WO2015045294A1 - 燃料ポンプ - Google Patents

燃料ポンプ Download PDF

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Publication number
WO2015045294A1
WO2015045294A1 PCT/JP2014/004601 JP2014004601W WO2015045294A1 WO 2015045294 A1 WO2015045294 A1 WO 2015045294A1 JP 2014004601 W JP2014004601 W JP 2014004601W WO 2015045294 A1 WO2015045294 A1 WO 2015045294A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
shaft
contact surface
fitting hole
fuel pump
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.)
Ceased
Application number
PCT/JP2014/004601
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
酒井　博美
裕二 日高
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
Priority to US15/024,132 priority Critical patent/US20160238016A1/en
Publication of WO2015045294A1 publication Critical patent/WO2015045294A1/ja
Anticipated expiration legal-status Critical
Ceased 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
    • F04D29/188—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

  • This disclosure relates to a fuel pump.
  • Patent Document 1 discloses a fuel pump including an impeller having a fitting hole that is formed to have a D-shaped cross-section and to which a motor shaft is fitted, and a hole to which a weight for correcting the weight distribution of the impeller is attached.
  • the shaft has two directions: a forward direction in which the impeller rotates to pressurize the fuel, and a reverse direction in which the rotor rotates to detect the position of the rotor relative to the stator. Rotate to. Since there is a manufacturing tolerance in the fitting hole of the impeller, a gap is formed between the inner wall that forms the fitting hole and the side wall that forms one end of the shaft that fits into the fitting hole. Yes. When one end of the shaft shifts from a state in which it can rotate in the forward or reverse direction to a state in which it can rotate in the reverse or forward direction, the shaft rotates in the fitting hole. The rotating torque of the rotating shaft acts on one contact surface that forms the fitting hole. For this reason, there exists a possibility that an impeller may be damaged.
  • the cross-sectional shape of the fitting hole and the cross-sectional shape of one end of the shaft are I-shaped, and the two abutments possessed by one end of the shaft 2.
  • a fuel pump in which a surface is simultaneously in contact with two contact surfaces formed as inner walls of a fitting hole.
  • An object of the present disclosure is to provide a fuel pump that effectively suppresses damage to the impeller.
  • a fuel pump including a pump case, a stator, a rotor, a shaft, and an impeller.
  • the pump case has a suction port for sucking fuel into the inside and a discharge port for discharging fuel to the outside.
  • the cylindrical stator has a plurality of windings wound therein and is accommodated in the pump case.
  • the rotor is rotatably provided inside the stator in the radial direction.
  • the shaft is provided coaxially with the rotor and rotates integrally with the rotor.
  • the impeller has a fitting hole that accommodates one end of the shaft. When the impeller rotates together with the shaft, the fuel sucked from the suction port is pressurized and discharged from the discharge port.
  • the shaft has at least one shaft-side contact surface that can contact the impeller at one end.
  • the fitting hole has at least one impeller side contact surface that faces at least one shaft side contact surface and is capable of contacting the at least one shaft side contact surface.
  • the impeller has at least one deformation permissible space that deforms when at least one shaft-side contact surface and at least one impeller-side contact surface come into contact with each other.
  • the shaft and the impeller are formed so that the shaft rotates integrally with the impeller while the shaft-side contact surface and the impeller-side contact surface are in contact with each other.
  • the shaft-side contact surface and the impeller-side contact surface may contact each other in an incorrect state depending on the processing accuracy of the fitting hole and the position of the shaft with respect to the fitting hole.
  • the impeller included in the fuel pump of the present disclosure when the shaft-side contact surface and the impeller-side contact surface come into contact with each other, the deformation allowable space is deformed by a force acting on the impeller from the shaft.
  • the shaft-side contact surface and the impeller-side contact surface are not affected by the processing accuracy of the fitting hole and the position of the shaft with respect to the fitting hole. Can be properly abutted. Thereby, the surface pressure which acts on the impeller when the shaft rotates is reduced, and the impeller can be effectively prevented from being damaged.
  • 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 the impeller of the fuel pump according to the first embodiment.
  • FIGS. 3A to 3D are schematic views for explaining the operation of the fuel pump according to the first embodiment.
  • FIG. 4 is a top view of the impeller of the fuel pump according to the second embodiment of the present disclosure.
  • FIG. 5 is a top view of the impeller of the fuel pump according to the third embodiment of the present disclosure.
  • FIG. 6 is a top view of the impeller of the fuel pump according to the fourth embodiment of the present disclosure.
  • FIG. 7 is a top view of the impeller of the fuel pump according to the fifth embodiment of the present disclosure.
  • the fuel pump 1 includes a motor unit 3, a pump unit 4, a housing 20, a pump cover 60, and a cover end 40.
  • the motor unit 3 and the pump unit 4 are accommodated in a space formed by the housing 20, the pump cover 60, and the cover end 40.
  • the fuel pump 1 sucks fuel in a fuel tank (not shown) from a suction port 61 shown at the lower side of FIG. 1 and discharges it to an internal combustion engine from a discharge port 41 shown at the upper side of FIG. In FIG. 1, the upper side is “top side” and the lower side is “ground side”.
  • the housing 20, the pump cover 60, and the cover end 40 correspond to the “pump case” of the present disclosure.
  • the housing 20 is formed in a cylindrical shape from a metal such as iron.
  • a pump cover 60 and a cover end 40 are provided at two ends 201 and 202 of the housing 20.
  • the pump cover 60 closes the end 201 on the suction port 61 side of the housing 20.
  • the pump cover 60 is fixed inside the housing 20 by crimping the edge of the end portion 201 of the housing 20 inward, so that the fuel pump 1 is prevented from coming off in the axial direction.
  • the pump cover 60 has a suction port 61 that opens to the ground side.
  • a suction passage 62 that penetrates the pump cover 60 in the direction of the rotation axis CA52 of the shaft 52 (axial direction) is formed inside the suction port 61.
  • a groove 63 connected to the suction passage 62 is formed on the surface of the pump cover 60 on the pump unit 4 side.
  • the cover end 40 is molded from resin and closes the end 202 on the discharge port 41 side of the housing 20.
  • the cover end 40 is fixed inside the housing 20 by crimping the edge of the end portion 202 of the housing 20, so that the fuel pump 1 is prevented from coming off in the axial direction.
  • the cover end 40 has a discharge port 41 that opens to the top side.
  • a discharge passage 42 that penetrates the cover end 40 in the direction of the rotation axis CA 52 of the shaft 52 is formed inside the discharge port 41.
  • An electrical connector portion 43 that accommodates three connection terminals 38 that receive power from the outside is provided at the end of the cover end 40 opposite to the side where the discharge passage 42 is formed.
  • a bearing housing portion 44 formed in a substantially cylindrical shape is provided on the inner side of the housing 20 of the cover end 40.
  • the bearing accommodating portion 44 has an accommodating space 440 for accommodating the end portion 521 of the shaft 52 and the bearing 55 that rotatably supports the end portion 521 therein.
  • the motor unit 3 generates rotational torque using a magnetic field generated when electric power is supplied.
  • the motor unit 3 includes a stator 10, a rotor 50, and a shaft 52.
  • the motor unit 3 of the fuel pump 1 according to the first embodiment is a brushless motor that detects the position of the rotor 50 with respect to the stator 10 by the rotation of the shaft 52.
  • the stator 10 has a cylindrical shape and is accommodated on the radially outer side in the housing 20.
  • the stator 10 has six cores 12, six bobbins, six windings, and three connection terminals.
  • the stator 10 is integrally formed by molding these with resin.
  • the core 12 is formed by overlapping a plurality of magnetic materials such as plate-like irons.
  • the cores 12 are arranged in the circumferential direction and are provided at positions facing the magnets 54 of the rotor 50 in the radial direction.
  • the bobbin 14 is formed from a resin material, and the core 12 is inserted into the bobbin 14 at the time of formation.
  • the bobbin 14 has an upper end portion 141 formed on the discharge port 41 side, an insert portion 142 into which a core is inserted, and a lower end portion 143 formed on the suction port 61 side.
  • the winding is, for example, a copper wire whose surface is covered with an insulating film.
  • One winding forms one coil by being wound around a bobbin 14 into which the core 12 is inserted.
  • One winding is formed on the upper end winding portion 161 wound around the upper end portion 141 of the bobbin 14, the insert winding portion (not shown) wound around the insert portion 142 of the bobbin 14, and the lower end portion 143 of the bobbin 14. It has a lower end winding part 163 to be wound.
  • the winding is electrically connected to the connection terminal 38 accommodated in the electrical connector portion 43.
  • connection terminal 38 passes through the cover end 40 and is fixed to the upper end 141 of the bobbin 14.
  • three connection terminals 38 are provided and receive three-phase power from a power supply device (not shown).
  • the rotor 50 is rotatably accommodated inside the stator 10.
  • the rotor is provided with a magnet 54 around the iron core 53.
  • the magnet 54 has N and S poles arranged alternately in the circumferential direction.
  • N poles and S poles are provided as 2 pole pairs, for a total of 4 poles.
  • the shaft 52 is press-fitted and fixed in a shaft hole 51 formed on the central axis of the rotor 50 and rotates together with the rotor 50.
  • An end 522 on the suction port 61 side of the shaft 52 corresponding to one end of the shaft 52 in the present disclosure is connected to the pump unit 4.
  • the end portion 522 of the shaft 52 extends in the vertical direction, and is formed in a flat shape as a “shaft-side first abutment surface or shaft-side abutment surface”.
  • a shaft second flat surface 524 is provided as a “shaft side second contact surface or shaft side contact surface” provided substantially parallel to the first plane 523.
  • the end portion 522 of the shaft 52 connects the one side of the shaft first plane 523 and the one side of the shaft second plane 524, and the shaft first curved surface 525 formed into a curved surface, and the shaft first
  • the shaft has a second curved surface 526 formed in a curved shape by connecting another side of the plane 523 and another side of the shaft second plane 524.
  • the cross-sectional shape in the direction perpendicular to the rotation axis CA52 of the end portion 522 of the shaft 52 is substantially I-shaped.
  • the pump unit 4 pressurizes the fuel sucked from the suction port 61 using the rotational torque generated by the motor unit 3 and discharges it into the housing 20.
  • the pump unit 4 includes a pump casing 70 and an impeller 65.
  • the pump casing 70 is formed in a substantially disc shape and is provided between the pump cover 60 and the stator 10.
  • a through hole 71 is formed in the center of the pump casing 70 so as to penetrate the pump casing 70 in the plate thickness direction.
  • a bearing 56 is fitted in the through hole 71. The bearing 56 rotatably supports the end portion 522 of the shaft 52. Thereby, the rotor 50 and the shaft 52 can rotate with respect to the cover end 40 and the pump casing 70.
  • a groove 73 is formed at a position facing the groove 63 of the pump cover 60 on the surface of the pump casing 70 on the impeller 65 side.
  • the groove 73 communicates with a fuel passage 74 that penetrates the pump casing 70 in the direction of the rotation axis CA52 of the shaft 52.
  • the impeller 65 is formed in a substantially disk shape with resin.
  • the impeller 65 is accommodated in a pump chamber 72 between the pump cover 60 and the pump casing 70.
  • a fitting hole 66 is formed in the approximate center of the impeller 65.
  • the fitting hole 66 is formed in a substantially I shape so that the cross-sectional shape thereof matches the cross-sectional shape of the end portion 522 of the shaft 52.
  • the end portion 522 of the shaft 52 is accommodated in the fitting hole 66.
  • the impeller 65 rotates in the pump chamber 72 by the rotation of the shaft 52.
  • the detailed shape of the impeller 65 will be described later.
  • the impeller 65 has a plurality of inclined surfaces 64 formed at positions corresponding to the grooves 63 and 73. As shown in FIG. 2, the inclined surfaces 64 are provided at equal intervals in the circumferential direction at the radially outer end of the impeller 65.
  • the impeller 65 rotates together with the rotor 50 and the shaft 52.
  • the fuel in the fuel tank that houses the fuel pump 1 is guided to the groove 63 via the suction port 61.
  • the fuel guided to the groove 63 is pressurized by the rotation of the impeller 65 and is guided to the groove 73.
  • the pressurized fuel passes through the fuel passage 74 and is guided to an intermediate chamber 75 formed between the pump casing 70 and the motor unit 3.
  • the fuel guided to the intermediate chamber 75 is a fuel passage 77 between the rotor 50 and the stator 10, a fuel passage 78 between the outer wall of the shaft 52 and the inner wall 144 of the bobbin 14, and radially outward of the bearing housing portion 44. It passes through the formed fuel passage 79.
  • the fuel guided to the intermediate chamber 75 passes through a fuel passage 76 formed between the inner wall of the housing 20 and the outer wall of the stator 10. The fuel passing through the fuel passages 76, 77, 78 and 79 is discharged to the outside through the discharge passage 42 and the discharge port 41.
  • the fuel pump 1 according to the first embodiment is characterized by the shape of the impeller 65.
  • the detailed shape of the impeller 65 will be described with reference to FIGS. 2 to 3D.
  • FIG. 2 is a top view of the impeller 65.
  • FIGS. 3A to 3D are schematic views showing the positional relationship between the fitting hole 66 and the shaft 52 when the fuel pump 1 is driven. 3B to 3D, the shape of the fitting hole 66 is exaggerated from the actual shape for convenience of explanation.
  • the impeller 65 has a fitting hole 66 as an impeller first flat surface 661 as an “impeller side first contact surface or impeller side contact surface” and as an “impeller side second contact surface or impeller side contact surface”.
  • the impeller first plane 661 is a plane formed to extend in the direction (axial direction) of the central axis CA66 of the fitting hole 66.
  • the central axis CA66 is also the central axis of the impeller 65.
  • the impeller first plane 661 is provided at a position facing the shaft first plane 523 and can contact the shaft first plane 523 when the shaft 52 rotates.
  • the impeller second plane 662 is a plane formed so as to extend in the direction of the central axis CA66.
  • the impeller second plane 662 is provided substantially parallel to the impeller first plane 661.
  • the impeller second plane 662 is provided at a position facing the shaft second plane 524 and can contact the shaft second plane 524 when the shaft 52 rotates.
  • the impeller first curved surface 663 connects one side parallel to the central axis CA66 of the impeller first plane 661 and one side parallel to the central axis CA66 of the impeller second plane 662.
  • the impeller first curved surface 663 is formed so that the cross-sectional shape thereof is a substantially arc shape that protrudes radially outward from a point on the central axis CA66.
  • the impeller first curved surface 663 is formed with a first groove 665 as a “deformation allowance space” substantially at the center (circumferential center).
  • the impeller second curved surface 664 connects another side parallel to the central axis CA66 of the impeller first plane 661 and another side parallel to the central axis CA66 of the impeller second plane 662.
  • the impeller second curved surface 664 is formed so that the cross-sectional shape is a substantially arc shape that protrudes radially outward from a point on the central axis CA66.
  • a second groove 666 is formed as a “deformation allowance space” substantially at the center (circumferential center).
  • the first groove 665 is formed in a slit shape so as to extend radially outward from the impeller first curved surface 663.
  • the first groove 665 is formed to communicate with the fitting hole 66 and penetrates the impeller 65 in the direction of the central axis CA66.
  • the second groove 666 is formed in a slit shape so as to extend radially outward from the impeller second curved surface 664.
  • the second groove 666 is formed to communicate with the fitting hole 66 and penetrates the impeller 65 in the direction of the central axis CA66.
  • the first groove 665 and the second groove 666 are formed so as to extend in opposite directions as viewed from the central axis CA66 and have the same radial length.
  • the shaft first plane 523 formed in the shaft 52 and the impeller first plane 661 forming the fitting hole 66 are parallel to each other.
  • the positional relationship between the shaft second plane 524 formed on the shaft 52 and the impeller second plane 662 forming the fitting hole 66 is preferably parallel.
  • the impeller 65 formed from resin by injection molding is difficult to be molded so as to satisfy these relationships, for example, when the shaft first plane 523 and the impeller first plane 661 are parallel, the shaft second In some cases, the plane 524 and the impeller second plane 662 are not parallel to each other.
  • the shaft first plane 523 and the impeller first plane 661 are parallel, but the shaft second plane 524 and the impeller second plane 662 are in a parallel positional relationship.
  • the fitting hole 66 may be formed such that the intersection line 667 between the impeller second plane 662 and the impeller second curved surface 664 is located away from a point on the center axis CA66 of the fitting hole 66.
  • the shape of the fitting hole 66 is changed and the shaft second plane 524 and the impeller second plane 662 which are separated from each other come into contact with each other.
  • the shapes of the fitting hole 66 and the first groove 665 before the first groove 665 is deformed are indicated by dotted lines.
  • either the impeller first plane 661 or the impeller second plane 662 in which the shaft 52 rotates in the fitting hole 66 and the shaft 52 forms the fitting hole 66.
  • the first groove 665 or the second groove 666 is brought into contact with the first hole 660, the shape of the fitting hole 66 is changed.
  • the shaft second plane 524 or the shaft first plane 523 of the shaft 52 abuts on the impeller second plane 662 or the impeller first plane 661 on which the shaft 52 does not abut, and the shaft 52 Two planes contact the inner wall of the fitting hole 66.
  • the rotational torque of the shaft 52 acts on both the impeller first plane 661 and the impeller second plane 662, and the surface pressure of the rotational torque acting on the impeller 65 is reduced. Therefore, the surface pressure acting on the impeller 65 becomes relatively small, and damage to the impeller 65 due to the rotational torque of the shaft 52 can be effectively suppressed.
  • first groove 665 and the second groove 666 are formed at the center of the impeller first curved surface 663 and the impeller second curved surface 664 facing each other. Further, the first groove 665 and the second groove 666 are formed to extend the same length in opposite directions when viewed from the central axis CA66.
  • FIG. 4 shows a top view of the impeller 67 provided in the fuel pump according to the second embodiment.
  • a fitting hole 68 is formed in the approximate center of the impeller 67.
  • the end portion 522 of the shaft 52 is accommodated in the fitting hole 66.
  • the fitting hole 68 is formed in a substantially I shape so that the cross-sectional shape thereof matches the cross-sectional shape of the end portion 522 of the shaft 52.
  • the fitting hole 68 includes an impeller first flat surface 681 as “impeller side first contact surface or impeller side contact surface” and an impeller second flat surface as “impeller side second contact surface or impeller side contact surface”. 682, an impeller first curved surface 683 as a “fitting hole first forming surface or a fitting hole forming surface”, and an impeller second curved surface 684 as a “fitting hole second forming surface or a fitting hole forming surface”.
  • the impeller first plane 681 is a plane formed so as to extend in the direction of the central axis CA67 of the fitting hole 68.
  • the impeller first plane 681 is provided at a position facing the shaft first plane 523 and can contact the shaft first plane 523 when the shaft 52 rotates.
  • the impeller second plane 682 is a plane formed so as to extend in the direction of the central axis CA67.
  • the impeller second plane 682 is provided substantially parallel to the impeller first plane 681.
  • the impeller second plane 682 is provided at a position facing the shaft second plane 524, and can contact the shaft second plane 524 when the shaft 52 rotates.
  • the impeller first curved surface 683 connects one side parallel to the central axis CA67 of the impeller first plane 681 and one side parallel to the central axis CA67 of the impeller second plane 682.
  • the impeller first curved surface 683 is formed so that the cross-sectional shape is a substantially arc shape that protrudes radially outward from a point on the central axis CA67.
  • the impeller first curved surface 683 is formed with a first groove 685 as a “deformation allowance space” substantially at the center (circumferential center).
  • the impeller second curved surface 684 connects another side parallel to the central axis CA67 of the impeller first plane 681 and another side parallel to the central axis CA67 of the impeller second plane 682.
  • the impeller second curved surface 684 is formed so that the cross-sectional shape is a substantially arc shape that protrudes radially outward from a point on the central axis CA67.
  • the impeller second curved surface 684 is formed with a second groove 686 as a “deformation allowance space” substantially at the center (circumferential center).
  • the first groove 685 is formed in a slit shape so as to extend radially outward from the impeller first curved surface 683.
  • the first groove 685 is formed to communicate with the fitting hole 68 and penetrates the impeller 67 in the direction of the central axis CA67.
  • the second groove 686 is formed in a slit shape so as to extend radially outward from the impeller second curved surface 684.
  • the second groove 686 is formed to communicate with the fitting hole 68 and penetrates the impeller 67 in the direction of the central axis CA67.
  • the first groove 685 and the second groove 686 are formed to extend in opposite directions as viewed from the central axis CA67 and have the same radial length.
  • a virtual circle having a center on the central axis CA67 and connecting radially inner portions of the plurality of inclined surfaces 64 of the impeller 67 in the circumferential direction is referred to as a virtual circle VL64, and the impeller is centered on the central axis CA67.
  • a virtual circle passing on the first curved surface 683 and the impeller second curved surface 684 is a virtual circle VL68
  • a radially outer wall surface 687 of the first groove 685 and a radially outer wall surface 688 of the second groove 686 are shown in FIG.
  • the virtual circle VL64 and the virtual circle VL68 are formed in the radially inward direction from the intermediate virtual circle VL67 that is equidistant in the radial direction (distance D2 in FIG. 4).
  • the first groove 685 and the second groove 686 are formed radially inward from the intermediate virtual circle VL67.
  • the impeller 67 can be appropriately deformed by the action from the shaft 52. Therefore, the fuel pump according to the second embodiment has the same effects as the first embodiment, and has a larger deformation allowance than the first embodiment, and more effectively suppresses damage to the impeller 67 due to the rotational torque of the shaft 52. it can.
  • the third embodiment differs from the first embodiment in the shape of the impeller.
  • symbol is attached
  • the impeller 85 has a plurality of inclined surfaces 84, fitting holes 86, and a plurality of through holes 87 as “deformation allowable spaces”.
  • a plurality of inclined surfaces 84 are formed at positions corresponding to the grooves 63 and the grooves 73 in the same manner as the inclined surface 64 of the first embodiment.
  • the fitting hole 86 is formed in a substantially I shape so that the cross-sectional shape thereof matches the cross-sectional shape of the end portion 522 of the shaft 52, similarly to the fitting hole 66 of the first embodiment.
  • the fitting hole 86 can abut on the impeller first plane 861 and the shaft second plane 524 as “impeller side first abutment surface or impeller side abutment surface” that can abut on the shaft first plane 523. It is formed from the impeller second flat surface 862 as the “impeller side second contact surface or impeller side contact surface”.
  • the through-hole 87 is formed to extend in the direction of the central axis CA85, and penetrates the impeller 85 in the direction of the central axis CA85.
  • six through-holes 87 are provided, and are equidistantly arranged on a circumference centered on a point on the central axis CA85 of the fitting hole 86 in the radially outward direction of the fitting hole 86. positioned.
  • Each of the plurality of through holes 87 is provided so as to be point symmetric with respect to another one through hole 87 with respect to a point on the central axis CA85.
  • the fuel pump according to the third embodiment when the shaft 52 rotates in the fitting hole 86 of the impeller 85, only one of the shaft first plane 523 and the shaft second plane 524 of the shaft 52 is fitted. There is a case where it abuts against an inner wall forming the hole 86. In this case, the shape of the fitting hole 86 changes due to the deformation of the through hole 87, and the inner wall of the shaft 52 that is not in contact with the shaft first plane 523 and the shaft second plane 524 forms the fitting hole 86. Abut. Thereby, the fuel pump according to the third embodiment has the same effects as the effects (a) and (b) of the first embodiment.
  • the plurality of through-holes 87 are equally spaced on a circumference centered on a point on the central axis CA85, and each of the plurality of through-holes 87 has another point on the central axis CA85 as a symmetric point. It is provided so as to be point-symmetric with respect to one through hole 87.
  • FIG. 6 shows a top view of the impeller 88 provided in the fuel pump according to the fourth embodiment.
  • the impeller 88 has a plurality of inclined surfaces 84, fitting holes 86, and a plurality of through holes 89 as “deformation allowable spaces”.
  • the through-hole 89 is formed to extend in the direction of the central axis CA88, and penetrates the impeller 88 in the direction of the central axis CA88.
  • six through-holes 89 are provided, and are equidistantly arranged on a circumference centered on a point on the central axis CA88 of the fitting hole 86 in the radially outward direction of the fitting hole 86. positioned.
  • a virtual circle having a center on the central axis CA88 and connecting radially inner portions of the plurality of inclined surfaces 84 formed on the radially outer side of the impeller 88 in the circumferential direction is referred to as a virtual circle VL84, and the central axis CA88
  • a virtual circle VL86 is defined as an imaginary circle VL86 having a center on the impeller first curved surface 863 as the “fitting hole forming surface” of the fitting hole 86 and the impeller second curved surface 864 as the “fitting hole forming surface”.
  • the through-hole 89 is formed in the radially inward direction from the intermediate virtual circle VL88 located at an equal distance (distance D4 in FIG. 6) in the radial direction from the virtual circle VL84 and the virtual circle VL86.
  • the through hole 89 is formed radially inward from the intermediate virtual circle VL88.
  • the impeller 88 can be appropriately deformed by the action from the shaft 52. Therefore, the fuel pump according to the fourth embodiment has the same effect as that of the third embodiment, and the deformation allowable amount is larger than that of the third embodiment, and the damage of the impeller 88 due to the rotational torque of the shaft 52 is further effectively suppressed. it can.
  • the fifth embodiment differs from the third embodiment in the shape of the end of the shaft and the shape of the impeller.
  • symbol is attached
  • FIG. 7 shows a top view of the impeller 95 provided in the fuel pump according to the fifth embodiment.
  • the impeller 95 includes a plurality of inclined surfaces 94, fitting holes 96, and a plurality of through holes 991 to 995 as “deformation allowable spaces”.
  • a plurality of inclined surfaces 94 are formed at positions corresponding to the grooves 63 formed in the pump cover 60 and the grooves 73 formed in the pump casing 70.
  • the fitting hole 96 is formed in a substantially D shape so that the cross-sectional shape thereof matches the cross-sectional shape of one end 922 of the shaft 92.
  • the fitting hole 96 is an “impeller side third that can abut on a shaft third plane 923 as a“ shaft side third abutment surface or shaft side abutment surface ”provided at one end 922 of the shaft 92.
  • the “third shaft curved surface or the third shaft curved surface or the shaft third curved surface or the impeller third contact surface 961 as a contact surface or an impeller side contact surface” is connected to both ends substantially parallel to the central axis CA95 of the shaft third plane 923 by a curved surface having a substantially arcuate cross section. It is formed from an impeller curved surface 963 as a “fitting hole forming surface” formed along the shaft third curved surface 925 as a “shaft curved surface”.
  • the through holes 991 to 995 are formed to extend in the direction of the central axis CA95, and penetrate the impeller 85 in the direction of the central axis CA95.
  • the impeller 95 has five through holes 991 to 995.
  • the through holes 991 to 995 are located at equal intervals on a circumference centered on a point on the central axis CA 95 of the fitting hole 96 in the radially outward direction of the fitting hole 96.
  • the two through holes 992 and 995 are provided in the vicinity of the portions 962 and 964 where the impeller third plane 961 and the impeller curved surface 963 are connected.
  • a virtual circle having a center on the central axis CA95 and connecting radially inner portions of the plurality of inclined surfaces 94 in the circumferential direction is defined as a virtual circle VL94, and has a center on the central axis CA95 and passes on the impeller curved surface 963.
  • the through holes 991 to 995 are, as shown in FIG. 7, intermediate virtual circles that are equidistant in the radial direction (distance D5 in FIG. 7) from the virtual circle VL94 and the virtual circle VL96. It is formed radially inward from VL98.
  • the impeller 95 is formed such that the fitting hole 96 has a D-shaped cross section with respect to the end 922 of the shaft 92 having a D-shaped cross section.
  • five through holes 991 to 995 of the impeller 95 are formed in accordance with the shape of the fitting hole 96.
  • the shaft third plane 923 is the impeller third plane 961 even if it is a D-shape that abuts only on one side.
  • the impeller 95 can be deformed so as to abut against. Therefore, 5th Embodiment has the same effect as 3rd Embodiment.
  • the through holes 991 to 995 are formed in the radially inward direction from the intermediate virtual circle VL98.
  • the impeller 95 can be appropriately deformed by the action from the shaft 52. Therefore, the fuel pump according to the fifth embodiment can more effectively suppress damage to the impeller 95 due to the rotational torque of the shaft 92.
  • the impeller 95 is formed with five through holes 991 to 995 in accordance with the shape of the fitting hole 96. Thereby, the weight balance of the whole impeller 95 is kept uniform, and it can suppress that malfunctions, such as a vibration, generate
  • first groove and the second groove are provided as the “deformation allowable space”.
  • a plurality of through holes are provided as “deformable spaces”.
  • shape of the “deformable space” is not limited to this. Any space provided on the impeller and capable of being deformed so as to increase the amount of elastic deformation of the impeller when the shaft and the impeller contact each other may be used.
  • the impeller first plane as the impeller second plane as the “impeller side second contact surface” is formed in a planar shape. However, these surfaces do not have to be formed flat. It may be curved, and the “shaft side first contact surface” and the “impeller side first contact surface” can contact each other, and the “shaft side second contact surface” and the “impeller side second contact” What is necessary is just to form so that a contact surface "can contact
  • the first groove and the second groove are formed at the center of the impeller first curved surface and the impeller second curved surface.
  • the place where the first groove and the second groove are formed is not limited to this.
  • the first groove and the second groove have the same radial length and are formed to extend in opposite directions.
  • the relationship between the first groove and the second groove is not limited to this.
  • the plurality of through holes are provided at equal intervals on the circumference centered on the point on the central axis of the impeller, and are arranged symmetrically with respect to each other.
  • the place where the plurality of through holes are arranged is not limited to this.
  • the motor unit included in the fuel pump is a brushless motor.
  • the motor need not be a brushless motor as long as the motor rotates the shaft in two directions, the forward direction and the reverse direction.
  • this indication is not limited to such embodiment, It can implement with a various form in the range which does not deviate from the summary.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2014/004601 2013-09-24 2014-09-08 燃料ポンプ Ceased WO2015045294A1 (ja)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US15/024,132 US20160238016A1 (en) 2013-09-24 2014-09-08 Fuel pump

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2013-196615 2013-09-24
JP2013196615 2013-09-24
JP2014095859A JP6135593B2 (ja) 2013-09-24 2014-05-07 燃料ポンプ
JP2014-095859 2014-05-07

Publications (1)

Publication Number Publication Date
WO2015045294A1 true WO2015045294A1 (ja) 2015-04-02

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JP (1) JP6135593B2 (enExample)
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WO2016208179A1 (ja) * 2015-06-26 2016-12-29 株式会社デンソー 回転子
CN110462220A (zh) * 2017-04-07 2019-11-15 爱三工业株式会社 燃料泵

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JP6064847B2 (ja) * 2013-09-17 2017-01-25 株式会社デンソー 燃料ポンプ
JP6056719B2 (ja) * 2013-09-17 2017-01-11 株式会社デンソー 燃料ポンプ
JP6361583B2 (ja) * 2015-05-28 2018-07-25 株式会社デンソー 燃料ポンプ
JP2016223323A (ja) * 2015-05-28 2016-12-28 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
JP2017008736A (ja) * 2015-06-17 2017-01-12 株式会社デンソー 燃料ポンプ
DE102018202276B4 (de) * 2018-02-14 2023-05-04 Ti Automotive Technology Center Gmbh Flüssigkeitspumpe mit Vibrationsdämpfungselement

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JP6135593B2 (ja) 2017-05-31
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