EP1348864A1 - Hochdruckkraftstoffförderpumpe - Google Patents

Hochdruckkraftstoffförderpumpe Download PDF

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Publication number
EP1348864A1
EP1348864A1 EP01900260A EP01900260A EP1348864A1 EP 1348864 A1 EP1348864 A1 EP 1348864A1 EP 01900260 A EP01900260 A EP 01900260A EP 01900260 A EP01900260 A EP 01900260A EP 1348864 A1 EP1348864 A1 EP 1348864A1
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EP
European Patent Office
Prior art keywords
pressure
pressurization chamber
plunger
chamber
cylinder
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.)
Withdrawn
Application number
EP01900260A
Other languages
English (en)
French (fr)
Other versions
EP1348864A4 (de
Inventor
Atsuji Automotive Products Hitachi Ltd SAITO
Hiroyuki Automotive Products Hitachi Ltd YAMADA
Toru Automotive Products Hitachi Ltd ONOSE
Masami Automotive Products Hitachi Ltd ABE
Hiroshi Automotive Products Hitachi Ltd ODAKURA
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 Ltd
Hitachi Automotive Systems Engineering Co Ltd
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
Publication of EP1348864A1 publication Critical patent/EP1348864A1/de
Publication of EP1348864A4 publication Critical patent/EP1348864A4/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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 feed pump for forcibly feeding high-pressure fuel into a fuel injection valve of an internal combustion engine
  • a housing of a pump (also referred to as a body or base) is provided with a recess, a cylinder (also referred to as plunger supporting member or cylindrical member) is fitted into the recess, and the open end of the cylinder is covered by a seal mechanism, whereby a pressurization chamber is formed inside the cylinder.
  • the housing of the pump is formed of a non-wear resistant metallic material such as an aluminum alloy and the cylinder is formed of an iron base wear resistant metallic material, thereby allowing the pump to be easily machined without deteriorating the capability of the pump over a long period of time.
  • JP-A-10-331735 and JP-A-8-68370 are known.
  • the cylinder is fitted or press-fitted into a recess or a bore in the pump housing since the pressurization chamber is formed in the cylinder, itself formed with a hard material. For this reason, there was a problem in that the cylinder may be deformed since local stresses are applied to the cylinder under the influence of the thermal expansion of the pump housing.
  • the object of the present invention is to solve the above problems and basically to provide a high-pressure fuel feed pump of high reliability at low cost.
  • an object of the present invention is to provide a seal mechanism in which neither the grinding of a sealing surface nor a sealing material such as an O-ring or a gasket is required.
  • Another object of the present invention is to provide a sealing material that is not fractured by the pressure fluctuation in the pressurization chamber.
  • a further object of the present invention is to provide a seal mechanism that hardly shows a drop in sealing capability even if a cavitation occurs due to a fuel flow with pressure fluctuation in the pressurization chamber.
  • An additional object of the present invention is to provide a high-pressure fuel feed pump in which no gap is formed in the fixing part of the cylinder and neither the deterioration in the sealing performance nor the shaking of the cylinder is caused by a change in temperature (for example, at high temperature), even if materials with different coefficients of linear thermal expansion are used for the housing and cylinder (for example, an aluminum material is used for the housing and a steel material is used for the cylinder).
  • a still further object of the present invention is to provide a high-pressure fuel feed pump, wherein the fuel is not gasified, where the lubricating performance between the sliding parts of the plunger, a sealing material and the cylinder is not deteriorated, and wear or seizure is hardly caused, even under high temperature.
  • a still further object of the present invention is to provide a high-pressure fuel pump, wherein the discharge valve is never closed too late after the termination of the compressing step of the pump, the high-pressure fuel does not backflow into the pressurization chamber, and a fuel cavitation does not arise.
  • Another object of the present invention is to provide a high-pressure fuel pump that makes it possible to secure the sealing performance even if a seat part and a guide part are not machined with high precision.
  • a recess for a pressurization chamber is formed in a pump housing, and a cylinder is mounted in the pump housing, to thereby define the recess as the pressurization chamber.
  • a recess used for a pressurization chamber which is formed in a pump housing formed of an aluminum alloy, and the recess is sealed by pressure-welding a cylinder, which is formed of an iron base metal, to an open end of the recess, whereby the recess is defined as the pressurization chamber.
  • a low-pressure chamber surrounds a sealing member defining the pressurization chamber.
  • multiple high-pressure sealing members are provided along a discharge port, which is formed in the pump housing that is made of an aluminum alloy.
  • a flange part of a flanged cylindrical member is sandwiched in an abutting portion between the pump housing and the cylinder, and a cylindrical part is installed along the inner circumferential wall of the pressurization chamber.
  • Fig. 1 is a vertical sectional view of an entire pump
  • Fig. 2 is an enlarged view inside the pump of Fig. 1
  • Fig. 3 is a constructional view of a fuel injection system.
  • the pump body 1 is provided with a fuel suction passage 10, a fuel discharge passage 11, and a pressurization chamber 12.
  • the suction passage 10 and the discharge passage 11 are provided with a suction valve 5 and a discharge valve 6, respectively, which are respectively maintained in one direction by springs 5a, 6a, whereby the valves serve as check valves for restricting the flowing directions of fuel.
  • the pressurization chamber 12 is formed by a pump chamber 12a having a pressurizing member, i.e., a plunger 2 slid therein, a suction bore 15b that communicates with the suction valve 5, and a discharge path 6b that communicates with the discharge valve 6.
  • the pump body 1 holds a solenoid 200 in a suction chamber 10a, and the solenoid 200 is provided with an engagement member 201 and a spring 202.
  • a biasing force is applied to the engagement member 201 in a direction to open the suction valve 5 by the spring 202 when the solenoid 200 is OFF. Since the biasing force of the spring 202 is larger than that of the suction valve spring 5a, the suction valve 5 is in its open state as shown in Figs. 1 and 2 when the solenoid 200 is OFF.
  • a low-pressure pump 51 guides the fuel from a tank 50 to the fuel inlet of the pump body 1 where the fuel is regulated at a predetermined pressure by a pressure regulator 52.
  • the common rail 53 has mounted thereon injectors 54, a relief valve 55 and a pressure sensor 56.
  • the injectors 54 are provided to meet the number of cylinders of an engine and inject fuel in response to signals from an engine control unit (ECU) 40.
  • the relief valve 55 is opened when the pressure in the common rail 53 exceeds a predetermined value, thereby preventing a piping system from being fractured.
  • a lifter 3 provided at a lower end of the plunger 2 is brought into press contact with a cam 100 by means of a spring 4.
  • the plunger 2 is slidably held in a cylinder 20, and reciprocated by the cam 100 rotated by an engine cam shaft or the like, thereby changing the volume within the pressurization chamber 12.
  • the lower end of the cylinder 20 in the drawing is provided with a plunger seal 30 for preventing fuel from flowing to the cam 100.
  • the suction valve 5 is automatically opened if the pressure of the pressurization chamber 12 is lower than that of the fuel inlet, the closing of the suction valve is determined by the operation of the solenoid 200.
  • the solenoid 200 When the solenoid 200 is maintained in its ON (conductive) state, the engagement member 201 and the suction valve 5 are separated since an electromagnetic force is produced which exceeds the biasing force of the spring 202 and the engagement member 201 is drawn to the solenoid 200. In this state, the suction valve 5 becomes an automatic valve that is opened and closed in synchronization with the reciprocating movements of the plunger 2. Accordingly, during the compressing step, the suction valve 5 is closed and the fuel, equivalent to the reduced volume of the pressurization chamber 12, pushes and opens the discharge valve 6, thereby forcibly feeding the fuel to the common rail 53.
  • the solenoid 200 when the solenoid 200 is maintained in the OFF (non-conductive) state, the engagement member 201 is engaged with the suction valve 5 by the biasing force of the spring 202, and maintains the suction valve 5 in its opened state. Accordingly, since the pressure of the pressurization chamber 12 is maintained in a low-pressure state approximately equal to that of the fuel inlet, the discharge valve 6 cannot be opened and the fuel, equivalent to the reduced volume of the pressurization chamber 12, is returned to the fuel inlet via the suction valve 5.
  • the solenoid 200 is turned to the ON state during the compression step, the fuel is forcibly fed to the common rail 53 from that time. Since the pressure within the pressurization chamber 12 rises once the forcible feed is initiated, the closed state of the suction valve 5 is maintained even if the solenoid 200 is turned to the OFF state thereafter, and the suction valve 5 is automatically opened in synchronization with the initiation of the suction step.
  • the pressurization chamber 12 is formed by pressure-welding a suction valve holder 50, a discharge valve seat 60 and the cylinder 20 to the pump body 1.
  • a protector 70 is used in a pressure-welded part between the cylinder 20 and the pump body 1 in the present embodiment, it is possible to directly pressure-welding the cylinder 20 to the body 1, and it is possible to select whether the protector 70 is used or not according to the using conditions which will be described later. Further, in order to obtain the same effects, it is also possible to use the protector in a pressure-welded part between the body 1 and any part other than the cylinder 20.
  • a suction chamber 10a, an annular chamber 10b and a fuel chamber 11b, which serves as fuel chambers, are provided outside the pressurization chamber 12 away from the pressure-welded part.
  • the hardness of the pressure-welded members is higher than that of the body 1, whereby the pressure-welded members bites into the pressure-welded surfaces at the body side, so that the sealing performance can be enhanced.
  • sealing surfaces may be occasionally fractured since the soft material is eroded (cavitated) due to the cavitation of fuel when the fuel is highly pressurized and a high-speed operation is performed.
  • the protector 70 is used, and two seal surfaces are provided, one seal surface 70a (flat surface) between the cylinder 20 and the body 1, and the other seal surface 70b (cylindrical surface) on the inner surface of the pump chamber 12a.
  • the seal surface 70a is press-welded to the body 1 by fastening the cylinder holder 12 with screws. Further, the seal surface 70b is pressure-welded to the body 1 by press-fitting the protector 70.
  • the seal surface is divided into 70a and 70b, the propagation of pressure from the pressurization chamber is alleviated in the divided part, thereby preventing the erosion of the seal surface 70a.
  • the protector 70 is provided in the pressure-welded part of the cylinder 20 in the present embodiment, the protector 70 may be provided in other pressure-welded parts.
  • the upper part of the pump chamber 12a which is a part of the pressurization chamber 12, is provided with the low-pressure chamber 10b, which communicates with the suction chamber 10a, and a wall part 1a between these chambers is formed as a most weakened part among all of the walls of the pressurization chamber 12.
  • the cylinder 20 is fastened with screws to the body 1 in the cylinder holder 21 provided at the outer peripheral part thereof.
  • the fastening portion C of the body 1 and the cylinder holder 21 is provided between the cylinder-fixing portion A at the body side and the cylinder fixing portion B at the cylinder holder side.
  • the inner diameter side of the cylinder holder 21 is provided with a fitting portion D in which the outer diameter of the cylinder 20 is fitted.
  • the fitting portion D and the engagement portion C of the cylinder holder 20 and the body 1 are located in different positions on the axis of the cylinder.
  • the engagement portion C is positioned closer to the upper open end of the cylinder holder 21 in the drawing than the fitting portion D.
  • the fitting portion has a small gap.
  • the cylinder holder 2 is formed of a material having lower heat conductivity than the body 1, heat is difficult to transfer from the body 1 to the cylinder 20, and thereby it is also possible to prevent the plunger 2 from being seized.
  • the outer peripheral part of the cylinder 20 is provided with the annular chamber 10b that communicates with the suction chamber 10a.
  • the plunger seal 30 is maintained to seal the outflow of fuel from the sliding part of the plunger 2 to the cam 100 and the penetration of oil from the cam side to the plunger sliding part.
  • a plunger seal chamber 30a of the plunger seal 30 inside the pump is connected to a fuel reservoir 20a provided in the cylinder through the sliding gap X between the cylinder 20 and the plunger 2, and it is connected to the annular chamber 10b through the passage 20b. Furthermore, the outer peripheral part of the cylinder 20 is provided in the cylinder holder 21. The outer peripheral part of the cylinder 20 is divided into the annular chamber 10b, which is connected to the suction chamber 10a, and the plunger seal chamber 30a by the fitting part B.
  • the plunger seal chamber 30a is connected to a return pipe 40 through a communication bore 21a provided in the cylinder holder 21.
  • the return pipe 40 is connected to the fuel tank 50 approximately at atmospheric pressure, through a return piping (not shown). Accordingly, since the plunger seal chamber 30a communicates with the fuel tank 50 through the return pipe 40, the plunger seal chamber 30a is under atmospheric pressure approximately equal to the fuel tank pressure.
  • the fuel leaked through the sliding gap between the cylinder 20 and the plunger 2 from the pressurization chamber 12 flows from the fuel reservoir 20a through the passage 20b to the suction chamber 10a side. Meanwhile, since low pressure is supplied to the fuel reservoir 20a from the suction chamber 10a, fuel flows to the plunger seal chamber 30a through the sliding gap X. This fuel flows to the fuel tank 50 through the return pipe 40. However, when the temperature is highly elevated, the fuel is apt to be gasified since the plunger seal chamber 30a is approximately at atmospheric pressure.
  • the length of the sliding gap X from the fuel reservoir 10a to the opening of the cylinder 20 of the plunger seal side is shorter than the reciprocating sliding length of the plunger.
  • a throttle part 21b is provided between the plunger seal chamber 30a and the return pipe 40.
  • the fuel easily remains within the plunger seal chamber 30a and the wear resistance of the plunger seal 30 and the cylinder opening can be enhanced thanks to the lubrication by the fuel.
  • the plunger seal 30 is higher than the return pipe 40 (the upper and lower parts are reversed from the shown state), it is more effective.
  • the solenoid 200 which controls the timing of the opening and closing of the suction valve 5, is held inside the suction chamber 10a by the solenoid holder 210, and the annular fuel chamber is formed at the outer periphery of the solenoid coil between the solenoid 200 and the solenoid holder 210.
  • the solenoid 200 can be cooled with the fuel. Further, the annular fuel chamber may be formed at the outer periphery of the solenoid without using the solenoid holder.
  • a threaded part is provided at the outer periphery of the solenoid holder 210 to be engaged with the housing, whereby it is possible to reduce heat transfer from the body 1 to the solenoid 200.
  • the solenoid holder 210 is formed of a material having lower heat conductivity than the body 1, whereby the heat of the body 1 is difficult to transfer to the solenoid 200, and thus it is possible to prevent the burnt-down of the solenoid 200.
  • the threaded part of the solenoid holder 210 is coated with resin, whereby it is possible to reduce heat transfer from the body 1.
  • the operation distance of the driving part of the solenoid 200 is made shorter than that of the suction valve 5.
  • the operation distance of the discharge valve 6 is made shorter than that of the suction valve 5.
  • Fig. 5 is an enlarged view of the discharge valve section of Fig. 1, and Figs. 6, 7(a) and 7(b) show other embodiments in Fig. 5.
  • the discharge valve 6 is a ball valve, a ball holder 63 fitted on the ball valve is provided, and a cylindrical part is formed at the outer periphery of the ball holder 63, so that the ball holder 63 is capable of sliding in the inner diameter side of the discharge valve holder 62.
  • the ball is held in the ball holder 63 at the time of the opening of the ball valve, it is possible to suppress the shaking of the ball and to stabilize the flow of fuel. Accordingly, it is possible to prevent cavitation generated by the turbulence of flow.
  • the outer diameter of the ball holder 63 is larger than the diameter of the ball valve, and notches are formed at several positions of the cylindrical part as shown in the section P-P in Fig. 5. Although the notches are formed at three positions in this embodiment, the number is not limited thereto.
  • This construction is not limited to a discharge valve. However, if it is employed for a discharge valve, it is possible to secure the oil tightly in a high-pressure piping in a more inexpensive technique than the case in which a conical valve is used.
  • the discharge valve seat 60 is pressure-welded to the pump body 1 to form the pressurization chamber, and the gasket 61 is provided at the outer periphery side of the valve seat 60 to form the fuel chamber 11b.
  • the discharge valve seat 60 and the gasket 61 are pressure-welded to the body 1 by fastening the valve holder 62 with screws. Accordingly, two portions are provided to be pressure-welded with the body 1 for forming the pressurization chamber 12.
  • the gasket 61 is made softer than the discharge valve seat 60 and the body 1, whereby it is possible to positively prevent the fuel from flowing outside the pump.
  • the second press-welded part is not directly subjected to the pressure fluctuation and fuel flow, it is possible to obtain a positive sealing performance without being subjected to the cavitation of fuel, even if the gasket 61 is formed of a soft material.
  • the protector 61a is interposed between the discharge valve seat 60 and the body 1, and the gasket 62, which is formed of the soft material, are pressure-welded to both of the discharge valve seat 60 and the discharge valve holder 62 at the outside thereof, thereby forming the fuel chamber 11b
  • Fig. 6 shows an embodiment, where the excessive cavitation of fuel is not generated, in which a sheet of gasket 61 is pressure-welded between the discharge valve seat 60 or the discharge valve 62, and the body 1.
  • the opposite side surfaces of the gasket 61 are formed with a groove 11c, by means of which the pressure-welded surface is bisected and the groove forms a fuel chamber (or space).
  • the groove is provided in the gasket surface, but it may not be provided on the opposite surface (body surface, etc.).
  • Fig. 8 is a partial enlarged view of the suction valve 5.
  • the suction valve 5 is a flat valve provided with a cup-shaped cylindrical part, wherein the outer periphery of the cylindrical part is slidably held in the inner diameter side of the suction valve holder 50.
  • notches are provided in some portions of the inner diameter of the suction valve holder 50 to form fuel passages. Although the notches are provided at five positions, the number is not limited thereto.
  • This construction is not limited to the suction valve, since a high responsiveness when the suction valve is opened can be obtained by employing the construction in the suction valve, and the pressure drop within the pressurization chamber caused by the delayed opening of the valve at the time of initiating the suction step can be suppressed. Accordingly, it is possible to prevent cavitation generated by the drop in pressure.
  • Fig. 12 is a view showing a section identical to Fig. 1, in which the reference numerals are similar to those used in Fig. 1.
  • Figs. 9 to 11 are partial enlarged views of the plunger seal in Fig. 12 and show other embodiments related to the shape of plunger seal.
  • Fig. 12 the return pipe 40 and communication bore 21a connected to the fuel tank 50 are not provided unlike Figs. 1 and 2.
  • the upper part of the plunger seal 30 in the drawing is provided with a plurality of seals in addition to the plunger seal 30.
  • the inside of the plunger seal 31 forms a blind passage which only communicates with the opening of the cylinder.
  • the inside of the plunger seal 31 is maintained at a certain pressure at the suction side, the gasification of fuel can be prevented and the lubricating performance can be maintained, and thus it is possible to enhance wear-resistance. Even if the pressure of the suction chamber 10a is pulsated by the operation of the pump, and since the pressure pulsation is attenuated in the sliding gap X between the plunger 2 and the cylinder 20, the pressure pulsation is not transferred to the plunger seal 31. Accordingly, it is possible to prevent the plunger seal from being fractured or worn.
  • lubricant oil, grease, etc.
  • plunger seals are used in this embodiment, it is effective even if only a lip type seal 30 is used as the plunger seal as in Fig. 1. That is, the inside of the plunger seal forms a blind passage which only communicates with the cylinder opening.
  • the inside of the plunger seal 30 is maintained at a certain pressure at the suction side, the gasification of fuel can be prevented, the lubricating performance can be maintained, and the wear-resistance can be enhanced. Further, even if the pressure of the suction chamber 10a is pulsated by the operation of the pump, and since the pressure pulsation is attenuated in the sliding gap X between the plunger 2 and the cylinder 20, the pressure pulsation is not transferred to the plunger seal 30. Accordingly, the damage and wear of the plunger 30 can be prevented.
  • lubricant oil, grease, etc.
  • a ring type seal 31 is added to the upper part of the plunger seal 30 in the drawing, making it possible to enhance the pressure resistance of the sealing material directly contacted with the fuel; it is also possible to relieve the pressure applied to the sealing material outside the pump; and it is possible to enhance the reliability of the sealing performance.
  • a plurality of sealing materials with different shapes are provided in the sliding part of the plunger and the sealing material provided outwardly of the pump is formed into a lip shape.
  • the ring type seal may be formed in the shape of an O-ring as shown in Fig. 12, an O-ring provided with the resin ring 31a in the sliding side as shown in Fig. 9, an X-ring as shown in Fig. 10, or a K-ring as shown in Fig. 11.
  • ring type seals such as O, X, K rings have a better formability than lip type seals and there is a greater degree of freedom in selecting material, it is possible to select a rubber material in accordance with a used fuel (alcohol and the like).
  • Fig. 13 is a vertical sectional view of the entire pump
  • Fig. 14 is an enlarged view inside the pump that is shown in Fig. 13.
  • the cylinder 20 and the pump body 1 are separately formed and the pressurization chamber 12 is formed by pressure-welding cylindrical tube members 5f, 6f to the suction valve holder 50, the discharge valve seat 60 and the cylinder 20 without being contacted with the pump body 1.
  • the cylinder 20 may be integrally formed with a plug 20f, although the plug 20 is pressure-welded to the upper part of the cylinder 20 in the drawing, thereby forming the pressurization chamber in order to improve the machinability of the cylinder 20.
  • cylindrical tube members are formed in a flange shape with one side of each pressure-welded part being in flat contact and the other side being in cylindrical contact, it is possible to absorb the unevenness in size for the two-directional components of the X and Y directions.
  • the body 1 is formed of a soft material such as aluminum, it is possible to prevent cavitation damage.
  • the body 1 and the cylinder 20 are formed of materials with largely different coefficients of linear expansion, it is possible to prevent the stack of the plunger generated when the sliding bore of the cylinder is deformed due to the fluctuation of temperature.
  • the body 1 is formed of aluminum, it is possible to provide a highly reliable pump that is contemplated to reduce the costs by improving machinability and to reduce the weight.
  • first and second welded parts are differentiated in materials, wherein the pressurization chamber side is formed of a hard material and the outside is formed of a soft material. As a result, it is possible to prevent the first pressure-welded part from being damaged by cavitation and it is also possible to enhance the sealing performance of the second pressure-welded part.
  • the hardness of the second pressure-welded member is softer than that of the housing, whereby the deformation of the housing side seal surface is reduced and a good sealing performance can be maintained only by replacing the pressure-welded member at the time of disassembly and reassembling thereof.
  • pressurization chamber and the low-pressure chamber are formed by the same member, and the partition wall between the pressurization and the low-pressure chamber is formed as the most weakened part in the pressurization chamber.
  • the cylinder holder for holding the cylinder formed of a material different from that of the housing is provided, and the engagement portion C of the cylinder holder and the housing is provided between the cylinder fixing portion A at the housing side and the cylinder fixing portion B at the cylinder holder side.
  • the outer diameter of the cylinder is preferably fitted in the inner diameter side of the cylinder holder, and the fitting portion and the engagement portion between the cylinder holder and the housing are located at different positions on the cylinder axis.
  • the sealing member for sealing the sliding part of the plunger is rendered to engage the cylinder holder.
  • the engagement portion C between the cylinder holder and the housing is positioned closer to the opening side of the cylinder holder than the fitting portion D between the cylinder holder and the cylinder.
  • the rigidity of the engagement portion C of the cylinder holder is lower than the fitting portion D, the radial deformation due to the expansion of the housing has difficulty arriving at the fitting portion D. Accordingly, it is possible to suitably maintain the gap of the plunger sliding part inside the cylinder and to prevent the seizure of the plunger.
  • the outer periphery of the cylinder holder is provided with the threaded part, so that the cylinder holder is engaged with the housing.
  • the cylinder holder is formed of a material having lower heat conductivity than the housing, the heat of the housing is hardly transferred to the cylinder, and thus the seizure of the plunger can be prevented.
  • the threaded part is coated with resin.
  • the annular fuel chamber is formed at the outer periphery of the cylinder, and the fuel chamber communicates with the low-pressure fuel chamber.
  • the heat transfer from the housing to the cylinder can be reduced and the cylinder can be cooled by fuel.
  • the plunger sliding part is provided with a sealing material
  • the fuel reservoir connected to the low-pressure fuel chamber is provided in a part of the sliding parts of the cylinder and the plunger, wherein the cylinder is connected to the inside of the sealing material.
  • the inside of the sealing material is made to form a blind passage which only communicates with the opening of the cylinder.
  • the inside of the sealing material can be maintained at a certain pressure at the suction side, the gasification of fuel can be prevented, and since the sealing performance is maintained, it is possible to enhance the wear-resistance. Further, even if the pressure within the low-pressure fuel chamber pulsates from the operation of the pump, the pressure pulsation is attenuated in the gap of the sliding part between the plunger and the cylinder. As a result, the pressure pulsation is not transferred to the inside of the sealing material. Accordingly, it is possible to prevent the damage and wear of the sealing material.
  • the plunger sliding part is provided with the sealing material and the fuel reservoir connected to the low-pressure fuel chamber is provided in a part of the sliding parts of the cylinder and the plunger, wherein the cylinder is connected to the inside of the sealing material.
  • the distance from the fuel reservoir to the sealing material side opening of the cylinder is formed to be shorter than the reciprocating sliding distance of the plunger.
  • the plunger sliding part is provided with a sealing material and the inside of the sealing material in the pump communicates with a chamber approximately under atmospheric pressure, such as a fuel tank, etc., and a throttle part is provided in a part of the communication passage.
  • the sealing material part is filled with fuel, it is possible to enhance the wear-resistance of the sealing material and the opening of the cylinder. In particular, it is more effective if the sealing material is positioned at a higher position than the communication passage.
  • a sealing material is provided in the plunger sliding part, and a lubricant (oil, grease, etc.) is enclosed inside the sealing material in the pump.
  • the annular fuel chamber is provided at the outer periphery of the heat generation portion (solenoid coil, etc.) of an actuator for controlling the ON/OFF timing of the suction valve, and the annular fuel chamber communicates with the low-pressure chamber.
  • the actuator can be cooled by fuel.
  • an actuator holder for holding the actuator is provided, and the outer periphery of the actuator is provided with a threaded part to engage the housing.
  • the heat transfer from the housing to the actuator can be reduced and the cylinder can be securely held by an inexpensive technique.
  • the actuator holder is formed of a material having lower heat conductivity than the housing, whereby the heat of the housing is hardly transferred to the actuator, and the burnt-down of the actuator can be prevented.
  • the threaded part is coated with resin.
  • the driving electric power of the actuator for controlling the ON/OFF timing of the suction valve is adapted to be gradually reduced at the OFF time.
  • the driving part of the actuator and the suction valve are separately formed and the operation distance is made smaller than that of the suction valve.
  • the operation distance of the actuator can be shortened to reduce the collision force and to secure a sufficient opening area of the suction valve.
  • the operation distance of the discharge valve is made lower than that of the suction valve.
  • At least one of the suction valve and discharge valve is a ball valve
  • a cylindrical member fitting around the ball valve is provided, and the outer periphery of the cylindrical member is adapted to be capable of sliding in the inner diameter side of the cylindrical part holding member.
  • the outer diameter of the cylindrical member is larger than the diameter of the ball valve, and notches are formed at several positions of the cylindrical part.
  • the above construction is employed in the discharge valve, whereby the oil tightness in high-pressure piping can be secured by an inexpensive technique.
  • At least one of the suction valve and discharge valve is a flat valve provided with a cup-shaped cylindrical part, wherein the outer periphery of the cylindrical part is slidably held in the inner diameter side of the cylindrical part holding part.
  • the cylindrical part is held when the flat valve is opened, it is possible to prevent the shaking of the valve body and to stabilize the flow of fuel. Accordingly, it is possible to prevent cavitation generated by the turbulence of flow. Further, since a spring for closing the valve can be located in the cup part, it is possible to reduce space.
  • notches are provided at some portions of the inner diameter of the cylindrical holding member to form fuel passages.
  • the above construction is employed in the suction valve, whereby a high responsiveness is obtained at the time of the opening of the suction valve, and the drop of pressure within the pressurization chamber caused by the delayed opening of the valve at the time of initiating the suction step, is suppressed. As a result, it is possible to prevent cavitation generated by the drop in fuel pressure.
  • the cylinder and the housing are separately formed and the cylindrical tube members are used for a part of the pressurization chamber.
  • cylindrical tube members are maintained by pressure-welding.
  • one side of pressure-welded parts is in flat contact and the other side thereof is in cylindrical contact, it is possible to absorb the unevenness in size for the two-directional components of X and Y directions.
  • the body is formed of aluminum, it is possible to provide a highly reliable pump to reduce the costs and to reduce the weight by improving machinability.
  • the sealing material provided outwardly of the pump is formed into a lip shape.
  • sealing materials directed inwardly of the pump may be formed in the shape of an O-ring (including a case that resin ring, etc., is disposed in the sliding side), an X-ring, or a K-ring.
  • ring type seals such as O, X, K rings have better formability than lip type seals, there is a greater degree of freedom in selecting the material. Accordingly, it is possible to select a rubber material in accordance with a used fuel (alcohol, etc.).
  • a high-pressure fuel pump which makes it possible to solve the problems encountered when a soft material such as aluminum alloy is used in a pump housing, and which has high reliability and has high cutting machinability. Accordingly it can be realized to reduce the cost and weight of the high-pressure fluid feed pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
EP01900260A 2001-01-05 2001-01-05 Hochdruckkraftstoffförderpumpe Withdrawn EP1348864A4 (de)

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 (2)

Publication Number Publication Date
EP1348864A1 true EP1348864A1 (de) 2003-10-01
EP1348864A4 EP1348864A4 (de) 2005-03-16

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Application Number Title Priority Date Filing Date
EP01900260A Withdrawn EP1348864A4 (de) 2001-01-05 2001-01-05 Hochdruckkraftstoffförderpumpe

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US (1) US20040052664A1 (de)
EP (1) EP1348864A4 (de)
JP (1) JPWO2002055870A1 (de)
WO (1) WO2002055870A1 (de)

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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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JP6397961B2 (ja) * 2017-05-22 2018-09-26 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
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EP1296061A3 (de) * 2001-09-21 2005-03-16 Hitachi, Ltd. Hochdruckkraftstoffpumpe
EP1296061A2 (de) * 2001-09-21 2003-03-26 Hitachi, Ltd. Hochdruckkraftstoffpumpe
FR2840366A1 (fr) * 2002-05-28 2003-12-05 Mitsubishi Electric Corp Appareil d'alimentation en carburant a haute pression
EP1739305A1 (de) * 2004-04-13 2007-01-03 NOK Corporation Kolbendichtung für pumpe
EP1739305A4 (de) * 2004-04-13 2007-07-18 Nok Corp Kolbendichtung für pumpe
EP1959142A1 (de) * 2004-04-13 2008-08-20 NOK Corporation Kolbendichtung für Pumpe
EP2067996A1 (de) * 2004-04-13 2009-06-10 NOK Corporation Kolbendichtung für eine Pumpe
DE102004041030A1 (de) * 2004-08-25 2006-03-02 Audi Ag Kraftstoffzumessung für einen Verbrennungsmotor mit Kraftstoffdirekteinspritzung
US8382458B2 (en) 2006-07-20 2013-02-26 Hitachi, Ltd. High-pressure fuel pump
EP1881191A3 (de) * 2006-07-20 2009-04-29 Hitachi, Ltd. Hochdruckbrennstoffpumpe
US8167577B2 (en) 2006-11-10 2012-05-01 Scania Cv Ab (Publ) Fuel pump device
WO2008057032A1 (en) * 2006-11-10 2008-05-15 Scania Cv Ab (Publ) Fuel pump device
DE102007019909A1 (de) * 2007-04-27 2008-11-06 Man Diesel Se Kraftstoffpumpe
DE102007019909B4 (de) 2007-04-27 2019-07-11 Man Energy Solutions Se Kraftstoffpumpe mit Leckagenuten
CN101424237B (zh) * 2007-11-01 2011-08-17 株式会社日立制作所 高压液体供给泵
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JPWO2002055870A1 (ja) 2004-05-20
US20040052664A1 (en) 2004-03-18
EP1348864A4 (de) 2005-03-16

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