EP0844385A1 - Dispositif d'injection de combustible à accumulation pour moteur à combustion interne - Google Patents

Dispositif d'injection de combustible à accumulation pour moteur à combustion interne Download PDF

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Publication number
EP0844385A1
EP0844385A1 EP97120502A EP97120502A EP0844385A1 EP 0844385 A1 EP0844385 A1 EP 0844385A1 EP 97120502 A EP97120502 A EP 97120502A EP 97120502 A EP97120502 A EP 97120502A EP 0844385 A1 EP0844385 A1 EP 0844385A1
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EP
European Patent Office
Prior art keywords
orifice
fuel
pressure
valve
orifice plate
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.)
Granted
Application number
EP97120502A
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German (de)
English (en)
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EP0844385B1 (fr
Inventor
Masashi Murakami
Tetsuya Toyao
Shuichi Matsumoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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Filing date
Publication date
Priority claimed from JP31047096A external-priority patent/JP3755143B2/ja
Priority claimed from JP31332896A external-priority patent/JP3719461B2/ja
Application filed by Denso Corp filed Critical Denso Corp
Publication of EP0844385A1 publication Critical patent/EP0844385A1/fr
Application granted granted Critical
Publication of EP0844385B1 publication Critical patent/EP0844385B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3827—Common rail control systems for diesel engines
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the present invention relates generally to an accumulator fuel injection apparatus equipped with a solenoid valve for injecting fuel stored within a common rail (i.e., surge tank) at a high pressure level into an internal combustion engine.
  • a common rail i.e., surge tank
  • U.S.P. No. 4,798,186 to Ganser issued on January 17, 1989 and U.S.P. No. 5,660,368 to De Matthaeis et al., issued on August 26, 1997 disclose electromagnetically controlled fuel injection systems designed to accumulate the fuel within a common rail under pressure through a high-pressure feed pump and inject the fuel into an internal combustion engine.
  • These fuel injection systems use a fuel injector and a solenoid operated two-way valve.
  • the fuel injector includes a pressure control chamber communicating with a high-pressure fuel passage.
  • the two-way valve selectively establishes and blocks fluid communication between the pressure control chamber and a low-pressure chamber to control the fuel pressure acting on a needle valve of the fuel injector for opening and closing a spray hole.
  • a first orifice is formed in a first orifice member to restrict the flow rate of fuel entering the pressure control chamber from the high-pressure fuel passage.
  • a second orifice is also formed in a second orifice member between the pressure control chamber and the low-pressure chamber to restrict the flow rate of fuel flowing from the pressure control chamber to the low-pressure chamber when the solenoid operated two-way valve is opened.
  • the quantity of fuel at the injection beginning, at the injection end, and during an early part of injection is determined by a difference in flow rate of fuels flowing from the high-pressure fuel passage to the pressure control chamber and flowing from the pressure control chamber to the low-pressure chamber when the solenoid operated two-way valve Is opened.
  • the quantity of fuel flowing out of the fuel injector after termination of injection and an interval between a time when the rate of injection shows a peak value and termination of injection are determined by the flow rate of fuel flowing from the high-pressure fuel passage to the pressure control chamber after the solenoid operated two-way valve is turned off or closed. Therefore, in order to ensure desired injection characteristics, it is necessary to adjust the flow rate characteristics of the first and second orifices by replacing the first and second orifice plates.
  • the fuel injection characteristics such as the injection timing, the injection quantity, and the rate of injection are, as described above, almost determined based on the flow rate characteristics of the first and second orifices, they will be changed greatly depending upon the shape, sectional area, circularity, inlet dimension, outlet dimension, surface roughness of the first and second orifices.
  • the optimum fuel injection over a wide range of engine operation which limits the rate of injection at an early part of injection and stops the injection at a high response rate, requires finely drilling the first and second orifices to have a diameter of approximately ⁇ 0.2 mm to ⁇ 0.4 mm.
  • the first and second orifices are formed in a single injector component.
  • both the first and second orifices must be replaced even when it is required to change the flow rate characteristics of either of the first and second orifices for adjusting the injection timing and/or the injection characteristics at early and/or late part of injection.
  • variations in machining accuracy in forming the first and second orifices may mutually affect, thereby making it more difficult to ensure the desired injection characteristics. This also increases the number of times the injector component is replaced until the desired injection characteristics are obtained in an injection characteristics adjustment process.
  • the first and second orifices are formed in different injector components and thus may be replaced separately for changing the flow rate characteristics.
  • One of the injector components having formed therein either of the first and second orifices supports the other slidably.
  • a clearance between sliding surfaces of the injector component pair having formed therein the first and second orifices is decreased as much as possible to facilitate sealing thereof for avoiding leakage of the high-pressure fuel out of the pressure control chamber. Therefore, replacement of only one of the injector component pair may result in an undesirable decrease in the clearance, thereby precluding the sliding motion of the injector components or in great increase in the clearance, thereby leading to the leakage of fuel.
  • an accumulator fuel injection apparatus for injecting high-pressure fuel stored within a common rail into an internal combustion engine which comprises: (a) a valve body having formed therein a fuel inlet passage and a spray hole, fuel inlet passage communicating with the common rail; (b) a valve member disposed slidably within the valve body for selectively establishing and blocking fluid communication between the fuel inlet passage and the spray hole; (c) a pressure control chamber formed within the valve body, the pressure control chamber being connected to the fuel inlet passage to introduce therein fuel pressure which acts on the valve member to block the fluid communication between the fluid inlet passage and the spray hole; (d) a fuel pressure drain passage formed within the valve body, connected to the pressure control chamber for draining the fuel pressure out of the valve body; (e) a solenoid valve selectively establishing and blocking fluid communication between the pressure control chamber and the fuel pressure drain passage; (f) a first orifice plate having formed therein a first orifice which provides a first flow resistance to fuel
  • the first orifice has a length extending in parallel to a thickness of the first orifice plate.
  • the second orifice has a length extending in parallel to a thickness of the second orifice plate.
  • the first and second orifices are formed by drilling the first and second orifice plates and reaming drilled holes.
  • the first and second orifices may alternatively be machined in an electron discharge method.
  • the first and second orifices may also be polished by forcing an abrasive solution made of a mixture of liquid and abrasive grain therethrough until the flow of the abrasive solution through the first and second orifices reaches a given flow rate.
  • Each of the first and second orifice plates Is made of a disc in which first and second through holes are formed.
  • Two knock pins are inserted into the valve body through the first and second through holes of the first and second orifice plates to fix angular positions of the first and second orifice plates relative to the valve body.
  • the first, and second through holes are formed at different intervals away from the center of each of the first and second orifice plates so that a line extending through the centers of the first and second through holes is offset from the center of each of the first and second orifice plates.
  • a first large-diameter hole which has a diameter greater than that of the first orifice may be formed in the first orifice plate coaxially with the first orifice in communication with the first orifice.
  • a second large-diameter hole which has a diameter greater than that of the second orifice may also be formed in the second orifice plate coaxially with the first orifice in communication with the second orifice.
  • the first and second orifice plates are so disposed within the valve body that the first orifice plate is exposed at a first surface to the pressure control chamber and at a second surface opposite the first surface in contact with a first surface of the second orifice plate, and the second orifice plate is exposed at a second surface opposite the first surface to the fuel pressure drain passage.
  • a cylindrical chamber is formed in the second surface of the second orifice plate in communication with the second orifice which has a diameter greater than that of the second orifice.
  • the solenoid valve includes a valve head which opens and closes the second orifice to establish and block the fluid communication between the pressure control chamber and the fuel pressure drain passage.
  • An annular valve seat on which the valve head of the solenoid valve is to be seated to block the fluid communication between the pressure control chamber and the fuel pressure drain passage, is formed on the second surface of the second orifice plate around an opening of the cylindrical chamber.
  • An annular groove is formed in the second surface of the second orifice plate around the annular valve seat of the second orifice plate in fluid communication with the fuel pressure drain passage.
  • the cylindrical chamber may alternatively be formed in the valve head opening to the second orifice of the second orifice plate which has a diameter greater than that of the second orifice.
  • a fuel injection apparatus for a diesel engine equipped with a solenoid-operated fuel injector 1 according to the first embodiment of the invention.
  • the fuel injector 1 is connected at an inlet port 70 to a common rail 141 through a fuel supply pipe. To the common rail 141, high-pressure fuel is supplied through a fuel pump 140. A control signal is inputted to a pin 29a of a wire harness connector 29 from an electronic control unit (ECU) 500 for controlling the fuel injection into a combustion chamber of the engine.
  • ECU electronice control unit
  • the fuel injector 1 includes a spray nozzle 2 and an injector body 91.
  • the spray nozzle 2 includes a nozzle body 213 having a spray hole 101a formed in the tip thereof.
  • a needle valve 220 is slidably disposed within the nozzle body 213 to close and open the spray hole 101a.
  • the nozzle body 213 and the injector body 91 are jointed through a packing chip 212 by a retaining nut 214.
  • a pressure pin 221 and a control piston 12 are disposed within the injector body 91 in alignment with the needle valve 220.
  • the control piston 12 is in contact with the pressure pin 221, but may alternatively be bonded thereto.
  • the pressure pin 221 is disposed within a spring 223.
  • the spring 223 urges the pressure pin 221 downward, as viewed in the drawing, to bring the needle valve 220 into constant engagement with the spray hole 101a.
  • the set load of the spring 223 is adjusted by load adjusting spacers 325 and 326.
  • the control piston 22 is exposed at an end opposite to the spray hole 101a to a pressure control chamber 30.
  • the high-pressure fuel entering the inlet port 70 passes through a fuel filter 361 and flows both to high-pressure fuel passages 61 and 64.
  • the part of the high-pressure fuel entering the high-pressure passage 61 is supplied directly to an annular fuel sump 324 formed around the periphery of the needle valve 220, while the other entering the high-pressure fuel passage 64 is supplied to the pressure control chamber 30.
  • the pressure of fuel in the fuel sump 324 acts on the needle valve 220 to lift it upward, as viewed in the drawing, for establishing fluid communication between the fuel sump 324 and the spray hole 101a, while the pressure of fuel in the pressure control chamber 30 acts on the control piston 12 to urge the needle valve 220 downward so that it closes the spray hole 101a.
  • the injector body 13 has also formed therein a fuel drain passage 365, as clearly shown in Fig. 3, which communicates with a spring chamber 327 and drains the fuel leaking out of sliding clearances between inner walls of the injector body 91 and the spray nozzle 2 and outer peripheral surfaces of the control piston 12 and the needle valve 220 to a low-pressure fuel chamber 68 through fuel passages 210b and 211b, as clearly shown in Fig. 2, formed in first and second orifice plates 210 and 211, as will be described later in detail.
  • a fuel drain passage 365 as clearly shown in Fig. 3, which communicates with a spring chamber 327 and drains the fuel leaking out of sliding clearances between inner walls of the injector body 91 and the spray nozzle 2 and outer peripheral surfaces of the control piston 12 and the needle valve 220 to a low-pressure fuel chamber 68 through fuel passages 210b and 211b, as clearly shown in Fig. 2, formed in first and second orifice plates 210 and 211, as will be described later in detail
  • the fuel within the low-pressure fuel chamber 68 passes through low-pressure fuel passages 345a formed in a valve cylinder 345, a low-pressure fuel passage 341a formed in a valve shaft 241, a low-pressure fuel passage 242a formed in a plunger 242, holes 334a formed in an armature 26 of a solenoid valve 20, a low-pressure fuel passage 25a extending along the center of a core 25 of the solenoid valve 20, and a low-pressure fuel passage 69 formed in a housing 50 and then flows out of a fuel withdrawal union 73 through a low-pressure fuel passage 73a, as shown in Fig. 1 so that excess fuel is drained outside the fuel injector 1.
  • the first and second orifice plates 210 and 211 are, as clearly shown in Fig. 2, disposed adjacent each other so that thicknesswise directions thereof coincide with each other and retained by the valve cylinder 345 within the injector body 91.
  • the first orifice plate 210 has formed therein a first orifice 66 which restricts the flow rate of fuel from the high-pressure fuel passage 64 to the pressure control chamber 30.
  • the second orifice plate 211 has a second orifice 67 formed in the center thereof which limits the flow rate of fuel from the pressure control chamber 30 to the low-pressure fuel chamber 68.
  • the first and second orifice plates 210 and 211 are, as shown in Figs. 5(a) to 6(b), made of discs.
  • the first and second orifices 66 and 67 communicate with large-diameter holes 66a and 67a formed in bottoms of the first and second orifice plates 210 and 211 coaxially with the first and second orifices 66 and 67 and extend parallel to vertical center lines (i.e., the thicknesswise directions) of the first and second orifice plates 210 and 211, respectively, so that they are easy to machine with high accuracy.
  • the first orifice plate 210 has formed therein two bores 210a.
  • the second orifice plate 211 has formed therein two bores 211a.
  • the bores 210a are arranged at the same interval away from the center of the first orifice plate 210 so that a line extending through the centers of the bores 210a is offset from the center of the first orifice plate 210.
  • the bores 211a are arranged at the same interval away from the vertical center line of the second orifice plate 211 so that a line extending through the centers of the bores 211a is offset from the center of the second orifice plate 211.
  • Two positioning knock pins 55 (only one is shown in Fig.
  • the second orifice plate 211 has, as shown in Figs. 2 and 6(b), an annular flat surface 211c formed on an upper surface around the center thereof (i.e., the second orifice 67).
  • the annular flat surface 211c works as a valve seat on which a ball 243 (i.e., a valve head), as will be described later in detail, of the solenoid valve 20 is seated.
  • a ball 243 i.e., a valve head
  • An annular path 155 is formed around the annular flat surface 211c which adds a given volume to the low-pressure fuel chamber 68 for facilitating ease of the fuel flow to the low-pressure fuel chamber 68 when the ball 243 is lifted away from the second orifice plate 211.
  • the first and second orifices 66 and 67 may be formed by drilling the first and second orifice plates 210 and 211 and reaming the drilled holes or by drilling the first and second orifice plates 210 and 211 in the electrical discharge machining.
  • the first and second orifices thus formed may also be polished in a finishing process by forcing an abrasive solution made of a mixture of liquid and abrasive grain therethrough until the flow of the abrasive solution through the first and second orifices 66 and 67 reaches a given flow rate.
  • the solenoid valve 20 is a two-way valve designed to selectively establish and block the fluid communication between the pressure control chamber 30 and the low-pressure fuel chamber 68.
  • the solenoid valve 20 is, as shown in Figs. 1 and 2, installed in the injector body 91 by the retaining nut 59.
  • a pin 153 is inserted into the housing 50 and the core 25 to fix an angular relation therebetween and also hold relative rotation of the core 25 and the housing 50 when the retaining nut 59 is fastened during assembly for preventing a rotational load from acting on feeder terminals 72 shown in Fig. 3.
  • the solenoid valve 20 includes, as shown in Fig. 2, a coil 24 and a movable member 240.
  • the coil 24 is made of wire wound within an annular groove formed in the core 25 and supplied with the power through the pin or terminal 29a of the connector 29.
  • the core 25 is formed with 0.2 mm-thick silicon steel plates laminated spirally and welded to a hollow cylinder 333 in which the plunger 242 is disposed.
  • the movable member 240 includes the valve shaft 241, the plunger 242, the ball 243, and the support 244.
  • the valve shaft 241 and the plunger 242 are urged into constant engagement with each other by the fuel pressure and spring pressure exerted from the pressure control chamber 30 and the spring 27, respectively, so that they are moved vertically together when the solenoid valve 20 is turned on and off.
  • the plunger 242 is made of a non-magnetic stainless steel for eliminating a magnetic effect on a magnetic circuit.
  • the valve shaft 241 is slidably supported within the valve cylinder 345 and is made from a wear resistant material such as a magnetic material because the valve shaft 241 is magnetically located out of the magnetic circuit.
  • the armature 26 is mounted on an upper portion of the valve shaft 241 in a press fit at a given interval away from a lower end of the core 25 of the solenoid valve 20 and made from, for example, a silicon steel since it needs to work as part of the magnetic circuit rather than needing to have wear resistance and has formed therein a plurality of bores 334a for reducing the fluid resistance during movement.
  • the armature 26 may alternatively be mounted on the valve shaft 241 in caulking, welding, or any other suitable manner.
  • the amount of lift of the movable member 240 may be adjusted by changing the thickness of a spacer 54.
  • the movable member 240 is lifted upward until the valve shaft 241 reaches the lower end of the cylinder 333.
  • the support 244 is made of a hollow cylindrical member and mounted on an end of the valve shaft 241 in a press fit or welding.
  • the ball 243 is disposed rotatably within a chamber defined by an inner wall of the support 244 and a cone-shaped recess formed in the end of the valve shaft 241 with a clearance of several ⁇ m between itself and the inner wall of the support 244.
  • the support 244 is caulked at an end thereof to retain the ball 243 therein.
  • the ball 243 is made from ceramic or cemented carbide and has formed thereon a flat surface which is seated on the annular flat surface 211c, as shown in Fig.
  • the amount of lift of the valve shaft 241 is approximately 100 ⁇ m, which allows the ball 243 to face at the flat surface to the second orifice plate 211 at all times regardless of the vertical position of the valve shaft 241 and to be seated on the annular flat surface 211c to close the second orifice 67 completely even when the ball 243 and the second orifice 67 are somewhat shifted in relative angular position.
  • the plunger 242 is disposed slidably within the cylinder 33 with a clearance with the inner wall thereof which is greater than the above sliding clearance.
  • the coil spring 27 is interposed between a spacer or shim 46 and a flange of the plunger 242 to urge the plunger 242 downward so that the ball 243 closes the second orifice 67.
  • the spring pressure acting on the plunger 242 may be adjusted by changing the thickness of the shim 46.
  • This embodiment has the following specifications on major parts of the structure:
  • the diameter of the second orifice 67 (corresponding to a seat diameter of the bail 243 when seated on the second orifice plate 211) is 0.32 mm, and the diameter d , as shown in Fig. 6(b), of a ball seat of the second orifice plate 211 on which the ball 243 is seated is 0.50 mm.
  • the fluid pressure urging the ball 243 in a valve-opening direction is 19.5 N which is smaller than the set load of the spring 47 urging the movable member 240 of the solenoid valve 20 in a valve-closing direction that is, as described above, 50 N, so that the movable member 240 is not lifted upward as long as the coil 24 is turned off.
  • the diameter of the control piston 12 is 5.0 mm
  • the diameter of the needle valve 220 is 4.0 mm
  • the seat diameter of the needle valve 220 is, as described above, 2.25 mm
  • a pressure-energized area of the control piston 12 is greater than that of the needle valve 220, and a difference therebetween is approximately 11 mm 2 .
  • the spring pressure of the coil spring 223 urges the needle valve 220 in the valve-closing direction
  • the sum of the fuel pressure within the pressure control chamber 30 urging the control piston 12 in the valve-closing direction and the spring pressure of the spring 223 is greater than the fuel pressure within the fuel sump 324 lifting the needle valve 220 upward as long as the coil 24 is turned off.
  • the solenoid valve 20 is in an off-position
  • the needle valve 220 continues to close the spray hole 101a.
  • the coil 24 of the solenoid valve 20 When the coil 24 of the solenoid valve 20 is energized, it produces an electromagnetic force of approximately 60 N attracting the armature 26, so that the sum of the electromagnetic force and the fuel pressure within the pressure control chamber 30 urging the movable member 240 in the valve-opening direction becomes greater than the spring pressure of the coil spring 27, thereby lifting the movable member 240 upward to move the ball 243 away from the second orifice plate 211.
  • This establishes the fluid communication between the second orifice 67 and the low-pressure fuel chamber 68 so that the fuel within the pressure control chamber 30 flows into the low-pressure fuel chamber 68 through the second orifice 67.
  • the fuel pressure within the pressure control chamber 30 drops immediately when the ball 243 is lifted up away from the second orifice 67.
  • the fuel pressure within the pressure control chamber 30 drops, and the sum of the fuel pressure within the pressure control chamber 30 urging the control piston 12 in the spray hole-closing direction and the spring pressure of the coil spring 223 becomes smaller than the fuel pressure within the fuel sump 324 lifting up the needle valve 220, it will cause the needle valve 220 to be moved away from the spray hole 101a to initiate fuel injection.
  • the coil 24 of the solenoid valve 20 is deenergized, so that the electromagnetic force attracting the armature 26 is decreased from 60 N to zero (0). This causes the movable member 240 to be moved by the spring force of the spring 27 away from the coil 24 to bring the ball 243 into engagement with the second orifice 67.
  • the fuel pressure within the pressure control chamber 30 is elevated by the fuel flowing from the high-pressure fuel passage 64 through the first orifice 66, so that the sum of the fuel pressure within the pressure control chamber 30 urging the control piston 12 in the spray hole-closing direction and the spring pressure of the spring 223 becomes greater than the fuel pressure within the fuel sump 324 lifting the needle valve 220 upward, thereby bringing the needle valve 220 into engagement with the spray hole 101a to terminate the fuel injection.
  • Figs. 7(a) to 7(d) show a displacement of the movable member 240, a variation in fuel pressure within the pressure control chamber 30, a displacement of the control piston 12, a rate of injection during one cycle of injection, respectively.
  • Solid lines indicate parameters when the first orifice 66 has a smaller diameter showing a greater flow resistance, while broken lines indicate parameters when the first orifice 66 has a greater diameter showing a smaller flow resistance.
  • the injection characteristics of the fuel injector 1 are almost determined by the flow rate of fuel flowing into the pressure control chamber 30 from the first orifice 66 and the flow rate of fuel flowing out of the pressure control chamber 30 into the low-pressure fuel chamber 68 through the second orifice 66.
  • the start time of injection and an increase in injection rate during an early part of injection are determined by a difference in flow rate between the fuel entering the pressure control chamber 30 and the fuel emerging from the pressure control chamber 30 into the low-pressure fuel chamber 68 after the solenoid valve 20 is turned on or opened.
  • variations in flow rate characteristic of the first and second orifices 66 and 67 will cause a dropping speed of the pressure within the pressure control chamber 30 immediately after the solenoid valve 20 is opened to be changed.
  • the dropping speed of pressure within the pressure control chamber 30 when the first orifice 66 shows a greater flow resistance, as indicated by the solid line, is higher than that when the first orifice 66 shows a smaller flow resistance, as indicated by the broken line. Additionally, the injection beginning is earlier and the increase in injection rate during the early part of injection is greater than those when the first orifice 66 shows the smaller flow resistance.
  • This constant pressure and the valve-opening pressure acting on the control piston 12 are determined by differences between pressure-energized areas of the needle valve 220 and the control piston 12 on which the fuel pressures act in the spray hole-opening and -closing directions and the spring pressure of the coil spring 223 urging the needle valve 220 in the spray hole-closing direction, and not the flow rate characteristics of the first and second orifices 66 and 67.
  • the duration for which the fuel pressure within the pressure control chamber 30 is maintained constant is the time required for the control piston 12 to reach a fully-lifted position and may be changed by changing the flow rate characteristics of the first and second orifices 66 and 67. Specifically, as shown in Fig. 7(b), the duration for which the fuel pressure within the pressure control chamber 30 is kept constant when the first orifice 66 shows the smaller flow resistance indicated by the broken line is longer than that when the first orifice 66 shows the greater flow resistance indicated by the solid line.
  • the pressure within the pressure control chamber 30 drops below the valve-opening pressure of the needle valve 220 or down to a pressure level which is determined by the difference in flow rate characteristic between the first and second orifices 66 and 67 and is kept constant. Within this constant pressure range, the rate of injection is almost kept constant as long as the pressure acting on the top portion of the needle valve 220 is at a fixed level.
  • the pressure within the pressure control chamber 30 rises up to a valve-closing pressure which is determined, similar to the valve-opening pressure, by the differences between pressure-energized areas of the needle valve 220 and the control piston 12 on which the fuel pressures act in the valve-opening and -closing directions and the spring pressure of the coil spring 223 urging the needle valve 220 in the valve-closing direction.
  • the control piston 12 is moved in the valve-closing direction. Specifically, when the coil 24 Is deenergized, the movable member 340 is moved downward, as viewed in Fig.
  • the valve-closing pressure of the control piston 12 is, similar to the valve-opening pressure, constant even if the flow rate characteristics of the first and second orifices 66 and 67 are changed.
  • the time interval between deenergization of the solenoid valve 20 and a time when the pressure within the pressure control chamber 30 reaches the valve-closing pressure of the control piston 12 will, however, change if the pressure within the pressure control chamber 30 during the energization of the solenoid valve 20 is changed by changes in flow rate characteristic of the first and second orifices 66 and 67.
  • the time required for closing the spray hole 101a in the valve-closing stroke of the control piston 12 is changed, similar to the valve-opening stroke, by the difference in flow rate of fuels flowing through the first and second orifices 66 and 67.
  • the time required for closing the spray hole 101a when the first orifice 66 shows the greater flow resistance, as indicated by the solid line in Fig. 7(c), is longer than that when showing the smaller flow resistance, as indicated by the broken line.
  • a decrease in rate of injection at termination of fuel injection when the first orifice 66 shows the greater flow resistance is slower than that when showing the smaller flow resistance.
  • the injection characteristics other than the injection cut-off period depend upon the difference in flow rate of fuels flowing into the first orifice 66 and out of the second orifice 67. Therefore, a change in flow resistance of the second orifice 67 without changing the flow resistance of the first orifice 66 also causes the injection beginning, the rate of initial injection, and the injection end to be changed.
  • the injection cut-off period is changed only by changing the flow resistance of the first orifice 66.
  • the first and second orifice plates 210 and 211 are made of separate members, which allows the flow rate characteristics of each of the first and second orifices 66 and 67 to be adjusted in an injection characteristic adjustment process when the fuel injector 1 is assembled by replacing corresponding one of the first and second orifice plates 210 and 211. Specifically, the injection beginning, the rate of initial injection, the injection end, and the injection cut-off period may be adjusted only by replacing one of the first and second orifice plates 210 and 211.
  • the flow rate characteristics of each spare orifice plate is determined by passing a gas oil that is fuel for diesel engines through an orifice thereof at 10 Mpa to measure the flow rate of the gas oil.
  • the flow rate characteristics of the first and second orifice plates 210 and 211 may be determined by monitoring variations in rate of injection, pressure within the pressure control chamber 30, and lift of the needle valve 220.
  • Fig. 8 shows the fuel injector 1 according to the second embodiment of the invention.
  • the same reference numbers as employed in the first embodiment refer to the same parts, and explanation thereof in detail will be omitted here.
  • the first orifice plate 56 has the first orifice 76 formed in a bottom surface exposed to the pressure control chamber 30. Specifically, the first orifice 76 is, unlike the first embodiment, exposed directly to the pressure control chamber 30, but identical in operation with the first embodiment.
  • the movable member 80 of the solenoid valve 20 includes the valve shaft 81, the hollow rod 82, the plunger 83, the ball 243, and the support 244.
  • An assembly of the rod 82 and the plunger 83 corresponds to the plunger 242 of the first embodiment.
  • the connector 84 which supplies the power to the coil 24 of the solenoid valve 20 extends diagonally up to the right in the drawing because the screw 90, as will be described in detail below, is mounted along a longitudinal center line of the solenoid valve 20.
  • the screw 90 is inserted into the housing 92 through the gasket 91.
  • the amount of insertion of the screw 90 may thus be adjusted by changing the thickness of the gasket 91, which allows the spring load of the coil spring 27 acting on the plunger 83 to be regulated from outside the fuel injector 1.
  • the second embodiment is designed to change the injection characteristics easily by adjusting the thickness of the gasket 91.
  • Figs. 9 and 10 show the third embodiment of the invention which is different from the above embodiments only in structure of the first and second orifice plates. Other arrangements are identical, and explanation thereof in detail will be omitted here.
  • the first orifice plate 100 as shown in Fig. 10, has formed therein through holes 100a and 100b.
  • the second orifice plate 101 as shown in Fig. 9, has formed therein through holes 101a and 101b.
  • the through holes 100a, 100b, 101a, and 101b serve to fix angular positions of the first and second orifice plates 100 and 101 relative to the injector body 91 using knock pins.
  • the through holes 100a, 100b, 101a, and 101b are arranged in the first and second orifice plates 100 and 101 so as to satisfy the following two geometrical specifications:
  • Each of the first and second orifice plates 100 and 101 may alternatively have formed therein three or more through holes and be designed to satisfy only the above second specification (2).
  • Figs. 11(a) and 11(b) show the fourth embodiment of the invention which is different from the above embodiments in structure of the second orifice plate 211. Other arrangements are identical, and explanation thereof in detail will be omitted here.
  • Fig. 11(b) shows only central portions of the first and second orifice plates 210 and 211 different from those in the above embodiments for the brevity of illustration.
  • the second orifice plate 211 has, as shown in Fig. 11(b), a cylindrical fuel chamber 168 formed in an upper surface thereof coaxially with the second orifice 67 in communication with the second orifice 67.
  • the cylindrical fuel chamber 168 is greater in diameter, that is, smaller in flow resistance than the second orifice 67 and establishes fluid communication between the second orifice 67 and the low-pressure fuel chamber 68 when the solenoid valve 20 is turned on to lift the ball 243 upward.
  • the cylindrical fuel chamber 168 has an opening area smaller than an area of a flat valve head 243a of the ball 243 of the solenoid valve 20.
  • the second orifice plate 211 has a flat valve seat 53 and a fuel relief path 54 formed on and in the upper surface thereof.
  • the flat valve seat 53 consists of a central annular seat 53a and four fan-shaped seats 53b which are all engageble with the flat valve head 243a in surface contact.
  • the annular seat 53a is formed around the periphery of the cylindrical fuel chamber 168.
  • the fan-shaped seats 53b are formed at regular intervals around the annular seat 53a.
  • the fuel relief path 54 includes a central annular path 54a and four radially extending paths 54b and establishes fluid communication with the low-pressure fuel chamber 68 at all times.
  • the annular path 54a is defined between an outer periphery of the annular seat 53a and inner peripheries of the fan-shaped seats 53b and coaxially with the cylindrical fuel chamber 168 for equalizing fuel pressures acting on the flat valve head 243a of the ball 243.
  • the radially extending paths 54b are each defined between adjacent two of the fan-shaped seats 53b and communicate with the annular path 54a at angular intervals of 90°.
  • annular path 155 Formed around the fan-shaped seats 53b is the annular path 155, as shown in Figs. 6(a) and 6(b), which communicates with the radially extending paths 54b.
  • the annular path 155 is, as described above, provided for adding a given volume to the low-pressure fuel chamber 68 to facilitate ease of the fuel flow to the low-pressure fuel chamber 68 when the ball 243 is lifted away from the second orifice plate 211.
  • the fourth embodiment has the following specifications on the structural elements as shown in Figs. 11(a) and 11(b):
  • the plunger 242 In operation of the fuel injector 1, when the coil 24 of the solenoid valve 20 is in an off-position, the plunger 242 is urged downward, as viewed in Fig. 2, by the spring pressure of the coil spring 27.
  • the ball 243 is seated on the second orifice plate 211 to block the fluid communication between the pressure control chamber 30 and the low-pressure fuel chamber 68.
  • the pressure distribution between contact surfaces of the flat valve head 243a of the ball 243 and the annular seat 53a is expressed by a logarithmic function showing the point symmetry in which a peak pressure that is the pressure within the pressure control chamber 30 (i.e., the pressure within the cylindrical fuel chamber 168) is developed at the inner edge of the annular seat 53a, and the lowest pressure appears at the outer edge of the annular seat 53a that is the pressure within the radially extending paths 54b.
  • the fuel relief path 54 serves to keep the fuel pressure lifting the ball 243 away from the second orifice plate 211 at low level when the solenoid valve 20 is in the off-position.
  • the inner diameter c of the annular seat 53a is, as described above, 0.4 mm, and the outer diameter of the annular seat 53a is 0.7 mm.
  • the fuel pressure supplied from the common rail 141 i.e., the pressure within the pressure control chamber 30
  • the fuel pressure urging the ball 243 in the valve-opening direction will be 35 N in view of the fuel pressure distributed between the flat valve head 243a of the ball 243 and the annular seat 53a in addition to the fuel pressure within the cylindrical fuel chamber 168.
  • the set load of the coil spring 27 is, as described above, 50 N which is greater than the fuel pressure of 35 N urging the bail 243 in the valve-opening direction.
  • the diameter of the control piston 12 is 5.0 mm
  • the diameter of the needle valve 220 is 4.0 mm
  • the seat diameter of the needle valve 220 is 2.25 mm
  • a pressure-energized surface of the control piston 12 is greater than that of the needle valve 220, and a difference therebetween is approximately 11 mm 2 .
  • the spring pressure of the coil spring 223 acts on the needle valve 220 in the spray hole-closing direction.
  • the sum of a force acting on the control piston 12 in the spray hole-closing direction, produced by the fuel pressure within the pressure control chamber 30 and the spring pressure of the coil spring 223 is kept greater than the fuel pressure within the fuel sump 324 lifting the needle valve 220 upward as long as the coil 24 is deenergized, so that the needle valve 220 closes the spray hole 101a.
  • the coil 24 of the solenoid valve 20 When the coil 24 of the solenoid valve 20 is energized, it produces an electromagnetic force of approximately 60 N attracting the armature 26, so that the sum of the electromagnetic force and the fuel pressure within the pressure control chamber 30 urging the movable member 240 in the valve-opening direction becomes greater than the spring pressure of the coil spring 27, thereby lifting the movable member 240 upward to move the ball 243 away from the second orifice plate 211.
  • This establishes the fluid communication between the second orifice 67 and the low-pressure fuel chamber 68 so that the fuel within the pressure control chamber 30 flows into the low-pressure fuel chamber 68 through the second orifice 67.
  • the diameter of the cylindrical fuel chamber 168 is, as already described, greater than that of the second orifice 67, so that the flow resistance drops as the fuel flows from the second orifice 67 to the cylindrical fuel chamber 168. Therefore, even if the amount of lift of the movable member 240 is decreased below that in the above embodiments, the flow resistance of fuel flowing out of the cylindrical fuel chamber 168 may be kept smaller than that of fuel passing through the second orifice 67.
  • the coil 24 of the solenoid valve 20 is deenergized, so that the electromagnetic force attracting the armature 26 is decreased from 60 N to zero (0).
  • This causes the movable member 240 to be moved by the spring force of the spring 27 away from the coil 24 to bring the ball 243 into engagement with the second orifice 67, thereby causing the needle valve 220 to be moved downward to close the spray hole 101a so that the fuel injection is terminated.
  • the fourth embodiment features the formation of the cylindrical fuel chamber 168 downstream of the second orifice 67 which shows the flow resistance smaller than that of the second orifice 67.
  • This allows the amount of lift of the movable member 240 to be decreased, thereby resulting in improved response rate and wear resistance and decrease in mechanical noise of the fuel injector 1.
  • a variation in amount of lift of the movable member 240 is minimized, thus reducing a variation in flow rate of fuel flowing into the low-pressure fuel chamber 68 when the solenoid valve 20 is turned on to open the spray hole 101a.
  • the fourth embodiment also features the formation of the fuel relief path 54 in the upper surface of the second orifice plate 211, which decreases the fuel pressure acting on the ball 242 of the solenoid valve 20 in the valve-opening direction when the solenoid valve 20 is turned off This allows the spring pressure of the coil spring 27 urging the movable member 240 downward to be decreased, thereby also allowing the electromagnetic attracting force produced by the coil 24 when energized to be decreased.
  • the annular path 54a is formed in the second orifice plate 211 coaxially with the cylindrical fuel chamber 168, thereby causing the fuel pressures acting on the flat valve head 243a of the ball 243 in the valve-opening direction to be equalized to minimize inclination of the flat valve head 243a relative to the valve seat 53 of the second orifice plate 211. This allows the injection quantity to be adjusted finely.
  • the cylindrical fuel chamber 168 may be first drilled to guide drilling of the second orifice 67. This facilitates easy of machining of the second orifice 67.
  • Figs. 12(a) and 12(b) shows the fifth embodiment of the invention which is a modification of the fourth embodiment.
  • the same reference numbers as employed in Figs. 11(a) and 11(b) refer to the same parts.
  • the ball 243 has formed in the flat valve head 243a a central cylindrical fuel chamber 243b which corresponds to the cylindrical fuel chamber 168 of the fourth embodiment.
  • the other dimensions a , b , d , e , g , and h are the same as those in the fourth embodiment.
  • An area of an opening of the cylindrical fuel chamber 243b is smaller than an area of the flat valve head 243a.
  • the second orifice 67 opens directly to an annular seat 53c formed on the upper surface of the second orifice plate 211 so that the inner diameter of the annular seat 53c is equal to the diameter b of the second orifice 67.
  • the width of the annular seat 53c is greater than that of the annular seat 53a as shown in Fig. 11(b).
  • the flow resistance of fuel flowing out of the second orifice 67 becomes smaller than when the cylindrical fuel chamber 243b is not formed in the flat valve head 243a. Specifically, the fuel flowing out of the second orifice 67, like the first embodiment, is not decreased in flow rate when passing between the annular seat 53c and the flat valve head 243a. This results in improved response rate and wear resistance and decrease in mechanical noise of the fuel injector 1.
  • the cylindrical fuel chambers 168 and 243b may be of cone-shape in which the inner diameter increases as approaching the opening.
  • the cylindrical fuel chamber 168 may also be formed in the second orifice plate 211 of the fifth embodiment, while the cylindrical fuel chamber 243b may also be formed in the flat valve head 243a of the fourth embodiment.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP19970120502 1996-11-21 1997-11-21 Dispositif d'injection de combustible à accumulation pour moteur à combustion interne Expired - Lifetime EP0844385B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP310470/96 1996-11-21
JP31047096 1996-11-21
JP31047096A JP3755143B2 (ja) 1996-11-21 1996-11-21 蓄圧式燃料噴射装置
JP31332896A JP3719461B2 (ja) 1996-11-25 1996-11-25 蓄圧式燃料噴射装置
JP31332896 1996-11-25
JP313328/96 1996-11-25

Publications (2)

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EP0844385A1 true EP0844385A1 (fr) 1998-05-27
EP0844385B1 EP0844385B1 (fr) 2003-03-05

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19859592C1 (de) * 1998-12-22 2000-05-04 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE19904720A1 (de) * 1999-02-05 2000-08-17 Siemens Ag Injektor für eine Einspritzanlage einer Brennkraftmaschine
EP0957262A3 (fr) * 1998-05-13 2000-11-22 Lucas Industries Limited Injecteur de combustible
WO2001012981A1 (fr) * 1999-08-17 2001-02-22 L'orange Gmbh Soupape d'injection pour moteur a combustion
DE19937677A1 (de) * 1999-08-10 2001-02-22 Siemens Ag Einspritzventil mit verbesserter Dichtflächenanordnung
WO2001018382A1 (fr) * 1999-09-09 2001-03-15 Robert Bosch Gmbh Injecteur a rampe commune
WO2001029397A1 (fr) * 1999-10-19 2001-04-26 Robert Bosch Gmbh Injecteur pour un systeme d'injection a rampe commune de moteurs a combustion interne, a compensation partielle des forces agissant sur l'aiguille
EP1136692A2 (fr) * 2000-03-21 2001-09-26 C.R.F. Società Consortile per Azioni Injecteur de carburant avec une aiguille de contrôle commandée par la pression du carburant dans une chambre de commande
EP1296054A1 (fr) * 2001-09-22 2003-03-26 Robert Bosch Gmbh Injecteur pour un moteur à combustion
EP1283354A3 (fr) * 2001-08-11 2003-11-26 Robert Bosch Gmbh Système d'injection de carburant
EP1387077A1 (fr) * 2002-07-30 2004-02-04 Magneti Marelli Powertrain S.p.A. Injecteur de carburant pour un moteur à combustion interne avec aiguille à actionnement hydraulique
WO2006021015A1 (fr) * 2004-08-24 2006-03-02 Robert Bosch Gmbh Soupape de commande pour injecteur
WO2009021821A1 (fr) * 2007-08-13 2009-02-19 Robert Bosch Gmbh Connecteur électrique avec retour de carburant
EP2053234A3 (fr) * 2007-10-24 2009-11-04 Denso Corporation Injecteur de carburant
CN105484921A (zh) * 2015-12-11 2016-04-13 中国北方发动机研究所(天津) 一种可变进油量孔式高压共轨喷油器控制阀及其控制体
WO2017067811A1 (fr) * 2015-10-19 2017-04-27 Delphi International Operations Luxembourg S.À R.L. Soupape d'admission numérique pour pompe à carburant haute pression

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US4566416A (en) * 1981-07-31 1986-01-28 Stanadyne, Inc. Accumulator nozzle fuel injection system
GB2185530A (en) * 1986-01-22 1987-07-22 Dereco Dieselmotoren Forschung Fuel injection system for an internal combustion engine
US4798186A (en) 1986-09-25 1989-01-17 Ganser-Hydromag Fuel injector unit
EP0304747A1 (fr) * 1987-08-25 1989-03-01 WEBER S.r.l. Soupape à injection de combustible commandée électromagnétiquement pour moteurs diesel
EP0740068A2 (fr) * 1995-04-28 1996-10-30 Lucas Industries public limited company Buse d'injection de combustible
JPH09158811A (ja) * 1995-12-05 1997-06-17 Denso Corp 燃料噴射装置
US5660368A (en) 1993-12-30 1997-08-26 Elasis Sistema Ricerca Fiat Nel Mezzogiorno Societa Consortile Per Azioni Metering valve for controlling the shutter of a fuel injector

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Publication number Priority date Publication date Assignee Title
US4566416A (en) * 1981-07-31 1986-01-28 Stanadyne, Inc. Accumulator nozzle fuel injection system
GB2185530A (en) * 1986-01-22 1987-07-22 Dereco Dieselmotoren Forschung Fuel injection system for an internal combustion engine
US4798186A (en) 1986-09-25 1989-01-17 Ganser-Hydromag Fuel injector unit
EP0304747A1 (fr) * 1987-08-25 1989-03-01 WEBER S.r.l. Soupape à injection de combustible commandée électromagnétiquement pour moteurs diesel
US5660368A (en) 1993-12-30 1997-08-26 Elasis Sistema Ricerca Fiat Nel Mezzogiorno Societa Consortile Per Azioni Metering valve for controlling the shutter of a fuel injector
EP0740068A2 (fr) * 1995-04-28 1996-10-30 Lucas Industries public limited company Buse d'injection de combustible
JPH09158811A (ja) * 1995-12-05 1997-06-17 Denso Corp 燃料噴射装置

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Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0957262A3 (fr) * 1998-05-13 2000-11-22 Lucas Industries Limited Injecteur de combustible
DE19859592C1 (de) * 1998-12-22 2000-05-04 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE19904720C2 (de) * 1999-02-05 2003-01-16 Siemens Ag Injektor für eine Einspritzanlage einer Brennkraftmaschine
DE19904720A1 (de) * 1999-02-05 2000-08-17 Siemens Ag Injektor für eine Einspritzanlage einer Brennkraftmaschine
DE19937677A1 (de) * 1999-08-10 2001-02-22 Siemens Ag Einspritzventil mit verbesserter Dichtflächenanordnung
DE19937677C2 (de) * 1999-08-10 2003-06-26 Siemens Ag Einspritzventil mit verbesserter Dichtflächenanordnung
WO2001012981A1 (fr) * 1999-08-17 2001-02-22 L'orange Gmbh Soupape d'injection pour moteur a combustion
WO2001018382A1 (fr) * 1999-09-09 2001-03-15 Robert Bosch Gmbh Injecteur a rampe commune
WO2001029397A1 (fr) * 1999-10-19 2001-04-26 Robert Bosch Gmbh Injecteur pour un systeme d'injection a rampe commune de moteurs a combustion interne, a compensation partielle des forces agissant sur l'aiguille
EP1136692B1 (fr) * 2000-03-21 2007-05-23 C.R.F. Società Consortile per Azioni Injecteur de carburant avec une aiguille de contrôle commandée par la pression du carburant dans une chambre de commande
EP1136692A2 (fr) * 2000-03-21 2001-09-26 C.R.F. Società Consortile per Azioni Injecteur de carburant avec une aiguille de contrôle commandée par la pression du carburant dans une chambre de commande
EP1283354A3 (fr) * 2001-08-11 2003-11-26 Robert Bosch Gmbh Système d'injection de carburant
EP1296054A1 (fr) * 2001-09-22 2003-03-26 Robert Bosch Gmbh Injecteur pour un moteur à combustion
EP1387077A1 (fr) * 2002-07-30 2004-02-04 Magneti Marelli Powertrain S.p.A. Injecteur de carburant pour un moteur à combustion interne avec aiguille à actionnement hydraulique
US6913206B2 (en) 2002-07-30 2005-07-05 Magneti Marelli Powertrain S.P.A. Fuel injector for an internal combustion engine with hydraulic pin actuation
WO2006021015A1 (fr) * 2004-08-24 2006-03-02 Robert Bosch Gmbh Soupape de commande pour injecteur
WO2009021821A1 (fr) * 2007-08-13 2009-02-19 Robert Bosch Gmbh Connecteur électrique avec retour de carburant
US8177568B2 (en) 2007-08-13 2012-05-15 Robert Bosch Gmbh Electric plug having fuel return
EP2053234A3 (fr) * 2007-10-24 2009-11-04 Denso Corporation Injecteur de carburant
WO2017067811A1 (fr) * 2015-10-19 2017-04-27 Delphi International Operations Luxembourg S.À R.L. Soupape d'admission numérique pour pompe à carburant haute pression
CN108474338A (zh) * 2015-10-19 2018-08-31 德尔福知识产权有限公司 用于高压燃料泵的数字式入口阀
US10724484B2 (en) 2015-10-19 2020-07-28 Delphi Technologies Ip Limited Digital inlet valve
CN105484921A (zh) * 2015-12-11 2016-04-13 中国北方发动机研究所(天津) 一种可变进油量孔式高压共轨喷油器控制阀及其控制体

Also Published As

Publication number Publication date
DE69719461D1 (de) 2003-04-10
EP0844385B1 (fr) 2003-03-05
DE69719461T2 (de) 2004-01-15

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