WO2020149382A1 - Non-positive displacement type pump and liquid supply device - Google Patents

Non-positive displacement type pump and liquid supply device Download PDF

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Publication number
WO2020149382A1
WO2020149382A1 PCT/JP2020/001379 JP2020001379W WO2020149382A1 WO 2020149382 A1 WO2020149382 A1 WO 2020149382A1 JP 2020001379 W JP2020001379 W JP 2020001379W WO 2020149382 A1 WO2020149382 A1 WO 2020149382A1
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WO
WIPO (PCT)
Prior art keywords
impeller
pump
case
suction port
discharge port
Prior art date
Application number
PCT/JP2020/001379
Other languages
French (fr)
Japanese (ja)
Inventor
多津也 蓮子
伸一郎 堀底
直樹 竹内
知司 大村
龍太郎 小林
Original Assignee
株式会社ミツバ
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 株式会社ミツバ filed Critical 株式会社ミツバ
Priority to BR112021014002-6A priority Critical patent/BR112021014002A2/en
Priority to EP20741647.0A priority patent/EP3913228A4/en
Priority to JP2020566487A priority patent/JP7350020B2/en
Priority to CN202080009587.6A priority patent/CN113423956B/en
Publication of WO2020149382A1 publication Critical patent/WO2020149382A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/08—Feeding by means of driven pumps electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/08—Feeding by means of driven pumps electrically driven
    • F02M37/10—Feeding by means of driven pumps electrically driven submerged in fuel, e.g. in reservoir
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides 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
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing 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
    • 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 non-positive displacement pump and a liquid supply device.
  • the non-volumetric pump includes a substantially disk-shaped impeller and a pump case formed so as to cover the entire impeller.
  • the impeller has a plurality of blades formed side by side in the circumferential direction.
  • a plurality of through-flow passages that penetrate the impeller in the plate thickness direction are formed between the blade portions.
  • the pump case houses the impeller rotatably. Further, the pump case has a suction port and a discharge port which are arranged on both sides of the impeller.
  • a non-volume pump is used as a liquid supply device (fuel pump) for vehicles such as motorcycles and four-wheeled vehicles. This type of liquid supply device is arranged in a fuel tank.
  • a seal is provided between the discharge port and the suction port in the direction of rotation of the impeller so that the discharge port and the suction port do not communicate with each other.
  • the circumferential length of the seal portion determines the flow rate characteristic of the non-displacement type pump. That is, if the length of the seal portion in the circumferential direction is short, the amount of fuel drawn into the through passage of the impeller is increased by that much, so that the discharge flow rate of the non-volumetric pump is increased. On the other hand, if the length of the seal portion in the circumferential direction is long, the amount of fuel drawn into the through flow passage of the impeller is reduced by that amount, so the discharge flow rate of the non-volumetric pump is reduced.
  • one of the objects of the present invention is to provide a non-volume pump and a liquid supply device capable of reducing noise during driving while ensuring an appropriate discharge flow rate.
  • the non-positive displacement pump according to the first aspect of the present invention is A disc-shaped impeller, A pump case formed so as to cover the entire impeller and rotatably accommodating the impeller with a radial center of the impeller as a rotation center;
  • the impeller is A plurality of blade portions formed side by side in the circumferential direction, near the outer peripheral portion of the impeller, A plurality of through-flow passages formed between the blade portions adjacent to each other in the circumferential direction and penetrating the impeller in the plate thickness direction
  • the pump case is A storage unit for storing the impeller, A suction port that penetrates the storage portion and the outside of the pump case in the plate thickness direction of the impeller, and that communicates with the through-flow passage, Disposed on the opposite side of the suction port with the impeller interposed therebetween, while penetrating the storage part and the outside of the pump case in the plate thickness direction, a discharge port communicating with the through flow passage, A seal portion provided between the suction port and the discharge port in the circumfer
  • the pump case is An upper case that is in sliding contact with one surface of the impeller and covers the one surface, A lower case that is in sliding contact with the other surface of the impeller opposite to the one surface, and covers the other surface,
  • the storage portion is defined by the upper case and the lower case,
  • the upper case is The discharge port, An arc-shaped first flow path groove provided on a first sliding contact surface facing the impeller and communicating with the discharge port,
  • the lower case is The inlet, An arc-shaped second flow path groove provided on a second sliding contact surface facing the impeller and communicating with the suction port,
  • the seal portion is It is between the discharge port and the suction port and on the rotation trajectory of the through-flow passage.
  • the liquid supply apparatus is The non-positive displacement pump according to the first aspect or the second aspect, A motor unit for driving the non-positive displacement pump, The rotation shaft of the motor unit and the impeller are connected so as not to rotate relative to each other.
  • an appropriate discharge flow rate of the non-displacement pump can be secured. Further, the circumferential distance of the seal portion can be made appropriate, and the reduced pressure boiling of the liquid sent from the discharge port to the suction port can be suppressed. Therefore, it is possible to reduce noise when the non-displacement pump is driven.
  • FIG. 1 is a perspective view of a liquid supply device according to an embodiment of the present invention.
  • FIG. 2 is a sectional view taken along the axial direction of the liquid supply apparatus according to the embodiment of the present invention.
  • FIG. 3 is a perspective view of the impeller according to the embodiment of the present invention.
  • FIG. 4 is a plan view of the upper case according to the embodiment of the present invention viewed from the lower case side.
  • FIG. 5 is a plan view of the lower case according to the embodiment of the present invention as viewed from the upper case side.
  • FIG. 6 is a schematic view of a cross section taken along the axial direction of the pump unit according to the embodiment of the present invention.
  • FIG. 7 is a graph comparing the discharge flow rate of fuel in the case where each sealing portion according to the embodiment of the present invention meets and does not satisfy the sealing condition.
  • FIG. 8 is a graph showing changes in the fuel discharge flow rate and the fuel sound pressure level in the embodiment of the present invention.
  • FIG. 1 is a perspective view of the liquid supply apparatus 1.
  • FIG. 2 is a sectional view taken along the axial direction of the liquid supply apparatus 1.
  • the liquid supply device 1 is used as a fuel pump for vehicles such as motorcycles and four-wheeled vehicles.
  • the liquid supply device 1 is a so-called in-tank type fuel pump arranged in a fuel tank (not shown).
  • the liquid supply device 1 is fitted into the substantially cylindrical metal housing 2 and the inner peripheral surface of the housing 2, and is arranged side by side in the axial direction of the housing 2.
  • the motor unit 3 and the pump unit 4 are provided.
  • the housing 2, the motor unit 3, and the pump unit 4 are arranged coaxially.
  • the liquid supply apparatus 1 is used with the pump unit 4 facing downward in the gravity direction. Therefore, in the following description, the motor unit 3 side may be referred to as the upper side and the pump unit 4 side may be referred to as the lower side.
  • the axial direction of the housing 2, the motor unit 3, and the pump unit 4 is simply the axial direction
  • the radial direction of the housing 2, the motor unit 3, and the pump unit 4 is simply the radial direction, the housing 2, and the motor unit.
  • the circumferential direction of 3 and the pump portion 4 is simply referred to as the circumferential direction.
  • the housing 2 has a motor fitting portion 11 into which the motor portion 3 is fitted, a pump fitting portion 12 into which the pump portion 4 is fitted, the diameter of which is reduced through a step from the motor fitting portion 11. Is integrally molded.
  • a positioning projection 13 is formed on the inner peripheral surface of the pump fitting portion 12 so as to project inward in the radial direction.
  • the positioning protrusion 13 is formed by pressing the housing 2 from the outside in the radial direction by, for example, pressing.
  • the positioning protrusion 13 positions the housing 2 and the pump unit 4 in the circumferential direction.
  • the positioning protrusion 13 is formed in a rectangular shape that is long in the axial direction when viewed in the radial direction.
  • an inner flange portion 12a that extends inward in the radial direction is bent and extends from the lower end of the pump fitting portion 12 in the housing 2.
  • the positioning protrusion 13 and the inner flange 12a position the housing 2 and the pump 4 in the axial direction.
  • the motor unit 3 for example, a brushed motor is adopted.
  • the motor unit 3 closes a substantially cylindrical yoke 5, a permanent magnet 8 provided on the inner peripheral surface of the yoke 5, an armature 6 rotatably provided in the yoke 5, and an upper opening 5 a of the yoke 5.
  • the outlet cover 7 and the brush 25 housed in the outlet cover 7 are the main components.
  • the outer peripheral surface of the yoke 5 is fitted to the inner peripheral surface of the housing 2.
  • the yoke 5 serves as a magnetic path through which the magnetic flux of the permanent magnet 8 passes.
  • the upper opening 5a of the yoke 5 is fitted to the outer peripheral surface of a spigot portion 31 of the outlet cover 7, which will be described later.
  • Positioning of the outlet cover 7 and the yoke 5 in the circumferential direction is carried out by concave and convex fitting between a positioning projection (not shown) formed on the outlet cover 7 and a yoke positioning recess (not shown) formed on the yoke 5.
  • Two permanent magnets 8 are provided on the inner peripheral surface of the yoke 5.
  • the permanent magnet 8 is formed in a substantially semicircular shape along the inner peripheral surface of the yoke 5 when viewed in the axial direction.
  • the axial length of the permanent magnet 8 is set longer than the axial length of the armature core 15.
  • the permanent magnets 8 are arranged so that both axial ends thereof protrude (overhang) from both axial ends of the armature core 15.
  • the magnetic field orientation of the permanent magnet 8 is along the radial direction (the thickness direction of the permanent magnet 8).
  • Such permanent magnets 8 are arranged to face each other in the radial direction around the rotary shaft 14.
  • a minute gap is formed between the inner peripheral surface of the permanent magnet 8 and the radially outer end of the tooth 17 and the resin mold portion 22 of the armature core 15 which will be described later.
  • the armature 6 is fitted and fixed to the rotating shaft 14, the armature core 15 fitted and fixed to the outer peripheral surface of the rotating shaft 14, and the outer peripheral surface of the rotating shaft 14 closer to the outlet cover 7 than the armature core 15.
  • the commutator 16 is mainly used.
  • the armature core 15 has a plurality of teeth 17 that radially extend outward in the radial direction. Winding wires (not shown) are wound around these teeth 17. The end portion of the winding (not shown) is connected to the commutator 16.
  • the commutator 16 is a so-called disc type commutator having a resin-made commutator main body 18 formed in a substantially disc shape. A plurality of segments 19 are arranged side by side in the circumferential direction on one surface 18a of the commutator body 18 opposite to the armature core 15.
  • a riser 21 that is bent and extends toward the armature core 15 side through the outer peripheral surface of the commutator body 18 is integrally formed at the radially outer end of the segment 19.
  • One end of a winding (not shown) is connected to each riser 21.
  • the resin mold portion 22 is formed in a substantially columnar shape. Further, the resin mold portion 22 extends from the pump portion 4 side with respect to the armature core 15 to approximately the center in the axial direction of the commutator body 18. Only the radially outer ends (outer peripheral surface) of the teeth 17 of the armature core 15 are exposed, and the winding wire (not shown) is buried in the resin mold portion 22. A round chamfered portion 22a is formed at a corner portion of the end of the resin mold portion 22 on the pump portion 4 side. As a result, the end of the resin mold portion 22 on the pump portion 4 side is tapered.
  • the outlet cover 7 is formed in a substantially bottomed tubular shape having an opening 7a on the armature core 15 side.
  • the bottom cylindrical portion 7b of the outlet cover 7 is integrally formed with a bearing cylindrical portion 23 projecting toward the armature core 15 side at a substantially radial center thereof.
  • the upper end portion 14a of the rotary shaft 14 is rotatably supported by the bearing cylindrical portion 23.
  • brush holders 24 are integrally formed on the bottom portion 7b of the outlet cover 7 on both sides of the bearing cylindrical portion 23.
  • the brush holder 24 is formed in a box shape having an opening on the commutator 16 side.
  • the brush 25 is accommodated in the brush holder 24 so as to be slidable along the axial direction.
  • a coil spring 26 is stored in the brush holder 24 in a compressed and deformed form.
  • the brush 25 is biased toward the commutator 16 side by a coil spring 26.
  • the tip of the brush 25 projects from the brush holder 24 and is in sliding contact with the segment 19.
  • the bottom portion 7b of the outlet cover 7 is provided with a terminal 27 that vertically penetrates the bottom portion 7b.
  • the brush 25 is connected to the terminal 27 via a pigtail (not shown).
  • An external power source (not shown) is connected to the terminal 27.
  • external power is supplied to the winding (not shown) via the terminal 27, the pigtail (not shown), the brush 25, and the segment 19.
  • a discharge port 28 protruding upward is integrally formed on the bottom portion 7b of the outlet cover 7.
  • the discharge port 28 is a portion where the fuel pumped up by the liquid supply device 1 is discharged, and is connected to a fuel flow path (not shown). Further, the inside and outside of the outlet cover 7 are communicated with each other via the discharge port 28.
  • a positioning piece 32 extending downward is integrally formed on the peripheral wall 7c of the outlet cover 7.
  • the positioning piece 32 is interposed between the permanent magnets 8 and positions the permanent magnet 8 (yoke 5) and the outlet cover 7.
  • the peripheral wall 7c of the outlet cover 7 is formed with a fitting ridge portion 29 over the entire outer peripheral surface so as to project radially outward.
  • the outer diameter of the fitting protruding portion 29 is set to be substantially the same as the inner diameter of the motor fitting portion 11 in the housing 2.
  • the outer peripheral surface of the fitting convex strip 29 is fitted to the inner peripheral surface of the motor fitting portion 11.
  • the upper opening edge 11a of the motor fitting portion 11 is caulked inward in the radial direction from above the fitting protruding portion 29 of the outlet cover 7.
  • a lower part of the peripheral wall 7c of the outlet cover 7 below the fitting protrusion part 29 is an inlay part 31 which is inlay-fitted with the yoke 5.
  • the lower end of the rotary shaft 14 is inserted into the pump unit 4.
  • a non-volume pump having an impeller 40 is used as the pump unit 4.
  • the pump unit 4 includes an impeller 40 and a pump case 41 formed so as to cover the entire impeller 40.
  • the pump case 41 is fitted into the pump fitting portion 12 of the housing 2.
  • FIG. 3 is a perspective view of the impeller 40.
  • the impeller 40 is a member made of a resin material and formed into a substantially disc shape.
  • An insertion hole 61 through which the lower end portion 14b of the rotary shaft 14 can be inserted is formed at a substantially center of the impeller 40 in the radial direction.
  • the lower end portion 14b of the rotary shaft 14 is formed in a substantially D-shaped cross section orthogonal to the axial direction.
  • the insertion hole 61 of the impeller 40 is formed in a substantially D shape when viewed in the axial direction so as to correspond to the cross-sectional shape of the lower end portion 14b of the rotary shaft 14.
  • a plurality of blade portions 62 (see also FIG. 6) having a substantially L-shaped cross section along the axial direction are formed near the outer peripheral portion of the impeller 40.
  • the blade portions 62 are arranged side by side at equal intervals in the circumferential direction so that the circumferential directions are the same.
  • a through passage 63 is formed between the blade portions 62 adjacent to each other in the circumferential direction. The through flow passage 63 penetrates in the plate thickness direction of the impeller 40.
  • the pump case 41 that covers the entire impeller 40 includes an upper case 43, a middle case 44, and a lower case 42.
  • FIG. 4 is a plan view of the upper case 43 viewed from the lower case 42 side (downward).
  • the upper case 43 is disposed on the motor section 3 side of the impeller 40.
  • the upper case 43 is formed in a substantially disc shape so as to cover the upper surface of the impeller 40.
  • a middle case 44 is joined to the outer peripheral portion of the upper case 43.
  • the outer diameter of the upper case 43 is set to be slightly smaller than the outer diameter of the yoke 5.
  • An insertion hole 46 through which the lower end portion 14b of the rotary shaft 14 can be inserted is formed at the center of the upper case 43 in the radial direction.
  • the rotary shaft 14 is rotatably supported in the insertion hole 46 via a slide bearing 59.
  • a substantially annular recess 47 is formed so as to surround the periphery of the insertion hole 46 when viewed in the axial direction.
  • the outer peripheral side of the recess 47 is a contact surface 43b with which the yoke 5 contacts. Since a sufficient space is secured for the contact surface 43b, buckling deformation of the contact surface 43b and the yoke 5 is suppressed even when the lower end of the yoke 5 is contacted with the contact surface 43b. It
  • a discharge port 48 penetrating the upper case 43 in the vertical direction is formed near the outer periphery of the recess 47.
  • a concave portion 48a that widens the opening of the ejection port 48 is formed at the periphery of the ejection port 48.
  • the recess 48a is formed so as to widen toward the lower surface 43c of the upper case 43.
  • the lower surface 43c of the upper case 43 is a first sliding contact surface 43d that is in sliding contact with the impeller 40.
  • a first flow channel groove 64 having a substantially arc shape (substantially C-shaped) when viewed from the axial direction is formed at a position facing the through flow channel 63 of the impeller 40 in the axial direction. ..
  • One end of the first flow path groove 64 in the circumferential direction is communicated with the discharge port 48 (recessed portion 48a).
  • a tapered portion 64a is formed at the other end of the first flow path groove 64 in the circumferential direction so as to be tapered when viewed in the axial direction.
  • the middle case 44 is formed in a substantially ring shape so as to surround the outer peripheral surface of the impeller 40.
  • the middle case 44 is formed integrally with the upper case 43.
  • the outer diameter of the middle case 44 is set to be slightly larger than the outer diameter of the upper case 43.
  • the thickness of the middle case 44 in the axial direction is formed to be substantially the same as or slightly larger than the plate thickness of the impeller 40.
  • FIG. 5 is a plan view of the lower case 42 seen from the upper case 43 side (upper side).
  • the lower case 42 is shown to be generally coincident.
  • the lower case 42 is arranged below the impeller 40.
  • the pump case 41 is formed by an upper case 43 integrally formed with a middle case 44 and a lower case 42 so as to cover the entire impeller 40.
  • the lower surface 43c of the upper case 43 and the upper surface 42a of the lower case 42 form a storage portion 60 that stores the impeller 40.
  • the lower case 42 is formed in a substantially disc shape.
  • the outer diameter of the lower case 42 is set to be substantially the same as the outer diameter of the middle case 44.
  • a substantially cylindrical suction port 53 protruding downward is formed on the outer peripheral side.
  • a tapered hole portion 53a is formed on the upper surface 42a side of the lower case 42 so that the opening area gradually increases toward the upper surface 42a.
  • a step portion 49 is formed on the outer peripheral edge of the lower surface 42b of the lower case 42. The step portion 49 is formed by reducing the diameter of the lower case 42 on the lower surface 42b side. The step portion 49 is formed at a position overlapping the inner flange portion 12a of the housing 2 when viewed in the axial direction.
  • the upper surface 42a of the lower case 42 is a second sliding contact surface 42c that is in sliding contact with the impeller 40.
  • a bearing accommodating recess 54 is formed at a substantially radial center thereof so that the lower end portion 14b of the rotary shaft 14 is exposed.
  • the thrust bearing 55 is housed in the bearing housing recess 54.
  • the lower end portion 14b of the rotary shaft 14 is rotatably supported by the lower case 42 while being in contact with the thrust bearing 55.
  • the thrust bearing 55 receives the thrust load of the rotary shaft 14.
  • the second sliding contact surface 42c of the lower case 42 is substantially axially opposed to the through passage 63 of the impeller 40 and to the first passage groove 64 of the upper case 43 in the axial direction.
  • An arcuate (substantially C-shaped) second flow path groove 65 is formed.
  • One end of the second flow path groove 65 in the circumferential direction is communicated with the suction port 53 (tapered hole portion 53a).
  • a tapered portion 65a is formed so as to be tapered when viewed in the axial direction.
  • a deaeration hole 68 is formed so as to penetrate in the plate thickness direction of the lower case 42, slightly closer to the suction port 53 than the center between the suction port 53 and the tapered portion 65a.
  • the deaeration hole 68 is a hole for discharging vapor (air bubbles) generated in the pump case 41.
  • the discharge port 48 communicated with one end in the circumferential direction of the first flow channel 64, the tapered portion 64 a formed at the other end in the circumferential direction of the first flow channel 64, and the second flow channel 65.
  • the suction port 53 which communicates with one end in the circumferential direction, and the tapered portion 65a, which is formed at the other end in the circumferential direction of the second flow channel groove 65, are arranged alternately. That is, the discharge port 48 axially faces the tapered portion 65a of the second flow path groove 65.
  • the suction port 53 axially faces the tapered portion 64a of the first flow channel 64.
  • the first seal portion 66 for performing the operation is provided between the suction port 53 (tapered hole portion 53a) in the second sliding contact surface 42c of the lower case 42 and the tapered portion 65a of the second flow path groove 65. Between the suction port 53 (tapered hole portion 53a) in the second sliding contact surface 42c of the lower case 42 and the tapered portion 65a of the second flow path groove 65, fuel leakage from the tapered portion 65a to the suction port 53 is suppressed.
  • the second seal portion 67 for The circumferential range (length) of the first seal portion 66 and the circumferential range (length) of the second seal portion 67 match.
  • first seal portion 66 and the second seal portion 67 Details of the first seal portion 66 and the second seal portion 67 will be described later. As can be understood from FIG. 6, the first seal portion 66 and the second seal portion 67 are located between the discharge port 48 and the suction port 53 and on the rotation trajectory of the through passage 63.
  • a square ring 50 as a seal member is attached to the step portion 49 formed on the lower surface 42b of the lower case 42.
  • the square ring 50 is a member having a substantially rectangular cross section and made of a material having excellent oil resistance such as fluororubber.
  • the outer diameter of the square ring 50 is set to be slightly smaller than the outer diameter of the lower case 42. For this reason, the outer peripheral surfaces of the upper case 43, the middle case 44, and the lower case 42 are fitted to the pump fitting portion 12 of the housing 2.
  • a minute gap is formed between the outer peripheral surface of the square ring 50 and the inner peripheral surface of the pump fitting portion 12 of the housing 2.
  • the square ring 50 is brought into contact with the inner flange portion 12a of the housing 2.
  • the positioning protrusion 13 of the housing 2 is inserted into a recess (not shown) formed on the outer peripheral surface of the pump case 41.
  • the housing 2 and the pump portion 4 are positioned in the circumferential direction.
  • the upper opening edge 11a of the motor fitting portion 11 is fitted to the fitting ridge portion of the outlet cover 7 while the square ring 50 is slightly crushed by the step portion 49 of the lower case 42 and the inner flange portion 12a. From above 29, crimp inward in the radial direction.
  • the pump portion 4 is fitted into the pump fitting portion 12 of the housing 2.
  • the motor portion 3 is fitted into the motor fitting portion 11 of the housing 2. Then, the motor part 3 and the pump part 4 are positioned with respect to the housing 2, and the housing 2, the motor part 3 and the pump part 4 are integrated. Further, the square ring 50 ensures the sealing property between the housing 2 and the pump portion 4.
  • FIG. 6 is a schematic view of a cross section along the axial direction of the pump unit 4.
  • the impeller 40 is rotated integrally with the rotating shaft 14.
  • the fuel N is sucked up into the pump case 41 through the suction port 53.
  • the sucked fuel N enters the through passage 63 of the impeller 40, and further enters the first passage groove 64 of the upper case 43 and the second passage groove 65 of the lower case 42.
  • a swirling flow is generated between the impeller 40 and the pump case 41. Due to this swirling flow, the pressure of the fuel in the through passage 63 is increased toward the discharge port 48.
  • the boosted fuel N is discharged into the yoke 5 of the motor unit 3 through the discharge port 48. That is, the pressure of the fuel N at the discharge port 48 is higher than the pressure of the fuel N at the suction port 53.
  • a first seal portion 66 and a second seal portion 67 are provided between the discharge port 48 and the suction port 53. Therefore, the fuel N discharged from the discharge port 48 may leak to a portion of the suction port 53, the first flow channel 64, and the second flow channel 65 that intersects the suction port 53 in the axial direction. It is suppressed.
  • the fuel N discharged into the yoke 5 is pressure-fed to the discharge port 28 through a minute gap between the permanent magnet 8 and the resin mold portion 22 (radially outer ends of the teeth 17 of the armature core 15). Then, the fuel is pressure-fed to the engine (not shown) or the like via the discharge port 28.
  • the circumferential range (length) of the first seal portion 66 and the circumferential range (length) of the second seal portion 67 are set as follows. It is set.
  • a straight line connecting both circumferential ends of the first seal portion 66 and the axis C of the rotary shaft 14 is defined as L1.
  • the both ends in the circumferential direction of the first seal portion 66 are a portion where the straight line L1 passing through the axis C contacts the tapered portion 64a of the first flow path groove 64 and a portion where the straight line L1 contacts the recess 48a of the discharge port 48. ..
  • a straight line connecting both circumferential ends of the second seal portion 67 and the axis C of the rotary shaft 14 is defined as L2.
  • the both ends in the circumferential direction of the second seal portion 67 are locations where the straight line L2 passing through the axis C contacts the tapered portion 65a of the second flow channel groove 65 and the taper hole portion 53a of the suction port 53.
  • the angles ⁇ 1 and ⁇ 2 are set so that 43° ⁇ 1 ⁇ 47° and 43° ⁇ 2 ⁇ 47°.
  • the first seal portion 66 and the second seal portion 67 are formed in a size capable of closing at least two through flow passages 63 between both ends in the circumferential direction.
  • the condition of each of the seal portions 66 and 67 having a size capable of closing the at least two through-flow passages 63 and satisfying the above expression (1) is referred to as a seal condition hereinafter.
  • FIG. 7 when the vertical axis represents the fuel discharge flow rate (hereinafter, simply referred to as fuel discharge flow rate) [L/h] by the pump unit 4, it does not satisfy the case where the seal portions 66 and 67 satisfy the seal condition. It is a graph which compared the discharge flow rate of fuel with the case.
  • “conventional” means that the angle ⁇ 1 between the two straight lines L1 of the first seal portion 66 is 22° and the angle ⁇ 2 between the two straight lines L2 of the second seal portion 67 is 24. This is the case.
  • the “conventional” angles ⁇ 1 and ⁇ 2 do not satisfy the above equation (1).
  • the vertical axis represents the fuel discharge flow rate [L/h] and the fuel sound pressure level [dB] near the suction port 53 when high-pressure fuel has been sent to the suction port 53.
  • 6 is a graph showing changes in the fuel discharge flow rate and the fuel sound pressure level when the axes are angles ⁇ 1 and ⁇ 2 [°] between the two straight lines L1 and L2 of the seal portions 66 and 67. As shown in FIG. 8, within the range in which the angles ⁇ 1 and ⁇ 2 between the two straight lines L1 and L2 of the respective seal portions 66 and 67 satisfy the above equation (1), while satisfying the desired discharge flow rate range W, It can be confirmed that the sound pressure level of can be reduced.
  • the range W of the discharge flow rate is defined as a range in which an acceptable sound pressure level and a practically desirable discharge flow rate can be achieved when the liquid supply apparatus 1 of this type is actually used.
  • the pump portion 4 when each of the seal portions 66 and 67 satisfies the seal condition, the pump portion 4 can secure an appropriate fuel discharge flow rate. Further, the angles ⁇ 1 and ⁇ 2 between the two straight lines L1 and L2 of the seal portions 66 and 67 satisfy the above equation (1), so that the circumferential range (length) of the seal portions 66 and 67 is appropriate. You can As a result, depressurization boiling of the fuel sent from the discharge port 48 to the suction port 53 can be suppressed, the sound pressure level of the pump unit 4 can be reduced, and the noise when the pump unit 4 is driven can be reduced.
  • the pump case 41 of the pump unit 4 has an upper case 43 that covers the upper surface of the impeller 40 and a lower case 42 that covers the lower surface of the impeller 40.
  • the upper case 43 has a discharge port 48 for discharging fuel from the pump unit 4, and a first flow path groove 64 formed in the first sliding contact surface 43d.
  • the lower case 42 has a suction port 53 for sucking fuel into the pump portion 4, and a second flow path groove 65 formed in the second sliding contact surface 42c.
  • the first seal portion 66 is formed between the discharge port 48 (recess 48 a) on the first sliding contact surface 43 d of the upper case 43 and the tapered portion 64 a of the first flow path groove 64.
  • a second seal portion 67 is formed between the suction port 53 (taper hole portion 53a) on the second sliding contact surface 42c of the lower case 42 and the tapered portion 65a of the second flow path groove 65.
  • the liquid supply device 1 used as a fuel pump for a vehicle such as a motorcycle or a four-wheel vehicle has been described.
  • the liquid supply device 1 can be used to pump various liquids.
  • the pump case 41 is configured by the upper case 43, the middle case 44, and the lower case 42 has been described.
  • the present invention is not limited to this, and the integrated upper case 43 and middle case 44 may be referred to as one upper case 43.
  • the pump case 41 only needs to have the storage portion 60 that rotatably stores the impeller 40, and may not be divided into the upper case 43 and the lower case 42.
  • the middle case 44 and the lower case 42 may be integrated, and the middle case 44 and the lower case 42 may be referred to as one lower case 42.
  • the non-positive displacement pump and the liquid supply device of the present invention for example, it is possible to suppress the depressurization boiling of the liquid leaked from the discharge port to the suction port while appropriately ensuring the discharge flow rate.
  • the present invention having this effect is useful for a fuel pump for vehicles such as motorcycles and four-wheeled vehicles.
  • SYMBOLS 1 Liquid supply device, 3... Motor part, 4... Pump part (non-volume pump), 14... Rotation shaft, 40... Impeller, 41... Pump case, 42... Lower case, 42c... 2nd sliding contact surface, 43... Upper case, 43d... First sliding contact surface, 48... Discharge port, 53... Suction port, 60... Storage section, 62... Blade section, 63... Through channel, 64... First channel groove, 65... Second flow Road groove, 66... First seal part (seal part), 67... Second seal part (seal part), C... Shaft center (rotation center), L1, L2... Straight line, ⁇ 1, ⁇ 2... Angle

Abstract

A pump unit (4), which is a non-positive displacement type pump provided in a liquid supply device (1), has a first seal section (66) and a second seal section (67) provided between an intake port (53) and a discharge port (48) in the circumferential direction of an impeller (40). An angle between the two straight lines connecting the circumferential ends of each seal portion (66, 67) and the center of rotation of the impeller (40) is 43° or more and 47° or less. Each seal portion (66, 67) has a size making it possible to close at least two through flow paths (63) between both ends in the circumferential direction.

Description

非容積型ポンプ及び液体供給装置Non-volume pump and liquid supply device
　本発明は、非容積型ポンプ及び液体供給装置に関する。 The present invention relates to a non-positive displacement pump and a liquid supply device.
　非容積型ポンプは、略円板状のインペラと、インペラの全体を覆うように形成されたポンプケースと、を備えている。インペラには、複数の羽根部が周方向に並んで形成されている。各羽根部の間には、インペラを板厚方向に貫通する複数の貫通流路が形成されている。ポンプケースは、インペラを回転自在に収容する。また、ポンプケースは、インペラを挟んで両側に配置された吸入口、及び吐出口を有している。
　このような非容積型ポンプは、例えば自動二輪車や四輪車等の車両用の液体供給装置（燃料ポンプ）として用いられる。この種の液体供給装置は、燃料タンク内に配置される。 The non-volumetric pump includes a substantially disk-shaped impeller and a pump case formed so as to cover the entire impeller. The impeller has a plurality of blades formed side by side in the circumferential direction. A plurality of through-flow passages that penetrate the impeller in the plate thickness direction are formed between the blade portions. The pump case houses the impeller rotatably. Further, the pump case has a suction port and a discharge port which are arranged on both sides of the impeller.
Such a non-volume pump is used as a liquid supply device (fuel pump) for vehicles such as motorcycles and four-wheeled vehicles. This type of liquid supply device is arranged in a fuel tank.
　このような構成のもと、インペラを回転させると、ポンプケースの吸入口を介してインペラの貫通流路に燃料が入り込む。貫通流路に入り込んだ燃料は、インペラの回転に伴って圧縮されながら吐出口へと送られる。この後、吐出口から燃料が吐出される。燃料が吐出された貫通流路には、インペラの回転に伴って再び吸入口を介して燃料が入り込む。 Under this structure, when the impeller is rotated, fuel enters the impeller through passage through the suction port of the pump case. The fuel that has entered the through passage is sent to the discharge port while being compressed as the impeller rotates. Then, the fuel is discharged from the discharge port. The fuel again flows into the through-flow passage from which the fuel has been discharged, through the suction port as the impeller rotates.
　ここで、インペラの回転方向に向かって吐出口から吸入口に至る間は、吐出口と吸入口とが連通しないようにシール部とされている。シール部を設けることにより、吐出口の燃料が吸入口側へと漏出されてしまうことを抑制できる。また、シール部の周方向の長さによって、非容積型ポンプの流量特性が決定される。すなわち、シール部の周方向の長さが短いと、この分インペラの貫通流路に引き込める燃料が増大されるので、非容積型ポンプの吐出流量が増大される。これに対し、シール部の周方向の長さが長いと、この分インペラの貫通流路に引き込める燃料が減少されるので、非容積型ポンプの吐出流量が減少される。 　Here, a seal is provided between the discharge port and the suction port in the direction of rotation of the impeller so that the discharge port and the suction port do not communicate with each other. By providing the seal portion, it is possible to prevent the fuel at the discharge port from leaking to the suction port side. Further, the circumferential length of the seal portion determines the flow rate characteristic of the non-displacement type pump. That is, if the length of the seal portion in the circumferential direction is short, the amount of fuel drawn into the through passage of the impeller is increased by that much, so that the discharge flow rate of the non-volumetric pump is increased. On the other hand, if the length of the seal portion in the circumferential direction is long, the amount of fuel drawn into the through flow passage of the impeller is reduced by that amount, so the discharge flow rate of the non-volumetric pump is reduced.
日本国特許第４９５２１８０号公報Japanese Patent No. 4952180 日本国特開２０１５－８６８０４号公報Japanese Patent Laid-Open No. 2015-86804
　しかしながら、上述の従来技術にあっては、吐出口でインペラの貫通流路から完全に燃料が排出しきれず、そのまま圧力の高い燃料が吸入口まで送られると、吸入口で急激に燃料が低圧となり、減圧沸騰が生じる可能性があった。この際の燃料の圧力変動により、騒音が発生する可能性があった。 However, in the above-mentioned conventional technique, when the fuel cannot be completely discharged from the through-flow passage of the impeller at the discharge port and the high-pressure fuel is sent to the suction port as it is, the fuel rapidly becomes low pressure at the suction port. There was a possibility that reduced pressure boiling could occur. At this time, noise may be generated due to the fuel pressure fluctuation.
　そこで、本発明の目的の一つは、適正な吐出流量を確保しつつ、駆動時の騒音を低減できる非容積型ポンプ及び液体供給装置を提供することである。 Therefore, one of the objects of the present invention is to provide a non-volume pump and a liquid supply device capable of reducing noise during driving while ensuring an appropriate discharge flow rate.
　本発明の第１の側面に係る非容積型ポンプは、
　円板状のインペラと、
　前記インペラの全体を覆うように形成され、前記インペラの径方向中心を回転中心とし
て前記インペラを回転自在に収容したポンプケースと、を備え、
　前記インペラは、
　前記インペラの外周部寄りに、周方向に並んで形成された複数の羽根部と、
　前記周方向に隣接する前記羽根部の間に形成され、前記インペラを板厚方向に貫通する複数の貫通流路と、を有し、
　前記ポンプケースは、
　前記インペラを収納する収納部と、
　前記収納部と前記ポンプケースの外側とを前記インペラの板厚方向に貫通するとともに、前記貫通流路に連通する吸入口と、
　前記インペラを挟んで前記吸入口とは反対側に配置され、前記収納部と前記ポンプケースの外側とを前記板厚方向に貫通するとともに、前記貫通流路に連通する吐出口と、
　前記周方向における前記吸入口と前記吐出口との間に設けられるシール部と、を有し、
　前記シール部の前記周方向における両端と、前記回転中心と、を結ぶ２つの直線の間の角度は、４３°以上４７°以下であり、
　前記シール部は、前記両端の間に少なくとも２つの前記貫通流路を閉塞可能な大きさを有する。 The non-positive displacement pump according to the first aspect of the present invention is
A disc-shaped impeller,
A pump case formed so as to cover the entire impeller and rotatably accommodating the impeller with a radial center of the impeller as a rotation center;
The impeller is
A plurality of blade portions formed side by side in the circumferential direction, near the outer peripheral portion of the impeller,
A plurality of through-flow passages formed between the blade portions adjacent to each other in the circumferential direction and penetrating the impeller in the plate thickness direction,
The pump case is
A storage unit for storing the impeller,
A suction port that penetrates the storage portion and the outside of the pump case in the plate thickness direction of the impeller, and that communicates with the through-flow passage,
Disposed on the opposite side of the suction port with the impeller interposed therebetween, while penetrating the storage part and the outside of the pump case in the plate thickness direction, a discharge port communicating with the through flow passage,
A seal portion provided between the suction port and the discharge port in the circumferential direction,
An angle between two straight lines connecting both ends of the seal portion in the circumferential direction and the rotation center is 43° or more and 47° or less,
The seal part has a size capable of closing at least two of the through flow paths between the both ends.
　このように構成することで、非容積型ポンプの適正な吐出流量を確保できる。また、シール部の周方向の距離を適正にでき、吐出口から吸入口に送られる液体の減圧沸騰を抑制できる。このため、非容積型ポンプの駆動時の騒音を低減できる。 With this configuration, it is possible to secure the proper discharge flow rate of the non-displacement type pump. Further, the circumferential distance of the seal portion can be made appropriate, and the reduced pressure boiling of the liquid sent from the discharge port to the suction port can be suppressed. Therefore, it is possible to reduce noise when the non-displacement pump is driven.
　本発明の第２の側面では、上記第１の側面において、
　前記ポンプケースは、
　前記インペラの一面に摺接され、前記一面を覆うアッパーケースと、
　前記インペラの前記一面とは反対側の他面に摺接され、前記他面を覆うロワケースと、を有し、
　前記アッパーケースと前記ロワケースとにより前記収納部が画成され、
　前記アッパーケースは、
　前記吐出口と、
　前記インペラに面する第１摺接面に設けられるとともに前記吐出口に連通される円弧状の第１流路溝と、を有し、
　前記ロワケースは、
　前記吸入口と、
　前記インペラに面する第２摺接面に設けられるとともに前記吸入口に連通される円弧状の第２流路溝と、を有し、
　前記シール部は、
　前記吐出口と前記吸入口との間であり且つ前記貫通流路の回転軌跡上にある。 In the 2nd side surface of this invention, in the said 1st side surface,
The pump case is
An upper case that is in sliding contact with one surface of the impeller and covers the one surface,
A lower case that is in sliding contact with the other surface of the impeller opposite to the one surface, and covers the other surface,
The storage portion is defined by the upper case and the lower case,
The upper case is
The discharge port,
An arc-shaped first flow path groove provided on a first sliding contact surface facing the impeller and communicating with the discharge port,
The lower case is
The inlet,
An arc-shaped second flow path groove provided on a second sliding contact surface facing the impeller and communicating with the suction port,
The seal portion is
It is between the discharge port and the suction port and on the rotation trajectory of the through-flow passage.
　このように構成することで、簡素な構造で適正な吐出流量を確保しつつ、駆動時の騒音を低減可能な非容積型ポンプを提供できる。 By configuring in this way, it is possible to provide a non-volumetric pump that can reduce noise during driving while ensuring an appropriate discharge flow rate with a simple structure.
　本発明の第３の側面に係る液体供給装置は、
　上記第１の側面又は上記第２の側面に記載の非容積型ポンプと、
　前記非容積型ポンプを駆動するモータ部と、を備え、
　前記モータ部の回転軸と前記インペラとが相対回転不能に連結されている。 The liquid supply apparatus according to the third aspect of the present invention is
The non-positive displacement pump according to the first aspect or the second aspect,
A motor unit for driving the non-positive displacement pump,
The rotation shaft of the motor unit and the impeller are connected so as not to rotate relative to each other.
　このように構成することで、適正な吐出流量を確保しつつ、駆動時の騒音を低減可能な非容積型ポンプを提供できる。 With this configuration, it is possible to provide a non-volumetric pump that can reduce noise during driving while ensuring an appropriate discharge flow rate.
　本発明によれば、非容積型ポンプの適正な吐出流量を確保できる。また、シール部の周方向の距離を適正にでき、吐出口から吸入口に送られる液体の減圧沸騰を抑制できる。このため、非容積型ポンプの駆動時の騒音を低減できる。 According to the present invention, an appropriate discharge flow rate of the non-displacement pump can be secured. Further, the circumferential distance of the seal portion can be made appropriate, and the reduced pressure boiling of the liquid sent from the discharge port to the suction port can be suppressed. Therefore, it is possible to reduce noise when the non-displacement pump is driven.
図１は、本発明の実施形態における液体供給装置の斜視図である。FIG. 1 is a perspective view of a liquid supply device according to an embodiment of the present invention. 図２は、本発明の実施形態における液体供給装置の軸方向に沿う断面図である。FIG. 2 is a sectional view taken along the axial direction of the liquid supply apparatus according to the embodiment of the present invention. 図３は、本発明の実施形態におけるインペラの斜視図である。FIG. 3 is a perspective view of the impeller according to the embodiment of the present invention. 図４は、本発明の実施形態におけるアッパーケースをロワケース側からみた平面図である。FIG. 4 is a plan view of the upper case according to the embodiment of the present invention viewed from the lower case side. 図５は、本発明の実施形態におけるロワケースをアッパーケース側からみた平面図である。FIG. 5 is a plan view of the lower case according to the embodiment of the present invention as viewed from the upper case side. 図６は、本発明の実施形態におけるポンプ部の軸方向に沿う断面の簡略図である。FIG. 6 is a schematic view of a cross section taken along the axial direction of the pump unit according to the embodiment of the present invention. 図７は、本発明の実施形態における各シール部がシール条件を満たす場合と満たさない場合との燃料の吐出流量を比較したグラフである。FIG. 7 is a graph comparing the discharge flow rate of fuel in the case where each sealing portion according to the embodiment of the present invention meets and does not satisfy the sealing condition. 図８は、本発明の実施形態における燃料の吐出流量、及び燃料の音圧レベルの変化を示すグラフである。FIG. 8 is a graph showing changes in the fuel discharge flow rate and the fuel sound pressure level in the embodiment of the present invention.
　次に、本発明の実施形態を図面に基づいて説明する。 Next, an embodiment of the present invention will be described with reference to the drawings.
（液体供給装置）
　図１は、液体供給装置１の斜視図である。図２は、液体供給装置１の軸方向に沿う断面図である。
　液体供給装置１は、自動二輪車や四輪車等の車両用の燃料ポンプとして用いられる。液体供給装置１は、不図示の燃料タンク内に配置されるいわゆるインタンク式の燃料ポンプである。 (Liquid supply device)
FIG. 1 is a perspective view of the liquid supply apparatus 1. FIG. 2 is a sectional view taken along the axial direction of the liquid supply apparatus 1.
The liquid supply device 1 is used as a fuel pump for vehicles such as motorcycles and four-wheeled vehicles. The liquid supply device 1 is a so-called in-tank type fuel pump arranged in a fuel tank (not shown).
　図１、図２に示すように、液体供給装置１は、略円筒状で金属製のハウジング２と、ハウジング２の内周面に嵌合され、それぞれハウジング２の軸方向に並んで配置されたモータ部３、及びポンプ部４と、を備えている。ハウジング２、モータ部３、及びポンプ部４は、同軸上に配置されている。
　液体供給装置１は、ポンプ部４を重力方向下側に向けて使用される。このため、以下の説明では、モータ部３側を上方、ポンプ部４側を下方などと称する場合がある。また、以下の説明では、ハウジング２、モータ部３、及びポンプ部４の軸方向を単に軸方向、ハウジング２、モータ部３、及びポンプ部４の径方向を単に径方向、ハウジング２、モータ部３、及びポンプ部４の周方向を単に周方向と称する。 As shown in FIGS. 1 and 2, the liquid supply device 1 is fitted into the substantially cylindrical metal housing 2 and the inner peripheral surface of the housing 2, and is arranged side by side in the axial direction of the housing 2. The motor unit 3 and the pump unit 4 are provided. The housing 2, the motor unit 3, and the pump unit 4 are arranged coaxially.
The liquid supply apparatus 1 is used with the pump unit 4 facing downward in the gravity direction. Therefore, in the following description, the motor unit 3 side may be referred to as the upper side and the pump unit 4 side may be referred to as the lower side. In the following description, the axial direction of the housing 2, the motor unit 3, and the pump unit 4 is simply the axial direction, and the radial direction of the housing 2, the motor unit 3, and the pump unit 4 is simply the radial direction, the housing 2, and the motor unit. The circumferential direction of 3 and the pump portion 4 is simply referred to as the circumferential direction.
　ハウジング２は、モータ部３が嵌合されるモータ嵌合部１１と、モータ嵌合部１１よりも段差を介して縮径形成され、ポンプ部４が嵌合されるポンプ嵌合部１２と、が一体成形されたものである。ポンプ嵌合部１２の内周面には、径方向内側に向かって突出する位置決め凸部１３が形成されている。位置決め凸部１３は、ハウジング２を径方向外側から例えばプレス加工等により押圧することでなる。位置決め凸部１３は、ハウジング２とポンプ部４との周方向の位置決めを行う。位置決め凸部１３は、径方向からみて軸方向に長い長方形状に形成されている。
　また、ハウジング２におけるポンプ嵌合部１２の下端には、径方向内側に向かう内フランジ部１２ａが屈曲延出されている。これら位置決め凸部１３、及び内フランジ部１２ａは、ハウジング２とポンプ部４との軸方向の位置決めを行う。 The housing 2 has a motor fitting portion 11 into which the motor portion 3 is fitted, a pump fitting portion 12 into which the pump portion 4 is fitted, the diameter of which is reduced through a step from the motor fitting portion 11. Is integrally molded. A positioning projection 13 is formed on the inner peripheral surface of the pump fitting portion 12 so as to project inward in the radial direction. The positioning protrusion 13 is formed by pressing the housing 2 from the outside in the radial direction by, for example, pressing. The positioning protrusion 13 positions the housing 2 and the pump unit 4 in the circumferential direction. The positioning protrusion 13 is formed in a rectangular shape that is long in the axial direction when viewed in the radial direction.
Further, an inner flange portion 12a that extends inward in the radial direction is bent and extends from the lower end of the pump fitting portion 12 in the housing 2. The positioning protrusion 13 and the inner flange 12a position the housing 2 and the pump 4 in the axial direction.
　モータ部３としては、例えばブラシ付きモータが採用される。モータ部３は、略円筒状のヨーク５と、ヨーク５の内周面に設けられた永久磁石８と、ヨーク５内に回転自在に設けられるアーマチュア６と、ヨーク５の上開口部５ａを閉塞するアウトレットカバー７と、アウトレットカバー７に収納されているブラシ２５と、を主構成としている。ヨーク５の外周面がハウジング２の内周面に嵌合されている。 As the motor unit 3, for example, a brushed motor is adopted. The motor unit 3 closes a substantially cylindrical yoke 5, a permanent magnet 8 provided on the inner peripheral surface of the yoke 5, an armature 6 rotatably provided in the yoke 5, and an upper opening 5 a of the yoke 5. The outlet cover 7 and the brush 25 housed in the outlet cover 7 are the main components. The outer peripheral surface of the yoke 5 is fitted to the inner peripheral surface of the housing 2.
　ヨーク５は、永久磁石８の磁束が通る磁路となる。ヨーク５の上開口部５ａは、アウトレットカバー７における後述のインロー部３１の外周面に嵌合される。アウトレットカバー７とヨーク５との周方向の位置決めは、アウトレットカバー７に形成される不図示の位置決め凸部とヨーク５に形成される不図示のヨーク位置決め凹部との凹凸嵌合により行われる。 The yoke 5 serves as a magnetic path through which the magnetic flux of the permanent magnet 8 passes. The upper opening 5a of the yoke 5 is fitted to the outer peripheral surface of a spigot portion 31 of the outlet cover 7, which will be described later. Positioning of the outlet cover 7 and the yoke 5 in the circumferential direction is carried out by concave and convex fitting between a positioning projection (not shown) formed on the outlet cover 7 and a yoke positioning recess (not shown) formed on the yoke 5.
　ヨーク５の内周面には、２つの永久磁石８が設けられている。永久磁石８は、軸方向からみてヨーク５の内周面に沿うように略半円状に形成されている。永久磁石８における軸方向の長さは、アーマチュアコア１５の軸方向の長さよりも長く設定されている。そして、アーマチュアコア１５の軸方向両端から永久磁石８の軸方向両端が突出するように（オーバーハングするように）配置されている。永久磁石８の磁場配向は径方向（永久磁石８の厚さ方向）に沿っている。
　このような永久磁石８は、回転軸１４を中心に径方向で対向配置されている。永久磁石８の内周面とアーマチュアコア１５における後述のティース１７及び樹脂モールド部２２の径方向外側端との間には、微小隙間が形成される。 Two permanent magnets 8 are provided on the inner peripheral surface of the yoke 5. The permanent magnet 8 is formed in a substantially semicircular shape along the inner peripheral surface of the yoke 5 when viewed in the axial direction. The axial length of the permanent magnet 8 is set longer than the axial length of the armature core 15. The permanent magnets 8 are arranged so that both axial ends thereof protrude (overhang) from both axial ends of the armature core 15. The magnetic field orientation of the permanent magnet 8 is along the radial direction (the thickness direction of the permanent magnet 8).
Such permanent magnets 8 are arranged to face each other in the radial direction around the rotary shaft 14. A minute gap is formed between the inner peripheral surface of the permanent magnet 8 and the radially outer end of the tooth 17 and the resin mold portion 22 of the armature core 15 which will be described later.
　アーマチュア６は、回転軸１４と、回転軸１４の外周面に嵌合固定されているアーマチュアコア１５と、回転軸１４のアーマチュアコア１５よりもアウトレットカバー７寄りの外周面に嵌合固定されているコンミテータ１６と、を主構成としている。 The armature 6 is fitted and fixed to the rotating shaft 14, the armature core 15 fitted and fixed to the outer peripheral surface of the rotating shaft 14, and the outer peripheral surface of the rotating shaft 14 closer to the outlet cover 7 than the armature core 15. The commutator 16 is mainly used.
　アーマチュアコア１５は、径方向外側に向かって放射状に延びる複数のティース１７を有している。これらティース１７に不図示の巻線が巻回されている。不図示の巻線の端末部は、コンミテータ１６に接続されている。
　コンミテータ１６は、略円板状に形成された樹脂製のコンミテータ本体１８を有する、いわゆるディスク型のコンミテータである。コンミテータ本体１８のアーマチュアコア１５とは反対側の一面１８ａに複数のセグメント１９が周方向に並んで配置されている。セグメント１９の径方向外側端には、コンミテータ本体１８の外周面を通ってアーマチュアコア１５側に屈曲延出されるライザ２１が一体成形されている。各ライザ２１に、不図示の巻線の一端が接続されている。 The armature core 15 has a plurality of teeth 17 that radially extend outward in the radial direction. Winding wires (not shown) are wound around these teeth 17. The end portion of the winding (not shown) is connected to the commutator 16.
The commutator 16 is a so-called disc type commutator having a resin-made commutator main body 18 formed in a substantially disc shape. A plurality of segments 19 are arranged side by side in the circumferential direction on one surface 18a of the commutator body 18 opposite to the armature core 15. A riser 21 that is bent and extends toward the armature core 15 side through the outer peripheral surface of the commutator body 18 is integrally formed at the radially outer end of the segment 19. One end of a winding (not shown) is connected to each riser 21.
　このように形成されたアーマチュア６は、殆どが樹脂モールド部２２によって覆われている。樹脂モールド部２２は、略円柱状に形成されている。また、樹脂モールド部２２は、アーマチュアコア１５よりもポンプ部４側からコンミテータ本体１８の軸方向略中央に至る間に延在されている。アーマチュアコア１５は、ティース１７の径方向外側端（外周面）のみが露出されており、不図示の巻線は樹脂モールド部２２に埋没されている。樹脂モールド部２２のポンプ部４側端には、角部に丸面取り部２２ａが形成されている。これにより、樹脂モールド部２２のポンプ部４側端は先細りになる。 Most of the armature 6 formed in this way is covered by the resin mold portion 22. The resin mold portion 22 is formed in a substantially columnar shape. Further, the resin mold portion 22 extends from the pump portion 4 side with respect to the armature core 15 to approximately the center in the axial direction of the commutator body 18. Only the radially outer ends (outer peripheral surface) of the teeth 17 of the armature core 15 are exposed, and the winding wire (not shown) is buried in the resin mold portion 22. A round chamfered portion 22a is formed at a corner portion of the end of the resin mold portion 22 on the pump portion 4 side. As a result, the end of the resin mold portion 22 on the pump portion 4 side is tapered.
　アウトレットカバー７は、アーマチュアコア１５側に開口部７ａを有する略有底筒状に形成されている。アウトレットカバー７の底部７ｂには、径方向略中央に、アーマチュアコア１５側に向かって突出する軸受円筒部２３が一体成形されている。この軸受円筒部２３に、回転軸１４の上端部１４ａが回転自在に支持されている。 The outlet cover 7 is formed in a substantially bottomed tubular shape having an opening 7a on the armature core 15 side. The bottom cylindrical portion 7b of the outlet cover 7 is integrally formed with a bearing cylindrical portion 23 projecting toward the armature core 15 side at a substantially radial center thereof. The upper end portion 14a of the rotary shaft 14 is rotatably supported by the bearing cylindrical portion 23.
　また、アウトレットカバー７の底部７ｂには、軸受円筒部２３を挟んで両側に、ブラシホルダ２４が一体成形されている。ブラシホルダ２４は、コンミテータ１６側が開口された箱状に形成されている。ブラシホルダ２４に、ブラシ２５が軸方向に沿ってスライド移動自在に収納されている。また、ブラシホルダ２４には、コイルスプリング２６が圧縮変形した形で収納されている。ブラシ２５は、コイルスプリング２６によってコンミテータ１６側に向かって付勢されている。ブラシ２５の先端は、ブラシホルダ２４から突出されてセグメント１９に摺接されている。 Further, brush holders 24 are integrally formed on the bottom portion 7b of the outlet cover 7 on both sides of the bearing cylindrical portion 23. The brush holder 24 is formed in a box shape having an opening on the commutator 16 side. The brush 25 is accommodated in the brush holder 24 so as to be slidable along the axial direction. A coil spring 26 is stored in the brush holder 24 in a compressed and deformed form. The brush 25 is biased toward the commutator 16 side by a coil spring 26. The tip of the brush 25 projects from the brush holder 24 and is in sliding contact with the segment 19.
　また、アウトレットカバー７の底部７ｂには、この底部７ｂを上下方向に貫通する端子２７が設けられている。ブラシ２５は、不図示のピグテールを介して端子２７に接続されている。端子２７には、不図示の外部電源が接続される。これにより、端子２７、不図示のピグテール、ブラシ２５、及びセグメント１９を介して不図示の巻線に外部電力が供給される。
　また、アウトレットカバー７の底部７ｂには、上方に向かって突出する吐出ポート２８が一体成形されている。吐出ポート２８は、液体供給装置１によって汲み上げられる燃料が吐出される箇所であり、不図示の燃料流路に接続されている。また、吐出ポート２８を介し、アウトレットカバー７の内外が連通されている。 Further, the bottom portion 7b of the outlet cover 7 is provided with a terminal 27 that vertically penetrates the bottom portion 7b. The brush 25 is connected to the terminal 27 via a pigtail (not shown). An external power source (not shown) is connected to the terminal 27. As a result, external power is supplied to the winding (not shown) via the terminal 27, the pigtail (not shown), the brush 25, and the segment 19.
A discharge port 28 protruding upward is integrally formed on the bottom portion 7b of the outlet cover 7. The discharge port 28 is a portion where the fuel pumped up by the liquid supply device 1 is discharged, and is connected to a fuel flow path (not shown). Further, the inside and outside of the outlet cover 7 are communicated with each other via the discharge port 28.
　アウトレットカバー７の周壁７ｃには、下方に向かって延出する位置決め片３２が一体成形されている。位置決め片３２は永久磁石８の間に介在され、永久磁石８（ヨーク５）とアウトレットカバー７との位置決めを行う。 A positioning piece 32 extending downward is integrally formed on the peripheral wall 7c of the outlet cover 7. The positioning piece 32 is interposed between the permanent magnets 8 and positions the permanent magnet 8 (yoke 5) and the outlet cover 7.
　また、アウトレットカバー７の周壁７ｃには、外周面に全周に渡って嵌合凸条部２９が径方向外側に張り出すように形成されている。嵌合凸条部２９の外径は、ハウジング２におけるモータ嵌合部１１の内径とほぼ同一に設定されている。このような嵌合凸条部２９の外周面が、モータ嵌合部１１の内周面に嵌合されている。モータ嵌合部１１の上開口縁部１１ａは、アウトレットカバー７の嵌合凸条部２９の上から径方向内側にかしめられる。また、アウトレットカバー７の周壁７ｃにおける嵌合凸条部２９よりも下側は、ヨーク５とインロー嵌合されるインロー部３１とされている。 Further, the peripheral wall 7c of the outlet cover 7 is formed with a fitting ridge portion 29 over the entire outer peripheral surface so as to project radially outward. The outer diameter of the fitting protruding portion 29 is set to be substantially the same as the inner diameter of the motor fitting portion 11 in the housing 2. The outer peripheral surface of the fitting convex strip 29 is fitted to the inner peripheral surface of the motor fitting portion 11. The upper opening edge 11a of the motor fitting portion 11 is caulked inward in the radial direction from above the fitting protruding portion 29 of the outlet cover 7. Further, a lower part of the peripheral wall 7c of the outlet cover 7 below the fitting protrusion part 29 is an inlay part 31 which is inlay-fitted with the yoke 5.
（ポンプ部）
　回転軸１４の下端部は、ポンプ部４に挿入されている。
　ポンプ部４は、インペラ４０を有する非容積型のポンプが用いられている。ポンプ部４は、インペラ４０と、インペラ４０の全体を覆うように形成されたポンプケース４１と、により構成されている。ポンプケース４１が、ハウジング２のポンプ嵌合部１２に嵌合される。 (Pump part)
The lower end of the rotary shaft 14 is inserted into the pump unit 4.
As the pump unit 4, a non-volume pump having an impeller 40 is used. The pump unit 4 includes an impeller 40 and a pump case 41 formed so as to cover the entire impeller 40. The pump case 41 is fitted into the pump fitting portion 12 of the housing 2.
（インペラ）
　図３は、インペラ４０の斜視図である。
　図２、図３に示すように、インペラ４０は、樹脂材料からなる略円板状に形成された部材である。インペラ４０の径方向略中央には、回転軸１４の下端部１４ｂを挿通可能な挿通孔６１が形成されている。ここで、回転軸１４の下端部１４ｂは、軸方向に直交する断面形状が略Ｄ字状に形成されている。また、インペラ４０の挿通孔６１は、回転軸１４における下端部１４ｂの断面形状に対応するように、軸方向からみて略Ｄ字状に形成されている。このような挿通孔６１に、回転軸１４の下端部１４ｂが挿入されることにより、回転軸１４とインペラ４０とが相対回転不能に一体となって回転される。 (Impeller)
FIG. 3 is a perspective view of the impeller 40.
As shown in FIGS. 2 and 3, the impeller 40 is a member made of a resin material and formed into a substantially disc shape. An insertion hole 61 through which the lower end portion 14b of the rotary shaft 14 can be inserted is formed at a substantially center of the impeller 40 in the radial direction. Here, the lower end portion 14b of the rotary shaft 14 is formed in a substantially D-shaped cross section orthogonal to the axial direction. Further, the insertion hole 61 of the impeller 40 is formed in a substantially D shape when viewed in the axial direction so as to correspond to the cross-sectional shape of the lower end portion 14b of the rotary shaft 14. By inserting the lower end portion 14b of the rotary shaft 14 into such an insertion hole 61, the rotary shaft 14 and the impeller 40 are integrally rotated so that they cannot rotate relative to each other.
　インペラ４０の外周部寄りには、軸方向に沿う断面が略Ｌ字状の羽根部６２（図６も参照）が複数形成されている。各羽根部６２は、周方向の向きが同じ向きとなるように、周方向に等間隔に並んで配置されている。周方向に隣接する各羽根部６２の間には、貫通流路６３が形成されている。貫通流路６３は、インペラ４０の板厚方向に貫通されている。 A plurality of blade portions 62 (see also FIG. 6) having a substantially L-shaped cross section along the axial direction are formed near the outer peripheral portion of the impeller 40. The blade portions 62 are arranged side by side at equal intervals in the circumferential direction so that the circumferential directions are the same. A through passage 63 is formed between the blade portions 62 adjacent to each other in the circumferential direction. The through flow passage 63 penetrates in the plate thickness direction of the impeller 40.
（ポンプケース）
　図２に示すように、インペラ４０の全体を覆うポンプケース４１は、アッパーケース４３と、ミドルケース４４と、ロワケース４２と、により構成されている。 (Pump case)
As shown in FIG. 2, the pump case 41 that covers the entire impeller 40 includes an upper case 43, a middle case 44, and a lower case 42.
　図４は、アッパーケース４３をロワケース４２側（下方）からみた平面図である。
　図２、図４に示すように、アッパーケース４３は、インペラ４０のモータ部３側に配置されている。アッパーケース４３は、インペラ４０の上面を覆うように略円板状に形成されている。アッパーケース４３の外周部に、ミドルケース４４が接合されている。アッパーケース４３の外径は、ヨーク５の外径よりも若干小さく設定されている。 FIG. 4 is a plan view of the upper case 43 viewed from the lower case 42 side (downward).
As shown in FIGS. 2 and 4, the upper case 43 is disposed on the motor section 3 side of the impeller 40. The upper case 43 is formed in a substantially disc shape so as to cover the upper surface of the impeller 40. A middle case 44 is joined to the outer peripheral portion of the upper case 43. The outer diameter of the upper case 43 is set to be slightly smaller than the outer diameter of the yoke 5.
　アッパーケース４３の径方向中央には、回転軸１４の下端部１４ｂを挿通可能な挿通孔４６が形成されている。この挿通孔４６に滑り軸受５９を介して回転軸１４が回転自在に支持されている。
　また、アッパーケース４３の上面４３ａには、挿通孔４６の周囲を取り囲むように軸方向からみて略円環状の凹部４７が形成されている。アッパーケース４３の上面４３ａにおいて、凹部４７よりも外周側は、ヨーク５が当接される当接面４３ｂとなる。当接面４３ｂは十分なスペースが確保されているので、当接面４３ｂにヨーク５の下端を当接させても、これら当接面４３ｂやヨーク５が座屈変形してしまうことが抑制される。 An insertion hole 46 through which the lower end portion 14b of the rotary shaft 14 can be inserted is formed at the center of the upper case 43 in the radial direction. The rotary shaft 14 is rotatably supported in the insertion hole 46 via a slide bearing 59.
Further, on the upper surface 43a of the upper case 43, a substantially annular recess 47 is formed so as to surround the periphery of the insertion hole 46 when viewed in the axial direction. On the upper surface 43a of the upper case 43, the outer peripheral side of the recess 47 is a contact surface 43b with which the yoke 5 contacts. Since a sufficient space is secured for the contact surface 43b, buckling deformation of the contact surface 43b and the yoke 5 is suppressed even when the lower end of the yoke 5 is contacted with the contact surface 43b. It
　また、アッパーケース４３の上面４３ａには、凹部４７の外周部寄りに、アッパーケース４３を上下方向に貫通する吐出口４８が形成されている。アッパーケース４３の下面４３ｃには、吐出口４８の周縁に、吐出口４８の開口を広げる凹部４８ａが形成されている。凹部４８ａは、アッパーケース４３の下面４３ｃに向かうに従って末広がりとなるように形成されている。 Further, on the upper surface 43a of the upper case 43, a discharge port 48 penetrating the upper case 43 in the vertical direction is formed near the outer periphery of the recess 47. On the lower surface 43c of the upper case 43, a concave portion 48a that widens the opening of the ejection port 48 is formed at the periphery of the ejection port 48. The recess 48a is formed so as to widen toward the lower surface 43c of the upper case 43.
　アッパーケース４３の下面４３ｃは、インペラ４０に摺接される第１摺接面４３ｄである。第１摺接面４３ｄには、軸方向でインペラ４０の貫通流路６３と対向する位置に、軸方向からみて略円弧状（略Ｃ字状）の第１流路溝６４が形成されている。第１流路溝６４の周方向一端は、吐出口４８（凹部４８ａ）に連通されている。第１流路溝６４の周方向他端には、軸方向からみて先細りとなるように先細り部６４ａが形成されている。 The lower surface 43c of the upper case 43 is a first sliding contact surface 43d that is in sliding contact with the impeller 40. On the first sliding contact surface 43d, a first flow channel groove 64 having a substantially arc shape (substantially C-shaped) when viewed from the axial direction is formed at a position facing the through flow channel 63 of the impeller 40 in the axial direction. .. One end of the first flow path groove 64 in the circumferential direction is communicated with the discharge port 48 (recessed portion 48a). A tapered portion 64a is formed at the other end of the first flow path groove 64 in the circumferential direction so as to be tapered when viewed in the axial direction.
　ミドルケース４４は、インペラ４０の外周面を取り囲むように略リング状に形成されている。ミドルケース４４は、アッパーケース４３と一体に形成されている。ミドルケース４４の外径は、アッパーケース４３の外径よりも若干大きく設定されている。ミドルケース４４によって、インペラ４０の径方向中心と、回転軸１４の軸心Ｃとが一致される。ミドルケース４４の軸方向の厚さは、インペラ４０の板厚と略同一か、若干厚くなるように形成されている。これにより、インペラ４０とアッパーケース４３との間、及びインペラ４０とロワケース４２との間に、それぞれ所定のクリアランスが形成される。 The middle case 44 is formed in a substantially ring shape so as to surround the outer peripheral surface of the impeller 40. The middle case 44 is formed integrally with the upper case 43. The outer diameter of the middle case 44 is set to be slightly larger than the outer diameter of the upper case 43. By the middle case 44, the radial center of the impeller 40 and the axis C of the rotary shaft 14 are aligned. The thickness of the middle case 44 in the axial direction is formed to be substantially the same as or slightly larger than the plate thickness of the impeller 40. As a result, predetermined clearances are formed between the impeller 40 and the upper case 43 and between the impeller 40 and the lower case 42, respectively.
　図５は、ロワケース４２をアッパーケース４３側（上方）からみた平面図である。説明の便宜上、図５では、図４に示すアッパーケース４３が有する第１シール部６６の周方向の位置と、図５に示すロワケース４２が有する第２シール部６７の周方向の位置と、が概ね一致するように、ロワケース４２が図示されている。
　図２、図５に示すように、ロワケース４２は、インペラ４０の下方に配置されている。ポンプケース４１は、ミドルケース４４が一体に形成されたアッパーケース４３と、ロワケース４２とで、インペラ４０の全体を覆うように形成されている。アッパーケース４３の下面４３ｃと、ロワケース４２の上面４２ａとにより、インペラ４０を収納する収納部６０が形成される。
　ロワケース４２は、略円板状に形成されている。ロワケース４２の外径は、ミドルケース４４の外径とほぼ同一に設定されている。 FIG. 5 is a plan view of the lower case 42 seen from the upper case 43 side (upper side). For convenience of description, in FIG. 5, the circumferential position of the first seal portion 66 of the upper case 43 shown in FIG. 4 and the circumferential position of the second seal portion 67 of the lower case 42 shown in FIG. The lower case 42 is shown to be generally coincident.
As shown in FIGS. 2 and 5, the lower case 42 is arranged below the impeller 40. The pump case 41 is formed by an upper case 43 integrally formed with a middle case 44 and a lower case 42 so as to cover the entire impeller 40. The lower surface 43c of the upper case 43 and the upper surface 42a of the lower case 42 form a storage portion 60 that stores the impeller 40.
The lower case 42 is formed in a substantially disc shape. The outer diameter of the lower case 42 is set to be substantially the same as the outer diameter of the middle case 44.
　ロワケース４２の下面４２ｂには、外周側に、下方に向かって突出した略円筒状の吸入口５３が形成されている。吸入口５３の内周面には、ロワケース４２の上面４２ａ側に、この上面４２ａに向かうに従って徐々に開口面積が大きくなるようにテーパ孔部５３ａが形成されている。
　また、ロワケース４２の下面４２ｂには、外周縁に、段差部４９が形成されている。段差部４９は、ロワケース４２の下面４２ｂ側を縮径させることにより形成される。段差部４９は、軸方向からみて、ハウジング２の内フランジ部１２ａと重なる位置に形成されている。 On the lower surface 42b of the lower case 42, a substantially cylindrical suction port 53 protruding downward is formed on the outer peripheral side. On the inner peripheral surface of the suction port 53, a tapered hole portion 53a is formed on the upper surface 42a side of the lower case 42 so that the opening area gradually increases toward the upper surface 42a.
Further, a step portion 49 is formed on the outer peripheral edge of the lower surface 42b of the lower case 42. The step portion 49 is formed by reducing the diameter of the lower case 42 on the lower surface 42b side. The step portion 49 is formed at a position overlapping the inner flange portion 12a of the housing 2 when viewed in the axial direction.
　ロワケース４２の上面４２ａは、インペラ４０に摺接される第２摺接面４２ｃである。ロワケース４２の上面４２ａには、径方向略中央に、回転軸１４の下端部１４ｂが臨まされる軸受収納凹部５４が形成されている。この軸受収納凹部５４に、スラスト軸受５５が収納されている。回転軸１４の下端部１４ｂは、スラスト軸受５５に当接された状態でロワケース４２に回転自在に支持される。スラスト軸受５５は、回転軸１４のスラスト荷重を受ける。 The upper surface 42a of the lower case 42 is a second sliding contact surface 42c that is in sliding contact with the impeller 40. On the upper surface 42a of the lower case 42, a bearing accommodating recess 54 is formed at a substantially radial center thereof so that the lower end portion 14b of the rotary shaft 14 is exposed. The thrust bearing 55 is housed in the bearing housing recess 54. The lower end portion 14b of the rotary shaft 14 is rotatably supported by the lower case 42 while being in contact with the thrust bearing 55. The thrust bearing 55 receives the thrust load of the rotary shaft 14.
　ロワケース４２の第２摺接面４２ｃには、軸方向でインペラ４０の貫通流路６３と対向する位置で、かつアッパーケース４３の第１流路溝６４と対向する位置に、軸方向からみて略円弧状（略Ｃ字状）の第２流路溝６５が形成されている。第２流路溝６５の周方向一端は、吸入口５３（テーパ孔部５３ａ）に連通されている。第２流路溝６５の周方向他端には、軸方向からみて先細りとなるように先細り部６５ａが形成されている。
　また、第２流路溝６５には、吸入口５３と先細り部６５ａとの間の中央よりもやや吸入口５３寄りに、脱気孔６８がロワケース４２の板厚方向に貫通形成されている。脱気孔６８は、ポンプケース４１内で発生するベーパ（気泡）を排出するための孔である。 The second sliding contact surface 42c of the lower case 42 is substantially axially opposed to the through passage 63 of the impeller 40 and to the first passage groove 64 of the upper case 43 in the axial direction. An arcuate (substantially C-shaped) second flow path groove 65 is formed. One end of the second flow path groove 65 in the circumferential direction is communicated with the suction port 53 (tapered hole portion 53a). At the other end of the second flow path groove 65 in the circumferential direction, a tapered portion 65a is formed so as to be tapered when viewed in the axial direction.
Further, in the second flow path groove 65, a deaeration hole 68 is formed so as to penetrate in the plate thickness direction of the lower case 42, slightly closer to the suction port 53 than the center between the suction port 53 and the tapered portion 65a. The deaeration hole 68 is a hole for discharging vapor (air bubbles) generated in the pump case 41.
　ここで、第１流路溝６４の周方向一端に連通されている吐出口４８、及び第１流路溝６４の周方向他端に形成されている先細り部６４ａと、第２流路溝６５の周方向一端に連通されている吸入口５３、及び第２流路溝６５の周方向他端に形成されている先細り部６５ａとは、互い違いに配置されている。すなわち、吐出口４８は、第２流路溝６５の先細り部６５ａと軸方向で対向している。吸入口５３は、第１流路溝６４の先細り部６４ａと軸方向で対向している。 Here, the discharge port 48 communicated with one end in the circumferential direction of the first flow channel 64, the tapered portion 64 a formed at the other end in the circumferential direction of the first flow channel 64, and the second flow channel 65. The suction port 53, which communicates with one end in the circumferential direction, and the tapered portion 65a, which is formed at the other end in the circumferential direction of the second flow channel groove 65, are arranged alternately. That is, the discharge port 48 axially faces the tapered portion 65a of the second flow path groove 65. The suction port 53 axially faces the tapered portion 64a of the first flow channel 64.
　また、アッパーケース４３の第１摺接面４３ｄにおける吐出口４８（凹部４８ａ）と第１流路溝６４の先細り部６４ａとの間は、吐出口４８から先細り部６４ａへの燃料の漏出を抑制するための第１シール部６６となる。ロワケース４２の第２摺接面４２ｃにおける吸入口５３（テーパ孔部５３ａ）と第２流路溝６５の先細り部６５ａとの間は、先細り部６５ａから吸入口５３への燃料の漏出を抑制するための第２シール部６７となる。第１シール部６６の周方向の範囲（長さ）と第２シール部６７の周方向の範囲（長さ）は、一致している。これら第１シール部６６及び第２シール部６７についての詳細は後述する。図６から理解されるように、第１シール部６６及び第２シール部６７は、吐出口４８と吸入口５３との間であり且つ貫通流路６３の回転軌跡上に位置している。 Further, between the discharge port 48 (recess 48 a) and the tapered portion 64 a of the first flow path groove 64 in the first sliding contact surface 43 d of the upper case 43, the leakage of fuel from the discharge port 48 to the tapered portion 64 a is suppressed. The first seal portion 66 for performing the operation is provided. Between the suction port 53 (tapered hole portion 53a) in the second sliding contact surface 42c of the lower case 42 and the tapered portion 65a of the second flow path groove 65, fuel leakage from the tapered portion 65a to the suction port 53 is suppressed. The second seal portion 67 for The circumferential range (length) of the first seal portion 66 and the circumferential range (length) of the second seal portion 67 match. Details of the first seal portion 66 and the second seal portion 67 will be described later. As can be understood from FIG. 6, the first seal portion 66 and the second seal portion 67 are located between the discharge port 48 and the suction port 53 and on the rotation trajectory of the through passage 63.
　ロワケース４２の下面４２ｂに形成された段差部４９には、シール部材としての角リング５０が装着される。角リング５０は、断面が略矩形状に形成されたフッ素ゴム等の耐油性に優れた材料からなる部材である。角リング５０の外径は、ロワケース４２の外径よりも若干小さく設定されている。このため、ハウジング２のポンプ嵌合部１２には、アッパーケース４３、ミドルケース４４、及びロワケース４２の外周面が嵌合される。角リング５０の外周面とハウジング２のポンプ嵌合部１２の内周面との間には、微小隙間が形成される。 A square ring 50 as a seal member is attached to the step portion 49 formed on the lower surface 42b of the lower case 42. The square ring 50 is a member having a substantially rectangular cross section and made of a material having excellent oil resistance such as fluororubber. The outer diameter of the square ring 50 is set to be slightly smaller than the outer diameter of the lower case 42. For this reason, the outer peripheral surfaces of the upper case 43, the middle case 44, and the lower case 42 are fitted to the pump fitting portion 12 of the housing 2. A minute gap is formed between the outer peripheral surface of the square ring 50 and the inner peripheral surface of the pump fitting portion 12 of the housing 2.
　このような構成のもと、ハウジング２内にモータ部３とポンプ部４とを収納する際、ハウジング２の内フランジ部１２ａに角リング５０を当接させる。この際、ポンプケース４１の外周面に形成されている不図示の凹部に、ハウジング２の位置決め凸部１３を挿入させる。これにより、ハウジング２とポンプ部４との周方向の位置決めが行われる。 With this configuration, when the motor unit 3 and the pump unit 4 are housed in the housing 2, the square ring 50 is brought into contact with the inner flange portion 12a of the housing 2. At this time, the positioning protrusion 13 of the housing 2 is inserted into a recess (not shown) formed on the outer peripheral surface of the pump case 41. As a result, the housing 2 and the pump portion 4 are positioned in the circumferential direction.
　また、ロワケース４２の段差部４９と内フランジ部１２ａとにより、角リング５０を若干押し潰した状態のまま、モータ嵌合部１１の上開口縁部１１ａを、アウトレットカバー７の嵌合凸条部２９の上から径方向内側にかしめる。これにより、ハウジング２のポンプ嵌合部１２に、ポンプ部４が嵌合される。また、ハウジング２のモータ嵌合部１１に、モータ部３が嵌合される。そして、ハウジング２に対するモータ部３及びポンプ部４の位置決めが行われ、ハウジング２、モータ部３、及びポンプ部４が一体化される。さらに、角リング５０により、ハウジング２とポンプ部４との間のシール性が確保される。 Further, the upper opening edge 11a of the motor fitting portion 11 is fitted to the fitting ridge portion of the outlet cover 7 while the square ring 50 is slightly crushed by the step portion 49 of the lower case 42 and the inner flange portion 12a. From above 29, crimp inward in the radial direction. As a result, the pump portion 4 is fitted into the pump fitting portion 12 of the housing 2. Further, the motor portion 3 is fitted into the motor fitting portion 11 of the housing 2. Then, the motor part 3 and the pump part 4 are positioned with respect to the housing 2, and the housing 2, the motor part 3 and the pump part 4 are integrated. Further, the square ring 50 ensures the sealing property between the housing 2 and the pump portion 4.
（液体供給装置の動作）
　次に、図２、図６に基づいて、液体供給装置１の動作について説明する。
　図６は、ポンプ部４の軸方向に沿う断面の簡略図である。
　図２、図６に示すように、モータ部３の回転軸１４を回転させると、この回転軸１４と一体となってインペラ４０が回転される。すると、吸入口５３を介してポンプケース４１内に燃料Ｎが吸い上げられる。吸い上げられた燃料Ｎは、インペラ４０の貫通流路６３内に入り込み、さらに、アッパーケース４３の第１流路溝６４、及びロワケース４２の第２流路溝６５に入り込む。そして、インペラ４０とポンプケース４１との間で旋回流が発生する。この旋回流により、吐出口４８に向かうに従って貫通流路６３内の燃料が昇圧される。 (Operation of liquid supply device)
Next, the operation of the liquid supply apparatus 1 will be described based on FIGS. 2 and 6.
FIG. 6 is a schematic view of a cross section along the axial direction of the pump unit 4.
As shown in FIGS. 2 and 6, when the rotating shaft 14 of the motor unit 3 is rotated, the impeller 40 is rotated integrally with the rotating shaft 14. Then, the fuel N is sucked up into the pump case 41 through the suction port 53. The sucked fuel N enters the through passage 63 of the impeller 40, and further enters the first passage groove 64 of the upper case 43 and the second passage groove 65 of the lower case 42. Then, a swirling flow is generated between the impeller 40 and the pump case 41. Due to this swirling flow, the pressure of the fuel in the through passage 63 is increased toward the discharge port 48.
　昇圧された燃料Ｎは、吐出口４８を介してモータ部３のヨーク５内に吐出される。つまり、吐出口４８の燃料Ｎの圧力は、吸入口５３の燃料Ｎの圧力に対して大きい。吐出口４８と吸入口５３との間には、第１シール部６６及び第２シール部６７が設けられている。このため、吸入口５３、第１流路溝６４、及び第２流路溝６５のうちの吸入口５３と軸方向で交わる箇所に、吐出口４８から吐出される燃料Ｎが漏出されることが抑制されている。
　ヨーク５内に吐出された燃料Ｎは、永久磁石８と樹脂モールド部２２（アーマチュアコア１５におけるティース１７の径方向外側端）との間の微小隙間を介し、吐出ポート２８に圧送される。この後、吐出ポート２８を介して不図示のエンジン等に燃料が圧送される。 The boosted fuel N is discharged into the yoke 5 of the motor unit 3 through the discharge port 48. That is, the pressure of the fuel N at the discharge port 48 is higher than the pressure of the fuel N at the suction port 53. A first seal portion 66 and a second seal portion 67 are provided between the discharge port 48 and the suction port 53. Therefore, the fuel N discharged from the discharge port 48 may leak to a portion of the suction port 53, the first flow channel 64, and the second flow channel 65 that intersects the suction port 53 in the axial direction. It is suppressed.
The fuel N discharged into the yoke 5 is pressure-fed to the discharge port 28 through a minute gap between the permanent magnet 8 and the resin mold portion 22 (radially outer ends of the teeth 17 of the armature core 15). Then, the fuel is pressure-fed to the engine (not shown) or the like via the discharge port 28.
　ここで、インペラ４０の貫通流路６３において、吐出口４８側で完全に燃料Ｎが吐出しきらず、そのまま圧力の高い燃料Ｎが吸入口５３近傍、詳しくは吸入口５３、第１流路溝６４、及び第２流路溝６５のうちの吸入口５３と軸方向で交わる箇所にまで漏出した場合、吸入口５３で急激に燃料Ｎが低圧となって減圧沸騰が生じ、この際の燃料Ｎの圧力変動により、騒音が発生する可能性がある。そこで、このような燃料Ｎの漏出を抑制するべく、第１シール部６６の周方向の範囲（長さ）、及び第２シール部６７の周方向の範囲（長さ）を、以下のように設定している。 Here, in the through flow passage 63 of the impeller 40, the fuel N is not completely discharged on the discharge port 48 side, and the fuel N having a high pressure is in the vicinity of the suction port 53, more specifically, the suction port 53, the first flow channel groove 64. , And in the portion of the second flow path groove 65 that intersects with the suction port 53 in the axial direction, the fuel N suddenly becomes a low pressure at the suction port 53 and depressurization boiling occurs. Noise can occur due to pressure fluctuations. Therefore, in order to suppress such leakage of the fuel N, the circumferential range (length) of the first seal portion 66 and the circumferential range (length) of the second seal portion 67 are set as follows. It is set.
　すなわち、図４に示すように、第１シール部６６の周方向両端と回転軸１４の軸心Ｃとを結ぶ直線をＬ１とする。ここで、第１シール部６６の周方向両端とは、軸心Ｃを通る直線Ｌ１が、第１流路溝６４の先細り部６４ａと接する箇所と、吐出口４８の凹部４８ａと接する箇所とする。
　また、図５に示すように、第２シール部６７の周方向両端と回転軸１４の軸心Ｃとを結ぶ直線をＬ２とする。ここで、第２シール部６７の周方向両端とは、軸心Ｃを通る直線Ｌ２が、第２流路溝６５の先細り部６５ａと接する箇所と、吸入口５３のテーパ孔部５３ａと接する箇所とする。 That is, as shown in FIG. 4, a straight line connecting both circumferential ends of the first seal portion 66 and the axis C of the rotary shaft 14 is defined as L1. Here, the both ends in the circumferential direction of the first seal portion 66 are a portion where the straight line L1 passing through the axis C contacts the tapered portion 64a of the first flow path groove 64 and a portion where the straight line L1 contacts the recess 48a of the discharge port 48. ..
Further, as shown in FIG. 5, a straight line connecting both circumferential ends of the second seal portion 67 and the axis C of the rotary shaft 14 is defined as L2. Here, the both ends in the circumferential direction of the second seal portion 67 are locations where the straight line L2 passing through the axis C contacts the tapered portion 65a of the second flow channel groove 65 and the taper hole portion 53a of the suction port 53. And
　アッパーケース４３の第１摺接面４３ｄのうち、２つの直線Ｌ１の間で、かつインペラ４０の羽根部６２及び貫通流路６３と軸方向で対向する箇所が、第１シール部６６を構成する。また、ロワケース４２の第２摺接面４２ｃのうち、２つの直線Ｌ２の間で、かつインペラ４０の羽根部６２及び貫通流路６３と軸方向で対向する箇所が、第２シール部６７を構成する。 A portion of the first sliding contact surface 43d of the upper case 43, which is between the two straight lines L1 and axially faces the blade portion 62 and the through passage 63 of the impeller 40, constitutes a first seal portion 66. .. Further, a portion of the second sliding contact surface 42c of the lower case 42 that is between the two straight lines L2 and that axially opposes the blade portion 62 and the through passage 63 of the impeller 40 constitutes the second seal portion 67. To do.
　２つの直線Ｌ１の間の角度θ１、及び２つの直線Ｌ２の間の角度θ２は、それぞれ
　θ１≒θ２＝４５°±２°・・・（１）
　を満たすように設定されている。換言すると、角度θ１及びθ２は、４３°≦θ１≦４７°であり且つ４３°≦θ２≦４７°であるように、設定されている。
　また、図６に詳示するように、第１シール部６６、及び第２シール部６７は、周方向両端の間に少なくとも２つの貫通流路６３を閉塞可能な大きさに形成されている。なお、この少なくとも２つの貫通流路６３を閉塞可能な大きさで、かつ上記式（１）を満たす各シール部６６，６７の条件を、以下ではシール条件という。 The angle θ1 between the two straight lines L1 and the angle θ2 between the two straight lines L2 are respectively θ1≈θ2=45°±2° (1)
Is set to meet. In other words, the angles θ1 and θ2 are set so that 43°≦θ1≦47° and 43°≦θ2≦47°.
Further, as shown in detail in FIG. 6, the first seal portion 66 and the second seal portion 67 are formed in a size capable of closing at least two through flow passages 63 between both ends in the circumferential direction. In addition, the condition of each of the seal portions 66 and 67 having a size capable of closing the at least two through-flow passages 63 and satisfying the above expression (1) is referred to as a seal condition hereinafter.
　次に、図７、図８に基づいて、シール条件を満たす各シール部６６，６７の効果について説明する。
　図７は、縦軸をポンプ部４による燃料の吐出流量（以下、単に燃料の吐出流量という）［Ｌ／ｈ］とした場合において、各シール部６６，６７がシール条件を満たす場合と満たさない場合との燃料の吐出流量を比較したグラフである。
　なお、図７において、「従来」とは、第１シール部６６の２つの直線Ｌ１の間の角度θ１が２２°であり、第２シール部６７の２つの直線Ｌ２の間の角度θ２が２４°である場合である。「従来」の角度θ１，θ２は、上記式（１）を満たさない。図７において、「４５°－１」とは、各シール部６６，６７の２つの直線Ｌ１，Ｌ２間の間の角度θ１，θ２が４５°－１である場合であり、上記式（１）を満たす。図７において、「４５°－２」とは、各シール部６６，６７の２つの直線Ｌ１，Ｌ２間の間の角度θ１，θ２が４５°－２である場合であり、上記式（１）を満たす。図７において、「６７°」とは、各シール部６６，６７の２つの直線Ｌ１，Ｌ２間の間の角度θ１，θ２が６７°である場合であり、上記式（１）を満たさない。 Next, based on FIGS. 7 and 8, the effects of the seal portions 66 and 67 satisfying the seal condition will be described.
In FIG. 7, when the vertical axis represents the fuel discharge flow rate (hereinafter, simply referred to as fuel discharge flow rate) [L/h] by the pump unit 4, it does not satisfy the case where the seal portions 66 and 67 satisfy the seal condition. It is a graph which compared the discharge flow rate of fuel with the case.
In FIG. 7, “conventional” means that the angle θ1 between the two straight lines L1 of the first seal portion 66 is 22° and the angle θ2 between the two straight lines L2 of the second seal portion 67 is 24. This is the case. The “conventional” angles θ1 and θ2 do not satisfy the above equation (1). In FIG. 7, “45°−1” is a case where the angles θ1 and θ2 between the two straight lines L1 and L2 of the seal portions 66 and 67 are 45°−1, and the above formula (1) is used. Meet In FIG. 7, “45°-2” is a case where the angles θ1 and θ2 between the two straight lines L1 and L2 of the seal portions 66 and 67 are 45°-2, and the above formula (1) is used. Meet In FIG. 7, “67°” means that the angles θ1 and θ2 between the two straight lines L1 and L2 of the seal portions 66 and 67 are 67°, which does not satisfy the above formula (1).
　図７に示すように、各シール部６６，６７がシール条件を満たす場合、従来と比較して、若干燃料の吐出流量が減少するものの、「６７°」と比較して燃料の吐出流量は多いことが確認できる。 As shown in FIG. 7, when each of the seal portions 66 and 67 satisfies the sealing condition, the fuel discharge flow rate is slightly reduced as compared with the conventional one, but the fuel discharge flow rate is larger than “67°”. You can confirm that.
　図８は、縦軸を燃料の吐出流量［Ｌ／ｈ］、及び圧力の高い燃料が吸入口５３まで送られてしまった場合の吸入口５３近傍における燃料の音圧レベル［ｄＢ］とし、横軸を各シール部６６，６７の２つの直線Ｌ１，Ｌ２間の間の角度θ１，θ２［°］とした場合の燃料の吐出流量、及び燃料の音圧レベルの変化を示すグラフである。
　図８に示すように、各シール部６６，６７の２つの直線Ｌ１，Ｌ２間の間の角度θ１，θ２が上記式（１）満たす範囲において、所望の吐出流量の範囲Ｗを満たしつつ、燃料の音圧レベルを低減できることが確認できる。吐出流量の範囲Ｗは、この種の液体供給装置１を実際に使用するにあたり、許容し得る音圧レベルと実用上望ましい吐出流量との両立を図り得る範囲として、定められている。
　各シール部６６，６７がシール条件を満たす場合、従来と比較して音圧レベルを低減することが可能であり、また、「６７°」と比較して流量の条件を満たすことが可能となる。そのため、各シール部６６，６７がシール条件を満たす場合、流量や音圧レベルにおける性能のバランスが良いことが確認できる。 In FIG. 8, the vertical axis represents the fuel discharge flow rate [L/h] and the fuel sound pressure level [dB] near the suction port 53 when high-pressure fuel has been sent to the suction port 53. 6 is a graph showing changes in the fuel discharge flow rate and the fuel sound pressure level when the axes are angles θ1 and θ2 [°] between the two straight lines L1 and L2 of the seal portions 66 and 67.
As shown in FIG. 8, within the range in which the angles θ1 and θ2 between the two straight lines L1 and L2 of the respective seal portions 66 and 67 satisfy the above equation (1), while satisfying the desired discharge flow rate range W, It can be confirmed that the sound pressure level of can be reduced. The range W of the discharge flow rate is defined as a range in which an acceptable sound pressure level and a practically desirable discharge flow rate can be achieved when the liquid supply apparatus 1 of this type is actually used.
When each of the seal portions 66 and 67 satisfies the seal condition, it is possible to reduce the sound pressure level as compared with the conventional case, and it is possible to satisfy the flow rate condition as compared with “67°”. .. Therefore, it can be confirmed that when the sealing portions 66 and 67 satisfy the sealing conditions, the performances at the flow rate and the sound pressure level are well balanced.
　したがって、上述の実施形態によれば、各シール部６６，６７がシール条件を満たす場合、ポンプ部４は、適正な燃料の吐出流量を確保できる。また、各シール部６６，６７の２つの直線Ｌ１，Ｌ２間の間の角度θ１，θ２が上記式（１）満たすことにより、各シール部６６，６７の周方向の範囲（長さ）を適正にできる。この結果、吐出口４８から吸入口５３に送られる燃料の減圧沸騰を抑制でき、ポンプ部４の音圧レベルを低減してポンプ部４の駆動時の騒音を低減できる。 Therefore, according to the above-described embodiment, when each of the seal portions 66 and 67 satisfies the seal condition, the pump portion 4 can secure an appropriate fuel discharge flow rate. Further, the angles θ1 and θ2 between the two straight lines L1 and L2 of the seal portions 66 and 67 satisfy the above equation (1), so that the circumferential range (length) of the seal portions 66 and 67 is appropriate. You can As a result, depressurization boiling of the fuel sent from the discharge port 48 to the suction port 53 can be suppressed, the sound pressure level of the pump unit 4 can be reduced, and the noise when the pump unit 4 is driven can be reduced.
　また、ポンプ部４のポンプケース４１は、インペラ４０の上面を覆うアッパーケース４３と、インペラ４０の下面を覆うロワケース４２と、を有している。アッパーケース４３は、ポンプ部４から燃料を吐出する吐出口４８と、第１摺接面４３ｄに形成された第１流路溝６４と、を有している。ロワケース４２は、ポンプ部４に燃料を吸い上げる吸入口５３と、第２摺接面４２ｃに形成された第２流路溝６５と、を有している。そして、アッパーケース４３の第１摺接面４３ｄにおける吐出口４８（凹部４８ａ）と第１流路溝６４の先細り部６４ａとの間を第１シール部６６としている。また、ロワケース４２の第２摺接面４２ｃにおける吸入口５３（テーパ孔部５３ａ）と第２流路溝６５の先細り部６５ａとの間を第２シール部６７としている。このような構成で、インペラ４０、第１流路溝６４、及び第２流路溝６５を利用して燃料をモータ部３に圧送し、各シール部６６，６７によって燃料の漏出を確実に抑制できるので、ポンプ部４の構成を簡素化できる。 The pump case 41 of the pump unit 4 has an upper case 43 that covers the upper surface of the impeller 40 and a lower case 42 that covers the lower surface of the impeller 40. The upper case 43 has a discharge port 48 for discharging fuel from the pump unit 4, and a first flow path groove 64 formed in the first sliding contact surface 43d. The lower case 42 has a suction port 53 for sucking fuel into the pump portion 4, and a second flow path groove 65 formed in the second sliding contact surface 42c. The first seal portion 66 is formed between the discharge port 48 (recess 48 a) on the first sliding contact surface 43 d of the upper case 43 and the tapered portion 64 a of the first flow path groove 64. A second seal portion 67 is formed between the suction port 53 (taper hole portion 53a) on the second sliding contact surface 42c of the lower case 42 and the tapered portion 65a of the second flow path groove 65. With such a configuration, the impeller 40, the first flow path groove 64, and the second flow path groove 65 are used to pressure-feed the fuel to the motor unit 3, and the seal portions 66 and 67 reliably suppress the leakage of the fuel. Therefore, the structure of the pump unit 4 can be simplified.
　なお、本発明は上述の実施形態に限られるものではなく、本発明の趣旨を逸脱しない範囲において、上述の実施形態に種々の変更を加えたものを含む。 The present invention is not limited to the above-described embodiment, and includes various modifications of the above-described embodiment without departing from the spirit of the present invention.
　例えば、上述の実施形態では、自動二輪車や四輪車等の車両用の燃料ポンプとして用いられる液体供給装置１について説明した。しかしながら、液体供給装置１は、さまざまな液体を圧送するために用いることが可能である。 For example, in the above-described embodiment, the liquid supply device 1 used as a fuel pump for a vehicle such as a motorcycle or a four-wheel vehicle has been described. However, the liquid supply device 1 can be used to pump various liquids.
　また、上述の実施形態では、モータ部３として、例えばブラシ付きモータを採用した場合について説明した。しかしながら、これに限られるものではなく、モータ部３として、例えばブラシレスモータを採用することも可能である。 Further, in the above-described embodiment, the case where a motor with a brush is adopted as the motor unit 3 has been described. However, the invention is not limited to this, and it is also possible to employ, for example, a brushless motor as the motor unit 3.
　また、上述の実施形態では、ポンプケース４１は、アッパーケース４３、ミドルケース４４、及びロワケース４２により構成されている場合について説明した。しかしながら、これに限られるものではなく、一体化されたアッパーケース４３とミドルケース４４とを１つのアッパーケース４３と称してもよい。さらに、ポンプケース４１は、インペラ４０を回転自在に収納する収納部６０を有していればよく、アッパーケース４３、とロワケース４２とで分割構成されていなくてもよい。例えば、ミドルケース４４とロワケース４２とを一体化し、これらミドルケース４４とロワケース４２とを１つのロワケース４２と称してもよい。 Further, in the above-described embodiment, the case where the pump case 41 is configured by the upper case 43, the middle case 44, and the lower case 42 has been described. However, the present invention is not limited to this, and the integrated upper case 43 and middle case 44 may be referred to as one upper case 43. Further, the pump case 41 only needs to have the storage portion 60 that rotatably stores the impeller 40, and may not be divided into the upper case 43 and the lower case 42. For example, the middle case 44 and the lower case 42 may be integrated, and the middle case 44 and the lower case 42 may be referred to as one lower case 42.
　本出願は、２０１９年１月１６日出願の日本特許出願（特願２０１９－００４８７７）に基づくものであり、それらの内容はここに参照として取り込まれる。 This application is based on the Japanese patent application (Japanese Patent Application No. 2019-004877) filed on January 16, 2019, the contents of which are incorporated herein by reference.
　本発明の非容積型ポンプ及び液体供給装置によれば、例えば、吐出流量を適正に確保しながら、吐出口から吸入口へ漏出した液体の減圧沸騰を抑制できる。この効果を奏する本発明は、例えば、自動二輪車や四輪車等の車両用の燃料ポンプに関して有用である。 According to the non-positive displacement pump and the liquid supply device of the present invention, for example, it is possible to suppress the depressurization boiling of the liquid leaked from the discharge port to the suction port while appropriately ensuring the discharge flow rate. The present invention having this effect is useful for a fuel pump for vehicles such as motorcycles and four-wheeled vehicles.
１…液体供給装置、３…モータ部、４…ポンプ部（非容積型ポンプ）、１４…回転軸、４０…インペラ、４１…ポンプケース、４２…ロワケース、４２ｃ…第２摺接面、４３…アッパーケース、４３ｄ…第１摺接面、４８…吐出口、５３…吸入口、６０…収納部、６２…羽根部、６３…貫通流路、６４…第１流路溝、６５…第２流路溝、６６…第１シール部（シール部）、６７…第２シール部（シール部）、Ｃ…軸心（回転中心）、Ｌ１，Ｌ２…直線、θ１，θ２…角度 DESCRIPTION OF SYMBOLS 1... Liquid supply device, 3... Motor part, 4... Pump part (non-volume pump), 14... Rotation shaft, 40... Impeller, 41... Pump case, 42... Lower case, 42c... 2nd sliding contact surface, 43... Upper case, 43d... First sliding contact surface, 48... Discharge port, 53... Suction port, 60... Storage section, 62... Blade section, 63... Through channel, 64... First channel groove, 65... Second flow Road groove, 66... First seal part (seal part), 67... Second seal part (seal part), C... Shaft center (rotation center), L1, L2... Straight line, θ1, θ2... Angle

Claims (3)

  1. 　円板状のインペラと、
    　前記インペラの全体を覆うように形成され、前記インペラの径方向中心を回転中心とし
    て前記インペラを回転自在に収容したポンプケースと、を備え、
    　前記インペラは、
    　前記インペラの外周部寄りに、周方向に並んで形成された複数の羽根部と、
    　前記周方向に隣接する前記羽根部の間に形成され、前記インペラを板厚方向に貫通する複数の貫通流路と、を有し、
    　前記ポンプケースは、
    　前記インペラを収納する収納部と、
    　前記収納部と前記ポンプケースの外側とを前記インペラの板厚方向に貫通するとともに、前記貫通流路に連通する吸入口と、
    　前記インペラを挟んで前記吸入口とは反対側に配置され、前記収納部と前記ポンプケースの外側とを前記板厚方向に貫通するとともに、前記貫通流路に連通する吐出口と、
    　前記周方向における前記吸入口と前記吐出口との間に設けられるシール部と、を有し、
    　前記シール部の前記周方向における両端と、前記回転中心と、を結ぶ２つの直線の間の角度は、４３°以上４７°以下であり、
    　前記シール部は、前記両端の間に少なくとも２つの前記貫通流路を閉塞可能な大きさを有する、
    　非容積型ポンプ。     A disc-shaped impeller,
    A pump case formed so as to cover the entire impeller and rotatably accommodating the impeller with a radial center of the impeller as a rotation center;
    The impeller is
    A plurality of blade portions formed side by side in the circumferential direction, near the outer peripheral portion of the impeller,
    A plurality of through-flow passages formed between the vane portions adjacent to each other in the circumferential direction and penetrating the impeller in the plate thickness direction,
    The pump case is
    A storage unit for storing the impeller,
    A suction port that penetrates the storage part and the outside of the pump case in the plate thickness direction of the impeller, and that communicates with the through-flow passage,
    Disposed on the opposite side of the suction port with the impeller interposed therebetween, while penetrating the storage part and the outside of the pump case in the plate thickness direction, and a discharge port communicating with the through flow passage,
    A seal portion provided between the suction port and the discharge port in the circumferential direction,
    An angle between two straight lines connecting both ends of the seal portion in the circumferential direction and the rotation center is 43° or more and 47° or less,
    The seal portion has a size capable of closing at least two of the through flow paths between the both ends,
    Non displacement pump.
  2. 　請求項１に記載の非容積型ポンプにおいて、
    　前記ポンプケースは、
    　前記インペラの一面に摺接され、前記一面を覆うアッパーケースと、
    　前記インペラの前記一面とは反対側の他面に摺接され、前記他面を覆うロワケースと、を有し、
    　前記アッパーケースと前記ロワケースとにより前記収納部が画成され、
    　前記アッパーケースは、
    　前記吐出口と、
    　前記インペラに面する第１摺接面に設けられるとともに前記吐出口に連通される円弧状の第１流路溝と、を有し、
    　前記ロワケースは、
    　前記吸入口と、
    　前記インペラに面する第２摺接面に設けられるとともに前記吸入口に連通される円弧状の第２流路溝と、を有し、
    　前記シール部は、
    　前記吐出口と前記吸入口との間であり且つ前記貫通流路の回転軌跡上にある
    　非容積型ポンプ。     The non-positive displacement pump according to claim 1,
    The pump case is
    An upper case that is in sliding contact with one surface of the impeller and covers the one surface,
    A lower case that is in sliding contact with the other surface of the impeller opposite to the one surface, and covers the other surface,
    The storage portion is defined by the upper case and the lower case,
    The upper case is
    The discharge port,
    An arc-shaped first flow path groove provided on a first sliding contact surface facing the impeller and communicating with the discharge port,
    The lower case is
    The inlet,
    An arc-shaped second flow path groove provided on a second sliding contact surface facing the impeller and communicating with the suction port,
    The seal portion is
    A non-volumetric pump that is located between the discharge port and the suction port and located on the rotation path of the through-flow passage.
  3. 　請求項１又は請求項２に記載の非容積型ポンプと、
    　前記非容積型ポンプを駆動するモータ部と、を備え、
    　前記モータ部の回転軸と前記インペラとが相対回転不能に連結されている、
    　液体供給装置。     A non-positive displacement pump according to claim 1 or 2,
    A motor unit for driving the non-positive displacement pump,
    The rotation shaft of the motor unit and the impeller are connected so as not to rotate relative to each other,
    Liquid supply device.
PCT/JP2020/001379 2019-01-16 2020-01-16 Non-positive displacement type pump and liquid supply device WO2020149382A1 (en)

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BR112021014002-6A BR112021014002A2 (en) 2019-01-16 2020-01-16 NON-POSITIVE DISPLACEMENT PUMP AND LIQUID SUPPLY DEVICE
EP20741647.0A EP3913228A4 (en) 2019-01-16 2020-01-16 Non-positive displacement type pump and liquid supply device
JP2020566487A JP7350020B2 (en) 2019-01-16 2020-01-16 Non-displacement pumps and liquid supply devices
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