WO1996041948A1 - Ajutage d'injection de carburant a ouverture variable - Google Patents

Ajutage d'injection de carburant a ouverture variable Download PDF

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Publication number
WO1996041948A1
WO1996041948A1 PCT/JP1996/001536 JP9601536W WO9641948A1 WO 1996041948 A1 WO1996041948 A1 WO 1996041948A1 JP 9601536 W JP9601536 W JP 9601536W WO 9641948 A1 WO9641948 A1 WO 9641948A1
Authority
WO
WIPO (PCT)
Prior art keywords
hole
fuel
injection
conical surface
rotary valve
Prior art date
Application number
PCT/JP1996/001536
Other languages
English (en)
Japanese (ja)
Inventor
Toshiyuki Hasegawa
Shinya Nozaki
Takeshi Miyamoto
Masanori Amemori
Takashi Kobayashi
Original Assignee
Zexel Corporation
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 Zexel Corporation filed Critical Zexel Corporation
Priority to GB9723123A priority Critical patent/GB2316130B/en
Priority to US08/945,660 priority patent/US5947389A/en
Priority to DE19681434T priority patent/DE19681434T1/de
Publication of WO1996041948A1 publication Critical patent/WO1996041948A1/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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1826—Discharge orifices having different sizes
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • 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
    • F02M2200/29—Fuel-injection apparatus having rotating means

Definitions

  • the present invention relates to a fuel injection nozzle having a variable injection hole area.
  • a fuel injection nozzle is widely used as a means for supplying fuel to a combustion chamber in an atomized state in a diesel engine or the like.
  • Such a fuel injection nozzle accommodates a needle valve slidably in the axial direction in a nozzle body, as disclosed in Japanese Patent Application Laid-Open No. 59-2000063, etc.
  • a cone-shaped pressure-receiving surface is formed at the tip of the dollar valve, the fuel pressure is applied to the cone-shaped pressure-receiving surface, the valve is opened, and a plurality of injection holes formed at the tip of the nozzle body enter the engine combustion chamber. It had a structure to eject.
  • Japanese Patent Laid-Open Publication No. Hei 6-241141 discloses a first group of injection holes (five) on the circumference of a wall near the lower part of a 21 dollar valve with a closed end.
  • a second injection hole group (five) with a different diameter from the first injection hole is provided on the circumference different from this, and the needle valve is moved in the axial direction within the sleeve.
  • the needle valve is moved in the axial direction within the sleeve.
  • Japanese Patent Laid-Open Publication No. Hei 7-1 7266 describes that a hole is formed at the tip of a nozzle body and a plurality of (eight) orifices communicating with the hole are formed on a wall surrounding the hole.
  • the rotary shaft is formed at intervals in the circumferential direction, the rotary shaft is passed through a through hole formed in the axis of the needle valve, the tip of the rotary shaft is positioned in the hole, and the dollar valve is opened on the rotary shaft.
  • a plurality of grooves (four) are provided to allow the fuel pressure chamber in the hole created at the time of the valve to communicate with the injection hole, and the numerical aperture of the injection hole is switched between eight and four by rotating the rotating shaft.
  • a proposal has been made in which the total area of the injection holes is changed according to the engine load and the number of revolutions.
  • the hole wall had a straight cylindrical shape parallel to the nozzle axis, and the rotary shaft as the rotary valve had only a cylindrical shape. For this reason, it is difficult to fix the rotary shaft as a one-way valve during fuel injection, and even if the injection hole is adjusted to the desired opening by the rotary shaft, the high injection pressure will not increase.
  • the rotating shaft is acted upon, the rotating shaft is inadvertently displaced in the rotational direction around the axis, which causes the relationship between the opening and the groove to shift, and the injection hole area increases from the set size or The decline was inevitable.
  • the prior art there was a problem that the total area of the injection holes corresponding to the engine load and the number of revolutions could not be accurately controlled.
  • there is no mechanism to fix the rotary valve during fuel injection as described above so a large motor with relatively large torque is required for the motor driving the rotating shaft, and the fuel injection nozzle is enlarged. There was a problem of doing.
  • a first object of the present invention is to make it possible to easily control the rotation position (change the injection hole area) of the mouthpiece valve with low torque when the needle valve is closed, that is, during non-fuel injection. It is an object of the present invention to provide a fuel injection nozzle that can firmly fix the position of a rotary valve only by fuel injection pressure when the valve is opened, that is, during fuel injection.
  • the injection hole can be made variable, which makes it possible to easily control the injection rate for rebuilt injection and the like.
  • a second object of the present invention in addition to the first object, has a spray pattern characteristic in which the spray angle with respect to the axis hardly changes, and the number of sprays on the plane and the spray direction hardly change. It is an object of the present invention to provide a fuel injection nozzle capable of determining a shielding area steplessly and finely adjusting it.
  • a third object of the present invention in addition to the first or second object, is to automatically correct even when the position of the rotary valve is shifted for each injection, and to reduce the variation of the spray for each injection. It is an object of the present invention to provide a fuel injection nozzle that can perform pressure reduction. Disclosure of the invention
  • the present invention provides a needle valve which has a hole at the tip end of a nozzle body for guiding pressurized fuel, and which is opened and closed at a predetermined fuel pressure at an inlet side of the hole.
  • a plurality of injection holes for injecting pressurized fuel are provided on the surrounding wall that defines the hole at intervals in the circumferential direction, and a rotary valve is provided in the hole, and the rotary valve is connected to the rotary valve by an actuator.
  • a fuel injection nozzle of the type in which the area of the injection hole opening is adjusted by rotating, the surrounding wall defining the hole has a conical surface, and the injection hole is opened in this conical surface.
  • the rotary valve has a pressure receiving surface at the upper end for receiving the pressure of the pressurized fuel, and has a conical surface on the outer periphery having an angle in accordance with the inclination angle of the conical surface of the hole.
  • Multiple fuel passages that open to the surface In per cent Li provided spaced manner, the injection hole of the fuel passage the hole-side It has a configuration that opens to the conical surface corresponding to.
  • the conical surface of the hole surrounding wall and the conical surface of the rotary valve generate a frictional holding torque exceeding the rotational torque that acts to rotate the rotary valve in the circumferential direction by the injection pressure during fuel injection.
  • Such angles are given.
  • a plurality of injection holes having the same diameter or different diameters are arranged on the hole surrounding wall having a conical surface, and the rotary valve is provided with a fuel passage capable of communicating with the injection holes. Therefore, if the rotation of the orifice valve is controlled by the actuator, the shielding area of the injection hole changes depending on the rotation angle, or the fuel passage selectively communicates with an arbitrary injection hole.
  • the one-way valve has a pressure-receiving surface at the upper end for receiving the pressure of the pressurized fuel, and has a conical surface on the outer periphery having an angle in accordance with the inclination angle of the conical surface of the peripheral wall of the hole.
  • the rotary valve Since the rotary valve is fixed by the fuel injection pressure, the rotary valve is rotated to inject fuel not only at the time of fuel injection but also at any time when fuel is injected with an arbitrary injection hole opening area set.
  • the holes can be made variable, which makes it easy to control the re-pilot injection rate. Also, since the rotary valve is tightly sealed with the inner wall of the hole, pressurized fuel opens the fuel passage. It does not flow from the mouth along the circumferential direction.
  • the present invention provides, in addition to the above-described configuration, the same diameter of each injection hole of the surrounding wall that defines the hole, and the opening on the conical surface of the fuel passage of the one-way valve
  • the diameter of the injection hole is made equal to or larger than the diameter of the injection hole, and the opening degree of each injection hole is gradually changed according to the rotation amount of the one-way valve.
  • the processing becomes easy.
  • spraying is always performed from each injection hole, and there is almost no change in the spray direction on a plane.
  • the amount of spray can be changed finely, it is possible to perform the optimum spray according to the engine load and the number of revolutions.
  • the present invention provides a rotation angle detection mechanism in a drive shaft system of a rotary valve, and an output side of the rotation angle detection mechanism is a controller for driving an actuator. Connected, the actuator is driven by a signal from the rotation angle detection mechanism during non-fuel injection or during fuel injection and during fuel injection to correct the rotation angle of the rotary valve.
  • FIG. 1 is a vertical sectional side view showing a first embodiment of the present invention.
  • FIG. 2 is a partially enlarged view of FIG.
  • FIG. 3 is a partially enlarged view showing a state in which the valve of FIG. 1 is opened from a closed state.
  • FIG. 3A is a partially enlarged view of FIG.
  • Fig. 4-A is a cross-sectional view taken along line X-X in Fig. 3 when the injection hole is opened.
  • Fig. 4-1B is a front view showing one injection hole in the state of Fig. 4-1A.
  • Fig. 5-A is a cross-sectional view taken along line X-X in Fig. 3 showing a state in which the injection hole is fully opened.
  • FIG. 5B is a front view showing one injection hole in the state of FIG. 5A.
  • FIG. 6 is a perspective view of the one-way valve in FIGS. 1 to 5.
  • FIG. 7 is a partially enlarged sectional view showing an example in which another rotary valve is used in the first embodiment.
  • FIG. 8 is a perspective view of the one-way valve in FIG.
  • FIG. 9 is a partially enlarged sectional view showing an example in which another rotary valve is used in the first embodiment.
  • FIG. 10 is a perspective view of the rotary valve in FIG.
  • FIG. 11A is a cross-sectional view showing a state in which a large diameter injection hole is selected by applying the first embodiment to an injection hole selection type fuel injection nozzle.
  • FIG. 11B is a cross-sectional view showing a state where the injection hole having the same small diameter is selected.
  • Fig. 12 shows the rotary valve when the one shown in Fig. 6 is used as the rotary valve. It is explanatory drawing which shows the parameter of pulp.
  • FIG. 12A is an explanatory view showing the force applied to the fuel passage in FIG.
  • Fig. 13 is an explanatory diagram showing the mechanical relationship of the valve around the mouth when closing the injection hole.
  • FIG. 14 is an explanatory diagram showing the parameters of the rotary valve when the rotary valve shown in FIG. 7 is used.
  • FIG. 15 is a torque diagram when the rotary valves shown in FIGS. 6 and 7 are used.
  • FIG. 16 is a longitudinal sectional side view showing a second embodiment of the present invention.
  • FIG. 17 is a partially enlarged view of FIG.
  • Fig. 18-A is a cross-sectional view along the line Y-Y of Fig. 17.
  • Fig. 18-B is a cross-sectional view of the state in which the rotary valve is being rotated from the state shown in Fig. 18-A and an injection hole is being selected.
  • Fig. 18-C is a cross-sectional view showing a state where another injection hole is selected from that in Fig. 18-A.
  • FIG. 19 is a perspective view showing an example of a one-way valve according to the second embodiment.
  • FIG. 20A is a plan view showing another example of the rotary valve according to the second embodiment.
  • FIG. 20B is a cross-sectional view taken along line Z—Z of FIG. 20A.
  • FIG. 21 is a cross-sectional view showing another example of the portal valve in the second embodiment.
  • FIG. 22 is a flowchart of the injection hole control according to the present invention. Detailed description of the invention
  • 1 to 10 show a first embodiment of the present invention.
  • 1 is a nozzle holder main body
  • 2 is a driving head that is oil-tightly fitted and fixed to an upper end of the nozzle holder main body 1 via an O-ring
  • 3 is a lower end of the nozzle holder main body 1.
  • the nozzle body is connected to the nozzle holder body 1 by a retaining nut 5.
  • Reference numeral 4 denotes a 21 dollar valve (nozzle 21 dollar) inserted in the nozzle body 3.
  • a first hole 100a to a third hole 100c whose diameter is gradually increased from a lower end toward an upper end is formed.
  • a push rod 101 is slidably inserted in a region from 00 a to the second hole 100 b.
  • an adjusting screw 102 screwed with the female screw of the third hole 100 c is fitted in the area from the third hole 100 c to the second hole 100 b.
  • a nozzle spring 103 is interposed between the steering screw 102 and the push rod 101.
  • the nozzle body 3 has a stepped portion 30 fitted to the bottom of the bag hole of the retaining nut 5 at the middle portion in the longitudinal direction of the outer surface, and a cylindrical shape extending through the retaining nut 5 below the stepped portion 30.
  • a main portion 31 is provided, and a tip portion 32 for forming an injection hole is formed in the main portion 31 via a taper portion.
  • a guide hole 300 concentric with the first hole 100 a of the nozzle holder body 1 is provided on the axis of the nozzle body 3 from the upper end to the lower end.
  • An oil reservoir 310 with a large diameter is also formed in the through hole 300, and a guide hole 300 in which the diameter of the guide hole 300 is relatively small is lower than the oil reservoir 310.
  • a hole 302 is drilled.
  • a conical sheet surface 303 is formed as shown in FIG. 2, FIG. 3 and FIG.
  • a bottomed hole 34 into which the pressurized fuel is guided is defined by a wall at the tip.
  • a pressurized fuel port 104 connected to an inlet connector is provided at one side of the nozzle holder main body 1, and the pressurized fuel port 104 is formed in the nozzle holder body 1 and the nozzle body 3.
  • the oil reservoir 310 is communicated with the oil reservoir 301 through the passage holes 105, 305, and the pressurized fuel is guided there.
  • the needle valve 4 has an engaging portion 41 with the push rod 101 at the upper end, and a guide portion 40 that slides on the guide hole 300 on the outer periphery.
  • a pressure receiving portion 42 for receiving the fuel pressure in the oil reservoir 310 is provided at the end of 40.
  • a thin shaft portion 43 for forming the cylindrical fuel passage A is provided below this pressure receiving portion 42, as shown in FIG.
  • a thin shaft portion 43 for forming the cylindrical fuel passage A is provided.
  • a conical seat surface 44 that is in contact with and separates from the seat surface 303 is formed.
  • the inside of the wall defining the hole 34 is a tapered conical surface 341, which is smoothly continuous with the sheet surface 03 as shown in FIGS. 2, 3 and 3A.
  • the lower end of the conical surface 3 4 1 is a hemispherical end wall.
  • a plurality of injection holes 35 communicating with the hole 34 ⁇ as shown in FIGS. It is arranged at equal intervals on the circumference.
  • the number of the injection holes 35 is five in this embodiment, and extends radially at intervals of 62 degrees on the circumference.
  • each injection hole 35 may be perpendicular to the nozzle axis, but in this embodiment, it has a predetermined inclination angle with respect to the nozzle axis.
  • the cross-sectional shape perpendicular to the axis of the injection hole 35 is circular in the embodiment, but may be polygonal. In the case of a polygonal cross-sectional shape, the amount of change in the injection hole area per unit rotation angle can be increased.
  • a rotary vanoleb 7 is arranged in the hole 34. The rotary valve 7 is driven by an actuator 9 attached to a drive head 2 through a drive shaft system 8 penetrating through a through-hole provided in the needle valve 4 and the adjusting screw 102. As a result, the nozzle is rotated around the nozzle axis.
  • a first hole 45a is formed in the shaft center of the needle valve 4 in a relatively short range from the lower end.
  • a conical surface 451 and a short hole 452 are provided in the terminal region of the second hole 45a, and the short hole 452 communicates with the second hole 45b having a larger diameter than the first hole 45a. ing.
  • the second hole 45b reaches the upper end of the needle valve 4.
  • a third hole 45c having a diameter substantially equal to that of the second hole 45b is formed in the axis of the push rod 101, and the axis of the adjusting screw 102 is formed in the axis of the push screw 102.
  • a fourth hole 45d is formed from the lower end to the upper end.
  • the fourth hole 4 ⁇ d has a moderately smaller diameter at the upper end region to prevent the drive shaft from blurring.
  • the drive shaft system 8 includes a shaft body 8a reaching the drive head 2, a joint pin 8b and a joint 10, and the rotary valve 7 It is connected to the joint pin 8b via a hand 10.
  • the shaft main body 8a has a length from the fourth hole 45d to the lower end region of the second hole 45b.
  • the joint pin 8b has a large diameter portion 80 that freely fits in the second hole 45b.
  • the upper end of the joint pin 8b and the lower end of the shaft main body 8a are connected to each other so that rotational force is transmitted by joints 811 and 801 of an Oldham type such as a type that allows backlash in the axial direction.
  • the joint 10 is for transmitting the rotational torque and the holding torque to the rotary knob 7 while allowing the axial play of the rotary valve 7 caused by the lift of the needle valve 4.
  • the joint 10 has a cylindrical portion having a diameter that fits loosely into the first hole 45a, and the lower end of the cylindrical portion is connected to a later-described rotor valve 7 so as to be relatively slidable in the axial direction. Groove 10b is formed.
  • a conical surface 10c At the upper end of the cylindrical portion of the joint 10 is formed a conical surface 10c that is seated on the conical surface 451, as shown in FIGS. 2 and 3, and the upper end of the conical surface 10c.
  • a short shaft portion 10 d that fits into the short hole 45 2 extends from the upper end, and a protruding piece 10 e is formed at the upper end of the short shaft 10 d.
  • the protruding piece 10 e has a large diameter portion 80. It is engaged with a groove provided at the lower end of the motor to transmit torque.
  • the actuator 9 is fixed to a space 200 provided in the driving head 2.
  • the actuator 9 is arbitrary as long as it has a characteristic capable of rotating (preferably reversible rotation) and holding at a predetermined rotational position, for example, a stepping motor or a servomotor.
  • the output shaft and the upper end of the shaft body 8a are directly connected or a transmission element such as an eccentric They are connected to pins or gears.
  • FIG. 6 shows the rotary valve 7 in a single state.
  • the rotary knob 7 has a flat pressure receiving surface 74 at the upper end on which the pressure of the pressurized fuel acts when the needle valve 4 is opened.
  • a protruding piece 70 is formed in the center of the pressure receiving surface 74, and the protruding piece 70 is fitted into the groove 10b of the joint 10 so as to be relatively slidable in the vertical direction. ing.
  • the rotary valve 7 has, below the pressure receiving surface 74, a conical surface 72 that is tapered and inclined at an angle that matches the conical surface 34 1 of the hole 34. And the conical surface 341 form a friction sheet surface. The height of the conical surface 72 is limited so that the lower end does not contact the bottom wall of the hole 34.
  • the rotary valve 7 has a plurality of fuel passages 73 each having one end opened to the pressure receiving surface 74. The other end of each of the fuel passages 73 is opened so as to communicate with the injection hole 35 provided on the conical surface 34 1 of the hole 34. It is necessary that the fuel passage 73 has a cross section perpendicular to the axis having a size equal to or larger than the diameter of the injection hole 35.
  • the fuel passage 73 is composed of five grooves opened in the conical surface 72, and the grooves correspond to the injection holes 35 provided in the conical surface 34 of the hole 34. Thus, they are formed at intervals of 62 degrees in the circumferential direction.
  • Each of the grooves has a groove bottom 735 substantially parallel to the inclination angle of the conical surface 72 of the one-way valve 7. Then, the lower end of each groove ends at a position corresponding to immediately below the injection hole 35.
  • FIGS. 7 and 8 show another example (second example) of the one-way valve 7 used in the first embodiment.
  • each groove has a groove bottom 735 parallel to the nozzle axis as is clear from FIG.
  • the other structures are the same as those shown in FIGS. 2 to 6, and the corresponding parts are denoted by the same reference numerals and description thereof will be omitted.
  • FIGS. 9 and 10 show still another example (third example) of the rotary valve 7 used in the first embodiment.
  • the fuel passage 73 is formed of a hole instead of a groove, and a plurality (five in this example) of lateral holes 730 that can communicate with the injection hole 35 are formed on the circumference. Radial holes are drilled at predetermined intervals (every 62 ° in this example), and a plurality of vertical holes 731 are formed from the pressure receiving surface 74 of the rotary valve 7 to the horizontal hole 730. It is necessary that the fuel passage 73 has a diameter equal to or greater than that of the injection hole 35.
  • the other structures are the same as those shown in FIGS. 2 to 6, and the corresponding parts are denoted by the same reference numerals and description thereof will be omitted.
  • FIGS. 11A and 11B show an example in which the first embodiment of the present invention is applied to select a type of injection hole having a plurality of types of diameters for the rotation of the rotary valve 7. I have.
  • the entire hole 34 has a conical surface. That is, as in a second embodiment to be described later, a straight cylindrical surface parallel to the nozzle axis is formed from the end of the sheet surface 303 to an intermediate portion, and the tapered conical shape is formed from the end of the straight cylindrical surface.
  • the surface may be 3 4 1.
  • the one-way valve 7 also has a straight cylindrical surface parallel to the nozzle axis from the pressure receiving surface 74 to the intermediate portion, and a conical surface 72 is formed from the end thereof. This is also included in the present invention.
  • the inclination angle of the conical surface 341 of the hole 34 and the conical surface 72 of the rotary valve ⁇ ⁇ is usually selected from the range of 50 to 70 °. Will be done. In the figure, it is 60 °.
  • the number of the injection holes 35 and the number of the fuel passages 73 are five, respectively. However, the number is not limited to this, and is four or six or more. You can. Also, in Fig. 11-A and B, the number of injection holes 35 is eight in total, and the number of fuel passages 73 of the rotary valve 7 is four, but the number may be more or less.
  • three first injection holes 35a and three second injection holes 35b may be provided, and three fuel passages 73 of the one-way valve 7 may be provided.
  • the diameter of the injection hole 35 may be large, medium, or small instead of two.
  • the timing when the rotary valve 7 is rotated by the actuator 9 generally corresponds to a period during which no axial force is applied to the drive shaft system 8 by the engine cylinder pressure, that is, the intake stroke or the exhaust stroke of the engine.
  • the engine cylinder pressure that is, the intake stroke or the exhaust stroke of the engine.
  • a controller 12 composed of a CPU is electrically connected to the actuator 9, and an engine or fuel injection pump rotation speed detection sensor 120 (or 20) is connected to an input of the controller 12.
  • a rotation angle detection sensor) and a load detection sensor 121 such as a rack sensor of the fuel injection pump are connected to each other.
  • the signal from the rotation speed detection sensor 120 is always input to the controller 12, and the drive signal is output to the actuator 9 when it is determined that the engine is in the above-described stroke.
  • the signals from the load detection sensor 122 are input simultaneously, and a predetermined drive amount (drive rotation angle), for example, low speed, low speed, is applied to the actuator 9 by a predetermined map formed in advance from the load and rotation speed data.
  • Drive control is performed such that the rotation angle gradually increases in the order of load—medium speed, medium load—high speed, and high load.
  • the drive shaft system is provided with a rotation angle detecting mechanism 11.
  • the rotation angle detection mechanism 11 detects the rotation angle for each fuel injection, sends this rotation angle signal to the controller 12 as a feedback signal, and sets it to the rotary valve 7. This is a means for performing a correction by outputting a drive signal from the controller 12 to the actuator 9 when there is an error in the rotation angle.
  • the rotation angle detection mechanism 11 is optional such as a potentiometer, an encoder, and a collimator. In this embodiment, a potentiometer is used.
  • a rotating member 110 is fixed to the shaft main body 8a, and the rotating member 110 and the rotating member 112 fixed to the shaft of the potentiometer main body 111 are connected to each other.
  • a regular polygon (in this example, a regular pentagon) reflecting piece corresponding to the number of injection holes is fixed to the shaft body 8a, while the wall of the driving head 2 is
  • a light source for irradiating a light beam to the reflecting piece may be attached, and a light receiving unit composed of a photoelectric conversion element, that is, a light receiving element array may be attached from the vicinity of the light source along the inner wall of the driving head 2.
  • the light receiving section is provided at least over an angle range obtained by dividing 360 ° by the number of injection holes (72 ° in this example), and the output side is connected to the controller 12.
  • the drive shaft system to which the rotation angle detection mechanism 11 is mounted is not necessarily limited to the shaft body 8a.
  • the output shaft that is coaxial with the shaft body 8a may be provided on the opposite shaft body side of the connector 9 and the rotating element of the rotation angle detecting mechanism 11 may be attached thereto.
  • the orifice valve 7 is provided with a series of operations by the actuator 9 before, during and after the re-injection in a flow chart as shown in FIG.
  • the conical surface 7 2 and the conical surface 3 41 of the hole 34 are held in position by frictional force due to the pressure of the pressurized fuel acting on the pressure receiving surface 74 of the rotary valve 7. Therefore, the single valve 7 can be rotated even during fuel injection.
  • FIGS. 12 to 15 show the torque applied to the one-way valve 7 in the first embodiment.
  • Fig. 12 and Fig. 12-A show the mechanical relationship when the first example shown in Figs. 2 to 6 (this is referred to as type 1) is used as the rotary knob 7.
  • the friction coefficient is ⁇
  • the radius of the pressure receiving surface is ri
  • the radius of the lower end of the conical surface 72 is r 2
  • the fuel passage 73 of the rotary valve 7 has a groove structure, and the groove bottom 735 is parallel to the inclination angle of the conical surface 72, so that FIG.
  • the reaction force R shown in A is generated. Therefore, if the area of the groove bottom 7 3 5 is A, the force F applied to the injection pressure is
  • T i ⁇ ri of by Uni rotor Ribarubu 7 satisfying T 2, r 2 only the fuel injection pressure can be positioned fixed to the rotor Ribarubu 7 by selecting and alpha.
  • the force F applied to the rotary valve 7 by the injection pressure can be changed.
  • the rotation torque can also be changed.
  • FIG. 14 shows the force applied to the rotary valve when the second example of FIGS. 7 and 8 (this is referred to as type 2) is used as the one-way valve 7.
  • type 2 this is referred to as type 2
  • the groove bottom 7 3 5 of the fuel passage 7 3 is parallel to the nozzle axis, holding the rotor Ribarubu torque T 2 (N m) is represented by the following formula (gamma).
  • T 2 ⁇ ,. ⁇ ⁇ (i 1 3 + r l 2 -i 2 ) / 2 ⁇ ? ...
  • Fig. 15 shows the torque diagram for Type 1 and Type 2.
  • the maximum torque generated by the fuel flow is not due to the frictional force between the mouth valve and the hole wall. It can be seen that the generated torque is higher than any of the injection pressures, and that the throttle valve can be reliably fixed at the desired rotational angle position. Also, when the fuel passage 73 has a hole type as shown in the third example of FIG. 9 and FIG. 10, the holding torque of the mouth valve 7 is almost the same as that of type 2.
  • FIG. 16 to FIG. 21 show a second embodiment of the present invention.
  • the diameter of the injection hole 35 of the hole 34 is made to be plural types, and the plural types of injection holes 35 are selectively shielded by the rotary valve 7, so that the total injection hole surface is made. The product is adjusted.
  • FIG. 16 shows the whole
  • FIG. 17 shows an enlarged view of the main part.
  • the bottomed hole 34 has a straight cylindrical surface 3400 parallel to the nozzle axis from the end of the sheet surface 303 to a required position.
  • the lower end of the conical surface 341 is a horizontal or curved end wall.
  • the wall defining the hole 34 has a plurality of injection holes 35 communicating with the hole 34 in a region corresponding to the conical surface 341, as shown in FIGS. At predetermined intervals.
  • the injection holes 35 are formed by four first injection holes 35a formed on the circumference at 90 ° intervals, and 45 ° on the circumference with the first injection holes 3a. And four second injection holes 35b drilled out of phase with each other, and the first injection hole 35a has a smaller diameter than the second injection hole 35b. ing.
  • the one-way valve 7 has a flat pressure-receiving surface 74 at the upper end for receiving the pressure of the pressurized fuel, and the outer periphery following the pressure-receiving surface 74 is formed in the above-described hole 34.
  • a straight cylindrical surface 7 1 having a diameter corresponding to the straight cylindrical surface 3 40, and the straight cylindrical surface 7 1 has a conical surface 7 2 as a surface contact portion which is tapered and inclined at an angle corresponding to the conical surface 3 4 1 from the lower end of the conical surface 3 4 1, and the lower end of the conical surface 7 2 is the bottom of the hole 3 4 It has a horizontal or arc-shaped end face so as not to contact the wall.
  • the one-way valve 7 is provided with a fuel passage 73 having one end opening to the conical surface 72 and the other end opening to the pressure receiving surface 74.
  • the fuel passage 73 is composed of a hole, and a plurality (four in this example) of lateral holes 73 that can communicate with the injection holes 35a and 35b of the surrounding wall surrounding the hole. 0 is radially drilled on the circumference at predetermined intervals (in this example, at intervals of 90 °), and a plurality of vertical holes 731, which penetrate from the pressure receiving surface 74 to the horizontal hole 7330, are drilled. ing.
  • the fuel passage 73 must have a diameter equal to or greater than the maximum diameter of the injection hole 35.
  • the cross-sectional shape perpendicular to the axis of the fuel passage 73 may be not only a circle but also a polygon or the like as in the above-described injection hole.
  • FIGS. 20-A and 20-B show other examples of the one-way valve 7 of the second embodiment.
  • the fuel passage 73 is formed of a hole, and one end thereof is open to the conical surface 72.
  • the fuel passage 73 intersects the axis of the one-way valve 7. It is composed of a plurality of (in this example, four) oblique holes 732, each of which is open at predetermined intervals (in this example, every 90 °) on the circumference. The other end (upper end) of the hole 732 opens into the pressure receiving surface 74.
  • the injection hole 35 has the same axis as the inclined hole 732.
  • the fuel passage 73 must have a diameter equal to or greater than the maximum diameter of the injection hole 35.
  • FIG. 21 shows another example of the mouth valve 7 of the second embodiment. This example corresponds to FIGS. 6 and 8 of the first embodiment.
  • the fuel passage 73 is not a hole but a plurality of (four in this example) grooves 733.
  • each groove 733 is spaced from the straight cylindrical surface 71 at regular intervals on the circumference (in this example, every 90 °) such that the lower end reaches a position slightly ahead of the injection hole 35. It is formed over a conical surface 72.
  • the width of each groove 733 needs to be equal to or greater than the maximum diameter of the injection hole 35.
  • the injection hole 35 is composed of four first injection holes 35a and four second injection holes 35b, and the fuel passage 73 of the one-way valve 7 It is individual, but may be more or less.
  • three first injection holes 35 a and three second injection holes 35 b may be provided, and three fuel passages 73 of the one-way valve 7 may be provided.
  • the injection hole 35 may have three types, large, medium, and small, instead of two types.
  • the holes 34 and the one-way valve 7 may have the same shapes as those shown in the first embodiment. That is, the conical surface 3 41 is immediately formed from the seat surface 3 0 3 without providing the straight cylindrical surface 3 4 0 in the hole 3 4, and the rotary valve 7 is also provided with the pressure receiving surface 7 4 A conical surface 72 may be formed immediately after.
  • the inclination angle of the conical surfaces 341, 72 of the hole 34 and the rotary valve 7 of the second embodiment is also generally selected from the range of 50 to 70 ° c. It is clear that the relationship between the holding torque and the rotation torque is the same as in the case of the first embodiment, and a description thereof will be omitted.
  • the rotary valve 7 is connected to the needle valve 4 and the fan valve as in the first embodiment.
  • a drive shaft system 8 penetrating through the justifying screw 102 and an actuator 9 attached to the drive head 2 rotate at a predetermined rotation angle.
  • the drive shaft system 8 also includes a shaft main body 8a, a joint pin 8b, and a joint 10 in the second embodiment.
  • the specific configuration may be the same as that of the first embodiment, but this embodiment has a slightly different configuration.
  • the first hole 45a is formed in the axial direction from the lower end of the needle valve to the middle position, and the second hole 45a, which is narrower than the end of the first hole 45a, is formed.
  • a hole 45b is formed, and a third hole 45c having the same diameter as the first hole 45a is formed from the end of the second hole 45b to the upper end of the bushing pad 101.
  • a fourth hole 45 d is formed in the adjusting screw 102 from the lower end to the upper end. The diameter of the fourth hole 45d is appropriately reduced at the upper end region to prevent blurring of the drive shaft.
  • the shaft body 8a has a length extending from the fourth hole 45d to the lower end region of the third hole 45c, and has a diameter smaller than that of the third hole 45. Since the joint pin 8b functions as a seal portion, the joint pin 8b has a large-diameter portion (face seal portion) 80 that is rotatably and precisely fitted into the first hole 45a. A small-diameter portion 81 that fits loosely into the second hole 45b is provided continuously from the end. Therefore, a step portion 82 for a flat head is formed at a boundary portion between the small diameter portion 81 and the large diameter portion 80, and the needle valve is brought into contact with the upper end surface of the first hole 45a to form a needle valve. 4 and move up and down together.
  • the upper end of the small diameter portion 81 and the lower end of the drive shaft body 8a are Oldham-shaped.
  • the joints are connected so that the rotational force is transmitted by joints 811 and 801 of a type that allows backlash in the axial direction.
  • the coupling 10 is connected to the large-diameter portion 80 of the joint pin 8b so as to allow relative sliding of the rotary valve 7 in the axial direction.
  • the coupling 10 is an Oldham force ring.
  • the coupling 10 has an outer diameter smaller than the diameter of the first hole 45a, and a protrusion 800 extending from the lower end of the large diameter portion of the joint pin 8b is formed in the upper half groove 10a.
  • the protruding piece 70 formed on the pressure receiving surface 74 of the mouthpiece valve 7 is fitted in the lower half groove 10b, which is 90 degrees out of phase with the groove 10a.
  • the coupling may have both upper and lower halves in the form of protrusions or grooves, in which case the coupling pin 8b and the one-way valve 7 have corresponding grooves or grooves. Protrusions are provided.
  • the actuator 9 uses a stepping motor or a servomotor, and its output shaft and the upper end of the shaft body 8a are directly connected or connected by a transmission element (for example, a gear or an eccentric pin) 90.
  • the timing when the rotary valve 7 is rotated by the actuator 9 is, as in the first embodiment, generally a period during which no axial force is applied to the drive shaft 8 by the engine cylinder pressure. Preferably, during the intake stroke or the exhaust stroke of the engine.
  • Such rotation timing control is the same as in the first embodiment. That is, as shown in FIG. 16, the actuator 9 is electrically connected to a controller 12 composed of a CPU or the like, and an engine or a fuel injection pump is connected to an input portion thereof. Input the signal from the rotation speed detection sensor (or rotation angle detection sensor) 120 and output a drive signal to the actuator 9 when it is determined that the engine is in the above stroke. Good. Then, a signal from a load detection sensor 122 such as a rack sensor of the fuel injection pump is input to the controller at the same time. A predetermined map formed in advance from data of the load and the number of rotations is input to the controller 12, and a predetermined drive amount (drive rotation angle) is given to the actuator by this map.
  • the first injection holes 35a are aligned with the fuel passage 73, and at high speeds and high loads, the second injection holes 35b are cut to the rotational positions aligned with the fuel passages 73.
  • a rotation angle detecting mechanism 11 may be provided on the drive shaft system 8, for example, the shaft body 8a.
  • the rotation angle detection mechanism 11 may be any encoder, collimator, potentiometer, or the like.
  • the drive shaft system 8 is not limited to the embodiments of the first embodiment and the second embodiment. That is, the drive shaft system 8 may be constituted by only the shaft main body 8a and the joint 10 without the joint pin 8b. In this case, the upper end of the joint 10 is engaged with the lower end of the shaft main body 8a so as to be relatively slidable in the axial direction. Next, the operation of the embodiment of the present invention will be described.
  • the pressurized fuel is sent from a fuel injection pump (not shown) to the pressurized fuel port 104 via a pipe, and is pushed into the oil reservoir 301 via the passage holes 105, 305. From there, go down the annular fuel passage 106.
  • This fuel pressure simultaneously acts on the pressure receiving surface 42 of the nozzle needle 4 located at the oil sump reservoir 301, and when the fuel pressure reaches a pressure exceeding the set force of the spring 103, the dollar valve 4 Is lifted, the seat surface 44 at the lower end of the needle valve is separated from the seat surface 303 of the nozzle body 3, and the valve is opened.
  • the state at this time is shown in FIG. 3, in which the pressurized fuel enters the hole 34 and flows into the fuel passage 73 of the one-way valve 7.
  • the needle valve 4 is pushed down by the biasing force of the spring 103 and is closed.
  • the needle valve 4 is closed, the fuel passages 73 of the rotary valve 7 are not aligned with the injection holes 35 passing through the wall of the hole 34, and the injection holes 35 are not connected to the fuel passages. Each is shielded by a conical surface between 73.
  • the drive signal is not sent from the controller 12 to the actuator 9, and the controller 12 is set in the holding mode.
  • the rotation speed (or rotation angle) and load information signals of the engine or the fuel injection pump are transmitted from the rotation speed detection sensor 120 and the load sensor 122 to the controller 12. , The rotation angles corresponding to these are calculated. Then, a drive amount signal corresponding thereto is sent to the actuator 9, the driving force of the actuator 9 is transmitted to the shaft body 8a, and the rotational torque is transmitted from the joint pin 8b and the joint 10 to the mouthpiece.
  • the rotary valve 7 is rotated to the required rotation angle, for example, clockwise.
  • the conical surface 7 2 does not make strong contact with the conical surface 3 4 1 of the hole 3 4 because no load is applied to the rotary valve 7 in the axial direction. Can be rotated to a corner.
  • the actual rotation angle position of the rear shaft body 8a is detected by the rotation angle detection mechanism 11.
  • the rotation angle detection signal is fed back to the controller 12 and the controller 12 determines whether there is an error with the set angle. If there is an error, the controller 12 transmits the rotation angle to the actuator 9.
  • a drive signal is sent to the motor, whereby the re-shaft main body 8a is minutely driven, and the position of the rotary valve 7 is corrected.
  • a holding signal is output from the controller 12 to the actuator 9, and the mouthpiece valve 7 is held at that position.
  • FIGS. 41A and 41B show a state in which the rotary valve 7 is rotated and the edge of the fuel passage 73 is located at a half position of the diameter of the injection hole 35, that is, the injection hole opening degree is reduced by half.
  • FIGS. 5A and 5B show a state in which the fuel valve 73 is further aligned with the injection hole 35 by further rotating the one-way valve 7, and the opening of the injection hole 35 is fully opened. I have.
  • the fuel injection pressure is applied to the pressure receiving surface 74 at the upper end of the rotary valve 7.
  • the rotary valve 7 is pressed down in the axial direction, and the outer conical surface ⁇ 2 comes into strong surface contact with the conical surface 3 4 1 of the hole 3 4 to form a surface seal, where the frictional force is generated.
  • the fixing force due to this friction is also the force that moves the rotary valve 7 in the rotation axis direction by the injection pressure applied to the injection hole 35. Surpass.
  • the rotary valve 7 rotated by a predetermined angle is firmly fixed at that position when the needle valve 4 is opened, that is, when fuel is injected.
  • the injection hole 35 of the hole 34 is shielded at the rotation angle given to the rotary valve 7, and the injection hole area can be arbitrarily changed in a stepless manner.
  • the fuel injection pressure increases as the injection hole area decreases, and the injection period becomes longer. This can be expected to promote atomization of the spray and increase the excess air ratio of the spray, thereby reducing NOx.
  • the fuel injection pressure is reduced as the injection hole area increases, shortening the injection period.
  • the required amount of spray can be uniformly dispersed and supplied at high load, and stable high-power combustion is performed.
  • the actuator 9 can be small and have a small torque, thereby avoiding an increase in the size of the re-injection nozzle and disposing it in the engine. And installation can be facilitated.
  • the position shift is detected by the rotation angle detection mechanism 11 after the injection in which the needle valve 4 is closed. Is detected again.
  • the position of the one-way valve 7 can be constantly detected and corrected, it is possible to reduce the variation of the spray for each spray.
  • the mouth one data Ribarubu holding torque T 2 and the relationship between the torque for rotating the mouth one data Ribarubu i.e. T 2 - and a small range by words it is possible to feel more alert changed only by a small torque to be given from the outside Li, the opening area of the even during fuel injection by rotating a rotor Ribarubu 7 nozzle hole 35 over the difference delta T between T 2, which This makes it possible to easily control the injection rate of the rebuilt rod and the like.
  • the fuel passage 73 of the rotary valve 7 is shown in FIGS.
  • the pressure receiving pressure is lower than when the groove bottom is parallel to the nozzle axis (second example) as shown in Figs. Since the area of the surface 74 can be increased, the holding torque of the rotary valve 7 can be relatively increased.
  • the control of the rotational position of the inlet valve 7, that is, the selection of the injection holes 35 is performed by transmitting a drive signal from the controller to the actuator 9 during the intake stroke or the exhaust stroke, Alternatively, the output shaft is driven to a required rotation angle in accordance with the rotation speed (or rotation angle) and load of the fuel injection pump, and the output shaft is transmitted to the shaft main body 8a.
  • the rotary valve 7 is rotated to the position shown in Fig. 18-A. 730) communicate with the first orifice 35a having a small diameter, and the second orifice 35b is shielded.
  • the mouthpiece valve 7 is rotated counterclockwise (or clockwise) from the state shown in Fig. 18-A as shown in Fig. 18-B.
  • the horizontal holes 730 of the fuel passage 73 communicate with the large-diameter second injection holes 35b, and the first injection holes 35a are shielded. Is done.
  • the fuel injection pressure is increased with a decrease in the injection hole area at a low load, and the injection period is lengthened. As a result, it is expected that the atomization of the re-spray will be promoted, the excess air ratio of the spray will increase, and NOX will be reduced.
  • the fuel injection pressure is reduced as the injection hole area increases, shortening the injection period. This ensures that the required amount of spray is supplied evenly distributed over the entire load at high load, and stable. High power combustion is performed.
  • the rotary valve 7 is not columnar or straight cylindrical, but has a conical surface 7 2 over a wide area, and the hole 3 4 has a conical surface 3 4 1 corresponding to the conical surface 7 2. ing.
  • An injection hole 3 ⁇ is provided on the conical surface 341, and an end of the fuel passage 73 is open on the conical surface 72. For this reason, at the time of the fuel injection described above, the fuel injection pressure acts on the pressure receiving surface 74, whereby the rotary valve 7 is firmly fixed by the frictional force due to the strong contact of the conical surfaces 341, 72 facing each other. It is held in that position.
  • the high-pressure fuel is injected only from the selected injection hole 35.
  • the fuel in Fig. 18- ⁇ , the fuel is injected only from the four small-diameter first injection holes 35a, and in Fig. 18-C, it is injected only from the four large-diameter second injection holes 35b. Therefore, it is possible to accurately form a spray in accordance with the selected orifice and to adjust the total area of the orifice substantially accurately. NOx, smoke and HC can be reduced and fuel efficiency can be improved
  • the opening of the selected injection holes can be adjusted to any size.
  • the large diameter portion 80 functions as a face seal portion. For this reason, it is possible to prevent a decrease in the injection pressure and a shortage of the injection amount during the injection due to the leakage of the fuel from the drive shaft system.
  • the fuel passage 73 of the one-way valve 7 is formed as a groove as shown in FIGS. 6 to 8 and FIG. 21, the fuel passage 73 is It has the advantage of easy processing and cost reduction.
  • the present invention can be used as a fuel injection nozzle for promoting combustion in an internal combustion engine represented by a diesel engine, improving output and fuel efficiency, and reducing combustion noise and NOx emissions.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

La présente invention concerne un ajutage d'injection de carburant pour moteur à combustion interne. L'ajutage de cet injecteur de carburant est pourvu à l'extrémité avant du corps d'ajutage d'un robinet rotatif faisant varier l'ouverture de l'ajutage par commande de l'angle de rotation du robinet. La paroi périphérique définissant l'ouverture de l'ajutage comporte une surface de régulation. Le robinet rotatif présente en son extrémité supérieure une face recevant la pression du carburant pressurisé, ainsi qu'une face conique dont l'angle correspond à l'angle de conicité de l'orifice au niveau sur sa circonférence extérieure. Plusieurs passages de carburant sont répartis régulièrement dans cette face conique dans une direction circonférentielle. Une pluralité de ces passages s'ouvre dans la face recevant la pression du carburant pressurisé au niveau d'une extrémité, chaque passage de carburant étant à l'état ouvert lorsque la face conique occupe, côté orifice, une position de correspondance de l'orifice d'ajutage. Grâce à cet agencement, la pression d'injection de carburant crée, entre le robinet rotatif et le corps de l'ajutage, un couple de friction supérieur à un couple du robinet rotatif tel que le robinet rotatif reste en état stationnaire dans n'importe quelle position, uniquement sous l'effet de la pression d'injection du carburant.
PCT/JP1996/001536 1995-06-09 1996-06-06 Ajutage d'injection de carburant a ouverture variable WO1996041948A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
GB9723123A GB2316130B (en) 1995-06-09 1996-06-06 Variable nozzle hole type fuel injection nozzle
US08/945,660 US5947389A (en) 1996-06-06 1996-06-06 Variable nozzle hole type fuel injection nozzle
DE19681434T DE19681434T1 (de) 1995-06-09 1996-06-06 Kraftstoffeinspritzdüse vom Typ mit variabler Düsenöffnung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP16710295 1995-06-09
JP7/167102 1995-06-09

Publications (1)

Publication Number Publication Date
WO1996041948A1 true WO1996041948A1 (fr) 1996-12-27

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KR (1) KR19990022026A (fr)
DE (1) DE19681434T1 (fr)
GB (1) GB2316130B (fr)
WO (1) WO1996041948A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0853195A1 (fr) * 1997-01-14 1998-07-15 Zexel Corporation Injecteur de combustible
WO1999004159A1 (fr) * 1997-07-18 1999-01-28 Zexel Corporation Injecteur de carburant
WO1999005413A1 (fr) * 1997-07-25 1999-02-04 Zexel Corporation Buse de projection de carburant
WO2000022295A1 (fr) * 1998-10-09 2000-04-20 Jun Arimoto Valve d'injection de carburant pour moteur diesel
US6776358B2 (en) 1998-10-09 2004-08-17 Jun Arimoto Fuel injection nozzle for a diesel engine
US7722689B2 (en) * 2003-10-22 2010-05-25 Airbus Deutschland Gmbh Device for supplying fuel to a burner in a fuel cell system comprising a reformer
JP2013534295A (ja) * 2010-08-16 2013-09-02 アカーテース パワー，インク． 対向ピストンエンジン用の燃料噴射噴霧パターン

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6206304B1 (en) * 1999-01-13 2001-03-27 Toyota Jidosha Kabushiki Kaisha Injector
JP5218583B2 (ja) 2011-03-09 2013-06-26 株式会社デンソー インジェクタ
CN104100428B (zh) * 2013-04-15 2017-01-25 浙江福爱电子有限公司 一种半球阀喷嘴及其喷射单元

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JPS55117066A (en) * 1979-03-01 1980-09-09 Sulzer Ag Injection valve for internal combustion engine with reciprocating piston
JPS6022071A (ja) * 1983-07-16 1985-02-04 Mitsubishi Heavy Ind Ltd 燃料噴射弁
JPS61286577A (ja) * 1985-06-14 1986-12-17 Tech Res Assoc Highly Reliab Marine Propul Plant 燃料噴射弁
JPS6487869A (en) * 1987-09-29 1989-03-31 Mitsubishi Motors Corp Fuel injector
JPH02114768U (fr) * 1989-02-28 1990-09-13
JPH0476266A (ja) * 1990-07-18 1992-03-11 Isuzu Motors Ltd 燃料噴射ノズル
JPH0722064U (ja) * 1993-09-17 1995-04-21 株式会社ゼクセル 燃料噴射ノズル
JPH0730366U (ja) * 1993-11-04 1995-06-06 株式会社ゼクセル 燃料噴射ノズル

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55117066A (en) * 1979-03-01 1980-09-09 Sulzer Ag Injection valve for internal combustion engine with reciprocating piston
JPS6022071A (ja) * 1983-07-16 1985-02-04 Mitsubishi Heavy Ind Ltd 燃料噴射弁
JPS61286577A (ja) * 1985-06-14 1986-12-17 Tech Res Assoc Highly Reliab Marine Propul Plant 燃料噴射弁
JPS6487869A (en) * 1987-09-29 1989-03-31 Mitsubishi Motors Corp Fuel injector
JPH02114768U (fr) * 1989-02-28 1990-09-13
JPH0476266A (ja) * 1990-07-18 1992-03-11 Isuzu Motors Ltd 燃料噴射ノズル
JPH0722064U (ja) * 1993-09-17 1995-04-21 株式会社ゼクセル 燃料噴射ノズル
JPH0730366U (ja) * 1993-11-04 1995-06-06 株式会社ゼクセル 燃料噴射ノズル

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0853195A1 (fr) * 1997-01-14 1998-07-15 Zexel Corporation Injecteur de combustible
WO1999004159A1 (fr) * 1997-07-18 1999-01-28 Zexel Corporation Injecteur de carburant
WO1999005413A1 (fr) * 1997-07-25 1999-02-04 Zexel Corporation Buse de projection de carburant
WO2000022295A1 (fr) * 1998-10-09 2000-04-20 Jun Arimoto Valve d'injection de carburant pour moteur diesel
US6776358B2 (en) 1998-10-09 2004-08-17 Jun Arimoto Fuel injection nozzle for a diesel engine
US7722689B2 (en) * 2003-10-22 2010-05-25 Airbus Deutschland Gmbh Device for supplying fuel to a burner in a fuel cell system comprising a reformer
JP2013534295A (ja) * 2010-08-16 2013-09-02 アカーテース パワー，インク． 対向ピストンエンジン用の燃料噴射噴霧パターン

Also Published As

Publication number Publication date
GB9723123D0 (en) 1998-01-07
KR19990022026A (ko) 1999-03-25
DE19681434T1 (de) 1998-05-07
GB2316130B (en) 1999-05-05
GB2316130A (en) 1998-02-18

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