WO2014039121A1 - Pompe à carburant multicanaux - Google Patents

Pompe à carburant multicanaux Download PDF

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Publication number
WO2014039121A1
WO2014039121A1 PCT/US2013/043117 US2013043117W WO2014039121A1 WO 2014039121 A1 WO2014039121 A1 WO 2014039121A1 US 2013043117 W US2013043117 W US 2013043117W WO 2014039121 A1 WO2014039121 A1 WO 2014039121A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow channel
plate flow
inlet plate
sectional area
outlet
Prior art date
Application number
PCT/US2013/043117
Other languages
English (en)
Inventor
Partab Jeswani
Mohammed Aslam
Philip M. Anderson
Original Assignee
Delphi Technologies, Inc.
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 Delphi Technologies, Inc. filed Critical Delphi Technologies, Inc.
Publication of WO2014039121A1 publication Critical patent/WO2014039121A1/fr

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
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/005—Regenerative pumps of multistage type the stages being radially offset
    • 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
    • F04D5/008—Details of the stator, e.g. channel shape

Definitions

  • the present invention relates to a fluid pump; more particularly to a fuel pump; even more particularly to a multi-channel fuel pump; and still even more particularly to a multi-channel fuel pump in which the channels are synchronized.
  • Fluid pumps and more particularly fuel pumps for pumping fuel, for example, from a fuel tank of a motor vehicle to an internal combustion engine of the motor vehicle, are known.
  • United States Patent No. 5,338,151 shows one type of fuel pump which includes an impeller with two arrays of blades that are concentric to each other such that one array of blades radially surrounds the other array of blades.
  • An inlet plate is disposed adjacent to one face of the impeller and includes first and second inlet plate flow channels that are arranged in series to each other.
  • One inlet plate flow channel is aligned with the first array of blades while the other inlet plate flow channel is aligned with the second array of blades, accordingly, one inlet plate flow channel is disposed radially outward of the other inlet plate flow channel.
  • An outlet plate is disposed adjacent to the face of the impeller that is opposite the inlet plate.
  • the outlet plate includes first and second outlet plate flow channels that are arranged in series to each other.
  • One outlet plate flow channel is aligned with the first array of blades while the other outlet plate flow channel is aligned with the second array of blades, accordingly, one outlet plate flow channel is disposed radially outward of the other outlet plate flow channel.
  • Rotation of the impeller by an electric motor pumps fuel from an inlet of the fuel pump, through one or more of the inlet and outlet plate flow channels, and subsequently to an outlet of the fuel pump.
  • the pumping efficiency of each inlet and outlet flow channel is affected by the radial distance of the flow channel from the center of rotation of the impeller, the cross-sectional area of the flow channel, and the rotational rate of impeller. Without consideration to the geometry of each of the flow channels relative to each other, the maximum pumping efficiency for each flow channel may occur at different rotational rates of the impeller which reduces the overall efficiency of the fuel pump.
  • a fluid pump includes an outlet for discharging fluid from the fluid pump, a housing, and a motor with a shaft that rotates about an axis.
  • the fluid pump also includes an impeller having a first array of blades radially surrounding the axis and a second array of blades radially surrounding the first array of blades.
  • the impeller is rotatable by the shaft of the motor.
  • the fluid pump also includes an inlet plate adjacent to the impeller and has an inlet for introducing fluid into the fluid pump, a first inlet plate flow channel aligned with the first array of blades and having a first inlet plate flow channel cross-sectional area, and a second inlet plate flow channel aligned with the second array of blades and having a second inlet plate flow channel cross-sectional area.
  • Rotation of the impeller pumps fluid from the inlet to the outlet.
  • the second inlet plate flow channel cross-sectional area is synchronized with the first inlet plate flow channel cross-sectional area.
  • FIG. 1 is an axial cross-sectional view of a fuel pump in accordance with the present invention
  • FIG. 2 is an enlarged axial cross-sectional view of a pump section of the fuel pump of Fig. 1;
  • FIG. 3 is an axial view of an inlet plate of the pump section of Fig. 2;
  • FIG. 4 is an axial view of an outlet plate of the pump section of Fig. 2;
  • Fig. 5 is an isometric view of an impeller of the pump section of Fig. 2;
  • Fig. 6 is graph showing the pumping efficiency of pumping channels of the fuel pump of Fig. 1 and the overall pumping efficiency of the fuel pump of Fig. 1;
  • Fig. 7 is a graph showing the pumping efficiency of the pumping channels of a non-synchronized fuel pump and the overall pumping efficiency of the non- synchronized fuel pump.
  • Fig. 1 is an axial cross-sectional view of a fluid pump illustrated as fuel pump 10 for pumping liquid fuel, for example gasoline or diesel fuel, from a fuel tank (not shown) to an internal combustion engine (not shown). While the fluid pump is illustrated as fuel pump 10, it should be understood that the invention is not to be limited to a fuel pump, but could also be applied to fluid pumps for pumping fluids other than fuel.
  • Fuel pump 10 generally includes a pump section 12 at one end, a motor section 14 adjacent to pump section 12, and an outlet section 16 adjacent to motor section 14 at the end of fuel pump 10 opposite pump section 12.
  • a housing 18 of fuel pump 10 retains pump section 12, motor section 14 and outlet section 16 together. Fuel enters fuel pump 10 at pump section 12, a portion of which is rotated by motor section 14 as will be described in more detail later, and is pumped past motor section 14 to outlet section 16 where the fuel exits fuel pump 10.
  • Motor section 14 includes electric motor 20 which is disposed within housing 18.
  • Electric motor 20 includes a shaft 22 extending therefrom into pump section 12. Shaft 22 rotates about axis 24 when an electric current is applied to electric motor 20. Electric motors and their operation are well known, consequently, electric motor 20 will not be discussed further herein.
  • pump section 12 includes an inlet plate 26, an impeller 28, an outlet plate 30, and a spacer ring 32.
  • Inlet plate 26 is disposed at the end of pump section 12 that is distal from motor section 14 while outlet plate 30 is disposed at the end of pump section 12 that is proximal to motor section 14.
  • Both inlet plate 26 and outlet plate 30 are fixed relative to housing 18 to prevent relative movement between inlet plate 26 and outlet plate 30 with respect to housing 18.
  • Impeller 28 is disposed axially between inlet plate 26 and outlet plate 30 and is fixed to shaft 22 such that impeller 28 rotates with shaft 22 in a one-to-one
  • Spacer ring 32 is also disposed axially between inlet plate 26 and outlet plate 30, however, spacer ring 32 is fixed relative to housing 18 to prevent relative movement between housing 18 and spacer ring 32.
  • Spacer ring 32 is dimensioned to be slightly thicker, i.e. the dimension of spacer ring 32 in the direction of axis 24 is slightly greater than the dimension of impeller 28 in the direction of axis 24. In this way, inlet plate 26, outlet plate 30, and spacer ring 32 are fixed within housing 18, for example by crimping the end of housing 18 proximal to outlet plate 30.
  • Spacer ring 32 is also dimensioned to have an inside diameter that is larger than the outside diameter of impeller 28 to allow impeller 28 to rotate freely within spacer ring 32 and axially between inlet plate 26 and outlet plate 30.
  • Inlet plate 26 is generally planer and circular in shape, i.e. disk shaped, and includes an inlet 34 that extends through inlet plate 26 in the same direction as axis 24. Inlet 34 is a passage which introduces fuel into fuel pump 10. Inlet plate 26 also includes an inlet plate first flow channel 36 and an inlet plate second flow channel 38 that are both formed in the face of inlet plate 26 that faces toward impeller 28. Inlet plate first flow channel 36 and inlet plate second flow channel 38 are joined together in series by inlet plate transition channel 40. Inlet plate first flow channel 36 is defined by an inner wall 42, an outer wall 44, and a bottom 46 such that inner wall 42 is radially inward of outer wall 44.
  • Inlet plate first flow channel 36 has a width W I H and a depth Dun such that outer wall 44 has a radius Run with a center at axis 24.
  • the ratio of width Wipi to depth Du is about 2.5: 1.
  • Inlet plate first flow channel 36 has a cross-sectional area Ai P1 defined by a plane passing through and parallel to axis 24 as viewed in Fig. 2.
  • Inlet plate second flow channel 38 is defined by an inner wall 48, an outer wall 50, and a bottom 52.
  • Inlet plate second flow channel 38 has a width Wn> 2 and a depth D IP2 such that outer wall 50 has a radius Ri P2 with a center at axis 24 such that inner wall 48 is radially inward of outer wall 50.
  • the ratio of width Wn> 2 to depth Dn> 2 is about 2.5: 1.
  • Inlet plate second flow channel 38 has a cross-sectional area An> 2 defined by a plane passing through and parallel to axis 24 as viewed in Fig. 2.
  • inlet plate second flow channel 38 is connected to inlet 34 while the other end of inlet plate second flow channel 38 is connected to one end of inlet plate first flow channel 36 via inlet plate transition channel 40.
  • Radius Rip 2 and width Wn> 2 are sized such that inlet plate second flow channel 38 is radially outward of inlet plate first flow channel 36 to define an inlet plate separation surface 53 radially between outer wall 44 of inlet plate first flow channel 36 and inner wall 48 of inlet plate second flow channel 38.
  • Outlet plate 30 is generally planer and circular in shape, i.e. disk shaped, and includes an outlet plate outlet plate passage 54 that extends through outlet plate 30 in the same direction as axis 24. Outlet plate outlet passage 54 is in fluid communication with outlet section 16 as will be describe in more detail later. Outlet plate 30 also includes an outlet plate first flow channel 56 and an outlet plate second flow channel 58 that are both formed in the face of outlet plate 30 that faces toward impeller 28. Outlet plate first flow channel 56 and outlet plate second flow channel 58 are joined together in series by outlet plate transition channel 60. Outlet plate first flow channel 56 is defined by an inner wall 62, an outer wall 64, and a bottom 66 such that inner wall 62 is radially inward of outer wall 64.
  • Outlet plate first flow channel 56 has a width Wopi and a depth D 0 pi such that outer wall 64 has a radius R 0 pi with a center at axis 24.
  • the ratio of width WOPI to depth D 0 pi is about 2.5: 1.
  • Outlet plate first flow channel 56 has a cross-sectional area A 0 pi defined by a plane passing through and parallel to axis 24 as viewed in Fig. 2.
  • One end of outlet plate first flow channel 56 is connected to outlet plate outlet passage 54 while the other end of outlet plate first flow channel 56 is connected to one end of outlet plate second flow channel 58 via outlet plate transition channel 60.
  • Outlet plate second flow channel 58 is defined by an inner wall 68, an outer wall 70, and a bottom 72 such that inner wall 68 is radially inward of outer wall 70.
  • Outlet plate second flow channel 58 has a width Wop 2 and a depth D 0 p 2 such that outer wall 70 has a radius R 0 p 2 with a center at axis 24.
  • the ratio of width Wop 2 to depth D 0 p2 is about 2.5: 1.
  • Outlet plate second flow channel 58 has a cross-sectional area A 0 p 2 defined by a plane passing through and parallel to axis 24 as viewed in Fig. 2.
  • Radius ROP2 and width Wop 2 are sized such that outlet plate second flow channel 58 is radially outward of outlet plate first flow channel 56 to define an outlet plate separation surface 73 radially between outer wall 64 of outlet plate first flow channel 56 and inner wall 68 of outlet plate second flow channel 58.
  • Impeller 28 includes a first plurality of blades 76 arranged in a polar array radially surrounding and centered about axis 24 such that blades 76 are aligned with inlet plate first flow channel 36 and outlet plate first flow channel 56. Blades 76 are each separated from each other by a first blade chamber 78 that passes through impeller 28 in the general direction of axis 24. Impeller 28 also includes a second plurality of blades 80 arranged in a polar array radially surrounding and centered about axis 24 and first array of blades 76 such that blades 80 are aligned with inlet plate second flow channel 38 and outlet plate second flow channel 58.
  • Blades 80 are each separated from each other by a second blade chamber 82 that passes through impeller 28 in the general direction of axis 24.
  • the first plurality of blades 76 are radially separated from the second plurality of blades 80 by a blade separation wall 84 that is located radially between the first plurality of blades 76 and the second plurality of blades 80.
  • Impeller 28 may be made, for example only, by a plastic injection molding process in which the preceding features of impeller 28 are integrally molded as a single piece of plastic.
  • Outlet section 16 includes outlet 86 for discharging fuel from fuel pump 10.
  • Outlet 86 may be connected to, for example, a conduit (not shown) for supplying fuel to an internal combustion engine (not shown).
  • Outlet 86 is in fluid communication with outlet plate outlet passage 54 of outlet plate 30 for receiving fuel that has been pumped by pump section 12.
  • inlet 34 is exposed to a volume of fuel (not shown) which is to be pumped to, for example, an internal combustion engine (not shown).
  • An electric current is supplied to electric motor 20 in order to rotate shaft 22 and impeller 28.
  • fuel is drawn through inlet 34 into inlet plate first flow channel 36, inlet plate second flow channel 38, and inlet plate transition channel 40.
  • First blade chambers 78 and second blade chambers 82 allow fuel from inlet plate first flow channel 36, inlet plate second flow channel 38, and inlet plate transition channel 40 to flow to outlet plate first flow channel 56, outlet plate second flow channel 58, and outlet plate transition channel 60.
  • Impeller 28 subsequently discharges the fuel through outlet plate outlet passage 54 and consequently through outlet 86.
  • inlet plate first flow channel 36 is synchronized with inlet plate second flow channel 38, i.e. area Ann is synchronized with area An> 2 , to provide maximum or near maximum pumping efficiency of inlet plate first flow channel 36 and inlet plate second flow channel 38 for a desired rate of rotation of impeller 28.
  • outlet plate first flow channel 56 is
  • outlet plate second flow channel 58 i.e. area A 0 pi is synchronized with area A 0 p 2 , to provide maximum or near maximum efficiency of outlet plate first flow channel 56 and outlet plate second flow channel 58 at the desired rate of rotation of impeller 28.
  • the term "synchronized" signifies that the geometry of inlet plate first flow channel 36 and the geometry of inlet plate second flow channel 38 have been given consideration relative to each other in order to provide maximum or near maximum pumping efficiency at a common rotational rate of impeller 28 and that the geometry of outlet plate first flow channel 56 and the geometry of outlet plate second flow channel 58 have been given consideration relative to each other in order to provide maximum or near maximum pumping efficiency at a common rotational rate of impeller 28.
  • the synchronization will be described in further detail.
  • fuel pump 10 is to have a maximum efficiency at a rotational rate of impeller 28 of ⁇ radians per second while delivering a volumetric flow rate Q m /s at pressure "pascals.
  • the total pressure "generated by the fuel pump 10 equals the sum of pressures generated by inlet plate first flow channel 36 and outlet plate first flow channel 56, inlet plate second flow channel 38, and outlet plate second flow channel 58 as indicated by the following equation:
  • inlet plate first flow channel 36 and inlet plate second flow channel 38 and between outlet plate first flow channel 56 and outlet plate second flow channel 58 It may be desirable to minimize leakage between inlet plate first flow channel 36 and inlet plate second flow channel 38 and between outlet plate first flow channel 56 and outlet plate second flow channel 58.
  • a separation ⁇ for example about 0.006m, is provided between inlet plate first flow channel 36 and inlet plate second flow channel 38 and between outlet plate first flow channel 56 and outlet plate second flow channel 58 such that ⁇ is equal to the radial dimension of inlet plate separation surface 53 plus Wn> 2 and also equal to the radial dimension of outlet plate separation surface 73 plus Wop 2 - Consequently, inlet plate second flow channel 38 is related to inlet plate first flow channel 36 as shown by equation 4 below. Similarly, outlet plate second flow channel 58 is related to outlet plate first flow channel 56 as shown by equation 4.
  • the cross section areas An , ⁇ > 2 , A 0 pi, and A 0 p 2 can be determined such that inlet plate first flow channel 36 and inlet plate second flow channel 38 are synchronized with each other and such that outlet plate first flow channel 56 and outlet plate second flow channel 58 are synchronized with each other.
  • the pumping efficiency of inlet plate first flow channel 36, inlet plate second flow channel 38, outlet plate first flow channel 56, and outlet plate second flow channel 58 are all substantially the same. Consequently, the overall pumping efficiency of fuel pump 10 is the same as each of inlet plate first flow channel 36, inlet plate second flow channel 38, outlet plate first flow channel 56, and outlet plate second flow channel 58.
  • Fig. 6 is a plot of the pumping efficiency of each of inlet plate first flow channel 36, inlet plate second flow channel 38, outlet plate first flow channel 56, and outlet plate second flow channel 58 as well as the overall pumping efficiency of fuel pump 10.
  • Trace 100 is shown which represents the pumping efficiency of each of inlet plate first flow channel 36, inlet plate second flow channel 38, outlet plate first flow channel 56, and outlet plate second flow channel 58 as well as the overall pumping efficiency of fuel pump 10. Since inlet plate first flow channel 36 is
  • the pumping efficiency of each of inlet plate first flow channel 36, inlet plate second flow channel 38, outlet plate first flow channel 56, and outlet plate second flow channel 58, and consequently, the overall pumping efficiency of fuel pump 10 is represented by a single trace in Fig. 6, that is, trace 100.
  • the maximum pumping efficiency of each of inlet plate first flow channel 36, inlet plate second flow channel 38, outlet plate first flow channel 56, and outlet plate second flow channel 58 as well as the overall pumping efficiency of fuel pump 10 occurs at a rotational rate of about 5000 RPM of impeller 28. Also as can be seen, the maximum pumping efficiency is about 50%.
  • Fig. 7 represents the pumping efficiency of a fuel pump (not shown) with multiple flow channels that are not synchronized.
  • Fig. 7 includes traces 102, 104, and 106 which correspond to the pumping efficiency of first flow channels in the inlet and outlet plates of the fuel pump, the pumping efficiency of second flow channels in the inlet and outlet plates of the fuel pump, and the overall pumping efficiency of the fuel pump respectively.
  • the maximum pumping efficiency of the first flow channels in the inlet and outlet plates is about 50% which occurs at about 6000 RPM while the maximum pumping efficiency of the second flow channels in the inlet and outlet plates is also about 50%, but occurs at about 4000 RPM.
  • Figs. 6 and 7 are provided for example only and greater pumping efficiencies may be realized and that maximum pumping efficiency may be realized at rotational rates of the impeller that differ from that shown in Figs. 6 and 7.
  • fuel pump 10 may have an impeller with a greater number of arrays of blades, such that in general, there are N arrays of blades where N > 2.
  • the inlet plate and the outlet plate will each have flow channels that correspond to the number of arrays of blades in the impeller and that the flow channels of the inlet plate will be synchronized with each other and the flow channels of the outlet plate will be synchronized with each other.
  • the flow channels are synchronized by determining the cross-sectional area of each pair of flow channels corresponding to one array of blades of the impeller, e.g. the cross sectional area of the flow channels of the inlet and outlet plates
  • a n — -— , n is an integeger from 1 to N equation 7
  • N is the number of arrays of blades of the impeller, and consequently, the number of flow channels in each of the inlet plate and the outlet plate, i.e. the inlet plate has N flow channels and the outlet plate has N flow channels.
  • Equations 1-4 can also be expressed generically in order to determine R n used in equation 7 above.
  • the equations expressed generically are as follows: p
  • R n+1 R n + ⁇ , n is an integer from l to N— 1 equation 10

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe à fluide qui comprend une sortie pour évacuer un fluide à partir de la pompe à fluide, un boîtier et un moteur ayant un arbre qui tourne autour d'un axe. La pompe à fluide comprend également une roue ayant un premier ensemble de pales entourant radialement l'axe et un second ensemble de pales entourant radialement le premier ensemble de pales. La pompe à fluide comprend également une plaque d'entrée adjacente à la roue et a une entrée pour introduire un fluide dans la pompe à fluide, un premier canal d'écoulement de plaque d'entrée aligné avec le premier ensemble de pales et ayant une surface de section transversale de premier canal d'écoulement de plaque d'entrée, et un second canal d'écoulement de plaque d'entrée aligné avec le second ensemble de pales et ayant une surface de section transversale de second canal d'écoulement de plaque d'entrée. La surface de section transversale de second canal d'écoulement de plaque d'entrée est synchronisée avec la surface de section transversale de premier canal d'écoulement de plaque d'entrée.
PCT/US2013/043117 2012-09-10 2013-05-29 Pompe à carburant multicanaux WO2014039121A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US13/608,171 US20140072425A1 (en) 2012-09-10 2012-09-10 Multi-channel fuel pump
US13/608,171 2012-09-10

Publications (1)

Publication Number Publication Date
WO2014039121A1 true WO2014039121A1 (fr) 2014-03-13

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Family Applications (1)

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PCT/US2013/043117 WO2014039121A1 (fr) 2012-09-10 2013-05-29 Pompe à carburant multicanaux

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WO (1) WO2014039121A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9423606B2 (en) * 2014-06-30 2016-08-23 Amazon Technologies, Inc. Method of manufacturing an electrowetting device
GB2594145A (en) 2020-03-04 2021-10-20 Eaton Intelligent Power Ltd Single wheel multi-stage radially-layered regenerative pump

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4678395A (en) * 1984-07-23 1987-07-07 Friedrich Schweinfurter Regenerative pump with force equalization
EP0735271A2 (fr) * 1995-03-31 1996-10-02 BITRON S.p.A. Pompe à carburant du type à écoulement latéral pour véhicule

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4678395A (en) * 1984-07-23 1987-07-07 Friedrich Schweinfurter Regenerative pump with force equalization
EP0735271A2 (fr) * 1995-03-31 1996-10-02 BITRON S.p.A. Pompe à carburant du type à écoulement latéral pour véhicule

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