the pump body facing the rotor comprise integrally formed channels enabling the fuel to pass from one stage to the next.
  • the channel recesses of compound spiral form are divided into two parts connected together by an essentially straight intermediate portion.
  • One of said two parts is preferably of constant cross-section.
  • at least one of said two parts has a variable passage cross-section which increases from the beginning to the end of the recesses.
  • the two pluralities of pocket cavities are divided by a circumferential baffle which divides the rotor into two circular bands, namely an inner and an outer.
  • the baffle is positioned at the intermediate portion of the channel recesses of compound spiral form. In this manner, the fuel can pass from a cavity pertaining to the first plurality of pocket cavities to a pocket cavity pertaining to the second plurality, by flowing exclusively through said intermediate portion of the recesses.
  • the intermediate portion can be in the form of a hole provided in the respective region of the pump body to join together two recesses of circular form.
  • the intermediate portion is also in the form of a recess, on which a plate-like element is positioned to conceal the intermediate portion from the rotor surface facing it.
  • the plate is positioned in a shallow seat provided in the respective region of the pump body.
  • the pump body is composed of two parts joined together by way of an interposed spacer, said two pluralities of pocket cavities defining the stages present within the pump.
  • the two rotor faces can either be connected together or not connected together by means of at least one passage, which is provided within the rotor and is preferably located in a position central to the rotor, ie in a position close to the rotation and/or keying axis.
  • the pocket cavities forming respectively the inner and outer band of the rotor, are of similar geometry and configuration.
  • said pocket cavities have a profile determined by two portions of rounded form which converge towards a section of minimum thickness.
  • the pocket cavities of a first peripheral stage of the pump which are positioned on the two opposing faces of the rotor, can communicate with each other via a passage provided in the thinnest part, in the immediate vicinity of the baffle which divides the two regions where the cavities are provided, or alternatively the pocket cavities of a first peripheral stage of the pump can be made non-communicating.
  • a passage must be provided for connecting together the two faces of the rotor.
  • the pump fuel intake aperture is coaxial with the pump axis, whereas the delivery aperture is located external to the rotor in a position peripheral to it, although remaining parallel to the pump axis.
  • the passage connecting the two rotor faces can be positioned in correspondence with the intake aperture, close to the centre of the rotor. In this manner the fuel reaching the intake aperture is distributed equally between the two rotor faces. To facilitate this distribution, the passage can be tapered along the axial direction between the two rotor faces. In addition, the initial portion of a first part of the parts in which the channel recesses of compound spiral form are divided opens into said intake aperture.
  • the pump intake body part comprises at the channel recesses a through hole acting as a vent hole.
  • This increases the priming capacity of the system and enables the air present in the ducts to be discharged during starting.
  • the hole is of very small dimensions. To balance the capacity loss due to the fuel passing through said hole (although the quantity of said fuel is very small), the cross-section of the peripheral channel preceding the vent hole can be enlarged in both body parts, ie intake and delivery.
  • the pump intake body part has an annular entry section with three intake apertures extending in directions parallel to the central axis of the pump body.
  • Said apertures are essentially of bean shape. They are arranged within an imaginary circular ring concentric with the intake part of the pump.
  • the peripheral pump of the present invention has extremely good operating properties. Its constructional and design characteristics minimize vibration so as to also reduce noise during operation. In particular, compared with currently used pumps, for equal conditions (engine r.p.m., fuel throughput, temperature) it provides a larger head because the fact of comprising two stages leads to greater efficiency than known designs. Alternatively, the pump of the present invention would rotate at a lower r.p.m. (and hence achieve an averagely greater life) for equal performance (head and capacity) requested by the client.
  • peripheral pump of the invention can be driven by a motor, preferably an electric motor, via a hollow shaft inserted through an aperture in the pump body and carrying the rotor keyed thereon.
  • Said shaft is housed in a bearing provided in the aperture in the pump body.
  • a pump indicated overall by 10, 110, consists of two facing parts 11, 12, 111, 112, known respectively as the delivery part and the intake part, between which a rotor 13, 113 is positioned.
  • Said rotor 13, 113 is in the form of a disc provided with blading.
  • Recesses 14, 15, 114, 115 of substantially compound spiral form are provided in the delivery and intake parts 11, 12, 111, 112.
  • the body of the pump 10, 110 is completed by a spacer 16, 116 arranged between the two parts 11, 12, 111, 112 comprising the recesses 14, 15, 114, 115, an intake duct 17, 117 provided in the intake part 12, 112 central to the rotor 13, 113 and about an imaginary central axis 17', 117' through the pump body, and a delivery duct 18, 118 peripheral to the rotor 13, 113 and provided in the delivery part 11, 111.
  • said spacer 16, 116 could be an integral part of one of the two constituent parts 11, 111, 12, 112 of the pump body so as to reduce the number of pieces used in the construction of the pump 10, 110 and hence avoid a double measurement uncertainty deriving from two machining tolerances.
  • the spacer 16, 116 is formed as a separate piece, the possibility of machining those surfaces of the spacer 16, 116 facing the two parts 11, 12, 111, 12 and the rotor 13, 113 in a single operation allows improved fitting and sealing and correct assembly.
  • the delivery duct 18, 118 leaves from the side opposite the inlet of the intake duct 17, 117. In embodiments not shown herein this situation may not occur, and both ducts 17, 18, 117, 118 may open from the same side of the pump 10, 110.
  • the pump body essentially consisting of the two parts 11, 111, 12, 112 and the spacer 16, 116, is housed within a casing 19, 119 comprising a motor (not shown) which drives the rotor 13, 113 via a shaft (not shown) on which it is keyed.
  • the two parts 11, 12, 111, 112 are of disc configuration.
  • the first part 11, 111 comprises the delivery duct 18, 118 with its axis parallel to but offset from the axis of the pump 10, 110, whereas the second part 12, 112 comprises the intake duct 17, 117 with its axis parallel to and coinciding with the axis of the pump 10, 110.
  • the two parts 11, 12, 111, 112 and the spacer 16, 116 also of disc form, comprise aligned through holes 20, 120 for receiving known fixing elements (not shown). In other possible embodiments, not shown herein, alignment between the parts 11, 12, 111, 112 and the spacer 16, 116 can advantageously be achieved by suitable recesses and projections provided on the contacting parts.
  • the intake duct 17, 117 of the part 12, 112 extends axially as a sleeve portion 21, 121 on the side not facing the rotor 13, 113.
  • the delivery part 11, 111 comprises in the opposite portion to that containing the recessing 14, 114 a housing 22, 122 for a bearing 23, 123, through which said drive shaft is inserted.
  • Said motor is preferably electric but can be of any type suitable for the purpose.
  • the rotor 13, 113 of the pump 10, 110 comprises two regions separated by a circumferential baffle 24, 124, said two regions consisting of an inner circular band and an outer circular band.
  • Each of these circular bands is subdivided by radial ribs 27, 28 127, 128 into a plurality of pockets forming the blading, the number of pockets of the outer circular band being normally greater than the number of pockets of the inner circular band.
  • These two regions which can be of equal or different geometry and configuration (as can be seen by comparing said Figures 3 and 22), define the two pumping stages, which can be of similar or different hydraulic performance.
  • the ribs 27, 28, 127, 128 forming the pocket cavities can be inclined to the corresponding radial directions by a predetermined angle.
  • passages 26, 126 which may be delimited by two successive ribs 27, 127 (as shown in Figure 3), or not (as shown in Figure 22). Said passages 26, 126 enable the fuel to flow from that rotor face facing the intake duct 17 to the opposite face facing the delivery duct 18.
  • the passages are of decreasing cross-section from the intake side to the delivery side, in accordance with the desired hydraulic characteristics.
  • the passages 126 are of constant cross-section.
  • the rotor 13, 113 is provided with a perimetral ring 29, 129 of height equal to the thickness of the rotor 13, 113 to delimit the second stage of the pump 10, 110 and join together the outer ribs 28, 128.
  • Figures 2, 4, 21 and 23 show the two different configurations of the pockets provided in the rotor 13, 113 of the pump 10, 110, in two preferred embodiments of the present invention.
  • the pockets forming the first stage and those forming the second stage are of curvilinear profile.
  • the upper and lower profiles are symmetrical.
  • the pockets forming the first stage consist of rounded cavities the ends of which terminate at the lateral surface of the rotor 13, on one side at the passages 26 and on the other side at the circumferential baffle 24.
  • the pockets forming the second stage consist of rounded cavities, which extend at both ends from the circumferential baffle 24, 124, to converge into a point of symmetry of the pocket, in a central plane parallel to the faces of the rotor 13, 113. It will also be noted that between the point of convergence of each pocket and the perimetral ring 29, 129 there exists a connection between the upper pocket and the lower pocket of the second stage of the pump 10, 110.
  • the pockets forming the first stage and those forming the second stage have a curved profile.
  • the upper and lower profiles are symmetrical and do not extend as far as the passage 126, so that their combination gives rise, in cross-section, to a figure similar to an arrow.
  • the pockets forming the first stage consist of rounded cavities, one end of which terminates at the lateral surface of the rotor 113 in a point external to the passage 126, and the other end of which connects to the circumferential baffle 124 in the central plane parallel to the faces of the rotor 113.
  • the pockets forming the second stage of the pump 110 have a configuration equal to that of the pockets of the first stage.
  • Figures 5 and 24 show two preferred embodiments of the recesses 14, 114 of compound spiral form present in the inner surface of one of the two constituent parts of the pump body, namely the delivery part 11, 111.
  • the ducts 18, 118 by which the fuel is delivered to the engine can be seen within the recesses 14, 114.
  • each recess 14, 15 is smaller in its initial inner portion than in its final outer portion.
  • the fluid fuel by the effect of the rotation of the rotor 13 (and hence by the effect of the centrifugal force transmitted) flows through said recess 14, 15 in one direction encountering an ever increasing passage cross-section. This enables part of the kinetic energy of the fluid to be converted into pressure, so increasing the total efficiency of the pump 10.
  • the inner terminal portion of the recess 115 opens into the intake duct 117.
  • each of the recesses 14, 15, 114, 115 is divided into two essentially circular parts 14a, 14b, 15a, 15b, 114a, 114b, 115a, 115b connected together by a substantially straight intermediate portion 14c, 15c, 114c, 115c.
  • a plate 30, 130 of trapezoidal shape can be provided at the passage region to conceal the straight intermediate portion 14c, 15c, 114c, 115c precisely in correspondence with the circumferential baffle 24, 124 which separates the two stages and is present on both of the two surfaces of the rotor 13, 113. In this manner a compulsory passageway is created for the fluid fuel, which passes from the first to the second stage of the rotor 13, 113 via this closed channel.
  • each of said respective parts 114a, 114b and 115a, 115b is of substantially constant cross-section along its entire length.
  • fuel passage can take place through a hole provided in that part comprising the recess 14, 15, 114, 115 to form a type of tunnel.
  • 111 of the pump 10, 110 there is provided an annular second recess 31, 131 coaxial with the axis of the seat 22, 122 housing the bearing 23, 123.
  • This second recess 31, 131 feeds the fluid arriving from the passages 26, 126 towards the facing face of the rotor 13, 113 and towards the successive portions of the recess 14, 114.
  • the initial portion of the recess 114 which terminates in the delivery duct 118, communicates with the annular recess 131.
  • the possible presence of a respective plate 30, 130 concealing a respective part 14c, 15c, 114c, 115c of the recess 14, 15, 114, 115 on each of the two constituent parts 11, 12, 111, 112 of the pump body is even more apparent in Figures 2 and 21.
  • These figures show the recesses 32, 132 in which the respective plates 30, 130 are located, exactly in correspondence with the baffles 24, 124 separating the first from the second stage of the rotor 13, 113.
  • the pockets of the first stage can be seen to have a flat base at constant depth.
  • the pockets of the second stage however are of exactly the same pattern as that shown in Figures 4 and 13.
  • the front view of the rotor 13 is essentially similar to that shown in Figure 3.
  • Figures 8 and 9 show a further embodiment of the rotor 13 according to the present invention.
  • the upper part and lower part of the rotor 13 are symmetrical with regard to the first stage, whereas the ribs 28 forming the second stage are provided in alternate positions on the two faces, as can be easily seen from the sectional view of Figure 9.
  • the pockets forming part of the second stage are present alternately in the upper part and lower part of the rotor 13 and have a common profile, of roundish pattern, similar to that already described for the preceding embodiments of the rotor 13.
  • the ribs 28 of the second stage of the pump 10 are inclined to the radial direction by a predetermined angle, preferably between 0° and 30°.
  • the ribs 27 forming the first stage are not rectilinear (as in the other embodiments of the rotor 13), but instead are curvilinear, for example in the form of a circumferential arc. In this manner, part of the centrifugal component of the fluid motion, caused by the rotation of the rotor 13, is transformed into a tangential component, creating less friction and hence a lesser pressure drop, with the result that the pump 10 is of increased efficiency compared with the other embodiments.
  • the passage 26 connecting together the two opposing faces of the rotor 13 is of constant cross-section along its entire length.
  • Figures 12 to 19 show further embodiments of the intake part 11 and delivery part 12, into which a rotor 13 is inserted having the pockets of its second stage open (ie without the perimetral containing ring 29).
  • the channels 14' and 15' provided in the surfaces facing the rotor 13 have their respective portions 14'b, 15'b not of roundish but of trapezoidal profile. It can be seen that in passing from the region 14'c, 15'c into the respective regions 14'b, 15'b, the cross-section available to the fluid decreases, so that the fluid is compelled to increase its velocity.
  • the regions 14'c, 15'c have a cross-section respectively greater than the neighbouring regions 14'a, 14'b, 15'a, 15'b.
  • Figures 26 and 27 show a further embodiment of the rotor 113 inserted into the pump 110 of the present invention.
  • the pockets of the first stage of the pump 110 which are situated between the ribs 127, do not touch the circumferential baffle 124 with their pointed end.
  • the passage 26 between the two opposing surfaces of the rotor 13 is lacking.
  • the upper part and the lower part of the rotor 113 are symmetrical with regard to the first stage, whereas the ribs 128 of the second stage are present in alternate positions on the two faces, as can be easily seen from the sectional view of Figure 27.
  • the pockets of the second stage are present alternately in the upper part and lower part of the rotor 113 and have a common profile, of roundish pattern, similar to that already described for the preceding embodiments.
  • the ring 29 which usually delimits the second stage in the radial direction is lacking.
  • the first stage comprises intercommunicating compartments between the delivery part 11, 111 and the intake part 12, 112 and an outer containing ring.
  • the first stage can be configured so as not to present intercommunicating compartments between the delivery part 111 and the intake part 112, the compartments of the second stage being staggered (as shown in Figure 26).
  • Figures 28 to 31 show further embodiments of the delivery part 111 and intake part 112.
  • the channels 114', 115' present in the surfaces facing the rotor 113 have their respective portions 114'b, 115'b of trapezoidal profile.
  • the delivery part 111 lacks the central channel 31, visible in Figures 12 and 16, and can hence be associated only with a rotor 113 which does not have a central passage between the two faces.
  • the delivery part 111, lacking the channel 31 can be associated with a rotor 113 having a central passage.
  • Figures 32 and 33 show a further possible embodiment of the intake part 112.
  • a small-dimension through vent hole 140 is provided along the fluid fuel passage duct in the intake body part (namely along the portion 115'b of the channel 115 of the first stage), or in the peripheral stage of the intake body part, to increase the priming capacity of the system, serving to discharge the air present in the ducts during starting.
  • the cross-section of the recess 115 can be increased in the portion 115'b prior to the through hole 140, in both the intake part 112 and the delivery part 111.
  • Figures 34 and 35 show a spacer 116 which can be used during the construction of the hydraulic part of the pump 10, 110.
  • the provision of three separate parts (delivery part 11, 111, intake part 12, 112 and spacer 16, 116) during the manufacture of the pump 10, 110 is of fundamental importance in achieving levelling of the rotor 13, 113 and the spacer 16, 116 (usually done by a grinder) in a single operation.
  • the spacer 16, 116 is suitably modified to present a sector between the points 141 and 142 of smaller diameter.
  • the inner diameter of the spacer 16, 116 is just a few hundredths of a millimetre greater than the outer diameter of the rotor 13, 113, to prevent back flow of the liquid.
  • a further embodiment of the intake part 12, 112 (as visible in Figures 36 and 37) comprises three apertures 117a, 117b, 117c of bean shape arranged with their axes parallel to each other and parallel to but offset from the central axis 17', 117' of the pump 10, 110. Said apertures 117a, 117b, 117c lie within a hypothetical circular band having two radii of constant value starting from the central axis 17', 117' of the pump 10, 110.
  • the present invention is not limited to the particular combinations of the form of the rotor 13, 113, the geometry of the pockets of the first and second stage and the form of the recesses 14', 15', 114', 115'. All possible combinations of the various embodiments of the rotor 13, 113, the pockets and the embodiments of the delivery part 11, 111 and intake part 12, 112 fall within the general scope of the present invention.
  • the pump 10, 110 of the present invention presents high efficiency, head characteristics and a working life which are better than known pumps. In addition it has a low noise level and a lower production cost than the state of the art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
EP19960200851 1995-03-31 1996-03-28 Seitenkanalbrennstoffpumpe für Kraftfahrzeug Expired - Lifetime EP0735271B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IT95MI000652A IT1275712B1 (it) 1995-03-31 1995-03-31 Pompa carburante per autoveicoli
ITMI950652 1995-03-31
ITMI960032 1996-01-11
ITMI960032 IT1281608B1 (it) 1996-01-11 1996-01-11 Pompa carburante a due stadi periferici per autoveicoli

Publications (3)

Publication Number Publication Date
EP0735271A2 true EP0735271A2 (de) 1996-10-02
EP0735271A3 EP0735271A3 (de) 1998-11-04
EP0735271B1 EP0735271B1 (de) 2002-06-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19960200851 Expired - Lifetime EP0735271B1 (de) 1995-03-31 1996-03-28 Seitenkanalbrennstoffpumpe für Kraftfahrzeug

Country Status (3)

Country Link
EP (1) EP0735271B1 (de)
DE (1) DE69621868T2 (de)
ES (1) ES2179152T3 (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2768192A1 (fr) * 1997-09-08 1999-03-12 Marwal Systems Pompe turbine a rendement ameliore notamment pour reservoir de carburant de vehicule automobile
FR2768191A1 (fr) * 1997-09-08 1999-03-12 Marwal Systems Pompe turbine notamment pour reservoir de carburant de vehicule automobile
FR2768193A1 (fr) * 1997-09-08 1999-03-12 Marwal Systems Pompe turbine notamment pour reservoir de carburant de vehicule automobile perfectionnee pour presenter un rendement ameliore
WO1999047814A1 (de) * 1998-03-18 1999-09-23 Robert Bosch Gmbh Mehrstufige seitenkanalpumpe für kraftstoff für ein kraftfahrzeug
DE19826902A1 (de) * 1998-06-17 1999-12-23 Mannesmann Vdo Ag Förderpumpe
JP2002332981A (ja) * 2001-05-09 2002-11-22 Mitsuba Corp 液体ポンプのインペラ
EP1295038A1 (de) * 2000-06-20 2003-03-26 Visteon Global Technologies, Inc. Kraftstoffpumpe mit verringerter empfindlichkeit für verschmutzung
US7632060B2 (en) 2005-01-24 2009-12-15 Ford Global Technologies, Llc Fuel pump having dual flow channel
WO2014039121A1 (en) * 2012-09-10 2014-03-13 Delphi Technologies, Inc. Multi-channel fuel pump
US9086071B2 (en) 2009-05-20 2015-07-21 Edwards Limited Side-channel pump with axial gas bearing

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004052439A1 (de) 2004-10-28 2006-05-04 Siemens Ag Kraftstoffpumpe und Kraftstoffversorgungsanlage für eine Brennkraftmaschine eines Kraftfahrzeuges mit einer Kraftstoffpumpe
DE102007026533A1 (de) * 2007-06-08 2008-12-11 Continental Automotive Gmbh Kraftstoffpumpe
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2112762A1 (de) * 1971-03-17 1972-10-12 Klein Schanzlin & Becker Ag Seitenkanalpumpe,insbesondere Wirbelpumpe
DE3303460A1 (de) * 1983-02-02 1984-08-02 Friedrich 8541 Röttenbach Schweinfurter Selbstansaugende seitenkanalpumpe
EP0170175A2 (de) * 1984-07-23 1986-02-05 Friedrich Schweinfurter Seitenkanalpumpe mit Kräfteausgleich
EP0397041A2 (de) * 1989-05-08 1990-11-14 Vickers Incorporated Rotationshydraulikpumpe
WO1992000449A1 (de) * 1990-06-28 1992-01-09 Robert Bosch Gmbh Aggregat zum fördern von kraftstoff vom vorratstank zur brennkraftmaschine eines kraftfahrzeuges

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2112762A1 (de) * 1971-03-17 1972-10-12 Klein Schanzlin & Becker Ag Seitenkanalpumpe,insbesondere Wirbelpumpe
DE3303460A1 (de) * 1983-02-02 1984-08-02 Friedrich 8541 Röttenbach Schweinfurter Selbstansaugende seitenkanalpumpe
EP0170175A2 (de) * 1984-07-23 1986-02-05 Friedrich Schweinfurter Seitenkanalpumpe mit Kräfteausgleich
EP0397041A2 (de) * 1989-05-08 1990-11-14 Vickers Incorporated Rotationshydraulikpumpe
WO1992000449A1 (de) * 1990-06-28 1992-01-09 Robert Bosch Gmbh Aggregat zum fördern von kraftstoff vom vorratstank zur brennkraftmaschine eines kraftfahrzeuges

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2768192A1 (fr) * 1997-09-08 1999-03-12 Marwal Systems Pompe turbine a rendement ameliore notamment pour reservoir de carburant de vehicule automobile
FR2768191A1 (fr) * 1997-09-08 1999-03-12 Marwal Systems Pompe turbine notamment pour reservoir de carburant de vehicule automobile
FR2768193A1 (fr) * 1997-09-08 1999-03-12 Marwal Systems Pompe turbine notamment pour reservoir de carburant de vehicule automobile perfectionnee pour presenter un rendement ameliore
WO1999013226A1 (fr) * 1997-09-08 1999-03-18 Marwal Systems Pompe turbine a rendement ameliore notamment pour reservoir de carburant de vehicule automobile
WO1999047814A1 (de) * 1998-03-18 1999-09-23 Robert Bosch Gmbh Mehrstufige seitenkanalpumpe für kraftstoff für ein kraftfahrzeug
DE19826902C2 (de) * 1998-06-17 2000-05-04 Mannesmann Vdo Ag Förderpumpe
DE19826902A1 (de) * 1998-06-17 1999-12-23 Mannesmann Vdo Ag Förderpumpe
EP1295038A1 (de) * 2000-06-20 2003-03-26 Visteon Global Technologies, Inc. Kraftstoffpumpe mit verringerter empfindlichkeit für verschmutzung
EP1295038A4 (de) * 2000-06-20 2003-03-26 Visteon Global Tech Inc Kraftstoffpumpe mit verringerter empfindlichkeit für verschmutzung
JP2002332981A (ja) * 2001-05-09 2002-11-22 Mitsuba Corp 液体ポンプのインペラ
US7632060B2 (en) 2005-01-24 2009-12-15 Ford Global Technologies, Llc Fuel pump having dual flow channel
US9086071B2 (en) 2009-05-20 2015-07-21 Edwards Limited Side-channel pump with axial gas bearing
US9127685B2 (en) 2009-05-20 2015-09-08 Edwards Limited Regenerative vacuum pump with axial thrust balancing means
US9334873B2 (en) 2009-05-20 2016-05-10 Edwards Limited Side-channel compressor with symmetric rotor disc which pumps in parallel
WO2014039121A1 (en) * 2012-09-10 2014-03-13 Delphi Technologies, Inc. Multi-channel fuel pump

Also Published As

Publication number Publication date
EP0735271B1 (de) 2002-06-19
ES2179152T3 (es) 2003-01-16
EP0735271A3 (de) 1998-11-04
DE69621868T2 (de) 2003-01-30
DE69621868D1 (de) 2002-07-25

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