WO2002055870A1 - Pompe d'alimentation en carburant haute pression - Google Patents

Pompe d'alimentation en carburant haute pression Download PDF

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Publication number
WO2002055870A1
WO2002055870A1 PCT/JP2001/000019 JP0100019W WO02055870A1 WO 2002055870 A1 WO2002055870 A1 WO 2002055870A1 JP 0100019 W JP0100019 W JP 0100019W WO 02055870 A1 WO02055870 A1 WO 02055870A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
plunger
pressure
cylinder
pressurized chamber
Prior art date
Application number
PCT/JP2001/000019
Other languages
English (en)
Japanese (ja)
Inventor
Atsuji Saito
Hiroyuki Yamada
Toru Onose
Masami Abe
Hiroshi Odakura
Original Assignee
Hitachi, Ltd.
Hitachi Car Engineering Co., 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, Ltd., Hitachi Car Engineering Co., Ltd. filed Critical Hitachi, Ltd.
Priority to PCT/JP2001/000019 priority Critical patent/WO2002055870A1/fr
Priority to EP01900260A priority patent/EP1348864A4/fr
Priority to JP2002556500A priority patent/JPWO2002055870A1/ja
Priority to US10/250,455 priority patent/US20040052664A1/en
Publication of WO2002055870A1 publication Critical patent/WO2002055870A1/fr

Links

Classifications

    • 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
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • 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
    • 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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F02M59/445—Selection of particular materials
    • 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve
    • 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
    • F04B53/04—Draining
    • 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
    • F04B53/1002—Ball valves
    • 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
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • 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
    • 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
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/02—Light metals
    • F05C2201/021—Aluminium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0436—Iron

Definitions

  • the present invention relates to a high-pressure fuel supply pump for pumping high-pressure fuel to a fuel injection valve of an internal combustion engine.
  • a recess is provided in a housing (also referred to as a body or a base) of a pump, and a cylinder (both a plunger support member and a tubular member) is provided in the recess.
  • the pressurized chamber is formed inside the cylinder by closing the open end of the cylinder with a seal mechanism.
  • the pump housing from a non-abrasion-resistant metal material such as an aluminum alloy, and by forming the cylinder from an iron-based wear-resistant material, the pump performance can be reduced in the long term. And that processing becomes easier.
  • the cylinder is fitted or press-fitted into a recess or a hole in the pump housing to form the pressurizing chamber in the cylinder itself formed of a hard material. For this reason, there was a possibility that a local stress would act on the cylinder under the influence of the thermal expansion of the pump housing, and the cylinder would be deformed.
  • An object of the present invention is to solve the above-mentioned problems, and basically to provide a low-cost and highly reliable high-pressure fuel supply pump.
  • the present invention provides a sealing mechanism that does not require grinding of a sealing surface or a sealing material such as an O-ring and a gasket.
  • the present invention provides a seal mechanism in which the seal material is not damaged by pressure fluctuation in the pressurized chamber.
  • the present invention provides a sealing mechanism in which sealing performance does not easily decrease even if cavitation occurs due to pressure-varying fuel flow in the pressurized chamber.
  • the stroke required to reduce the suction valve passage resistance during inhalation operates the actuator drive unit, which increases the operating distance and the operation stopper.
  • the parts could be worn or damaged.
  • a high-pressure fuel supply pump in which there is no delay in closing a discharge valve after a pump pressurizing step, and high-pressure fuel does not flow back into a pressurized chamber and fuel cavitation does not occur.
  • the present invention provides a high-pressure fuel supply pump that can ensure the sealing performance without performing high-precision processing of the seat portion and the guide portion.
  • a recess for a pressurizing chamber is formed in a pump housing, and this recess is defined as a pressurizing chamber by mounting a cylinder on the pump housing.
  • a recess for a pressurizing chamber is formed in a pump housing made of aluminum alloy, and a ferrous metal cylinder is pressed into contact with an opening of the recess. Then, the recess was sealed, and the recess was defined as a pressure chamber.
  • the low pressure chamber surrounds the periphery of the seal defining the pressure chamber.
  • multiple high-pressure seal portions are formed in a discharge direction at a discharge port portion formed on an aluminum alloy pump housing.
  • a flange portion of a cylindrical member with a flange is sandwiched between contact portions of a pump housing and a cylinder, and the cylindrical portion is formed along the inner peripheral wall of the pressurizing chamber. It was attached like so.
  • FIG. 1 is a vertical sectional view of an embodiment according to the present invention.
  • FIG. 2 is a partially enlarged sectional view of FIG.
  • FIG. 3 is a partially exploded perspective view of the embodiment shown in FIGS.
  • FIG. 4 is a diagram showing a configuration of a fuel injection system using the present embodiment.
  • Figs. 5 (a) and (b) are enlarged views of the discharge valve unit of the first embodiment.
  • FIG. 6 is a view showing another embodiment of the 5-discharge valve unit.
  • Fig. 7 (a) and (b) are diagrams showing still another embodiment of the discharge valve unit.
  • Figs. 8 (a) and (b) are enlarged sectional views showing a first embodiment of the suction valve unit.
  • FIG. 9 is a drawing showing another embodiment of the plunger seal portion.
  • FIG. 10 is a drawing showing still another embodiment of the plunge palm portion.
  • FIG. 11 is a drawing showing still another embodiment of the plunge palm portion.
  • FIG. 12 is a longitudinal sectional view showing a second embodiment of the high-pressure fuel supply pump.
  • FIG. 13 is a longitudinal sectional view showing a third embodiment of the high-pressure fuel supply pump.
  • FIG. 14 is a partially enlarged sectional view of the high-pressure fuel supply pump shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 is a vertical sectional view of the entire pump
  • FIG. 2 is a sectional view of FIG.
  • FIG. 3 is an enlarged view of the inside of the pump
  • FIG. 3 is a configuration diagram of the fuel injection system.
  • the pump body 1 has a fuel intake passage 10, a discharge passage 11, and a pressurizing chamber 12.
  • the suction passage 10 and the discharge passage 11 are provided with a suction valve 5 and a discharge valve 6, which are held in one direction by springs 5a and 6a, respectively, and are check valves for restricting a fuel flow direction. It has become.
  • the pressurizing chamber 12 is formed by a pump chamber 12 in which the plunger 2 as a pressurizing member slides, a suction hole 5 b communicating with the suction valve 5, and a discharge flow 6 b communicating with the discharge valve 6. ing.
  • a solenoid 200 is held in the pump body 1 in the suction chamber 100a, and an engaging member 201 and a spring 202 are arranged in the solenoid 200. I have.
  • the engaging member 201 is biased by the spring 202 in a direction to open the suction valve 5. Since the biasing force of the spring 200 is greater than the biasing force of the suction valve spring 5a, when the solenoid 200 is OFF, the suction valve 5 is opened as shown in FIGS. It is in the valve state.
  • the fuel is regulated from the tank 50 to the fuel inlet of the pump body 1 by the low-pressure pump 51, and is regulated to a constant pressure by the prestressing pump 52 to be introduced.
  • the pump body 1 is pressurized by the pump body 1 and is fed to the common rail 53 from the fuel discharge port.
  • An injector 54, a relief valve 55, and a pressure sensor 56 are mounted on the common rail 53.
  • the injectors 54 are mounted in accordance with the number of cylinders of the engine, and fire when the engine control unit (ECU) 40 signals.
  • the relief valve 55 opens when the pressure in the common rail 53 exceeds a predetermined value to prevent damage to the piping system.
  • a lifter 3 provided at the lower end of the plunger 2 is pressed against the cam 100 by a spring 4.
  • Plunger 2 is slidably held by cylinder 20
  • the cam 100 is rotated by an engine camshaft or the like, and reciprocates to change the volume in the pressurizing chamber 12.
  • a plunger 30 is provided to prevent fuel from flowing out to the cam 100 side.
  • the suction valve 5 automatically opens when the pressure in the pressurizing chamber 12 becomes lower than the fuel introduction port, but the closing of the valve is determined by the operation of the solenoid 200.
  • the suction valve 5 is an automatic valve that opens and closes in synchronization with the reciprocation of the plunger 2. Therefore, during the compression process, the suction valve 5 is closed, and the fuel corresponding to the reduced volume of the pressurizing chamber 12 pushes the discharge valve 6 open and is fed to the common rail 53.
  • the solenoid 200 is turned on during the compression process, the fuel is fed to the common rail 53 from this time. Also, once the pressure feed starts, the pressure in the pressurizing chamber 12 increases, and then the solenoid 200 Even if is turned off, the suction valve 5 remains closed, and the suction process is automatically opened in synchronization with the start.
  • the pressurizing chamber 12 is formed by bringing the suction valve holder 50, the discharge valve seat 60, and the cylinder 20 into pressure contact with the pump body 1.
  • the protector 70 is used between the cylinder 20 and the press-contact portion of the main body 1.
  • the cylinder 20 can be directly press-contacted to the main body 1, and it is determined whether the protector 70 is used. It can be selected according to the use conditions described later. Further, in order to obtain the same effect, it is also possible to use it for a pressure contact portion with another main body 1 other than the cylinder 20.
  • a suction chamber 10a, an annular chamber 10b, and a fuel chamber 11b, which are fuel chambers, are provided outside the pressurizing chamber 12 of the press-contact portion.
  • the pressure-contact member harder than the main body 1, the pressure-contact member can bite into the main-body-side pressure-contact surface, and the sealing performance can be improved.
  • the sealing performance can be further improved.
  • the soft material is eroded (eroded) by the fuel cavitation, and the seal surface may be damaged.
  • the sealing surface 70a (flat surface) between the cylinder 20 and the main body 1 and the sealing surface 7Ob (cylindrical surface) inside the pump chamber 12a are formed. Two sealing surfaces are provided. Seal surface 70 a The holder 21 is screwed to the main body 1 by screwing. Further, the sealing surface 7 Ob is pressed into contact with the main body 1 by press-fitting the protector 70.
  • sealing surface is divided into 70a and 70b, the propagation of the pressure from the pressurizing chamber is alleviated at the divided portion, and the erosion of the sealing surface 70a can be prevented.
  • the protector 70 is provided at the press-contact portion of the cylinder 20.
  • the protector 70 may be provided at another press-contact portion.
  • a low-pressure chamber 10b communicating with the suction chamber 10a is provided in the upper part of the pump chamber 12a in the drawing, which is a part of the pressurizing chamber 12, and a wall 1a between the chambers is provided. It is the weakest part of all walls of the pressurizing chamber 12.
  • the cylinder 20 is screwed to the main body 1 by a cylinder holder 21 provided on the outer peripheral portion.
  • the fastening portion C between the main body 1 and the cylinder holder 21 is provided between the cylinder fixing portion A on the main body side and the cylinder fixing portion B on the cylinder holder side.
  • the main body 1 is made of aluminum and the cylinder 20 is made of a material with a different linear expansion coefficient (aluminum> steel), such as steel, the length of the expanded part (A to C) on the main body is reduced. Because the length of the expansion part on the cylinder side is shorter (from part A to part B), the expansion length on the aluminum side and the cylinder side that occurs when the temperature changes (expansion length-expansion part length X-ray expansion coefficient X change temperature) The difference Can be reduced. Therefore, no clearance is generated at the contact surface between the cylinder 20 and the main body 1, and no reduction in sealing performance due to a reduction in the pressure contact force occurs.
  • aluminum> steel such as steel
  • a fitting portion D is provided on the inner diameter side of the cylinder holder 21 for fitting with the outer diameter of the cylinder 20.
  • the fitting portion D and the engaging portion C of the cylinder holder 20 and the main body 1 are located at different positions on the cylinder axis.
  • the engaging portion C is provided on the upper opening end side of the cylinder holder 21 in the drawing from the fitting portion D.
  • the joint D has a slight gap.
  • the heat of the main body 1 is less likely to be transmitted to the cylinder 20, and the seizure of the plunger 2 can be prevented. .
  • annular chamber 10 b communicating with the suction chamber 10 a is provided on the outer peripheral portion of the cylinder 20.
  • the plunger seal 30 and the plunger 2 as a sliding material can be held coaxially. Good sealing performance of the sliding part can be maintained.
  • the plunger seal chamber 30a inside the pump of the plunger seal 30 passes through the clearance X between the cylinder 20 and the sliding part of the plunger 2, and is connected to the fuel sump 20a provided in the cylinder. Passing through passageway 20b, it is connected to annular chamber 10b.
  • the outer periphery of the cylinder 20 is provided on the cylinder holder 21. At joint B, it is divided into an annular chamber 10b connected to the suction chamber 10a and a plunge palm chamber 30a.
  • the plunger seal chamber 30 a passes through a communication hole 2 la provided in the cylinder holder 21 and is connected to a return pipe 40.
  • the return pipe 40 is connected to a fuel tank 50 at substantially atmospheric pressure through a return pipe (not shown). Therefore, since the plunge palm chamber 30a communicates with the fuel tank 50 through the return pipe 40, the atmospheric pressure is substantially equal to the fuel tank pressure.
  • the fuel leaking from the sliding gap between the cylinder 20 and the plunger 2 from the pressurizing chamber 12 flows from the fuel reservoir 20a to the suction chamber 10a through the passage 20b.
  • the fuel since low pressure is supplied to the fuel reservoir 20a from the suction chamber 10a, the fuel flows through the sliding clearance X to the plunge sill chamber 30a. This fuel flows to the fuel tank 50 through the return pipe 40.
  • the plunger seal chamber 30a is almost at atmospheric pressure, so the fuel is easily gasified.
  • the distance of the sliding clearance X from the fuel reservoir 10a to the opening of the cylinder 20 on the plunger seal side is shorter than the reciprocating sliding length of the plunger.
  • the portion of the plunger .2 where fuel is wet at the fuel pool 20a at the top dead center passes through the cylinder opening at the bottom dead center, so that a fuel oil film at the opening can be secured and lubricity is improved. In addition, wear can be reduced.
  • a throttle 21b is provided between the plunger seal chamber 30a and the return pipe 40.
  • the fuel is more likely to remain in the plunger chamber 30a, and the plunger seal 30 and the cylinder opening by fuel lubrication are provided.
  • the wear resistance of the portion can be improved. This is particularly effective when the plunger seal 30 is located above the return pipe 40 when the pump is installed (upside down in the direction shown).
  • a solenoid 200 for controlling the opening / closing timing of the suction valve 5 is held inside the suction chamber 10a by a solenoid holder 210, and the solenoid 200 An annular fuel chamber is formed around the solenoid coil between the solenoid holders 210.
  • an annular fuel chamber may be formed on the outer periphery of the solenoid.
  • the solenoid holder 210 a material with lower thermal conductivity than the body 1 is used for the solenoid holder 210. By using this, it becomes difficult for the heat of the main body 1 to be transmitted to the solenoid 200, and burning of the solenoid 200 can be prevented.
  • the drive current of the solenoid 200 is gradually reduced at the time of OFF to reduce the collision force at the time of OFF and prevent wear and damage of the collision part. it can.
  • the suction valve 5 is quickly opened when the pressure in the pressurizing chamber changes (when shifting from the discharge process to the suction process). By opening the valve, the opening area of the suction valve 5 can be sufficiently ensured, and the operating distance of the solenoid 200 can be reduced to reduce the collision force.
  • the passage resistance in the suction valve 5 is reduced, so that the pressure in the pressurizing chamber during the suction process can be prevented from lowering, and the occurrence of cavitation can be suppressed.
  • FIG. 5 Another press-contact method for forming a pressurizing chamber will be described with reference to FIGS. 5, 6, and 7.
  • FIG. 5 Another press-contact method for forming a pressurizing chamber will be described with reference to FIGS. 5, 6, and 7.
  • FIG. 5 is an enlarged view of the discharge valve portion of FIG. 1, and FIGS. 6 and 7 (a) and (b) are other embodiments of FIG.
  • the discharge valve 6 is a pole valve, and has a pole holder 6 3 that fits into the pole valve.
  • a cylindrical portion is formed on the outer periphery of the pole holder 6 3 so that the discharge valve 6 can slide on the inner diameter side of the discharge valve holder 6 2. I have.
  • the pole is held by the pole holder 63 when the pole valve is opened, so that the pole swing can be suppressed and the fuel flow can be stabilized. Therefore, it is possible to prevent cavitation caused by anyone of the flow.
  • the outer diameter of the pole holder 63 is made larger than the diameter of the pole valve, and a cutout is formed in a part of the outer diameter of the cylindrical portion as shown in the cross section taken along line PP in FIG. In this embodiment, three places are provided, but the number is not limited.
  • an appropriate fuel passage can be formed in the valve mechanism, so that cavitation caused by a decrease in fuel pressure due to pressure loss can be prevented.
  • This structure is not limited to the discharge valve, but by adopting it as a discharge valve, it is possible to secure oil tightness of the high-pressure pipe with a cheaper method than when a conical valve is used. .
  • the discharge valve seat 60 is pressed against the pump body 1 to form a pressurized chamber, and the gasket 61 is provided on the outer peripheral side of the discharge valve seat 60.
  • the fuel chamber lib is formed.
  • the discharge valve sheet 60 and the gasket 61 are pressed against the main body 1 by screwing the discharge valve holder 62. Therefore, two press contact portions with the main body 1 for forming the pressurizing chamber 12 are provided.
  • the gasket 61 is made to be softer than the discharge valve seat 60 and the body 1. Thus, fuel leakage to the outside of the pump can be reliably prevented. Further, since the second pressure contact portion does not directly receive the pressure fluctuation and the fuel flow in the pressurized chamber, even if a soft material is used for the gasket 61, it does not receive the fuel cavitation generated in the pressurized chamber. It can have a reliable sealing property.
  • a protection plate 61a is placed between the discharge valve seat 60 and the main body 1, and a soft material gasket 61 is placed outside the discharge valve seat 60 and the discharge valve holder 62.
  • the fuel chamber 11b is formed by being pressed against the fuel chamber.
  • FIG. 6 shows an embodiment in which excessive fuel cavitation does not occur.
  • One gasket 61 is pressed between the discharge valve seat 60, the discharge valve 62, and the main body 1 in a press-fit manner. I have. On both sides of the gasket 61, there is a groove 11c, which divides the pressure contact surface into two parts, and the groove serves as a fuel chamber (or space).
  • the groove is provided on the gasket surface, but may be provided on the opposite surface (such as the main body surface).
  • FIG. 8 shows an enlarged view of the fifth part of the suction valve.
  • the suction valve 5 is a flat valve having a cup-shaped cylindrical portion, and the outer peripheral portion of the cylindrical portion is slidably held on the inner diameter side of the suction valve holder 50.
  • the cylindrical portion is held when the flat valve is opened, so that the valve body can be prevented from swaying and the fuel flow can be stabilized. Therefore, cavitation caused by the flow can be prevented.
  • the valve closing spring 5a can be disposed in the cup portion, space can be saved.
  • a cut-out portion forming a fuel passage is provided in a part of the inner diameter of the suction valve holder 50, as shown in the cross section Q—Q in FIG. In this embodiment, five locations are provided, but the number is not limited.
  • this structure is not limited to the suction valve, the adoption of the suction valve ensures a high response when the valve is opened, thus suppressing the pressure drop in the pressurized chamber due to the delay of the valve opening at the beginning of the suction process. Therefore, cavitation caused by a decrease in fuel pressure can be prevented.
  • FIG. 9 a second embodiment of the present invention will be described with reference to FIGS. 9, 10, 11, and 12.
  • FIG. 9 a second embodiment of the present invention will be described with reference to FIGS. 9, 10, 11, and 12.
  • FIG. 12 is a view showing the same cross section as FIG. 1, and the reference numerals in the figure are the same as those in FIG. Fig. 9 to Fig. 11 show the plunger seal of Fig. 12 It is an enlarged view and shows the other Example regarding the plunger seal shape.
  • the return pipe 40 connected to the fuel tank 50 and the communication hole 21 a are not provided in FIGS. 1 and 2.
  • a ring-type seal 31 has been added to the upper part of the plunge bottle 30 in the figure to provide a plurality of seals.
  • the inner portion of the plunger seal 31 becomes a dead end that communicates only with the cylinder opening.
  • the inside of the plunger palm 31 is maintained at the pressure on the suction side, so that gasification of fuel can be prevented, and lubrication is provided, so that wear resistance is improved. Also, even when the pressure in the suction chamber 10a pulsates due to the pump operation, the pressure pulsation is attenuated in the sliding portion X between the plunger 2 and the cylinder 20 and is transmitted to the plunger seal 31. None is done. Therefore, breakage and wear of the plunger seal 31 can be prevented.
  • the present invention is also effective when only the lip-type seal 30 is used as shown in FIG. That is, the inner portion of the plunger seal 30 is a dead end that communicates only with the cylinder opening.
  • the pressure inside the plunger seal 30 is maintained at the pressure on the suction side, so that gasification of the fuel can be prevented, and lubrication is provided.
  • the top is peeled off. Further, even when the pressure in the suction chamber 10a pulsates due to the pump operation, the pressure pulsation is attenuated in the sliding portion X between the plunger 2 and the cylinder 20 and is transmitted to the plunger seal 30. None is done. Therefore, breakage and wear of the plunge palm 30 can be prevented.
  • the pressure resistance of the seal material that directly touches the fuel can be improved, and the outside of the pump can be improved.
  • the pressure applied to the sealing material at the part can be reduced, and the reliability of sealing can be improved.
  • a plurality of sealing materials having different shapes are provided on the plunger sliding portion, and the sealing material in the outer direction of the pump has a lip shape.
  • the ring type seal shape is as follows: O-ring in Fig. 12, O-ring with resin ring 3 la on the sliding side in Fig. 9, or X-ring in Fig. 10, K-ring in Fig. 11 Such a shape.
  • ring seals such as O, X, and K have better formability than lip seals, and there is a high degree of freedom in material selection. Therefore, rubber materials can be selected according to the fuel (alcohol, etc.) used. Can be selected.
  • FIG. FIG. 13 is a vertical sectional view of the entire pump
  • FIG. 14 is an enlarged view of the inside of the pump of FIG.
  • the cylinder 20 and the main body 1 are separated from each other, and the pressurizing chamber 12 does not touch the pump main body 1, and the suction valve holder 50, the discharge valve sheet 60, the cylinder 20
  • the cylindrical pipes 5 f and 6 f are pressed into contact with each other.
  • a pressurizing chamber is formed by pressing a plug 20f on the upper part of the cylinder 20 in the drawing in order to improve the workability of the cylinder 20, but the pressure chamber is formed integrally with the cylinder. Good.
  • cylindrical tube material with a flanged shape and making one of the press contact portions a flat surface contact and the other a cylindrical surface contact, it is possible to absorb the dimensional variation of the two components in the X and Y directions. .
  • the material of the first press-contact portion and the material of the second press-contact portion by separating the material of the first press-contact portion and the material of the second press-contact portion, and using a hard material on the pressurizing chamber side and a soft material on the outside, it is possible to prevent the first press-contact portion from being damaged by the cavity. In addition, it is possible to improve the sealing property of the second press contact portion.
  • the hardness of the second pressure contact member softer than that of the housing, deformation of the seal surface on the housing side is reduced, and when disassembling and reassembling, even if only the pressure contact member is replaced, Good sealing performance can be maintained.
  • the pressurizing chamber and the low-pressure chamber are formed of the same member, and the strength of the separating wall between the pressurizing chamber and the low-pressure chamber is made the weakest part of the pressurizing chamber.
  • a cylinder holder for fixing the housing and a separate cylinder is provided, and an engagement portion C between the cylinder holder and the housing is provided between the cylinder fixing portion A on the housing side and the cylinder fixing portion B on the cylinder holder side.
  • the expansion length on the aluminum side is smaller than that on the cylinder side. Can be made equal to the expansion length on the cylinder side. Therefore, no clearance is generated at the contact surface between the cylinder and the housing, and no reduction in sealing performance due to a reduction in the pressure contact force is generated.
  • the outer diameter of the cylinder is fitted to the inner diameter side of the cylinder holder, and the fitting portion and the engaging portion between the cylinder holder and the housing are connected to the cylinder shaft. Different positions on the line.
  • a seal member for sealing the sliding portion of the plunger is engaged with the cylinder holder.
  • the cylinder and the seal member can be held coaxially, and the sealability of the plunger insertion portion can be kept good.
  • the engaging portion C between the cylinder holder and the housing is provided closer to the opening end of the cylinder holder than the cylinder and the mating portion D.
  • the rigidity of the engaging portion C of the cylinder holder is lower than that of the fitting portion D, so that deformation in the inner diameter direction due to expansion of the housing does not easily reach the fitting portion D. Therefore, the clearance of the plunger sliding portion inside the cylinder can be appropriately maintained, and seizure of the plunger can be prevented.
  • a screw portion is provided on the outer peripheral portion of the cylinder holder so as to engage with the housing.
  • the cylinder can be securely fixed by an inexpensive method.
  • the heat of the housing is less likely to be transmitted to the cylinder, and seizure of the plunger can be prevented.
  • the screw portion is coated with a resin.
  • annular fuel chamber is formed on the outer periphery of the cylinder, and this fuel chamber is Communicate with pressure chamber.
  • a sealing material is provided on the sliding part of the plunger, and a fuel reservoir connected to the low-pressure fuel chamber is provided on a part of the sliding part of the cylinder and the plunger connected to the inside of the sealing material.
  • the inside of the sealing material shall be a blind lane communicating only with the cylinder opening.
  • the inside of the sealing material is kept at the pressure on the suction side, so that gasification of the fuel can be prevented, and the lubricating property is improved, so that the wear resistance is improved. Also, even when the pressure in the low-pressure fuel chamber pulsates due to the pump operation, the pressure pulsation is attenuated at the clearance between the sliding portion of the plunger and the cylinder, so that the pressure pulsation may be transmitted to the inside of the seal material. Absent. Therefore, breakage and wear of the sealing material can be prevented.
  • a sealing material is provided on the sliding portion of the plunger, and a cylinder connected to the inner portion of the sealing material and a fuel reservoir connected to the low-pressure fuel chamber are provided in a part of the insertion portion of the plunger. Make the distance to the seal material opening shorter than the reciprocating sliding length of the plunger.
  • the plunger that has been wetted by the fuel in the fuel reservoir at the top dead center passes through the cylinder opening at the bottom dead center, so that an oil film can be secured at the opening, lubrication is improved, and wear is reduced. be able to.
  • a sealing material is provided on the sliding portion of the plunger, and the inside of the pump of the sealing material is communicated with a room such as a fuel tank which has a substantially atmospheric pressure.
  • the abrasion resistance of the sealing material and the opening of the cylinder can be improved. This is particularly effective when the sealing material is above the communication passage.
  • a sealing material for the sliding part of the plunger and fill the inside of the pump with lubricating oil (oil, grease, etc.).
  • annular fuel chamber is formed on the outer periphery of the heating section (such as the coil section of the solenoid) that controls the opening and closing timing of the suction valve, and this fuel chamber is connected to the low-pressure chamber.
  • the reactor can be cooled with fuel.
  • an actuator holder for fixing the actuator holder is provided, and a screw portion is provided on an outer peripheral portion of the actuator holder to engage with the housing.
  • the heat transfer from the housing to the actuator can be reduced, and the cylinder can be securely fixed by an inexpensive method. Also, by using a material having a lower thermal conductivity than the housing for the actuator holder, the heat of the housing is less likely to be transferred to the actuator, thereby preventing burning of the actuator.
  • the screw portion is coated with a resin.
  • the drive power supply for the actuator controlling the opening / closing timing of the suction valve is gradually reduced at the time of OFF.
  • the driving unit for the actuator and the suction valve are separated from each other, and the operating distance of the driving unit for the actuator is smaller than the operating distance of the suction valve.
  • the collision distance can be reduced by reducing the operating distance of the actuator, and the opening area of the suction valve can be sufficiently secured.
  • the operating distance of the discharge valve shall be shorter than the suction valve.
  • At least one of the suction valve and the discharge valve is a pole valve, and has a cylindrical member that fits into the pole valve, so that the outer peripheral portion of the cylindrical member can slide toward the inner diameter side of the cylindrical portion holding member.
  • the outer diameter of the cylindrical member is made larger than the diameter of the poll valve, and a cutout portion is formed at a part of the outer diameter of the cylindrical member.
  • an appropriate fuel passage can be formed in the valve mechanism, so that the pressure loss This can prevent cavitation caused by a decrease in fuel pressure due to fuel pressure.
  • At least one of the suction valve and the discharge valve is a flat valve having a cup-shaped cylindrical portion, and the outer peripheral portion of the cylindrical portion is slidably held on the inner diameter side of the cylindrical holding member.
  • the cylindrical portion is held when the flat valve is opened, so that the valve body can be restrained from oscillating and the fuel flow can be stabilized. Therefore, cavitation caused by only the flow can be prevented. Further, a spring for closing the valve can be arranged in the cup portion, so that space can be saved.
  • a cutout portion for forming a fuel passage is provided in a part of the inner diameter of the cylindrical portion holding member.
  • a high response at the time of opening the valve can be achieved, so that the pressure drop in the pressurizing chamber due to the delay of opening the valve at the beginning of the suction process can be suppressed, so that the cavitation caused by the decrease in fuel pressure can be achieved. Can be prevented.
  • the cylindrical tube is held by pressure welding.
  • one of the press-contact portions is in planar contact and the other is in cylindrical contact, so that dimensional variations in the X- and Y-direction components can be absorbed.
  • a plurality of sealing materials having different shapes are provided on the plunger sliding portion.
  • the sealing material in the outer direction of the pump has a lip shape.
  • seal material in the pump inner direction shall be shaped like an O-ring (including a resin ring etc. on the sliding side) or an XK ring.
  • ring type seals such as ⁇ , X, and K have better formability than the lip type seals, so there is flexibility in selecting materials. Therefore, the rubber material can be selected according to the fuel used.

Abstract

Cette invention concerne une pompe d'alimentation en carburant haute pression dans laquelle on trouve carter de pompe en alliage d'aluminium, un cylindre réalisé dans un métal à base de fer, un élément tubulaire à rebord dont la collerette est maintenue en contact entre le carter de pompe et le cylindre, l'élément tubulaire étant monté dans le carter de pompe contre la paroi intérieure de ce dernier. Il n'y a pas de corrosion de la surface jointive du fait que la cavitation se produit entre la pointe de l'élément tubulaire et le carter de pompe.
PCT/JP2001/000019 2001-01-05 2001-01-05 Pompe d'alimentation en carburant haute pression WO2002055870A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2001/000019 WO2002055870A1 (fr) 2001-01-05 2001-01-05 Pompe d'alimentation en carburant haute pression
EP01900260A EP1348864A4 (fr) 2001-01-05 2001-01-05 Pompe d'alimentation en carburant haute pression
JP2002556500A JPWO2002055870A1 (ja) 2001-01-05 2001-01-05 高圧燃料供給ポンプ
US10/250,455 US20040052664A1 (en) 2001-01-05 2001-01-05 High-pressure fuel feed pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2001/000019 WO2002055870A1 (fr) 2001-01-05 2001-01-05 Pompe d'alimentation en carburant haute pression

Publications (1)

Publication Number Publication Date
WO2002055870A1 true WO2002055870A1 (fr) 2002-07-18

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Country Status (4)

Country Link
US (1) US20040052664A1 (fr)
EP (1) EP1348864A4 (fr)
JP (1) JPWO2002055870A1 (fr)
WO (1) WO2002055870A1 (fr)

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EP1394452A4 (fr) * 2001-06-04 2007-09-19 Nok Corp Dispositif d'etancheite
JP2008248788A (ja) * 2007-03-30 2008-10-16 Denso Corp 高圧燃料ポンプ
JP2008267373A (ja) * 2007-03-29 2008-11-06 Denso Corp 高圧燃料ポンプ
JP2009287733A (ja) * 2008-05-30 2009-12-10 Denso Corp 電磁弁、電磁弁を備えた流体ポンプ、および、電磁弁を備えた流体噴射装置
JP2014105618A (ja) * 2012-11-27 2014-06-09 Toyota Motor Corp 高圧燃料ポンプ
JP2014177949A (ja) * 2014-07-04 2014-09-25 Denso Corp 高圧ポンプ
JP2015503057A (ja) * 2011-12-20 2015-01-29 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツングＲｏｂｅｒｔ Ｂｏｓｃｈ Ｇｍｂｈ 流量制御弁および流量制御弁を備えた高圧ポンプ
JP2016029283A (ja) * 2015-12-03 2016-03-03 株式会社デンソー 高圧ポンプ
JP2016118211A (ja) * 2016-03-28 2016-06-30 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
JP2016191367A (ja) * 2015-03-31 2016-11-10 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及び高圧燃料供給ポンプの組立て方法
CN108350846A (zh) * 2015-09-21 2018-07-31 德尔福知识产权有限公司 燃料泵组件
US10422330B2 (en) 2011-11-30 2019-09-24 Hitachi Automotive Systems, Ltd. High pressure fuel pump
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JP5103138B2 (ja) * 2007-11-01 2012-12-19 日立オートモティブシステムズ株式会社 高圧液体供給ポンプ
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JP6344267B2 (ja) * 2015-03-04 2018-06-20 トヨタ自動車株式会社 高圧燃料ポンプ
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EP1394452A4 (fr) * 2001-06-04 2007-09-19 Nok Corp Dispositif d'etancheite
US6895992B2 (en) 2002-07-05 2005-05-24 Hitachi, Ltd. Fuel pump for inter-cylinder direct fuel injection apparatus
JP2006514204A (ja) * 2003-02-21 2006-04-27 ローベルト ボッシュ ゲーエムベーハー 内燃機関の燃料噴射装置
JP2008267373A (ja) * 2007-03-29 2008-11-06 Denso Corp 高圧燃料ポンプ
JP2008248788A (ja) * 2007-03-30 2008-10-16 Denso Corp 高圧燃料ポンプ
JP2009287733A (ja) * 2008-05-30 2009-12-10 Denso Corp 電磁弁、電磁弁を備えた流体ポンプ、および、電磁弁を備えた流体噴射装置
US10422330B2 (en) 2011-11-30 2019-09-24 Hitachi Automotive Systems, Ltd. High pressure fuel pump
JP2015503057A (ja) * 2011-12-20 2015-01-29 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツングＲｏｂｅｒｔ Ｂｏｓｃｈ Ｇｍｂｈ 流量制御弁および流量制御弁を備えた高圧ポンプ
US9791064B2 (en) 2011-12-20 2017-10-17 Robert Bosch Gmbh Quantity control valve and high-pressure pump with quantity control valve
JP2014105618A (ja) * 2012-11-27 2014-06-09 Toyota Motor Corp 高圧燃料ポンプ
JP2014177949A (ja) * 2014-07-04 2014-09-25 Denso Corp 高圧ポンプ
JP2016191367A (ja) * 2015-03-31 2016-11-10 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及び高圧燃料供給ポンプの組立て方法
CN108350846A (zh) * 2015-09-21 2018-07-31 德尔福知识产权有限公司 燃料泵组件
JP2018527515A (ja) * 2015-09-21 2018-09-20 デルフィ・テクノロジーズ・アイピー・リミテッド 燃料ポンプアセンブリ
JP2016029283A (ja) * 2015-12-03 2016-03-03 株式会社デンソー 高圧ポンプ
JP2016118211A (ja) * 2016-03-28 2016-06-30 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
WO2023209949A1 (fr) * 2022-04-28 2023-11-02 日立Astemo株式会社 Pompe à carburant

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EP1348864A1 (fr) 2003-10-01
US20040052664A1 (en) 2004-03-18
JPWO2002055870A1 (ja) 2004-05-20
EP1348864A4 (fr) 2005-03-16

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