WO2015064281A1 - 高圧燃料供給ポンプ - Google Patents

高圧燃料供給ポンプ Download PDF

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Publication number
WO2015064281A1
WO2015064281A1 PCT/JP2014/076235 JP2014076235W WO2015064281A1 WO 2015064281 A1 WO2015064281 A1 WO 2015064281A1 JP 2014076235 W JP2014076235 W JP 2014076235W WO 2015064281 A1 WO2015064281 A1 WO 2015064281A1
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WO
WIPO (PCT)
Prior art keywords
passage
valve
fuel
valve seat
bent
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2014/076235
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
俊亮 有冨
悟史 臼井
斉藤　淳治
達夫 河野
菅波　正幸
徳尾　健一郎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
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 Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Priority to EP14858910.4A priority Critical patent/EP3064760B1/en
Priority to US15/032,941 priority patent/US9797387B2/en
Priority to CN201480059935.5A priority patent/CN105683557B/zh
Publication of WO2015064281A1 publication Critical patent/WO2015064281A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/368—Pump inlet valves being closed when actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1087—Valve seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/025—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by a single piston

Definitions

  • the present invention relates to a high-pressure fuel supply pump used for an internal combustion engine.
  • JP 2012-154297 A Patent Document 1
  • a suction valve is provided on the pressure chamber side of a valve seat formed on a cylindrical valve body fixed to the inner wall of the supply passage, and the supply passage is blocked by the suction valve seating on the valve seat.
  • a high-pressure pump high-pressure fuel supply pump
  • a needle configured separately from the intake valve is configured to be able to contact an end surface on the valve seat side of the intake valve, and the end portion of the needle that contacts an end surface on the valve seat side of the intake valve
  • a movable core is provided at the end opposite to the side.
  • a tapered portion having an outer diameter on the suction valve side smaller than the outer diameter on the movable core side is provided on the radially outer side of the needle in the inner flow path formed on the inner diameter side of the valve body.
  • valve seat portion flow passage formed between the valve seat and the intake valve separated from the valve seat, and this valve seat portion flow passage And an inner flow path formed on the downstream side.
  • the valve seat is formed as a surface (hereinafter referred to as a valve seat surface) perpendicular to the central axis of the needle, and the inner flow path is formed as an inner flow path parallel to the central axis of the needle. For this reason, the valve seat part flow path and the internal flow path constitute a flow path bent at a right angle.
  • valve seat surface and the inner peripheral surface of the valve body connected to the valve seat constitute the inner peripheral flow path surface of the bent flow path and include the central axis of the needle. When viewed on a cross section parallel to, they intersect at right angles.
  • the fuel flow from the pressurizing chamber side to the damper chamber side is peeled off from the flow path surface at the bent portion on the inner peripheral side of the bent flow path, and a vortex is generated. Further, when the fuel passes through the valve seat, bubbles are generated. Bubbles generated when passing through the valve seat stay in the vicinity of the bent portion on the inner peripheral side of the bent flow path due to the vortex and disappear in the vicinity of the bent portion on the inner peripheral side. That is, cavitation occurs in the vicinity of the bent portion on the inner peripheral side of the bent flow path. If this bubble disappears in the vicinity of the bent portion on the inner peripheral side, that is, in the vicinity of the valve seat surface, erosion may occur on the valve seat surface.
  • An object of the present invention is to reduce erosion due to cavitation in the vicinity of a valve seat in a high-pressure fuel supply pump in which a fuel flow path having a bent portion is formed in the vicinity of the valve seat.
  • a high-pressure fuel supply pump includes a plunger that reciprocates, a fuel pressure chamber whose volume changes due to the reciprocating motion of the plunger, and a fuel passage that communicates with the pressure chamber.
  • a fluid valve provided in the fuel passage, the fluid valve being held in a movable state in the fuel passage, and being seated or separated from the valve seat.
  • a valve member that closes or opens the fuel passage by being seated, and the fuel passage includes a gap passage portion formed in a gap between the valve seat and the valve member, and a downstream of the gap passage portion.
  • a high-pressure fuel supply pump having a bent passage portion extending in a direction bent with respect to the gap passage portion on an inner side of the bent fuel passage portion formed by the gap passage portion and the bent passage portion
  • a path surface is obtained by forming a recess in the passage surface of the upstream end portion of the bent passage portion.
  • the fuel flow containing the bubbles is separated from the passage surface at the bent portion and flows to the downstream passage portion beyond the recess formed on the inner peripheral passage surface of the bent portion.
  • the fuel flow is stagnated in the recess, and the bubbles flow downstream without remaining in the vicinity of the valve seat. For this reason, bubbles do not disappear near the valve seat, but disappear at a position away from the valve seat. Thereby, generation
  • FIG. 2 is an enlarged cross-sectional view of an electromagnetically driven intake valve in the high-pressure fuel supply pump of FIG. 1, showing a state when the valve is opened (at the time of fuel intake and spill).
  • FIG. 5 is a cross-sectional view showing the vicinity of a valve seat and a valve member in an electromagnetically driven intake valve, and is a view showing a modification of FIG. 4.
  • FIG. 5 is a cross-sectional view showing the vicinity of a valve seat and a valve member in an electromagnetically driven intake valve, and is a view showing a modification of FIG. 4. It is sectional drawing which shows the Example which applied this invention to the non-return valve which comprises a discharge valve. It is sectional drawing which shows the Example which applied this invention to the internal opening valve. As a comparative example with the present invention, it is a cross-sectional view showing the vicinity of a valve seat and a valve member in an electromagnetically driven intake valve, and is a view showing a state during backflow.
  • FIG. 1 is a longitudinal sectional view showing the overall structure of a high-pressure fuel supply pump according to a first embodiment of the present invention.
  • FIG. 2 is a system configuration diagram showing an example of a fuel supply system using the high-pressure fuel supply pump of FIG.
  • FIG. 3 is an enlarged cross-sectional view showing the electromagnetically driven intake valve in the high-pressure fuel supply pump of FIG. 1, and is a view showing a state when the valve is opened (at the time of fuel intake and spilling).
  • symbol cannot be attached
  • the pump housing 1 is provided with a recess 12A that forms a bottomed cylindrical space with one end open, and a cylinder 20 is inserted into the recess 12A from the open end side.
  • the outer periphery of the cylinder 20 and the pump housing 1 are sealed by a pressure contact portion 20A. Since the piston plunger 2 is slidingly engaged with the cylinder 20, the space between the inner peripheral surface of the cylinder 20 and the outer peripheral surface of the piston plunger 2 is sealed with fuel that enters between the sliding surfaces.
  • the pressurizing chamber 12 is defined between the tip of the piston plunger 2, the inner wall surface of the recess 12A, and the outer peripheral surface of the cylinder 20.
  • a cylindrical hole 200H is formed from the peripheral wall of the pump housing 1 toward the pressurizing chamber 12, and the cylindrical hole 200H has a suction valve portion INV and an electromagnetic drive mechanism portion EMD of the electromagnetically driven suction valve mechanism 200. A part of is inserted.
  • the joint surface 200R between the outer peripheral surface of the electromagnetically driven suction valve mechanism 200 and the cylindrical hole 200H is joined by the gasket 300, whereby the inside of the pump housing 1 is sealed from the atmosphere.
  • the cylindrical hole 200H sealed by attaching the electromagnetically driven intake valve mechanism 200 functions as the low pressure fuel chamber 10a.
  • a cylindrical hole 60 ⁇ / b> H is provided from the peripheral wall of the pump housing 1 toward the pressurizing chamber 12 at a position facing the cylindrical hole 200 ⁇ / b> H across the pressurizing chamber 12.
  • a discharge valve unit 60 is mounted in the cylindrical hole 60H.
  • the discharge valve unit 60 has a valve seat (valve seat) 61 formed at the tip, and a valve seat member (valve seat member) 61B provided with a through hole 11A serving as a discharge passage at the center.
  • a valve holder 62 surrounding the periphery of the valve seat 61 is fixed to the outer periphery of the valve seat member 61B.
  • a valve (valve element) 63 and a spring 64 that urges the valve 63 in a direction of pressing the valve 63 against the valve seat 61 are provided in the valve holder 62.
  • a discharge joint 11 fixed to the pump housing 1 by screw fastening is provided at the opening portion on the side opposite to the pressure chamber of the cylindrical hole 60H.
  • the electromagnetically driven suction valve mechanism 200 includes a plunger rod 201 that is electromagnetically driven.
  • a valve (valve element) 203 is provided at the tip of the plunger rod 201, and a valve seat (valve seat) 214S formed in a valve housing (valve seat member) 2 14 provided at the end of the electromagnetically driven intake valve mechanism 200. Are facing each other.
  • a plunger rod biasing spring 202 is provided at the other end of the plunger rod 201, and the valve 203 biases the plunger rod 201 in a direction away from the valve seat 214S.
  • a valve stopper S0 is fixed to the inner periphery of the tip of the valve housing 214.
  • the valve 203 is held between the valve seat 214S and the valve stopper S0 so as to be able to reciprocate.
  • a valve urging spring S4 is disposed between the valve 203 and the valve stopper S0, and the valve 203 is urged in a direction away from the valve stopper S0 by the valve urging spring S4.
  • valve 203 and the tip of the plunger rod 201 are urged by respective springs in opposite directions.
  • the plunger rod urging spring 202 is formed of a stronger spring, the plunger rod 201 is urged by the valve.
  • the valve 203 is pressed against the force of the spring S4 in the direction away from the valve seat 214S (right direction in the drawing), and as a result, the valve 203 is pressed against the valve stopper S0.
  • the plunger rod 201 causes the plunger 203 biasing spring 202 to connect the valve 203 to FIGS. As shown in FIG. 3, the valve is kept in the open position (detailed configuration will be described later).
  • the fuel is guided from the fuel tank 50 to the suction joint 10 (see FIG. 1) as a fuel inlet of the pump housing 1 by the low pressure pump 51.
  • a plurality of injectors 54 and pressure sensors 56 are mounted on the common rail 53.
  • the injectors 54 are mounted in accordance with the number of cylinders of the engine, and inject high-pressure fuel sent to the common rail 53 into each cylinder in response to a signal from an engine control unit (ECU) 600.
  • ECU engine control unit
  • a relief valve mechanism (not shown) built in the pump housing 1 opens when the pressure in the common rail 53 exceeds a predetermined value, and returns excess high-pressure fuel to the upstream side of the discharge valve 60.
  • a lifter 3 provided at the lower end of the piston plunger 2 is pressed against a cam 7 by a spring 4.
  • the piston plunger 2 is slidably held by the cylinder 20 and reciprocates by the cam 7 rotated by an engine cam shaft or the like to change the volume in the pressurizing chamber 12.
  • the outer periphery of the lower end of the cylinder 20 is held by a cylinder holder 21, and the cylinder holder 21 is fixed to the pump housing 1 and is pressed against the pump housing 1 by a metal seal portion 20 ⁇ / b> A.
  • the cylinder holder 21 is provided with a plunger seal 5 for sealing the outer periphery of the small diameter portion 2A formed on the lower end side of the piston plunger 2.
  • the assembly of the cylinder 20 and the piston plunger 2 is inserted into the pressurizing chamber, and the male thread portion 21A formed on the outer periphery of the cylinder holder 21 is the thread portion 1A of the female thread portion formed on the inner periphery of the open side end of the recess 12A of the pump housing 1. Screw in.
  • the cylinder holder 21 pushes the cylinder 20 toward the pressurizing chamber while the stepped portion 21D of the cylinder holder 21 is engaged with the peripheral edge of the cylinder 20 on the side opposite to the pressurizing chamber. It is pressed against the pump housing 1 to form a seal portion by metal contact.
  • the O-ring 21B seals between the inner peripheral surface of the mounting hole EH formed in the engine block ENB and the outer peripheral surface of the cylinder holder 21.
  • the O-ring 21 ⁇ / b> C seals the space between the inner peripheral surface of the recess 12 ⁇ / b> A of the recess 12 ⁇ / b> A of the pump housing 1 and the outer peripheral surface of the cylinder holder 21 at the position of the screw portion 21 ⁇ / b> A (1 ⁇ / b> A) on the anti-pressurization chamber side.
  • the pump is screwed to the engine block with a flange (details are omitted) of the pump housing 1 and is thereby fixed to the engine block.
  • a damper chamber 10b is formed in the middle of the passage from the suction joint 10 to the low pressure fuel chamber 10a, and a double metal diaphragm type damper 80 is accommodated in the state sandwiched between the damper holder 30 and the damper cover 40. Yes.
  • the double metal diaphragm damper 80 has a pair of upper and lower metal diaphragms 80A and 80B butted together and welded around the entire circumference to seal the inside.
  • An inert gas such as argon is sealed in the hollow portion formed by the two-plate metal diaphragms 80A and 80B, and the volume of the hollow portion changes in response to an external pressure change. Play.
  • a step portion is formed on the inner periphery of the damper cover 40, and an annular groove is provided in the step portion, and the outer peripheral weld portion of the double metal diaphragm type damper 80 is completely fitted in this groove, so that the peripheral wall surface Arranged so that the external force is not transmitted and the inner surface of the stepped portion is held on the inner side of the outer peripheral welded portion of the surface of one side of the double metal diaphragm type damper 80 (the surface of the damper cover where the suction joint 10 is attached). To do.
  • the damper holder 30 is a cup-shaped member having no bottom (a member having a curved hole with a hole in the center and a cross-section bent inward around the hole), and the outer periphery is press-fitted into the inner peripheral surface of the damper cover 40.
  • the end surface portion of the bent portion is in contact with the annular surface inside the welded portion on the outer periphery of the double metal diaphragm damper 80 over the entire circumference.
  • the double metal diaphragm type damper 80 is combined with the damper holder 30 and the damper cover 40 into one set.
  • the damper chamber 10b is formed by screwing the pump housing 1 and the damper cover 40 together.
  • the suction joint 10 is formed integrally with the damper cover 40 so as to be perpendicular to the center of the upper surface of the damper cover 40. For this reason, even if the threaded portion formed on the outer periphery of the damper cover 40 is screwed into the threaded portion engraved on the inner wall of the pump housing 1, the posture of the suction joint 10 becomes the same at any position in the rotational direction. Since the screwing position is not limited, the assembly of the damper cover 40 is improved.
  • the fuel passage 80U between the diaphragm 80A on one side of the two-plate metal diaphragm damper 80 and the damper cover 40 is a damper chamber 10b (two sheets) as a fuel passage through a groove passage 80C provided in the inner peripheral wall of the damper cover 40. And a fuel passage faced by a diaphragm 80B on one side of the metal diaphragm damper 80.
  • the damper chamber 10b communicates with the low-pressure fuel chamber 10a in which the electromagnetically driven intake valve 20 is located by a communication hole 10c formed in the pump housing 1 constituting the bottom wall of the damper chamber 10b.
  • the fuel sent from the feed pump 50 flows into the damper chamber 10b of the pump from the suction joint 10 and acts on both diaphragms 80A and 80B of the double metal diaphragm damper 80 while passing through the communication hole 10c and the low pressure fuel chamber 10a. It flows to.
  • the connecting portion between the small diameter portion 2A of the piston plunger 2 and the large diameter portion 2B sliding with the cylinder 21 is connected by a conical surface 2K.
  • a fuel subchamber 250 is formed between the plunger seal 5 and the lower end surface of the cylinder 21 around the conical surface.
  • the fuel sub chamber 250 captures fuel leaking from the sliding surface between the cylinder 20 and the piston plunger 2.
  • An annular passage 21G defined between the inner peripheral surface of the pump housing 1, the outer peripheral surface of the cylinder 21, and the upper end surface of the cylinder holder 21 has one end at the damper chamber 10b by a vertical passage 250B formed through the pump housing 1. And is connected to the fuel sub chamber 250 via a fuel passage 250 ⁇ / b> A formed in the cylinder holder 21.
  • the damper chamber 10A and the fuel sub chamber 250 communicate with each other by the longitudinal passage 250B, the annular passage 21G, and the fuel passage 250A.
  • the taper surface 2K reciprocates in the fuel sub chamber, so that the volume of the fuel sub chamber 250 changes.
  • the volume of the fuel sub chamber 250 increases, fuel flows from the damper chamber 10b into the fuel sub chamber 250 through the vertical passage 250B, the annular passage 21G, and the fuel passage 250A.
  • the volume of the fuel sub chamber 250 decreases, fuel flows from the fuel sub chamber 250 into the damper chamber 10b via the vertical passage 250B, the annular passage 21G, and the fuel passage 250A.
  • the damper chamber 10b is configured such that the fuel from the suction joint 10, the fuel from the fuel sub chamber 250, the overflow fuel from the pressurizing chamber 12, and the fuel from the relief valve (not shown) join together. .
  • the fuel pulsation of the respective fuels merges in the damper chamber 10b and is absorbed by the double metal diaphragm damper 80.
  • the electromagnetically driven intake valve 200 includes a yoke 205 that also serves as the body of the electromagnetically driven mechanism EMD on the inner peripheral side of the annularly formed coil 204.
  • a fixed core 206 and an anchor 207 are accommodated in an inner peripheral portion with a plunger rod biasing spring 202 interposed therebetween.
  • the yoke 205 is divided into a side yoke 205A and an upper yoke 205B and joined by press-fitting.
  • the fixed core 206 is divided into an outer core 206A and an inner core 206B and joined by press-fitting.
  • the anchor 207 is fixed to the end of the plunger rod 201 opposite to the valve by welding, and faces the inner core 206B via a magnetic gap GP.
  • the coil 204 is housed in the yoke 205, and both are fixed by screwing and fastening a screw portion provided on the outer periphery of the open end portion of the side yoke 205A with the screw portion 1SR of the pump housing 1.
  • the flange portion 206F formed by the open end portion of the side yoke 205A on the outer periphery of the outer core 206A is pushed toward the pump housing, and the outer periphery of the open-side end tubular portion 206G of the outer core 206A is the pump housing. It is inserted into the inner peripheral surface of one guide hole 1GH. Further, an annular enlarged diameter portion 206GS formed as a stepped portion on the outer periphery of the open side end tubular portion 206G of the outer core 206A is press-contacted to the annular surface portion 1GS formed around the opening side of the guide hole 1GH of the pump housing 1. To do.
  • the seal ring 206SR disposed between the annular surface portion 1GS formed around the opening side of the guide hole 1GH of the pump housing 1 formed at this time and the flange portion 206F formed on the outer periphery of the outer core 206A is compressed.
  • the space on the low pressure side including the space on the inner peripheral portion of the fixed core 206 and the low pressure fuel chamber 10a is sealed against the atmosphere.
  • a closed magnetic path CMP that crosses the magnetic gap GP is formed around the coil 204 by the side yoke 205A and the upper yoke 205B, the outer core 206A and the inner core 206B, and the anchor 207.
  • the portion of the outer core 206A that faces the periphery of the magnetic gap GP is formed thin (a groove is formed when viewed from the outer periphery), and this groove portion is a magnetic diaphragm 206S (magnetic resistance) of the closed magnetic circuit CMP.
  • the urging force SP1 of the plunger rod urging spring 202 is set larger than the urging force of the urging force SP2 of the valve urging spring S4, the urging forces of both springs urge the valve 203 in the valve opening direction at this time. Further, the valve 203 is opened by the pressure difference between the static pressure P1 of the fuel acting on the outer surface of the valve 203 represented by the flat portion 203F of the valve 203 located in the low pressure fuel chamber 10a and the fuel pressure P12 in the pressurized chamber. Receives force in the valve direction.
  • the fluid frictional force P2 generated between the fuel flow flowing into the pressurizing chamber 12 along the arrow R4 through the fuel introduction passage 10P and the peripheral surface of the cylindrical portion 203H of the valve 203 causes the valve 203 to open in the valve opening direction.
  • the dynamic pressure P3 of the fuel flow passing through the annular fuel passage 10S formed between the valve seat 214S and the annular surface portion 203R of the valve 203 acts on the annular surface portion 203R of the valve 203 to attach the valve 203 in the valve opening direction.
  • the valve 203 having a weight of several milligrams is quickly opened when the piston plunger 2 starts to descend by these urging forces, and strokes until it collides with the stopper S0.
  • the valve seat 214 is formed on the outer side in the diameter direction than the cylindrical portion 203H of the valve 203 and the fuel introduction passage 10P. As a result, the area on which P1, P2, and P3 act can be increased, and the valve opening speed of the valve 203 can be increased. At this time, the plunger rod 201 and the anchor 207 are filled with the staying fuel, and the friction force with the bearing 214B acts, so that the plunger rod 201 and the anchor 207 are slightly more than the valve opening speed of the valve 203. The stroke to the right of the drawing is delayed. As a result, a slight gap is formed between the distal end surface of the plunger rod 201 and the flat portion 203F of the valve 203.
  • valve opening force provided from the plunger rod 201 falls for a moment.
  • the valve 203 is opened to reduce the valve opening force applied from the plunger rod 201 (plunger rod biasing spring 202).
  • the fluid force in the direction is compensated.
  • the valve 203 is opened, the static pressure and dynamic pressure of the fluid act on the entire surface of the valve 203 on the low pressure fuel chamber 10a side, so that the valve opening speed is increased.
  • valve guide formed by the cylindrical surface SG of the protruding portion ST of the valve stopper S0, and the valve 203 is not displaced in the radial direction. Stroke smoothly.
  • the cylindrical surface SG forming the valve guide is formed across the upstream side and the downstream side across the surface on which the valve seat 214S is formed, and not only can the stroke of the valve 203 be sufficiently supported, Since the circumferential dead space can be used effectively, the axial dimension of the suction valve portion INV can be shortened.
  • valve biasing spring S4 is installed between the end surface SH of the valve stopper S0 and the bottom surface of the flat surface portion 203F of the valve 203 on the valve stopper S0 side, the valve biasing spring S4 is formed between the opening 214P and the cylindrical portion 203H of the valve 203.
  • the valve 203 and the valve biasing spring S4 can be arranged inside the opening 214C while ensuring a sufficient passage area of the fuel introduction passage 10p formed therebetween.
  • the valve biasing spring S4 can be disposed by effectively utilizing the dead space on the inner peripheral side of the valve 203 located inside the opening 214C forming the fuel introduction passage 10p, the dimension of the intake valve portion INV in the axial direction can be arranged. Can be shortened.
  • the valve 203 has a valve guide SG at its center, and has an annular protrusion 203S that contacts the receiving surface S2 of the annular surface S3 of the valve stopper S0 on the outer periphery of the valve guide SG. Further, a valve seat 214S is formed at a position on the radially outer side. On the radially outer side of the valve seat 214S and the annular surface portion 203R of the valve 203, there are three fuel passages Sn1 to Sn3 with the guide hole 1GH formed in the pump housing 1 as the passage wall surface in the circumferential direction of the guide hole 1GH, etc. Arranged at intervals. Since the fuel passages Sn1 to Sn3 are formed on the radially outer side of the valve seat 214S, there is an advantage that the cross-sectional areas of the fuel passages Sn1 to Sn3 can be made sufficiently large.
  • annular gap SGP is provided on the outer peripheral portion of the annular protrusion 203S, when the valve 203 is pressed against the valve seat 214 by quickly applying the fluid pressure P4 on the pressure chamber side to the annular gap SGP during the valve closing operation.
  • the valve closing speed can be increased.
  • valve 203 Presses the valve 203 against the stopper S0. Rather, the valve 203 and the stopper S0 are attracted by the fluid force pressing the valve 203 toward the stopper S0 by the dynamic pressure of the fuel flowing into the annular fuel passage 10S of the valve seat 214 and the suction effect of the fuel flow flowing around the outer periphery of the annular gap SGP. The valve 203 is firmly pressed against the stopper S0 by the fluid force acting on.
  • the fuel in the pressurizing chamber 12 flows into the low-pressure fuel chamber 10a in the order of the fuel passages Sn1 to Sn3, the annular fuel passage 10S, and the fuel introduction passage 10P.
  • the fuel passage cross-sectional area of the fuel passage 10S is set smaller than the fuel passage cross-sectional areas of the fuel passages Sn1 to Sn3 and the fuel introduction passage 10P. That is, the smallest fuel flow path cross-sectional area is set in the annular fuel path 10S.
  • the fuel in the storage chamber 206K of the magnetic gap GP and the plunger rod biasing spring 202 is discharged to the low pressure passage through the through hole 201H or from the fuel passage 214K to the low pressure passage through the periphery of the anchor 207.
  • the anchor 207 and the plunger rod 201 are smoothly displaced toward the inner core 206B.
  • the anchor 207 and the plunger rod 201 stop moving.
  • the valve 203 starts a valve closing motion.
  • the pressure in the annular gap SGP located on the outer peripheral side of the annular protrusion 203S becomes higher than the pressure on the low-pressure fuel 10a side as the pressure in the fuel pressurizing chamber 12 increases, and the valve 203 is closed.
  • the valve 203 comes into contact with the seat 214 and closes, and the annular fuel passage 10S formed between the valve seat 214 and the annular surface portion 203R of the valve 203 in FIG. 3 is closed.
  • the annular gap SGP has an effect of assisting the valve closing movement of the valve 203.
  • the valve closing force of the intake valve is too small, and the valve closing motion is not stable. Therefore, by providing pressure equalizing holes S5 and S6, fuel is supplied to the spring housing space SP through the pressure equalizing holes S5 and S6 when the valve 203 is closed. Thereby, the pressure in the spring housing space SP becomes constant, and the force applied when the valve 203 is closed is stabilized, so that the valve closing timing of the valve 203 can be stabilized. And while improving the responsiveness of both valve opening and closing, variation in valve closing timing can be further reduced.
  • the discharge valve 63 of the discharge valve unit 60 overcomes the force of the discharge valve urging spring 64 and moves away from the valve seat 61, and passes through the discharge joint 11 from the discharge passage 11A through the arrow R6.
  • the fuel is discharged in the direction along
  • the annular gap SGP has an effect of assisting the valve closing movement of the valve 203.
  • the valve closing force of the intake valve is too small, and the valve closing motion is not stable.
  • the fuel is supplied to the spring accommodating space SP through the equalizing holes S5 and S6 when the valve 203 is closed. Therefore, the pressure in the spring accommodating space SP becomes constant, and the valve 203 Since the force applied when the valve is closed is stabilized, the valve closing timing of the valve 203 can be stabilized. As a result, it is possible to further improve the responsiveness of both opening and closing of the valve, and further reduce the variation in valve closing timing.
  • FIG. 9 is a cross-sectional view showing the vicinity of the valve seat 214S ′ and the valve 203 in the electromagnetically driven intake valve as a comparative example with the present embodiment, and shows a state at the time of backflow.
  • the fuel flows from the pressurizing chamber 12 side to the damper chamber 10b side, and becomes a reverse flow with respect to the fuel flow in the fuel discharge state described above.
  • the upstream side and the downstream side are set based on the backflow state.
  • valve seat passage formed between the valve seat (valve seat) 214S ′ and the valve (valve member) 203 is provided in the middle of the fuel passage from the pressurizing chamber 12 side to the damper chamber 10b side.
  • 10S ′ and a fuel introduction passage 10P ′ formed on the downstream side of the annular fuel passage 10S ′ are provided.
  • the valve seat 214S ′ is formed as a surface (hereinafter referred to as a valve seat surface) perpendicular to the central axis of the plunger rod 201 (the driving axis of the valve 203), and the fuel introduction passage 10P ′ is a fuel parallel to the central axis of the plunger rod 201. It is formed as a passage.
  • the annular fuel passage 10S 'and the fuel introduction passage 10P' constitute a flow path bent at a right angle.
  • the valve seat 214S ′ and the inner peripheral surface (the outer peripheral surface of the fuel introduction passage 10P ′) 214D ′ of the valve housing 214 ′ connected to the valve seat 214S ′ constitute an inner peripheral flow path surface of the bent portion, and the plunger When viewed on a cross section including the central axis of the rod 201 and parallel to the central axis, they intersect at a right angle.
  • the annular fuel passage (valve seat passage) 10S ′ is a fuel passage portion formed in a gap between the valve seat (valve seat) 214S ′ and the valve (valve member) 203. It may also be referred to as a radial passage portion 10S ′ or a gap passage portion 10S ′.
  • the fuel introduction passage 10P ′ is a fuel passage portion extending in a direction bent with respect to the gap passage portion 10S ′ on the downstream side of the gap passage portion 10S ′, and in this specification, the axial passage portion 10P. It may be referred to as 'or a bent passage portion 10P'.
  • the fuel flow from the pressurizing chamber 12 side to the damper chamber 10b side is separated from the flow path surface by the inner peripheral side bent portion 214E 'of the bent portion, and a vortex is generated. Further, when the fuel passes through the valve seat 214S ', bubbles are generated. Bubbles generated when passing through the valve seat 214S 'stay in the vicinity of the inner peripheral bent portion 214E' by the vortex, and disappear in the vicinity of the inner peripheral bent portion 214E '. That is, cavitation occurs in the vicinity of the inner peripheral side bent portion 214E '. If this bubble disappears in the vicinity of the bent portion on the inner peripheral side, that is, in the vicinity of the valve seat surface, erosion may occur in the valve seat (seat surface) 214S '.
  • FIG. 4 is a cross-sectional view showing the vicinity of the valve seat 214S and the valve 203 in the electromagnetically driven suction valve, and shows a state at the time of backflow.
  • valve seat (valve seat) 214S fixed to the fuel passage and held in a movable state in the fuel passage, A valve (valve member) 203 that closes or opens the fuel passage by being seated or separated from the seat 214S is disposed.
  • valve seat (valve seat) 214S is formed between the valve seat (valve seat) 214S and the valve (valve member) 203 in the middle of the fuel passage from the pressurizing chamber 12 side to the damper chamber 10b side.
  • An annular fuel passage (valve seat passage) 10S and a fuel introduction passage 10P formed on the downstream side of the annular fuel passage 10S are provided.
  • the valve seat 214S is formed as a surface (hereinafter referred to as a valve seat surface) orthogonal to the central axis of the plunger rod 201 (drive axis of the valve 203), and the fuel introduction passage 10P is a fuel passage parallel to the central axis of the plunger rod 201. Is formed.
  • the annular fuel passage 10S and the fuel introduction passage 10P constitute a flow path bent at a right angle.
  • the valve seat 214S and the inner peripheral surface (the outer peripheral surface of the fuel introduction passage 10P) 214D of the valve housing 214 connected to the valve seat 214S constitute an inner peripheral flow path surface of the bent portion, and the central axis of the plunger rod 201
  • the inner peripheral surface 214D of the valve housing 214 and the valve seat 214S are at an angle of 90 ° at an inner peripheral side bent portion (inner peripheral side corner) 214E.
  • a minute inclined surface for chamfering or an R portion may be formed on the inner peripheral side bent portion 214E. The widths of these inclined surfaces and the R portion are much smaller than the width of the valve seat 214S.
  • the annular fuel passage (valve seat portion passage) 10S is a fuel passage portion formed in the gap between the valve seat (valve seat) 214S and the valve (valve member) 203, and in this specification the radial direction It may be called the passage portion 10S or the gap passage portion 10S.
  • the fuel introduction passage 10P is a fuel passage portion extending in a direction bent with respect to the gap passage portion 10S on the downstream side of the gap passage portion 10S, and in this specification, the axial passage portion 10P or the bent passage. It may be called the part 10P.
  • This embodiment is effective in reducing erosion generated on the seat surface of the valve seat 214S.
  • the cause of this erosion is cavitation.
  • the angle formed by the inner peripheral surface 214D of the valve housing 214 and the valve seat 214S is 90 ° or less, the fuel flow is caused to flow at the inner peripheral side bent portion 214E (in particular, the inner peripheral side bent portion 214E). Peel from the downstream passage surface.
  • a recess 214A that is recessed from the inner peripheral passage surface 214DA is formed in the inner peripheral passage surface 214D of the fuel introduction passage (bent passage portion) 10P located downstream of the inner peripheral bending portion 214E.
  • the recessed portion 214A is formed in the valve housing 214 in which the valve seat 214S is formed, the upstream end reaches the annular fuel passage (gap passage portion) 10S, and the downstream end is the feed introduction formed in the valve housing 214.
  • the passage (bent passage portion) 10P is provided halfway in the fuel flow direction.
  • the fuel introduction passage (bent passage portion) 10P located on the downstream side of the recess 214A is formed on the inner peripheral passage surface 214D of the valve housing 214 and has a step (D2-D1) from the recess 214A.
  • (Bent passage portion) A passage surface 214DA projecting toward the center of 10P is formed.
  • the inner peripheral surface 214D of the valve housing 214 and the valve seat 214S intersect at an angle of 90 ° at the inner peripheral side bent portion (inner peripheral side corner portion) 214E. It has a structure. Even when the angle exceeds 90 °, in an angle range close to 90 °, for example, an angle range exceeding 90 ° several degrees, the fuel flow may be separated to cause vortices. When bubbles generated in the valve seat 214S are confined in this vortex and stay in the vicinity of the valve seat 214S, erosion occurs in the valve seat 214S.
  • the erosion of the valve seat 214S can be prevented by providing the recess 214A. be able to.
  • the configuration in which the angle formed by the inner peripheral surface 214D of the valve housing 214 and the valve seat 214S is 90 ° or less is intended to limit the above-described configuration in which cavitation, fuel flow separation, and erosion in the valve seat 214S occur. is there. Therefore, if the cavitation, fuel flow separation, and erosion in the valve seat 214S occur, the angle is substantially 90 ° or less even if the angle is in an angle range exceeding 90 °. It does not matter if it belongs to the angle range.
  • the valve housing 214 forms a passage surface 214DA that protrudes from the recess 214A to the center side of the fuel introduction passage (bent passage portion) 10P with a step (D2-D1).
  • a step surface forming member 214B (FIG. 5) or 214B ′ (FIG. 6) separate from the valve housing 214 is used to form the passage surface 214DA and the step (D2- D1) may be formed.
  • the step (D2-D1) and the passage surface 214DA that has this step and protrudes from the bottom surface of the recess 214A toward the center of the bent flow passage portion 10P are connected to the valve housing 214 that is a valve seat member. Is formed as a separate member and assembled to the valve housing 214. Thereby, the step (D2-D1) and the passage surface 214DA are formed in the valve housing 214.
  • the entire inner peripheral surface of the valve housing 214 can be formed to be flush with the bottom surface of the recess 214A. Thereby, the processing man-hour of the valve housing 214 is reduced, and the manufacture of the valve housing 214 is facilitated.
  • the upstream end surface and the downstream end surface of the step forming member 214B are each formed by a tapered surface.
  • the recess 214A constitutes the passage surface of the large-diameter fuel passage portion
  • the passage surface 214DA corresponds to the passage surface of the large-diameter fuel passage portion.
  • a passage surface of the small-diameter fuel passage portion is formed.
  • FIG. 7 is a cross-sectional view showing an embodiment in which the concave portion according to the present invention is applied to a check valve constituting the discharge valve unit 60.
  • a valve seat (valve seat) 61 is formed on the end face of the valve seat member 61B.
  • the valve seat 61 is formed as a surface perpendicular to the drive shaft direction of the valve (valve member) 63.
  • a through hole 61C penetrating in the direction of the drive shaft of the valve 63 is formed in the central portion (center portion) of the valve seat member 61B, and this through hole 61C constitutes a fuel passage 61C.
  • the end surface of the valve 63 facing the valve seat 61 is seated or separated from the valve seat 61 to close or open the fuel passage. For this reason, the valve seat 61 is fixed to the fuel passage, and the valve 63 is held in a movable state in the fuel passage.
  • the backflow of fuel occurs during the period from the end of fuel discharge until the valve 63 moves from the valve open position to the valve close position.
  • the upstream side and the downstream side are set based on the backflow state.
  • the fuel passage portion 61C is formed in the drive shaft direction of the valve 63, and may be referred to as an axial passage portion 61C or a bent passage portion 61c.
  • the gap passage portion 301A corresponds to the annular fuel passage 10S in the first embodiment
  • the bent passage portion 61C corresponds to the bent passage portion 10P in the first embodiment
  • the through hole (fuel passage) 61C is the inner peripheral side in the first embodiment.
  • the passage surface 61CA of the bent passage portion 61C corresponds to the passage surface 214DA in the first embodiment
  • the recess 61A corresponds to the recess 214A in the first embodiment.
  • the valve (valve member) 203 is disposed inside the valve housing 214 having the valve seat 214S
  • the valve 63 has the valve seat 61. It is arranged outside 61B.
  • Erosion in the valve seat 61 can be reduced when the recess 61A and the passage surface 61CA have the same effects as the recess 214A and the passage surface 214DA in the first embodiment.
  • the recess 61A constitutes a passage surface of the large-diameter fuel passage portion
  • the passage surface 61C corresponds to the passage surface of the large-diameter fuel passage portion.
  • the passage surface of the small-diameter fuel passage portion is configured.
  • the passage surface 61CA and the step between the bottom surface of the recess 61A and the passage surface 61CA are defined as the valve seat member 61B that is a valve member.
  • the passage surface 61CA and the step may be formed in the valve seat member 61B by being formed as a separate member and assembled to the valve seat member 61B.
  • the passage surface 61CA forms a passage surface protruding from the bottom surface of the recess 61A toward the center of the fuel passage (61C) due to the step.
  • FIG. 8 is a sectional view showing an embodiment in which the present invention is applied to an inner opening valve.
  • a valve seat 800A is formed on the valve seat member 800, and the valve member 801 is disposed inside the valve seat member 800.
  • the reverse fuel flow flows from the radially inner side to the outer side through the gap passage portion 302A formed in the gap between the valve seat 800A and the valve member 801.
  • the upstream side and the downstream side are set and described based on the backflow state.
  • a bent passage portion (axial passage portion) 302B extending in a direction bent with respect to the gap passage portion 302A is provided on the downstream side of the gap passage portion 302A.
  • the valve seat 800A is formed as a surface orthogonal to the drive axis of the valve member 801, and the bent passage 302B is formed as a fuel passage parallel to the drive axis (center axis) of the valve member 801. For this reason, the gap passage portion 302A and the bent passage portion 302B constitute a flow path bent at a right angle.
  • the contact surface (end surface) 801B of the valve member 801 that contacts the valve seat 800A and the outer peripheral surface 801C of the valve member 801 connected to the contact surface 801B are the inner peripheral side flow of the bent portions in the fuel passages 302A and 302B. It constitutes the road surface.
  • the contact surface (end surface) 801B of the valve member 801 and the outer peripheral surface 801C of the valve member 801 are the inner peripheral side when viewed on a cross section (FIG. 8) including the central axis of the valve member 801 and parallel to the central axis. In the bent portion (inner peripheral side corner) 801D, they intersect at an angle of 90 °. In addition, a minute inclined surface for chamfering or an R portion may be formed on the inner peripheral side bent portion 801D. The width of these inclined surfaces and the R portion is much smaller than the width of the valve seat 800A.
  • a concave portion 801A that is recessed from the inner peripheral side passage surface 801CA is formed on the inner peripheral side passage surface (outer peripheral surface of the valve member 801) 801C of the bent passage portion 302B located on the downstream side of the inner peripheral side bent portion 801D. is doing.
  • the recess 801A is formed in the valve member 801, the upstream end reaches the gap passage 302A, and the downstream end is in the fuel flow direction of the bent passage 302B formed on the outer peripheral surface 801C of the valve member 801. Is provided.
  • valve member 801 is formed on the inner peripheral side passage surface 801C of the bent passage portion 302B located on the downstream side of the concave portion 801A, and the passage protruding from the concave portion 801A toward the central portion side of the bent passage portion 302B with a step difference DS.
  • a road surface 801CA is configured.
  • the gap passage portion 302A corresponds to the annular fuel passage 10S in the first embodiment
  • the bent passage portion 302B corresponds to the bent passage portion 10P in the first embodiment
  • Reference numeral 801C corresponds to the inner circumferential side passage surface 214D in the first embodiment
  • the passage surface 801CA corresponds to the passage surface 214DA in the first embodiment
  • the concave portion 801A corresponds to the concave portion 214A in the first embodiment.
  • the concave portion 214A is formed on the outer peripheral side passage surface of the bent passage portion 10P, whereas in the present embodiment, the concave portion 801A is formed on the inner peripheral side passage surface of the bent passage portion 302B. .
  • Erosion in the valve seat 800A can be reduced when the recess 801A and the passage surface 801CA exhibit the same effects as the recess 214A and the passage surface 214DA in the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
PCT/JP2014/076235 2013-10-29 2014-10-01 高圧燃料供給ポンプ Ceased WO2015064281A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP14858910.4A EP3064760B1 (en) 2013-10-29 2014-10-01 High-pressure fuel pump
US15/032,941 US9797387B2 (en) 2013-10-29 2014-10-01 High-pressure fuel supply pump
CN201480059935.5A CN105683557B (zh) 2013-10-29 2014-10-01 高压燃料供给泵

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JP2013-223859 2013-10-29
JP2013223859A JP6224415B2 (ja) 2013-10-29 2013-10-29 高圧燃料供給ポンプ

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US10330065B2 (en) * 2016-03-07 2019-06-25 Stanadyne Llc Direct magnetically controlled inlet valve for fuel pump
US20180010600A1 (en) 2016-07-08 2018-01-11 Delphi Technologies, Inc. High-pressure fuel pump
JP6743302B2 (ja) * 2017-06-27 2020-08-19 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
DE102017215547A1 (de) * 2017-09-05 2019-03-07 Robert Bosch Gmbh Elektromagnetisch betätigbares Saugventil für eine Hochdruckpumpe sowie Hochdruckpumpe
US12480465B2 (en) * 2021-03-09 2025-11-25 Hitachi Astemo, Ltd. Fuel pump
WO2022269977A1 (ja) * 2021-06-25 2022-12-29 日立Astemo株式会社 電磁吸入弁機構及び燃料ポンプ

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JP2012154297A (ja) 2011-01-28 2012-08-16 Denso Corp 高圧ポンプ
WO2012116850A1 (de) * 2011-03-02 2012-09-07 Robert Bosch Gmbh Ventileinrichtung zum schalten oder zumessen eines fluids
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CN102325987B (zh) * 2009-02-20 2015-04-01 日立汽车系统株式会社 高压燃料供给泵及用于该泵的排出阀单元
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JP5370792B2 (ja) * 2011-05-12 2013-12-18 株式会社デンソー 弁装置、及びこの弁装置を用いた高圧ポンプ

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JP2012154297A (ja) 2011-01-28 2012-08-16 Denso Corp 高圧ポンプ
WO2012116850A1 (de) * 2011-03-02 2012-09-07 Robert Bosch Gmbh Ventileinrichtung zum schalten oder zumessen eines fluids
WO2012123130A1 (de) * 2011-03-14 2012-09-20 Robert Bosch Gmbh Ventileinrichtung zum schalten oder zumessen eines fluids

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US20160281693A1 (en) 2016-09-29
EP3064760B1 (en) 2018-12-12
JP6224415B2 (ja) 2017-11-01
CN105683557A (zh) 2016-06-15
JP2015086736A (ja) 2015-05-07
EP3064760A4 (en) 2017-06-07
EP3064760A1 (en) 2016-09-07
US9797387B2 (en) 2017-10-24

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