US20160238016A1 - Fuel pump - Google Patents

Fuel pump Download PDF

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Publication number
US20160238016A1
US20160238016A1 US15/024,132 US201415024132A US2016238016A1 US 20160238016 A1 US20160238016 A1 US 20160238016A1 US 201415024132 A US201415024132 A US 201415024132A US 2016238016 A1 US2016238016 A1 US 2016238016A1
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United States
Prior art keywords
impeller
contact surface
shaft
engaging hole
groove
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.)
Abandoned
Application number
US15/024,132
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English (en)
Inventor
Hiromi Sakai
Yuuji Hidaka
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.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HIDAKA, YUUJI, SAKAI, HIROMI
Publication of US20160238016A1 publication Critical patent/US20160238016A1/en
Abandoned 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
    • F04D29/20—Mounting rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • 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
    • F04D29/181—Axial flow rotors
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/528—Casings; Connections of working fluid for axial pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F04D3/005—Axial-flow pumps with a conventional single stage rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps

Definitions

  • the present disclosure relates to a fuel pump.
  • a fuel pump that includes an impeller, which is rotatable in a pump chamber, and a motor, which generates a drive force to rotate the impeller.
  • the fuel pump pumps fuel of a fuel tank to an internal combustion engine through rotation of the impeller.
  • the patent literature 1 recites a fuel pump that includes an impeller.
  • the impeller includes an engaging hole, which has a cross section of a D-shape and receives a shaft of an electric motor, and a hole, which receives a weight that corrects weight distribution of the impeller.
  • the shaft is rotatable in two opposite directions, i.e., a normal direction, which is a rotational direction at the time of pressurizing the fuel with the impeller, and a reverse direction, which is a rotational direction at the time of sensing a rotational position of the rotor relative to the stator.
  • a normal direction which is a rotational direction at the time of pressurizing the fuel with the impeller
  • a reverse direction which is a rotational direction at the time of sensing a rotational position of the rotor relative to the stator.
  • both of the cross section of the engaging hole and the cross-section of the one end portion of the shaft have an I-shape, so that two contact surfaces of the one end portion of the shaft simultaneously contact two contact surfaces of an inner wall of the engaging hole of the impeller.
  • the impeller which is molded through the injection molding, it is difficult to form the impeller such that the two contact surfaces of the impeller can simultaneously contact the two contact surfaces of the shaft. Therefore, at the time of contacting the shaft against the impeller, only one of the two contact surfaces of the shaft may possibly contact the impeller to possibly cause the damage of the impeller.
  • Patent Literature 1 JPH11-082208A
  • a fuel pump which includes a pump case, a stator, a rotor, a shaft and an impeller.
  • the pump case includes a suction port, through which fuel is drawn into the pump case, and a discharge port, through which the fuel is discharged from the pump case.
  • a plurality of windings is wound around the stator, which is configured into a tubular form, and the stator is received in the pump case.
  • the rotor is rotatably placed on a radially inner side of the stator.
  • the shaft is coaxial with the rotor and rotates integrally with the rotor.
  • the impeller includes an engaging hole, which receives one end portion of the shaft.
  • the impeller When the impeller is rotated integrally with the shaft, the impeller pressurizes the fuel drawn through the suction port and discharges the pressurized fuel through the discharge port.
  • the one end portion of the shaft includes at least one shaft side contact surface that is contactable with the impeller.
  • the engaging hole includes at least one impeller side contact surface, which opposes the at least one shaft side contact surface and is contactable with the at least one shaft side contact surface.
  • the impeller includes at least one deformation enabling space that is deformed when the at least one shaft side contact surface and the at least one impeller side contact surface contact with each other.
  • the shaft and the impeller are formed such that the shaft and the impeller integrally rotate while the shaft side contact surface and the impeller side contact surface contact with each other.
  • the shaft side contact surface and the impeller side contact surface may possibly contact with each other in an incorrect state depending on the processing accuracy of the engaging hole and/or the position of the shaft relative to the engaging hole.
  • the deformable space is deformed by a force, which is applied from the shaft to the impeller.
  • the resiliently deformable amount of the impeller is increased.
  • the shape of the engaging hole is changed, and the shaft side contact surface correctly contacts the impeller side contact surface.
  • the shaft side contact surface and the impeller side contact surface can correctly contact with each other through the deformation of the deformation enabling space without being influenced by the processing accuracy of the engaging hole and/or the position of the shaft relative to the engaging hole.
  • the surface pressure, which is applied to the impeller at the time of rotating the shaft becomes small, and the damage of the impeller can be effectively limited.
  • FIG. 1 is a cross-sectional view of a fuel pump according to a first embodiment of the present disclosure.
  • FIG. 2 is a top view of an impeller of the fuel pump of the first embodiment.
  • FIGS. 3( a ) to 3( d ) are schematic diagrams for describing an operation of the fuel pump according to the first embodiment.
  • FIG. 4 is a top view of an impeller of a fuel pump according to a second embodiment of the present disclosure.
  • FIG. 5 is a top view of an impeller of a fuel pump according to a third embodiment of the present disclosure.
  • FIG. 6 is a top view of an impeller of a fuel pump according to a fourth embodiment of the present disclosure.
  • FIG. 7 is a top view of an impeller of a fuel pump according to a fifth embodiment of the present disclosure.
  • a fuel pump according to a first embodiment of the present disclosure will be described with reference to FIGS. 1 to 3 ( d ).
  • the fuel pump 1 includes a motor device 3 , a pump device 4 , a housing 20 , a pump cover 60 and a cover end 40 .
  • the motor device 3 and the pump device 4 are received in a space, which is formed by the housing 20 , the pump cover 60 and the cover end 40 .
  • the fuel pump 1 draws fuel from a fuel tank (not shown) through a suction port 61 , which is indicated in a lower side of FIG. 1 , and discharges the fuel toward an internal combustion engine through a discharge port 41 , which is indicated in an upper side in FIG. 1 .
  • the upper side will be referred to as “the upside”, and the lower side will be referred to as “the downside.”
  • the housing 20 , the pump cover 60 and the cover end 40 serve as a pump case of the present disclosure.
  • the housing 20 is configured into a cylindrical tubular form and is made of metal (e.g., iron).
  • the pump cover 60 and the cover end 40 are installed to two end portions 201 , 202 , respectively, of the housing 20 .
  • the pump cover 60 closes the end portion 201 of the housing 20 , at which the suction port 61 is located. A peripheral edge part of the end portion 201 of the housing 20 is inwardly swaged, so that the pump cover 60 is fixed at the inside of the housing 20 . Thereby, removal of the pump cover 60 from the housing 20 in the axial direction of the fuel pump 1 is limited.
  • the pump cover 60 includes the suction port 61 , which opens toward the downside.
  • An intake passage 62 is formed in an inside of the suction port 61 to extend through the pump cover 60 in a direction (axial direction) of a rotational axis CA 52 of a shaft 52 .
  • a groove 63 which is connected to the intake passage 62 , is formed in a surface of the pump cover 60 , which is located on a side where the pump device 4 is placed.
  • the cover end 40 is made of resin and closes the end portion 202 of the housing 20 , at which the discharge port 41 is located. A peripheral edge part of the end portion 202 of the housing 20 is swaged, so that the cover end 40 is fixed in the inside of the housing 20 . Therefore, the removal of the cover end 40 from the housing 20 in the axial direction of the fuel pump 1 is limited.
  • the cover end 40 includes the discharge port 41 , which opens toward the upside.
  • a discharge passage 42 is formed in an inside of the discharge port 41 to extend through the cover end 40 in the direction of the rotational axis CA 52 of the shaft 52 .
  • An electric connector portion 43 which receives three connecting terminals 38 to receive an electric power from an outside, is formed in an end portion of the cover end 40 , which is located on a side that is opposite from the side where the discharge passage 42 is formed.
  • a bearing receiving portion 44 which is configured into a generally tubular form, is formed in an inside of the cover end 40 , which is placed in the inside of the housing 20 .
  • the bearing receiving portion 44 includes a receiving space 440 that is formed in an inside of the bearing receiving portion 44 to receive an end portion 521 of the shaft 52 and a bearing 55 .
  • the bearing 55 rotatably supports the end portion 521 of the shaft 52 .
  • the motor device 3 generates a rotational torque through use of a magnetic field that is generated when the electric power is supplied to the motor device 3 .
  • the motor device 3 includes a stator 10 , a rotor 50 and the shaft 52 .
  • the motor device 3 of the fuel pump 1 of the first embodiment is a brushless motor that senses a position of the rotor 50 relative to the stator 10 through sensing of rotation of the shaft 52 .
  • the stator 10 is configured into a cylindrical tubular form and is received at a radially outer side location in the inside of housing 20 .
  • the stator 10 includes six cores 12 , six bobbins, six windings and the three connecting terminals.
  • the stator 10 is integrally formed through resin molding of these components.
  • Each core 12 is formed by stacking a plurality of plates, which are made of a magnetic material (e.g., iron).
  • the cores 12 are arranged one after another in a circumferential direction to radially oppose a magnet 54 of the rotor 50 .
  • the bobbins 14 are made of a resin material. At the time of manufacturing, the cores 12 are inserted into and integrated with the bobbins 14 , respectively.
  • Each bobbin 14 includes an upper end portion 141 , an insert portion 142 and a lower end portion 143 .
  • the upper end portion 141 is formed on the discharge port 41 side.
  • Each core 12 is inserted into the insert portion 142 of the corresponding bobbin 14 .
  • the lower end portion 143 is formed on the suction port 61 side.
  • Each of the windings is, for example, a copper wire that has an outer surface coated with a dielectric film.
  • Each winding is wound around the corresponding bobbin 14 , into which the core 12 is inserted, to form one coil.
  • Each winding includes an upper end winding portion 161 , an insert winding portion (not shown) and a lower end winding portion 163 .
  • the upper end winding portion 161 is wound around the upper end portion 141 of the corresponding bobbin 14 .
  • the insert winding portion is wound around the insert portion 142 of the bobbin 14 .
  • the lower end winding portion 163 is wound around the lower end portion 143 of the bobbin 14 .
  • the windings are electrically connected to the connecting terminals 38 received in the electric connector portion 43 .
  • Each connecting terminal 38 extends through the cover end 40 and is fixed to the upper end portion 141 of the corresponding bobbin 14 .
  • the number of the connecting terminals 38 is three, and these connecting terminals 38 receive the three-phase electric power from an electric power source device (not shown).
  • the rotor 50 is rotatably received on the inner side of the stator 10 .
  • the rotor 50 includes the magnet 54 , which is placed to surround an iron core 53 .
  • the magnet 54 is magnetized to have N-poles and S-poles, which are alternately arranged one after another in the circumferential direction. In the first embodiment, the number of pole pairs of the N-pole and the S-pole is two, so that the total number of the poles is four.
  • the shaft 52 is securely press fitted into a shaft hole 51 of the rotor 50 , which extends along a central axis of the rotor 50 , and the shaft 52 is rotated integrally with the rotor 50 .
  • An end portion 522 of the shaft 52 which serves as one end portion of the shaft 52 of the present disclosure and is located on the suction port 61 side, is connected to the pump device 4 .
  • the end portion 522 of the shaft 52 includes a shaft first planar surface (serving as a shaft side first contact surface or a shaft side contact surface) 523 , which extends in the vertical direction and is formed as a planar surface, and a shaft second planar surface (serving as a shaft side second contact surface or a shaft side contact surface) 524 , which is formed as a planar surface and is generally parallel to the shaft first planar surface 523 .
  • the end portion 522 of the shaft 52 includes a shaft first curved surface 525 and a shaft second curved surface 526 .
  • the shaft first curved surface 525 connects between one side of the shaft first planar surface 523 and one side of the shaft second planar surface 524 and is formed as a curved surface.
  • the shaft second curved surface 526 connects between another side of the shaft first planar surface 523 and another side of the shaft second planar surface 524 and is formed as a curved surface.
  • a cross section of the end portion 522 of the shaft 52 which is taken in a direction perpendicular to the rotational axis CA 52 of the shaft 52 , has a generally I-shape.
  • the pump device 4 pressurizes the fuel drawn through the suction port 61 and discharges the pressurized fuel into the inside of the housing 20 through use of the rotational torque generated by the motor device 3 .
  • the pump device 4 includes a pump casing 70 and an impeller 65 .
  • the pump casing 70 is configured into a generally circular disk form and is placed between the pump cover 60 and the stator 10 .
  • a through-hole 71 is formed in a center portion of the pump casing 70 to extend through the pump casing 70 in a plate thickness direction of the pump casing 70 .
  • a bearing 56 is fitted into the through-hole 71 .
  • the bearing 56 rotatably supports the end portion 522 of the shaft 52 . In this way, the rotor 50 and the shaft 52 are rotatable relative to the cover end 40 and the pump casing 70 .
  • a groove 73 is formed at a location that is opposed to the groove 63 of the pump cover 60 .
  • a fuel passage 74 which extends through the pump casing 70 in the direction of the rotational axis CA 52 of the shaft 52 , is communicated with the groove 73 .
  • the impeller 65 is made of resin and is configured into a generally circular disk form.
  • the impeller 65 is received in a pump chamber 72 , which is formed between the pump cover 60 and the pump casing 70 .
  • An engaging hole 66 is formed generally in a center of the impeller 65 .
  • a cross section of the engaging hole 66 is configured to have a generally I-shape to correspond with the cross section of the end portion 522 of the shaft 52 .
  • the end portion 522 of the shaft 52 is received in the engaging hole 66 .
  • the impeller 65 is rotated in the pump chamber 72 by the rotation of the shaft 52 .
  • the details of the shape of the impeller 65 will be described later.
  • the impeller 65 includes a plurality of tilt surfaces 64 , which are placed at a location that corresponds to the grooves 63 , 73 . As shown in FIG. 2 , the tilt surfaces 64 are arranged one after another at generally equal intervals in the circumferential direction in a radially outer end part of the impeller 65 .
  • the impeller 65 when the electric power is supplied to the windings of the motor device 3 through the terminals 38 , the impeller 65 is rotated together with the rotor 50 and the shaft 52 .
  • the fuel in the fuel tank which receives the fuel pump 1 , is guided to the groove 63 through the suction port 61 .
  • the fuel, which is guided to the groove 63 is pressurized through the rotation of the impeller 65 and is guided to the groove 73 .
  • the pressurized fuel is guided to an intermediate chamber 75 , which is formed between the pump casing 70 and the motor device 3 , through the fuel passage 74 .
  • the fuel, which is guided to the intermediate chamber 75 is conducted through a fuel passage 77 , which is formed between the rotor 50 and the stator 10 , a fuel passage 78 , which is formed between an outer wall of the shaft 52 and inner walls 144 of the bobbins 14 , and a fuel passage 79 , which is formed on a radially outer side of the bearing receiving portion 44 . Furthermore, the fuel, which is guided to the intermediate chamber 75 , is conducted through a fuel passage 76 that is formed between an inner wall of the housing 20 and an outer wall of the stator 10 . The fuel, which flows through the fuel passages 76 , 77 , 78 , 79 , is discharged to the outside of the fuel pump 1 through the discharge passage 42 and the discharge port 41 .
  • FIG. 2 is a top view of the impeller 65 .
  • FIGS. 3( a ) to 3( d ) are schematic diagrams showing a positional relationship between the engaging hole 66 and the shaft 52 at the time of driving the fuel pump 1 .
  • the shape of the engaging hole 66 of FIGS. 3( b ) to 3( d ) is exaggerated in comparison to the actual shape of the engaging hole 66 for the descriptive purpose.
  • the engaging hole 66 of the impeller 65 is formed by an impeller first planar surface (serving as an impeller side first contact surface or an impeller side contact surface) 661 , an impeller second planar surface (serving as an impeller side second contact surface or an impeller side contact surface) 662 , an impeller first curved surface (serving as an engaging hole first forming surface or an engaging hole forming surface) 663 and an impeller second curved surface (serving as an engaging hole second forming surface or an engaging hole forming surface) 664 .
  • an impeller first planar surface serving as an impeller side first contact surface or an impeller side contact surface
  • an impeller second planar surface serving as an impeller side second contact surface or an impeller side contact surface
  • an impeller first curved surface serving as an engaging hole first forming surface or an engaging hole forming surface
  • an impeller second curved surface serving as an engaging hole second forming surface or an engaging hole forming surface
  • the impeller first planar surface 661 is a planar surface that is formed to extend in a direction (axial direction) of a central axis CA 66 of the engaging hole 66 .
  • the central axis CA 66 also serves as a central axis of the impeller 65 .
  • the impeller first planar surface 661 is formed at a corresponding location, at which the impeller first planar surface 661 opposes the shaft first planar surface 523 . When the shaft 52 is rotated, the impeller first planar surface 661 is contactable with the shaft first planar surface 523 .
  • the impeller second planar surface 662 is a planar surface that is formed to extend in the direction of the central axis CA 66 .
  • the impeller second planar surface 662 is generally parallel to the impeller first planar surface 661 .
  • the impeller second planar surface 662 is formed at a corresponding location, at which the impeller second planar surface 662 opposes the shaft second planar surface 524 . When the shaft 52 is rotated, the impeller second planar surface 662 is contactable with the shaft second planar surface 524 .
  • the impeller first curved surface 663 connects between one side of the impeller first planar surface 661 , which is parallel to the central axis CA 66 , and one side of the impeller second planar surface 662 , which is parallel to the central axis CA 66 .
  • a cross section of the impeller first curved surface 663 is generally configured into a shape of an arc, which is centered at the central axis CA 66 and is radially outwardly bulged.
  • a first groove (serving as a deformation enabling space) 665 is formed generally in a center (circumferential center) of the impeller first curved surface 663 .
  • the impeller second curved surface 664 connects between another side of the impeller first planar surface 661 , which is parallel to the central axis CA 66 , and another side of the impeller second planar surface 662 , which is parallel to the central axis CA 66 .
  • a cross section of the impeller second curved surface 664 is generally configured into a shape of an arc, which is centered at the central axis CA 66 and is radially outwardly bulged.
  • a second groove (serving as a deformation enabling space) 666 is formed generally in a center (circumferential center) of the impeller second curved surface 664 .
  • the first groove 665 is configured into a form of a slit and extends from the impeller first curved surface 663 in the radially outward direction.
  • the first groove 665 is formed to communicate with the engaging hole 66 and extends through the impeller 65 in the direction of the central axis CA 66 .
  • the second groove 666 is configured into a form of a slit and extends from the impeller second curved surface 664 in the radially outward direction.
  • the second groove 666 is formed to communicate with the engaging hole 66 and extends through the impeller 65 in the direction of the central axis CA 66 .
  • the first groove 665 and the second groove 666 extend in opposite directions, respectively, which are opposite to each other when the first groove 665 and the second groove 666 are viewed from the central axis CA 66 . Furthermore, a radial length of the first groove 665 and a radial length of the second groove 666 are equal to each other.
  • the impeller 65 which is made of resin and is formed through injection molding, it is difficult to form the impeller 65 in a manner that satisfies the above relationship. Therefore, in some cases, for example, in a state where the shaft first planar surface 523 and the impeller first planar surface 661 are placed parallel to each other, the shaft second planar surface 524 and the impeller second planar surface 662 may not be parallel to each other.
  • the engaging hole 66 may be formed such that although the shaft first planar surface 523 and the impeller first planar surface 661 are held parallel to each other, the shaft second planar surface 524 and the impeller second planar surface 662 are not parallel to each other, and an intersection line 667 between the impeller second planar surface 662 and the impeller second curved surface 664 is held further away from the point along the central axis CA 66 of the engaging hole 66 .
  • the impeller 65 is deformed such that the first groove 665 is expanded, as shown in FIG. 3( d ) . Due to the deformation of the first groove 665 , the shape of the engaging hole 66 is changed such that the shaft second planar surface 524 and the impeller second planar surface 662 , which were previously spaced from each other, now contact with each other.
  • a dotted line indicates the shape of the engaging hole 66 and the shape of the first groove 665 before the occurrence of the deformation of the first groove 665 .
  • the two planar surfaces of the shaft 52 contact the inner wall of the engaging hole 66 .
  • the rotational torque of the shaft 52 is applied to both of the impeller first planar surface 661 and the impeller second planar surface 662 , and thereby the surface pressure of the rotational torque applied to the impeller 65 is reduced. Therefore, the surface pressure, which is applied to the impeller 65 , becomes relatively small, and thereby it is possible to effectively limit the damage of the impeller 65 caused by the rotational torque of the shaft 52 .
  • the first groove 665 and the second groove 666 are formed in the center of the impeller first curved surface 663 and the center of the impeller second curved surface 664 , respectively, which are opposed to each other.
  • the first groove 665 and the second groove 666 extend for the same length in the two opposite directions, respectively, which are opposite to each other when the two opposite directions are viewed from the central axis CA 66 .
  • the impeller 65 is deformed to the similar shape.
  • the concentration of the stress on any particular portion of the impeller 65 can be limited.
  • FIG. 4 a fuel pump according to a second embodiment of the present disclosure will be described with reference to FIG. 4 .
  • the second embodiment differs from the first embodiment with respect to the shape of the impeller.
  • components, which are similar to those of the first embodiment, will be indicated by the same reference numerals and will not be described further.
  • FIG. 4 is a top view of an impeller 67 of a fuel pump according to the second embodiment.
  • An engaging hole 68 is formed generally in a center of the impeller 67 .
  • the end portion 522 of the shaft 52 is received in the engaging hole 66 .
  • a cross section of the engaging hole 68 is configured to have a generally I-shape to correspond with the cross section of the end portion 522 of the shaft 52 .
  • the engaging hole 68 is formed by an impeller first planar surface (serving as an impeller side first contact surface or an impeller side contact surface) 681 , an impeller second planar surface (serving as an impeller side second contact surface or an impeller side contact surface) 682 , an impeller first curved surface (serving as an engaging hole first forming surface or an engaging hole forming surface) 683 and an impeller second curved surface (serving as an engaging hole second forming surface or an engaging hole forming surface) 684 .
  • an impeller first planar surface serving as an impeller side first contact surface or an impeller side contact surface
  • an impeller second planar surface serving as an impeller side second contact surface or an impeller side contact surface
  • an impeller first curved surface serving as an engaging hole first forming surface or an engaging hole forming surface
  • an impeller second curved surface serving as
  • the impeller first planar surface 681 is formed to extend in a direction of a central axis CA 67 of the engaging hole 68 .
  • the impeller first planar surface 681 is formed at a corresponding location, at which the impeller first planar surface 681 opposes the shaft first planar surface 523 .
  • the impeller first planar surface 681 is contactable with the shaft first planar surface 523 .
  • the impeller second planar surface 682 is a planar surface that is formed to extend in the direction of the central axis CA 67 .
  • the impeller second planar surface 682 is generally parallel to the impeller first planar surface 681 .
  • the impeller second planar surface 682 is formed at a corresponding location, at which the impeller second planar surface 662 opposes the shaft second planar surface 524 . When the shaft 52 is rotated, the impeller second planar surface 682 is contactable with the shaft second planar surface 524 .
  • the impeller first curved surface 683 connects between one side of the impeller first planar surface 681 , which is parallel to the central axis CA 67 , and one side of the impeller second planar surface 682 , which is parallel to the central axis CA 67 .
  • a cross section of the impeller first curved surface 683 is configured into a shape of an arc, which is centered at the point along the central axis CA 67 and is radially outwardly bulged.
  • a first groove (serving as a deformation enabling space) 685 is formed generally in a center (circumferential center) of the impeller first curved surface 683 .
  • the impeller second curved surface 684 connects between another side of the impeller first planar surface 681 , which is parallel to the central axis CA 67 , and another side of the impeller second planar surface 682 , which is parallel to the central axis CA 67 .
  • a cross section of the impeller second curved surface 684 is configured into a shape of an arc, which is centered at the point along the central axis CA 67 and is radially outwardly bulged.
  • a second groove (serving as a deformation enabling space) 686 is formed generally in a center (circumferential center) of the impeller second curved surface 684 .
  • the first groove 685 is configured into a form of a slit and extends from the impeller first curved surface 683 in the radially outward direction.
  • the first groove 685 is formed to communicate with the engaging hole 68 and extends through the impeller 67 in the direction of the central axis CA 67 .
  • the second groove 686 is configured into a form of a slit and extends from the impeller second curved surface 684 in the radially outward direction.
  • the second groove 686 is formed to communicate with the engaging hole 68 and extends through the impeller 67 in the direction of the central axis CA 67 .
  • the first groove 685 and the second groove 686 extend in two opposite directions, respectively, which are opposite to each other when the two directions are viewed from the central axis CA 67 . Furthermore, a radial length of the first groove 685 and a radial length of the second groove 686 are equal to each other.
  • an imaginary circle which is centered at the central axis CA 67 and circumferentially connects radially inner side parts of the tilt surfaces 64 of the impeller 67
  • an imaginary circle which is centered at the central axis CA 67 and extends along the impeller first curved surface 683 and the impeller second curved surface 684 , is an imaginary circular VL 68 .
  • a radially outer side wall surface 687 of the first groove 685 and a radially outer side wall surface 688 of the second groove 686 , are formed on a radially inner side of an intermediate imaginary circle VL 67 that is radially equally spaced (by a distance D2 in FIG. 4 ) from both of the imaginary circle VL 64 and the imaginary circle VL 68 , as shown in FIG. 4 .
  • the first groove 685 and the second groove 686 are formed on the radially inner side of the intermediate imaginary circle VL 67 .
  • the impeller 67 can be appropriately deformed by the action of the shaft 52 . Therefore, the fuel pump of the second embodiment achieves the advantages, which are similar to those of the first embodiment. Also, in the fuel pump of the second embodiment, the tolerable amount of deformation is increased in comparison to that of the first embodiment. Thereby, the damage of the impeller 67 caused by the rotational torque of the shaft 52 can be further effectively limited.
  • the third embodiment differs from the first embodiment with respect to the shape of the impeller.
  • components, which are similar to those of the first embodiment, will be indicated by the same reference numerals and will not be described further.
  • the impeller 85 includes a plurality of tilt surfaces 84 , an engaging hole 86 and a plurality of through-holes (serving as deformation enabling spaces) 87 .
  • the tilt surfaces 84 are formed at the location that corresponds to the grooves 63 , 73 .
  • a cross section of the engaging hole 86 is configured to have a generally I-shape to correspond with the cross section of the end portion 522 of the shaft 52 .
  • the engaging hole 86 is formed by an impeller first planar surface (serving as an impeller side first contact surface or an impeller side contact surface) 861 , which is contactable with the shaft first planar surface 523 , and an impeller second planar surface (serving as an impeller side second contact surface or an impeller side contact surface) 862 , which is contactable with the shaft second planar surface 524 .
  • the through-holes 87 extend through the impeller 85 in a direction of a central axis CA 85 .
  • the total number of the through-holes 87 is six, and these through-holes 87 are arranged one after another at equal intervals along an imaginary circle, which is located on a radially outer side of the engaging hole 86 and is centered at a point along the central axis CA 85 of the engaging hole 86 .
  • Each of the through-holes 87 is formed at a corresponding location which is point symmetric to another one of the through-holes 87 about a symmetric point that is a point along the central axis CA 85 .
  • the fuel pump of the third embodiment can achieve the advantages, which are similar to the advantages discussed in the sections (a) and (b) of the first embodiment, can be achieved.
  • the through-holes 87 are arranged one after another at equal intervals along the imaginary circle, which is centered at the point along the central axis CA 85 , and each of the through-holes 87 is formed at the corresponding location which is point symmetric to another one of the through-holes 87 about the symmetric point that is the point along the central axis CA 85 .
  • the impeller 85 is deformed to the similar shape.
  • the concentration of the stress (force) on any particular portion of the impeller 85 can be limited.
  • the fourth embodiment differs from the third embodiment with respect to the shape of the impeller.
  • components, which are similar to those of the third embodiment, will be indicated by the same reference numerals and will not be described further.
  • FIG. 6 is a top view of an impeller 88 of a fuel pump according to the fourth embodiment.
  • the impeller 88 includes the tilt surfaces 84 , the engaging hole 86 and a plurality of through-holes (serving as deformation enabling spaces) 89 .
  • the through-holes 89 extend through the impeller 88 in the direction of the central axis CA 88 .
  • the total number of the through-holes 89 is six, and these through-holes 89 are arranged one after another at equal intervals along an imaginary circle, which is located on a radially outer side of the engaging hole 86 and is centered at a point along the central axis CA 88 of the engaging hole 86 .
  • an imaginary circle which is centered at the central axis CA 88 and circumferentially connects radially inner side parts of the tilt surfaces 84 located at the radially outer side in the impeller 88
  • an imaginary circle which is centered at the central axis CA 88 and extends along the impeller first curved surface (serving as the engaging hole forming surface) 863 and the impeller second curved surface (serving as the engaging hole forming surface) 864 of the engaging hole 86 , is an imaginary circular VL 88 .
  • the through-holes 89 are formed on a radially inner side of an intermediate imaginary circle VL 88 that is radially equally spaced (by a distance D4 in FIG. 6 ) from both of the imaginary circle VL 84 and the imaginary circle VL 86 , as shown in FIG. 6 .
  • the through-holes 89 are formed on the radially inner side of the intermediate imaginary circle VL 88 .
  • the impeller 88 can be appropriately deformed by the action of the shaft 52 . Therefore, the fuel pump of the fourth embodiment achieves the advantages, which are similar to those of the third embodiment. Also, according to the fourth embodiment, the tolerable amount of deformation is increased in comparison to that of the third embodiment. Thereby, the damage of the impeller 88 caused by the rotational torque of the shaft 52 can be further effectively limited.
  • a fuel pump according to a fifth embodiment of the present disclosure will be described with reference to FIG. 7 .
  • the shape of the end portion of the shaft and the shape of the impeller are different from those of the third embodiment.
  • components, which are similar to those of the third embodiment, will be indicated by the same reference numerals and will not be described further.
  • FIG. 7 is a top view of an impeller 95 of a fuel pump according to the fifth embodiment.
  • the impeller 95 includes a plurality of tilt surfaces 94 , an engaging hole 96 and a plurality of through-holes (serving as deformation enabling spaces) 991 - 995 .
  • the tilt surfaces 94 are formed at a location, which corresponds to the groove 63 formed in the pump cover 60 and the groove 73 formed in the pump casing 70 .
  • the cross section of the engaging hole 96 is configured into a generally D-shape to correspond with a cross section of the one end portion 922 of the shaft 92 .
  • the engaging hole 96 is formed by an impeller third planar surface (serving as an impeller side third contact surface or an impeller side contact surface) 961 and an impeller curved surface (serving as an engaging hole forming surface) 963 .
  • the impeller third planar surface 961 is contactable with a shaft third planar surface (serving as a shaft side third contact surface or a shaft side contact surface) 923 formed in the one end portion 922 of the shaft 92 .
  • the impeller curved surface 963 is formed to extend along a shaft third curved surface (serving as a shaft third curved surface or a shaft curved surface) 925 .
  • the shaft third curved surface 925 is an arcuately curved surface and connects between two ends of the shaft third planar surface 923 , which are generally parallel to a central axis CA 95 .
  • the through-holes 991 - 995 extend through the impeller 95 in the direction of the central axis CA 95 .
  • the impeller 95 includes the five through-holes 991 - 995 .
  • the through-holes 991 - 995 are arranged one after another at equal intervals along an imaginary circle, which is located on the radially outer side of the engaging hole 96 and is centered at the point along the central axis CA 95 of the engaging hole 96 .
  • the through-holes 991 - 995 of the impeller 95 two of them, i.e., the through-holes 992 , 995 are placed adjacent to two points 962 , 964 , respectively, at each of which the impeller third planar surface 961 and the impeller curved surface 963 are connected with each other.
  • an imaginary circle which is centered at the central axis CA 95 and circumferentially connects radially inner side parts of the tilt surfaces 94
  • an imaginary circle which is centered at the central axis CA 95 and extends along the impeller curved surface 963
  • an imaginary circular VL 96 is an imaginary circular VL 96 .
  • the through-holes 991 - 995 are formed on a radially inner side of an intermediate imaginary circle VL 98 that is radially equally spaced (by a distance D5 in FIG. 7 ) from both of the imaginary circle VL 94 and the imaginary circle VL 96 , as shown in FIG. 7 .
  • the cross section of the end portion 922 of the shaft 92 has the D-shape
  • the cross section of the engaging hole 96 has the D-shape.
  • the total number of the through-holes 991 - 995 is five, which is the odd number and corresponds to the shape of the engaging hole 96 .
  • the impeller 95 can be deformed such that the shaft third planar surface 923 contacts the impeller third planar surface 961 . Therefore, in the fifth embodiment, the advantages, which are similar to those of the third embodiment, are achieved.
  • the through-holes 991 - 995 are formed on the radially inner side of the intermediate imaginary circle VL 98 .
  • the impeller 95 can be appropriately deformed by the action of the shaft 52 .
  • the fuel pump of the fifth embodiment can further effectively limit the damage of the impeller 95 caused by the rotational torque of the shaft 92 .
  • the number of the through-holes 991 - 995 is five, which corresponds to the shape of the engaging hole 96 .
  • the weight balance of the impeller 95 is kept uniform throughout the impeller 95 , so that occurrence of defects, such as vibrations, at the time of rotation of the impeller 95 can be limited.
  • the first groove and the second groove are formed as deformation enabling spaces, respectively.
  • the through-holes are formed as deformation enabling spaces, respectively.
  • the shape of the deformation enabling space(s) is not limited to any of these shapes.
  • the shape of each deformation enabling space can be any other suitable shape as long as the deformation enabling space is formed in the impeller and can be deformed to increase the resiliently deformable amount of the impeller at the time of occurrence of the contact between the shaft and the impeller.
  • the shaft first planar surface (serving as the shaft side first contact surface), the shaft second planar surface (serving as the shaft side second contact surface), the impeller first planar surface (serving as the impeller side first contact surface), and the impeller second planar surface (serving as the impeller side second contact surface) are formed as the planar surfaces, respectively.
  • any one or more of these surfaces may be formed as, for example, a curved surface or any other suitable form as long as the shaft side first contact surface and the impeller side first contact surface are contactable with each other, and the shaft side second contact surface and the impeller side second contact surface are contactable with each other.
  • the shaft first planar surface (serving as the shaft side first contact surface) and the shaft second planar surface (serving as the shaft side second contact surface) are formed to be generally parallel to each other.
  • the shaft first planar surface and the shaft second planar surface may be formed to be non-parallel to each other.
  • the plurality of deformation enabling spaces is formed in the first and second embodiments.
  • the first groove and the second groove are formed in the center of the impeller first curved surface and the center of the impeller second curved surface, respectively.
  • the location of the first groove and the location of the second groove should not be limited to these locations.
  • the radial length of the first groove and the radial length of the second groove are equal to each other, and the first groove and the second groove extend to the opposite directions, respectively.
  • the relationship between the first groove and the second groove should not be limited to this relationship.
  • the through-holes are arranged one after another at equal intervals along the imaginary circle, which is centered at the point along the central axis of the impeller, in the impeller, and each of these through-holes is point-symmetric to another one of these through-holes.
  • the locations of the through-holes should not be limited to these locations.
  • the total number of the through-holes of the impeller is six. Furthermore, in the fifth embodiment, the total number of the through-holes of the impeller is five. In the case where the cross section of the engaging hole of the impeller is the I-shape, it is desirable that the total number of the through-holes is even number. Furthermore, in the case where the cross section of the engaging hole of the impeller is the D-shape, it is desirable that the total number of the through-holes is odd number. However, the total number of the through-holes is not limited to any of these.
  • the motor device of the fuel pump is the brushless motor.
  • the motor can rotate the shaft in the two directions, i.e., the normal direction and the reverse direction, any other suitable motor, which is other than the brushless motor, may be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US15/024,132 2013-09-24 2014-09-08 Fuel pump Abandoned US20160238016A1 (en)

Applications Claiming Priority (5)

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JP2013196615 2013-09-24
JP2013-196615 2013-09-24
JP2014-095859 2014-05-07
JP2014095859A JP6135593B2 (ja) 2013-09-24 2014-05-07 燃料ポンプ
PCT/JP2014/004601 WO2015045294A1 (ja) 2013-09-24 2014-09-08 燃料ポンプ

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US20160238016A1 true US20160238016A1 (en) 2016-08-18

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US15/024,132 Abandoned US20160238016A1 (en) 2013-09-24 2014-09-08 Fuel pump

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JP (1) JP6135593B2 (enExample)
WO (1) WO2015045294A1 (enExample)

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US20160201692A1 (en) * 2013-09-17 2016-07-14 Denso Corporation Fuel pump
US20160201679A1 (en) * 2013-09-17 2016-07-14 Denso Corporation Fuel pump
US20180142653A1 (en) * 2015-05-28 2018-05-24 Denso Corporation Fuel pump
DE102018202276A1 (de) * 2018-02-14 2019-08-14 Ti Automotive Technology Center Gmbh Flüssigkeitspumpe mit Vibrationsdämpfungselement
US10385863B2 (en) 2015-06-26 2019-08-20 Denso Corporation Rotor

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JP2016223323A (ja) * 2015-05-28 2016-12-28 株式会社デンソー 燃料ポンプ
JP2017008736A (ja) * 2015-06-17 2017-01-12 株式会社デンソー 燃料ポンプ
JP2017008734A (ja) * 2015-06-17 2017-01-12 株式会社デンソー 燃料ポンプ
JP6786436B2 (ja) * 2017-04-07 2020-11-18 愛三工業株式会社 燃料ポンプ

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Cited By (8)

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Publication number Priority date Publication date Assignee Title
US20160201692A1 (en) * 2013-09-17 2016-07-14 Denso Corporation Fuel pump
US20160201679A1 (en) * 2013-09-17 2016-07-14 Denso Corporation Fuel pump
US10107291B2 (en) * 2013-09-17 2018-10-23 Denso Corporation Fuel pump
US20180142653A1 (en) * 2015-05-28 2018-05-24 Denso Corporation Fuel pump
US10233881B2 (en) * 2015-05-28 2019-03-19 Denso Corporation Fuel pump
US10385863B2 (en) 2015-06-26 2019-08-20 Denso Corporation Rotor
DE102018202276A1 (de) * 2018-02-14 2019-08-14 Ti Automotive Technology Center Gmbh Flüssigkeitspumpe mit Vibrationsdämpfungselement
DE102018202276B4 (de) 2018-02-14 2023-05-04 Ti Automotive Technology Center Gmbh Flüssigkeitspumpe mit Vibrationsdämpfungselement

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