WO2005119047A1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
WO2005119047A1
WO2005119047A1 PCT/JP2005/010532 JP2005010532W WO2005119047A1 WO 2005119047 A1 WO2005119047 A1 WO 2005119047A1 JP 2005010532 W JP2005010532 W JP 2005010532W WO 2005119047 A1 WO2005119047 A1 WO 2005119047A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel
pressure
valve body
orifice
fuel injection
Prior art date
Application number
PCT/JP2005/010532
Other languages
French (fr)
Japanese (ja)
Inventor
Natsuki Hosoya
Kenichi Kubo
Kiyoshi Matsuzaki
Original Assignee
Bosch 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 Bosch Corporation filed Critical Bosch Corporation
Priority to EP05748486A priority Critical patent/EP1757799A1/en
Publication of WO2005119047A1 publication Critical patent/WO2005119047A1/en

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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
    • F02M55/004—Joints; Sealings
    • F02M55/005—Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
    • 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
    • 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
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston
    • 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
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0043—Two-way valves

Definitions

  • the present invention relates to a fuel injection valve.
  • FIG. 4 is a diagram for explaining a configuration of a conventional fuel injection valve.
  • the fuel injection valve 1 is used for injecting and supplying high-pressure fuel stored in the common rail 12 to the cylinder of a diesel internal combustion engine (not shown).
  • the fuel F in the fuel tank 10 is used for the fuel pump 11.
  • the pressurized fuel is stored in the common rail 12 as high-pressure fuel.
  • the fuel injection valve 1 has an injector housing 2, a nozzle body 3, a nozzle needle 4, a valve piston 5, a valve body 6, a back pressure control unit 7, and a connecting rod 8.
  • a nozzle body 3 is attached to a tip of the injector housing 2 by a nozzle nut 9, and a connecting rod 8 is attached to an upper portion thereof.
  • a fuel passage 13 extending from the connecting rod 8 through the injector housing 2 to the nozzle body 3 is formed, and a fuel storage chamber 14 is formed facing the pressure receiving portion 4A of the nozzle needle 4. ing. Further, in the injector housing 2, a fuel recirculation path 15 is formed near the connecting rod 8, which branches off from the fuel path 13 and communicates with the low fuel pressure section through the back pressure control section 7. In the nozzle body 3, the tip of the nozzle needle 4 is seated on the seat 17 connected to the injection hole 16 so that the injection hole 16 is closed and the nozzle needle 4 is lifted from the seat 17. Thus, the injection hole 16 is opened, thereby enabling the start and stop of fuel injection.
  • a nozzle spring 18 for urging the nozzle 21 in the direction of seating the seat 17 on the nozzle 21 is provided above the nozzle 21.
  • the pin 5 is slidably inserted into the sliding hole 2A of the injector housing 2 and the sliding hole 6A of the valve body 6.
  • FIG. 5 is an enlarged sectional view of a main part of the valve body 6 and the back pressure control unit 7.
  • a control pressure chamber 19 is formed in the valve body 6, and a distal end portion ′ of the valve piston 5 faces the control pressure chamber 19 from below.
  • the control pressure chamber 19 communicates with an introduction orifice 20 formed in the valve body 6.
  • the introduction side orifice 20 is communicated with the fuel passage 13 via a pressure introduction chamber 21 formed between the valve body 6 and the injector housing 2, and the introduction pressure from the common rail 12 is provided. Is supplied to the control pressure chamber 19.
  • a sealing member 22 made of a resin material, rubber material, copper material, or other soft material is provided, and the pressure introduction chamber 21 on the high pressure side and the fuel low pressure side are provided. The gap 28 between the injector housing 2 and the valve body 6 is blocked.
  • the control pressure chamber 19 is also connected to an opening / closing orifice 23, and the opening / closing orifice 23 can be opened and closed by a valve ball 24 of the back pressure control section 7.
  • the pressure receiving area of the top 5A of the valve piston 5 in the control pressure chamber 19 is larger than the pressure receiving area of the pressure receiving section 4A of the nozzle needle 4 (FIG. 4).
  • the back pressure control unit includes a magnet 25, an armature 27, a valve ball 24 integral with the armature 27, and a control pressure chamber 19. .
  • the magnet 25 By supplying a drive signal to the magnet 25, the magnet 25 sucks the armature 27 against the urging force of the valve spring 26 and moves the valve ball 24 from the opening / closing orifice 23.
  • the control is released, and the pressure in the control pressure chamber 19 can be released to the fuel recirculation path 15 side.
  • valve ball 24 by operating the valve ball 24 as described above, the pressure in the control pressure chamber 19 is controlled, and by controlling the back pressure of the nozzle needle 4 via the valve piston 5, the seat portion of the nozzle needle 4 is controlled.
  • the seat to 17 and the lift from the seat section 17 can be controlled.
  • the high-pressure fuel from the common rail 12 is connected to the connection rail. It acts on the pressure receiving portion 4A of the nozzle 21 in the fuel reservoir 14 from the groove 8 via the fuel passage 13 and the control pressure via the pressure introduction chamber 21 and the introduction orifice 20. It also acts on the top 5 A of valve piston 5 in chamber 19.
  • the nozzle needle 4 receives the back pressure of the control pressure chamber 19 via the valve piston 5 and the nozzle spring 18 Along with the urging force, the nozzle body 3 is seated on the seat 17 and the injection hole 16 is closed.
  • the armature 27 is sucked by supplying a drive signal to the magnet 25 at a predetermined timing, and when the valve ball 24 opens the opening / closing orifice 23, the high pressure in the control pressure chamber 19 increases the opening / closing orifice. Since the fuel is returned to the fuel tank 10 through the fuel recirculation path 15 through 23, the high pressure acting on the top 5A of the valve piston 5 in the control pressure chamber 19 is released, and the nozzle needle 4 is The high pressure acting on the pressure receiving portion 4A lifts the sheet 17 from the sheet portion 17 against the urging force of the nozzle spring 18 and opens the injection hole 16 to inject fuel.
  • valve ball 24 closes the opening / closing orifice 23 by demagnetizing the magnet 25
  • the pressure in the control pressure chamber 19 moves the nozzle needle 4 via the valve piston 5 to its seat position (sheet position). Seat to section 17), close injection hole 16 and terminate fuel injection.
  • the pressure introduction chamber 21 is located at the inlet to the control pressure chamber 19 that controls the fuel injection amount and the injection pressure from the injection hole 16, the fuel pressure in the pressure introduction chamber 21 is equal to the injection pressure. Therefore, a high pressure equivalent to the injection pressure is applied to the seal member 22.
  • valve piston 5 As shown in FIG. 5, a clearance is required between the valve piston 5 and the valve body 6 to allow the valve piston 5 that moves integrally with the nozzle needle 4 to slide in the axial direction. If the valve body 6 is press-fitted into the injector housing 2, the valve body 6 may be slightly deformed inward and hinder the sliding of the valve piston 5. A gap 28 is also provided between 2 and the valve body 6 as a slight clearance. Because the seal structure of the conventional fuel injection valve is as described above, the seal member is pushed toward the gap (low-pressure part) between the engine housing and the valve body by the high pressure in the pressure introduction chamber. It may be deformed and its sealing function may be reduced.
  • JP-A-2003-28021 discloses that a metal back-up ring is installed on the low-pressure side (gap side) of the seal member so that the seal member has a low-pressure side.
  • a configuration for preventing extrusion to the outside There is disclosed a configuration for preventing extrusion to the outside.
  • this configuration there is a tendency that a failure occurs due to collapse or the like caused by a high pressure load in the pressure release passage of the back coupling. If such a rise of the seal ring occurs, the sealing performance may be degraded.
  • control pressure chamber is formed in the small diameter portion below the valve body, so that the valve body is easily deformed, which hinders the smoothness of the sliding movement of the valve piston.
  • An object of the present invention is to provide a fuel injection valve that can solve the above-described problems in the related art. Disclosure of the invention
  • a feature of the present invention for solving the above problem is that a valve body in which a valve piston is slidably inserted is provided in an injector housing, and a valve body in which one end of the valve piston faces one end.
  • a fuel injection valve configured to send high-pressure fuel from the injector housing into the control pressure chamber of the fuel injection valve, wherein an annular step is provided in the injector X.
  • a corresponding annular projection is provided, the annular projection is seated on the annular step portion via a seal plate with an orifice, and high-pressure fuel enters the control pressure chamber from the injector housing side via the orifice. The point is to send.
  • FIG. 1 is a partially sectional view showing an embodiment of a fuel injection valve according to the present invention.
  • FIG. 2 is an enlarged view of a main part of FIG.
  • FIG. 3 is an enlarged plan view of the seal plate of FIG.
  • FIG. 4 is a view for explaining the configuration of a conventional fuel injection valve.
  • FIG. 5 is an enlarged sectional view showing a main part of the valve body and the back pressure control unit shown in FIG. 4 in an enlarged manner.
  • FIG. 1 is a view showing one embodiment of a fuel injection valve according to the present invention
  • FIG. 2 is an enlarged view of a main part of FIG.
  • the fuel injection valve 30 includes an injector housing 32, a nozzle body 33, a nozzle needle 34, a valve piston 35, a valve body 36, and a back. It has a pressure control section 37 and an inlet connector 38.
  • a nozzle body 33 is attached to a tip end of the injector housing 32 by a nozzle nut 39, and an inlet connector 38 is attached to an upper portion thereof.
  • the fuel injection valve 30 also supplies high-pressure fuel accumulated in the common rail into the cylinder of a diesel internal combustion engine (not shown). It is used for
  • a fuel passage 38 A extending from the inlet connector 38 to the nozzle body 33 is formed in the injector housing 32, and faces the pressure receiving portion 34 A of the nozzle needle 34.
  • a fuel reservoir 33A is formed. Since the configuration of this nozzle portion is a known configuration similar to that shown in FIG. 4, detailed description thereof will be omitted.
  • the valve body 36 is a generally cylindrical member having a large diameter portion 36 1 and a small diameter portion 36 2.
  • the valve body 36 has a valve body storage chamber 3 in the injector housing 32. In 21, the valve body 36 is coaxial with the injector housing 32. It is housed so.
  • the valve body 36 has a sliding hole 3 63 opening on the small-diameter portion 36 2 side, and the rear end 3 51 of the valve piston 35 is oiled in the sliding hole 36 3. It is inserted so as to be slidable in the axial direction while maintaining a tight state.
  • the sliding hole 3 6 3 extends into the large diameter portion 3 6 1, and one end of the valve screw 3 5 is inserted into the large diameter portion 3 6 1 opposite to the open end of the sliding hole 3 6 3.
  • a control pressure chamber 3 6 4 is formed.
  • the control pressure chamber 364 also communicates with an opening / closing orifice 365, and the opening / closing orifice 365 can be opened and closed by a valve ball 371 of the back pressure control section 37. .
  • the pressure receiving area of the top 35 A of the valve piston 35 in the control pressure chamber 365 is larger than the pressure receiving area of the pressure receiving section 34 A of the nozzle needle 34 (FIG. 1).
  • the back pressure control unit 37 includes a magnet 372, an armature 373, and a valve ball 371 integrated with the armature 373, and supplies a drive signal to the magnet 372.
  • the magnet 372 sucks the armature 373 against the urging force of the valve spring 374, and lifts the valve ball 371 from the opening / closing orifice 365 to control the control chamber.
  • the pressure of 364 can be released to the low-pressure side of the fuel via a fuel recirculation path (not shown). Therefore, by operating the valve ball 371, as described above, the pressure of the control pressure chamber 3664 is controlled, and by controlling the back pressure of the nozzle 21-4 via the valve piston 35, The lift of the nozzle needle 34 can be controlled.
  • the valve body housing chamber 3 2 1 for housing the valve body 36 is a space having a size and shape corresponding to the valve body 36.
  • the annular projection 3 61 A of the large diameter portion 36 1 is seated on the annular step 3 21 A via the seal plate 50 so that the vane rep body 36 is attached to the valve body storage chamber 3 2. Housed in one.
  • the valve body 36 housed in the valve body housing chamber 3 21 as described above is The sealing nut 50 is pushed into the valve body chamber 31 by the tightening nut 40, so that the seal plate 50 has an upper surface 321Aa of the annular step 321A and a lower surface of the annular protrusion 361A. It is in close contact with 36 1 A a, and is in a state where the oil-tight state between the upper surface 3 21 A a and the lower surface 36 1 A a can be kept good.
  • the seal plate 50 is an annular member having an orifice 501, and is here made of a chromium-containing iron-based metal material. Further, in order to stabilize the sealing performance, the seal plate 50 is counterbored on the upper and lower surfaces of the plate, leaving the periphery of the orifice 501 and a part of the inner and outer peripheral portions of the plate. Reference numerals 502 and 503 indicate positioning holes, and by using these holes 502 and 503, the orifice 501 communicates with the fuel passage 38A. In this manner, the seal plate 50 can be easily arranged between the injector housing 32 and the valve body 36.
  • a high-pressure fuel supply chamber 41 is formed in the annular step portion 3 21 A in the injector housing 32 so as to face the orifice 501.
  • the high-pressure fuel supplied from the inlet connector 38 is guided to the high-pressure fuel supply chamber 41 through the fuel passage 38A.
  • one end communicates with the control pressure chamber 364 in the large diameter portion 361 of the valve body, and the other end faces the orifice 501 on the lower surface 361 Aa.
  • the high-pressure fuel sent from the fuel passage 38 A enters the passage 42 via the orifice 501 and is sent to the control pressure chamber 364.
  • the performance can be easily adjusted. .
  • the seal plate 50 is in close contact with the upper surface 3 2 1 A a of the annular step 3 2 1 A and the lower surface 3 6 1 A a of the annular protrusion 3 6 1 A, and the upper surface 3 2 1 A a and the lower surface 3 6 1 A Since the oil-tight state between the a and the lower surface is maintained in a good condition, the high-pressure fuel in the high-pressure fuel supply chamber 41 is supplied to the valve body 36 and the injector housing 3. It is sent into the control pressure chamber 364 without leaking between it and 2.
  • control pressure chamber 3 6 4 is formed in the large diameter portion 3 6 1 of the valve body 36, the control pressure chamber 3 6 Even when the high-pressure fuel is filled in 4, the large thickness of the large-diameter portion 361 reduces deformation to a small extent. As a result, the deformation of the entire valve body 36 can be reduced, and the valve piston 35 can be slid smoothly in the sliding hole 365.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

A fuel injection valve (30) constructed such that a valve body (36), in which a valve piston (35) is slidably inserted, is provided in an injector housing (32) and that a high-pressure fuel is sent from the injector housing (32) into a control pressure chamber (364) in the valve body (36) in which one end of the valve piston (35) is exposed. An annular step section (321A) is provided in the injector housing (32), and an annular projection section (361A) corresponding to the annular step section (321A) is provided on the valve body (36). The annular projection section (361A) is seated on the annular step section (321A) with a seal plate (50), having an orifice (501), in between. A high-pressure fuel is sent from the injector housing (32) side through the orifice (501) into a control pressure chamber (364). Leakage of the high-pressure fuel between the injector housing (32) and the valve body (36) can be reliably prevented.

Description

明細書 燃料噴射弁 技術分野  Description Fuel injector Technical field
本発明は燃料噴射弁に関するものである。 背景技術  The present invention relates to a fuel injection valve. Background art
第 4図は、 従来の燃料噴射弁の構成を説明するための図である。 燃料噴射弁 1 は、 コモンレール 1 2内に蓄積されている高圧燃料を図示しないディーゼル内燃 機関の気筒内に噴射供給するために用いられるもので、 燃料タンク 1 0内の燃料 Fは燃料ポンプ 1 1によって加圧され、 加圧された燃料がコモンレール 1 2内に 高圧燃料として蓄積される。 燃料噴射弁 1は、 インジヱクタハウジング 2と、 ノ ズルボディ 3と、 ノズルニードル 4と、 バルブビストン 5と、 バルブボディ 6と 背圧制御部 7と、 コネクティ ングロッ ド 8とを有している。 インジヱクタハウジ ング 2の先端部にはノズルボディ 3がノズルナッ ト 9により取り付けられ、 その 上方部にコネクティ ングロッ ド 8が取り付けられている。  FIG. 4 is a diagram for explaining a configuration of a conventional fuel injection valve. The fuel injection valve 1 is used for injecting and supplying high-pressure fuel stored in the common rail 12 to the cylinder of a diesel internal combustion engine (not shown). The fuel F in the fuel tank 10 is used for the fuel pump 11. The pressurized fuel is stored in the common rail 12 as high-pressure fuel. The fuel injection valve 1 has an injector housing 2, a nozzle body 3, a nozzle needle 4, a valve piston 5, a valve body 6, a back pressure control unit 7, and a connecting rod 8. A nozzle body 3 is attached to a tip of the injector housing 2 by a nozzle nut 9, and a connecting rod 8 is attached to an upper portion thereof.
コネクティ ングロッ ド 8からインジヱクタハウジング 2を通って、 ノズルポデ ィ 3にまで延びる燃料通路 1 3が形成されており、 ノズルニードル 4の受圧部 4 Aに対向して燃料溜まり室 1 4が形成されている。 さらに、 インジヱクタハウジ ング 2には、 コネクティ ングロッ ド 8付近において燃料通路 1 3から分岐して背 圧制御部 7を通って燃料低圧部に連通する燃料還流路 1 5が形成されている。 ノズルボディ 3は、 噴射孔 1 6につながるシート部 1 7にノズルニードル 4の 先端部がシートすることにより噴射孔 1 6が閉鎖され、 ノズルニードル 4がシ一 ト部 1 7からリフ卜することにより噴射孔 1 6が開放される構成となっており、 これにより燃料の噴射開始、 停止が可能となっている。  A fuel passage 13 extending from the connecting rod 8 through the injector housing 2 to the nozzle body 3 is formed, and a fuel storage chamber 14 is formed facing the pressure receiving portion 4A of the nozzle needle 4. ing. Further, in the injector housing 2, a fuel recirculation path 15 is formed near the connecting rod 8, which branches off from the fuel path 13 and communicates with the low fuel pressure section through the back pressure control section 7. In the nozzle body 3, the tip of the nozzle needle 4 is seated on the seat 17 connected to the injection hole 16 so that the injection hole 16 is closed and the nozzle needle 4 is lifted from the seat 17. Thus, the injection hole 16 is opened, thereby enabling the start and stop of fuel injection.
ノズル二一ドル 4の上方部には、 ノズル二一ドル 4をシート部 1 7にシートす る方向に付勢するためのノズルスプリング 1 8が設けられており、 バルブビスト ン 5はィンジヱクタハウジング 2の摺動孔 2 A及びバルブボディ 6の摺動孔 6 A 内に摺動可能に挿入されている。 A nozzle spring 18 for urging the nozzle 21 in the direction of seating the seat 17 on the nozzle 21 is provided above the nozzle 21. The pin 5 is slidably inserted into the sliding hole 2A of the injector housing 2 and the sliding hole 6A of the valve body 6.
第 5図は、 バルブボディ 6及び背圧制御部 7の要部拡大断面図である。 バルブ ボディ 6には制御圧室 1 9が形成されており、 バルブビストン 5の先端部'を下方 側から制御圧室 1 9に臨ませている。  FIG. 5 is an enlarged sectional view of a main part of the valve body 6 and the back pressure control unit 7. A control pressure chamber 19 is formed in the valve body 6, and a distal end portion ′ of the valve piston 5 faces the control pressure chamber 19 from below.
制御圧室 1 9は、 バルブボディ 6に形成した導入側ォリフィ ス 2 0に連通して いる。 導入側ォリフィ ス 2 0は、 バルブボディ 6とインジヱクタハウジング 2と の間に形成された圧力導入室 2 1を介して燃料通路 1 3に連通されており、 コモ ンレール 1 2からの導入圧力が制御圧室 1 9に供給される構成となっている。 圧力導入室 2 1の下端部には、 樹脂材、 ゴム材あるいは銅材その他の軟質材に よるシール部材 2 2が設けられており、 高圧側となる圧力導入室 2 1と、 燃料低 圧側となるインジヱクタハウジング 2とバルブボディ 6との間の間隙 2 8とを遮 断している。  The control pressure chamber 19 communicates with an introduction orifice 20 formed in the valve body 6. The introduction side orifice 20 is communicated with the fuel passage 13 via a pressure introduction chamber 21 formed between the valve body 6 and the injector housing 2, and the introduction pressure from the common rail 12 is provided. Is supplied to the control pressure chamber 19. At the lower end of the pressure introduction chamber 21, a sealing member 22 made of a resin material, rubber material, copper material, or other soft material is provided, and the pressure introduction chamber 21 on the high pressure side and the fuel low pressure side are provided. The gap 28 between the injector housing 2 and the valve body 6 is blocked.
制御圧室 1 9は、 開閉用ォリフィ ス 2 3にも連通しており、 開閉用ォリフィ ス 2 3は背圧制御部 7のバルブボール 2 4によって開閉可能となっている。 なお、 制御圧室 1 9におけるバルブピストン 5の頂部 5 Aの受圧面積は、 ノズルニード ル 4の受圧部 4 A (第 4図） の受圧面積より大きく してある。  The control pressure chamber 19 is also connected to an opening / closing orifice 23, and the opening / closing orifice 23 can be opened and closed by a valve ball 24 of the back pressure control section 7. The pressure receiving area of the top 5A of the valve piston 5 in the control pressure chamber 19 is larger than the pressure receiving area of the pressure receiving section 4A of the nozzle needle 4 (FIG. 4).
第 4図に示すように、 背圧制御部了は、 マグネッ ト 2 5と、 ァーマチュア 2 7 と、 ァ一マチュア 2 7に一体のバルブボール 2 4と、 制御圧室 1 9とを備えてい る。 マグネッ ト 2 5へ駆動信号を供給することにより、 マグネッ ト 2 5はバルブ スプリング 2 6の付勢力に抗してァ一マチュア 2 7を吸引し、 バルブボール 2 4 を開閉用ォリフィ ス 2 3からリ フ トさせ、 制御圧室 1 9の圧力を燃料還流路 1 5 側に解放可能とする。  As shown in FIG. 4, the back pressure control unit includes a magnet 25, an armature 27, a valve ball 24 integral with the armature 27, and a control pressure chamber 19. . By supplying a drive signal to the magnet 25, the magnet 25 sucks the armature 27 against the urging force of the valve spring 26 and moves the valve ball 24 from the opening / closing orifice 23. The control is released, and the pressure in the control pressure chamber 19 can be released to the fuel recirculation path 15 side.
したがって、 バルブボール 2 4を上述の如く動作させることにより制御圧室 1 9の圧力を制御し、 バルブビストン 5を介してノズルニードル 4の背圧を制御す ることにより、 ノズルニードル 4のシート部 1 7へのシート及ぴシート部 1 7か らのリフ トを制御することができる。  Therefore, by operating the valve ball 24 as described above, the pressure in the control pressure chamber 19 is controlled, and by controlling the back pressure of the nozzle needle 4 via the valve piston 5, the seat portion of the nozzle needle 4 is controlled. The seat to 17 and the lift from the seat section 17 can be controlled.
燃料噴射弁 1 においては、 コモンレール 1 2からの高圧燃料は、 コネクティ ン グロッ ド 8から燃料通路 1 3を介して燃料溜まり室 1 4内のノズル二一ドル 4の 受圧部 4 Aに作用するとともに、 圧力導入室 2 1及び導入側オリフィス 2 0を介 して制御圧室 1 9内のバルブビストン 5の頂部 5 Aにも作用する。 In the fuel injection valve 1, the high-pressure fuel from the common rail 12 is connected to the connection rail. It acts on the pressure receiving portion 4A of the nozzle 21 in the fuel reservoir 14 from the groove 8 via the fuel passage 13 and the control pressure via the pressure introduction chamber 21 and the introduction orifice 20. It also acts on the top 5 A of valve piston 5 in chamber 19.
したがって、 バルブボール 2 4によって制御圧室 1 9が燃料低圧側と遮断され ていると、 ノズルニードル 4は、 バルブピストン 5を介して制御圧室 1 9の背圧 を受け、 ノズルスプリング 1 8の付勢力と併せて、 ノズルボディ 3のシート部 1 7にシートし、 噴射孔 1 6を閉鎖している。  Therefore, when the control pressure chamber 19 is isolated from the low fuel pressure side by the valve ball 24, the nozzle needle 4 receives the back pressure of the control pressure chamber 19 via the valve piston 5 and the nozzle spring 18 Along with the urging force, the nozzle body 3 is seated on the seat 17 and the injection hole 16 is closed.
マグネッ ト 2 5に所定タイミングで駆動信号を供給することによりァ一マチュ ァ 2 7を吸引し、 バルブボール 2 4が開閉用ォリフィス 2 3を開放すると、 制御 圧室 1 9の高圧が開閉用オリフィス 2 3を介し燃料還流路 1 5を通って燃料タン ク 1 0に還流するため、 制御圧室 1 9におけるバルブピストン 5の頂部 5 Aに作 用していた高圧が解放され、 ノズルニードル 4は受圧部 4 Aに作用している高圧 によりノズルスプリング 1 8の付勢力に抗してシ一ト部 1 7からリフトし、 噴射 孔 1 6を開放して燃料が噴射される。  The armature 27 is sucked by supplying a drive signal to the magnet 25 at a predetermined timing, and when the valve ball 24 opens the opening / closing orifice 23, the high pressure in the control pressure chamber 19 increases the opening / closing orifice. Since the fuel is returned to the fuel tank 10 through the fuel recirculation path 15 through 23, the high pressure acting on the top 5A of the valve piston 5 in the control pressure chamber 19 is released, and the nozzle needle 4 is The high pressure acting on the pressure receiving portion 4A lifts the sheet 17 from the sheet portion 17 against the urging force of the nozzle spring 18 and opens the injection hole 16 to inject fuel.
マグネッ ト 2 5を消磁することによりバルブボール 2 4が開閉用オリフィス 2 3を閉鎖すると、 制御圧室 1 9内の圧力がバルブピス トン 5を介してノズルニー ドル 4をそのシ一 ト位置 （シー ト部 1 7 ) にシー トさせ、 噴射孔 1 6を閉鎖し、 燃料噴射を終了させる。  When the valve ball 24 closes the opening / closing orifice 23 by demagnetizing the magnet 25, the pressure in the control pressure chamber 19 moves the nozzle needle 4 via the valve piston 5 to its seat position (sheet position). Seat to section 17), close injection hole 16 and terminate fuel injection.
圧力導入室 2 1は噴射孔 1 6からの燃料噴射量及び噴射圧を制御する制御圧室 1 9への入口部に位置することになるため、 圧力導入室 2 1における燃料圧力は 噴射圧と同等であり、 シール部材 2 2には噴射圧力と同等の高圧力がかかること になる。  Since the pressure introduction chamber 21 is located at the inlet to the control pressure chamber 19 that controls the fuel injection amount and the injection pressure from the injection hole 16, the fuel pressure in the pressure introduction chamber 21 is equal to the injection pressure. Therefore, a high pressure equivalent to the injection pressure is applied to the seal member 22.
第 5図に示すように、 バルブピストン 5とバルブボディ 6との間には、 ノズル ニードル 4と一体運動をするバルブビストン 5の軸方向の摺動を許容するクリァ ランスが必要である。 このバルブボディ 6をインジヱクタハウジング 2内に圧入 する構造を採用すると、 バルブボディ 6がわずかに内方に変形してバルブピスト ン 5の摺動を阻害する虞があるため、 ィンジヱクタハウジング 2とバルブボディ 6との間にもわずかなクリァランスとして間隙 2 8が設けられている。 従来の燃料噴射弁のシール構造は以上のようになっているので、 シール部材が、 圧力導入室における高圧力により、 ィンジ工クタハウジングとバルブボディとの 間の間隙 （低圧部） に向けて押され、 変形し、 そのシール機能が低下する可能性 がある。 As shown in FIG. 5, a clearance is required between the valve piston 5 and the valve body 6 to allow the valve piston 5 that moves integrally with the nozzle needle 4 to slide in the axial direction. If the valve body 6 is press-fitted into the injector housing 2, the valve body 6 may be slightly deformed inward and hinder the sliding of the valve piston 5. A gap 28 is also provided between 2 and the valve body 6 as a slight clearance. Because the seal structure of the conventional fuel injection valve is as described above, the seal member is pushed toward the gap (low-pressure part) between the engine housing and the valve body by the high pressure in the pressure introduction chamber. It may be deformed and its sealing function may be reduced.
この問題を回避するため、 特開 2 0 0 3— 2 8 0 2 1号公報には、 シール部材 の低圧側 （隙間側） に金属製バックアツプリングを設置することで、 シール部材 の低圧側への押し出しを防止するようにした構成が開示されている。 しかし、 こ の構成によると、 バックアツプリングの圧力逃がし流路の高圧負荷によるつぶれ 等により不具合が発生する傾向を有する。 このようなシールリングの浮き上がり が生じるとシール性能が低下する可能性がある。  In order to avoid this problem, JP-A-2003-28021 discloses that a metal back-up ring is installed on the low-pressure side (gap side) of the seal member so that the seal member has a low-pressure side. There is disclosed a configuration for preventing extrusion to the outside. However, according to this configuration, there is a tendency that a failure occurs due to collapse or the like caused by a high pressure load in the pressure release passage of the back coupling. If such a rise of the seal ring occurs, the sealing performance may be degraded.
また、 第 5図から判るように、 制御圧室がバルブボディの下方の細径部分に形 成されているため、 バルブボディに変形が生じやすく、 バルブピストンの摺動運 動の円滑性に支障を来たす虞があるという問題点を有している。  In addition, as can be seen from Fig. 5, the control pressure chamber is formed in the small diameter portion below the valve body, so that the valve body is easily deformed, which hinders the smoothness of the sliding movement of the valve piston. There is a problem in that the
本発明の目的は、 従来技術における上述の問題点を解決することができる、 燃 料噴射弁を提供することにある。 発明の開示  An object of the present invention is to provide a fuel injection valve that can solve the above-described problems in the related art. Disclosure of the invention
上記課題を解決するための本発明の特徴は、 バルブビストンを摺動可能に挿入 したバルブボディがィンジヱクタハウジング内に設けられて成り、 前記バルブピ ストンの一端を臨ませているバルブボディ内の制御圧室内に高圧燃料を前記ィン ジヱクタハウジングより送るように構成された燃料噴射弁において、 前記インジ X.クタハウジング内に環状段部を設けると共に前記バルブボディに前記環状段部 に対応した環状突部を設け、 該環状突部をォリフィス付のシールプレートを介し て前記環状段部に着座せしめ、 前記オリフィスを介して前記ィンジヱクタハウジ ング側から前記制御圧室内に高圧燃料を送るようにした点にある。  A feature of the present invention for solving the above problem is that a valve body in which a valve piston is slidably inserted is provided in an injector housing, and a valve body in which one end of the valve piston faces one end. A fuel injection valve configured to send high-pressure fuel from the injector housing into the control pressure chamber of the fuel injection valve, wherein an annular step is provided in the injector X. A corresponding annular projection is provided, the annular projection is seated on the annular step portion via a seal plate with an orifice, and high-pressure fuel enters the control pressure chamber from the injector housing side via the orifice. The point is to send.
本発明によれば、 高圧燃料がシールプレートのオリフィスを介してインジェク タハウジングからバルブボディの制御圧室内に送られる構成であるから、 高圧燃 料がインジヱクタハウジングとバルブボディとの隙間に漏出されるのがシールプ レー卜によって有効に防止される。 図面の簡単な説明 According to the present invention, since the high-pressure fuel is sent from the injector housing to the control pressure chamber of the valve body through the orifice of the seal plate, the high-pressure fuel leaks into the gap between the injector housing and the valve body. What is sealed Rate is effectively prevented. Brief Description of Drawings
第 1図は本発明による燃料噴射弁の一実施例を一部断面して示す図である。 第 2図は第 1図の要部拡大図である。  FIG. 1 is a partially sectional view showing an embodiment of a fuel injection valve according to the present invention. FIG. 2 is an enlarged view of a main part of FIG.
第 3図は第 1図のシールプレートの拡大平面図である。  FIG. 3 is an enlarged plan view of the seal plate of FIG.
第 4図は従来の燃料噴射弁の構成を説明するための図である。  FIG. 4 is a view for explaining the configuration of a conventional fuel injection valve.
第 5図は第 4図のバルブボディ及び背圧制御部を拡大して示す要部拡大断面図 める。 発明を実施するための最良の形態  FIG. 5 is an enlarged sectional view showing a main part of the valve body and the back pressure control unit shown in FIG. 4 in an enlarged manner. BEST MODE FOR CARRYING OUT THE INVENTION
本発明をより詳細に説述するために、 添付の図面に従ってこれを説明する。 第 1図は、 本発明による燃料噴射弁の一実施例を示す図、 第 2図は第 1図の要 部拡大図である。 第 1図及び第 2図を参照すると、 燃料噴射弁 3 0は、 インジ クタハウジング 3 2と、 ノズルボディ 3 3と、 ノズルニードル 3 4と、 バルブピ ストン 3 5と、 バルブボディ 3 6と、 背圧制御部 3 7と、 インレッ トコネクタ 3 8とを有している。 インジェクタハウジング 3 2の先端部にはノズルボディ 3 3 がノズルナツ ト 3 9により取り付けられ、 その上方部にインレツ トコネクタ 3 8 が取り付けられている。 燃料噴射弁 3 0もまた、 第 4図、 第 5図に示した燃料噴 射弁 1と同様に、 コモンレール内に蓄積されている高圧燃料を図示しないディ一 ゼル内燃機関の気筒内に噴射供給するために用いられるものである。  The present invention will be described in more detail with reference to the accompanying drawings. FIG. 1 is a view showing one embodiment of a fuel injection valve according to the present invention, and FIG. 2 is an enlarged view of a main part of FIG. Referring to FIG. 1 and FIG. 2, the fuel injection valve 30 includes an injector housing 32, a nozzle body 33, a nozzle needle 34, a valve piston 35, a valve body 36, and a back. It has a pressure control section 37 and an inlet connector 38. A nozzle body 33 is attached to a tip end of the injector housing 32 by a nozzle nut 39, and an inlet connector 38 is attached to an upper portion thereof. Similarly to the fuel injection valve 1 shown in FIGS. 4 and 5, the fuel injection valve 30 also supplies high-pressure fuel accumulated in the common rail into the cylinder of a diesel internal combustion engine (not shown). It is used for
インジヱクタハウジング 3 2内には、 インレツ トコネクタ 3 8からノズルボデ ィ 3 3にまで延びる燃料通路 3 8 Aが形成されており、 ノズル二一ドル 3 4の受 圧部 3 4 Aに対向して燃料溜まり室 3 3 Aが形成されている。 このノズル部の構 成は第 4図に示すそれと同様の公知の構成であるので、 その詳細説明は省略する。 バルブボディ 3 6は、 太径部 3 6 1と細径部 3 6 2とを有する全体として略円 筒状の形態をなす部材であり、 インジヱクタハウジング 3 2内のバルブボディ収 容室 3 2 1内には、 バルブボディ 3 6がインジヱクタハウジング 3 2と同軸とな るように収容されている。 バルブボディ 3 6には細径部 3 6 2側に開口する摺動 穴 3 6 3が形成されており、 摺動穴 3 6 3内にはバルブピストン 3 5の後端部 3 5 1が油密状態を保ってその軸線方向に摺動可能なように挿入されている。 A fuel passage 38 A extending from the inlet connector 38 to the nozzle body 33 is formed in the injector housing 32, and faces the pressure receiving portion 34 A of the nozzle needle 34. Thus, a fuel reservoir 33A is formed. Since the configuration of this nozzle portion is a known configuration similar to that shown in FIG. 4, detailed description thereof will be omitted. The valve body 36 is a generally cylindrical member having a large diameter portion 36 1 and a small diameter portion 36 2. The valve body 36 has a valve body storage chamber 3 in the injector housing 32. In 21, the valve body 36 is coaxial with the injector housing 32. It is housed so. The valve body 36 has a sliding hole 3 63 opening on the small-diameter portion 36 2 side, and the rear end 3 51 of the valve piston 35 is oiled in the sliding hole 36 3. It is inserted so as to be slidable in the axial direction while maintaining a tight state.
摺動穴 3 6 3は太径部 3 6 1内にまで延びており、 摺動穴 3 6 3の開口端と反 対側の太径部 3 6 1内にはバルブビス トン 3 5の一端を臨ませている制御圧室 3 6 4が形成されている。 制御圧室 3 6 4は、 開閉用ォリフィス 3 6 5にも連通し ており、 開閉用ォリフィス 3 6 5は背圧制御部 3 7のバルブボール 3 7 1によつ て開閉可能となっている。 なお、 制御圧室 3 6 4におけるバルブピス トン 3 5の 頂部 3 5 Aの受圧面積は、 ノズルニードル 3 4の受圧部 3 4 A (第 1図） の受圧 面積より大きく してある。  The sliding hole 3 6 3 extends into the large diameter portion 3 6 1, and one end of the valve screw 3 5 is inserted into the large diameter portion 3 6 1 opposite to the open end of the sliding hole 3 6 3. A control pressure chamber 3 6 4 is formed. The control pressure chamber 364 also communicates with an opening / closing orifice 365, and the opening / closing orifice 365 can be opened and closed by a valve ball 371 of the back pressure control section 37. . The pressure receiving area of the top 35 A of the valve piston 35 in the control pressure chamber 365 is larger than the pressure receiving area of the pressure receiving section 34 A of the nozzle needle 34 (FIG. 1).
背圧制御部 3 7は、 マグネッ ト 3 7 2と、 ァーマチュア 3 7 3と、 ァ一マチュ ァ 3 7 3に一体のバルブボール 3 7 1とを備え、 マグネッ ト 3 7 2へ駆動信号を 供給することにより、 マグネッ ト 3 7 2はバルブスプリング 3 7 4の付勢力に抗 してァーマチュア 3 7 3を吸引し、 バルブボール 3 7 1を開閉用ォリフィス 3 6 5からリフ トさせ、 制御庄室 3 6 4の圧力を図示しない燃料還流路を介して燃料 低圧側に解放可能とする構成となっている。 したがって、 バルブボール 3 7 1を 上述の如く動作させることにより制御圧室 3 6 4の圧力を制御し、 バルブピス ト ン 3 5を介してノズル二一ドル 3 4の背圧を制御することにより、 ノズルニード ル 3 4のリフトを制御することができる。 上述した燃料噴射制御のための背圧制 御の構成それ自体は公知であるので、 これについての詳しい説明は省略する。 次に、 インレツ トコネクタ 3 8から供給される高圧燃料をィンジヱクタハウジ ング 3 2を通ってバルブボディ 3 6内の制御圧室 3 6 4に送るための構成につい て説明する。  The back pressure control unit 37 includes a magnet 372, an armature 373, and a valve ball 371 integrated with the armature 373, and supplies a drive signal to the magnet 372. As a result, the magnet 372 sucks the armature 373 against the urging force of the valve spring 374, and lifts the valve ball 371 from the opening / closing orifice 365 to control the control chamber. The pressure of 364 can be released to the low-pressure side of the fuel via a fuel recirculation path (not shown). Therefore, by operating the valve ball 371, as described above, the pressure of the control pressure chamber 3664 is controlled, and by controlling the back pressure of the nozzle 21-4 via the valve piston 35, The lift of the nozzle needle 34 can be controlled. Since the configuration of the back pressure control for the fuel injection control described above is known per se, a detailed description thereof will be omitted. Next, a configuration for sending the high-pressure fuel supplied from the inlet connector 38 to the control pressure chamber 364 in the valve body 36 through the injector housing 32 will be described.
バルブボディ 3 6を収容するバルブボディ収容室 3 2 1は、 バルブボディ 3 6 に相応した寸法形状の空間となっている。 その環状段部 3 2 1 Aに、 シールプレ ート 5 0を介して太径部 3 6 1の環状突部 3 6 1 Aが着座するようにして、 バノレ プボディ 3 6がバルブボディ収容室 3 2 1内に収容されている。  The valve body housing chamber 3 2 1 for housing the valve body 36 is a space having a size and shape corresponding to the valve body 36. The annular projection 3 61 A of the large diameter portion 36 1 is seated on the annular step 3 21 A via the seal plate 50 so that the vane rep body 36 is attached to the valve body storage chamber 3 2. Housed in one.
バルブボディ収容室 3 2 1内に上述の如く して収容されたバルブボディ 3 6は、 締付ナツ ト 4 0によってバルブボディ収容室 3 1内に押し込まれるので、 シ一 ルプレート 5 0は環状段部 3 2 1 Aの上面 3 2 1 A aと環状突部 3 6 1 Aの下面 3 6 1 A aとに密着し、 上面 3 2 1 A aと下面 3 6 1 A aとの間の油密状態を良 好に保つことができる状態となっている。 The valve body 36 housed in the valve body housing chamber 3 21 as described above is The sealing nut 50 is pushed into the valve body chamber 31 by the tightening nut 40, so that the seal plate 50 has an upper surface 321Aa of the annular step 321A and a lower surface of the annular protrusion 361A. It is in close contact with 36 1 A a, and is in a state where the oil-tight state between the upper surface 3 21 A a and the lower surface 36 1 A a can be kept good.
第 3図に示すように、 シールプレート 5 0は、 オリフィス 5 0 1を有する円環 状の部材であり、 ここでは、 クロム含有の鉄系金属材料を用いて作られている。 また、 シールプレート 5 0は、 シール性能を安定させるために、 プレートの上下 面においてォリフィス 5 0 1の周辺及びプレート内周部と外周部の一部を残して 座繰加工を施してある。 符号 5 0 2、 5 0 3で示されるのは位置決め用の孔であ り、 これらの孔 5 0 2、 5 0 3を用いることにより、 オリフィス 5 0 1が燃料通 路 3 8 Aに連通するようにしてシールプレート 5 0をインジヱクタハウジング 3 2とバルブボディ 3 6との間に容易に配設することができる。  As shown in FIG. 3, the seal plate 50 is an annular member having an orifice 501, and is here made of a chromium-containing iron-based metal material. Further, in order to stabilize the sealing performance, the seal plate 50 is counterbored on the upper and lower surfaces of the plate, leaving the periphery of the orifice 501 and a part of the inner and outer peripheral portions of the plate. Reference numerals 502 and 503 indicate positioning holes, and by using these holes 502 and 503, the orifice 501 communicates with the fuel passage 38A. In this manner, the seal plate 50 can be easily arranged between the injector housing 32 and the valve body 36.
第 2図に示されているように、 インジヱクタハウジング 3 2内の環状段部 3 2 1 Aにはオリフィス 5 0 1に対向するようにして高圧燃料供給室 4 1が形成され ており、 高圧燃料供給室 4 1にはインレツ トコネクタ 3 8から供給される高圧燃 料が燃料通路 3 8 Aを通って導かれている。 一方、 バルブボディ 3 6の太径部 3 6 1内には、 一端が制御圧室 3 6 4に連通しており、 他端が下面 3 6 1 A aにお いてオリフィス 5 0 1に対向するように開口している通路 4 2が設けられている。 この結果、 燃料通路 3 8 Aから送られた高圧燃料はォリフィス 5 0 1を介して通 路 4 2内に入り、 制御圧室 3 6 4に送られる。 以上説明したように、 インレツ ト コネクタ 3 8からの高圧燃料は、 シールプレート 5 0のオリフィス 5 0 1を通つ て制御圧室 3 6 4に送られる構成であるから、 性能調整が容易となる。  As shown in FIG. 2, a high-pressure fuel supply chamber 41 is formed in the annular step portion 3 21 A in the injector housing 32 so as to face the orifice 501. The high-pressure fuel supplied from the inlet connector 38 is guided to the high-pressure fuel supply chamber 41 through the fuel passage 38A. On the other hand, one end communicates with the control pressure chamber 364 in the large diameter portion 361 of the valve body, and the other end faces the orifice 501 on the lower surface 361 Aa. There is provided a passage 42 that is open. As a result, the high-pressure fuel sent from the fuel passage 38 A enters the passage 42 via the orifice 501 and is sent to the control pressure chamber 364. As described above, since the high-pressure fuel from the inlet connector 38 is sent to the control pressure chamber 364 through the orifice 501 of the seal plate 50, the performance can be easily adjusted. .
既に説明したように、 シールプレート 5 0は環状段部 3 2 1 Aの上面 3 2 1 A aと環状突部 3 6 1 Aの下面 3 6 1 A aとに密着し、 上面 3 2 1 A aと下面 3 6 1 A aとの間の油密状態を良好に保つことができる状態となっているので、 高圧 燃料供給室 4 1内の高圧燃料はバルブボディ 3 6とインジヱクタハウジング 3 2 との間に漏れ出すことなく、 制御圧室 3 6 4内に送られる。 そして、 制御圧室 3 6 4はバルブボディ 3 6の太径部 3 6 1内に形成されているため、 制御圧室 3 6 4内に高圧燃料が充満した場合でも、 太径部 3 6 1の大きな肉厚により変形が小 さく抑えられる。 この結果、 バルブボディ 3 6全体の変形を小さくすることがで き、 バルブビストン 3 5を摺動穴 3 6 3内で円滑に摺動させることができる。 産業上の利用可能性 As described above, the seal plate 50 is in close contact with the upper surface 3 2 1 A a of the annular step 3 2 1 A and the lower surface 3 6 1 A a of the annular protrusion 3 6 1 A, and the upper surface 3 2 1 A a and the lower surface 3 6 1 A Since the oil-tight state between the a and the lower surface is maintained in a good condition, the high-pressure fuel in the high-pressure fuel supply chamber 41 is supplied to the valve body 36 and the injector housing 3. It is sent into the control pressure chamber 364 without leaking between it and 2. Since the control pressure chamber 3 6 4 is formed in the large diameter portion 3 6 1 of the valve body 36, the control pressure chamber 3 6 Even when the high-pressure fuel is filled in 4, the large thickness of the large-diameter portion 361 reduces deformation to a small extent. As a result, the deformation of the entire valve body 36 can be reduced, and the valve piston 35 can be slid smoothly in the sliding hole 365. Industrial applicability
本発明によれば、 インジヱクタハウジングとバルブボディとの間の高圧燃料漏 れを確実に防止でき、 燃料噴射弁の改善に役立つ。  ADVANTAGE OF THE INVENTION According to this invention, high pressure fuel leakage between an injector housing and a valve body can be reliably prevented, and it contributes to improvement of a fuel injection valve.

Claims

請求の範囲 The scope of the claims
1 . バルブビストンを摺動可能に揷入したバルブボディがインジヱクタハウジ ング内に設けられて成り、 前記バルブビストンの一端を臨ませているバルブボデ ィ内の制御圧室内に高圧燃料を前記インジェクタハウジングより送るように構成 された燃料噴射弁において、 前記インジヱクタハウジング内に環状段部を設ける と共に前記バルブボディに前記環状段部に対応した環状突部を設け、 該環状突部 をオリフィス付のシールプレートを介して前記環状段部に着座せしめ、 前記オリ フィスを介して前記ィンジェクタハウジング側から前記制御圧室内に高圧燃料を 送るようにしたことを特徴とする燃料噴射弁。 1. A valve body in which a valve piston is slidably inserted is provided in an injector housing, and high-pressure fuel is injected into a control pressure chamber in a valve body that faces one end of the valve piston. In a fuel injection valve configured to be fed from a housing, an annular step is provided in the injector housing, and an annular protrusion corresponding to the annular step is provided in the valve body, and the annular protrusion is provided with an orifice. A fuel injection valve which is seated on the annular step portion via the seal plate, and sends high-pressure fuel from the injector housing side into the control pressure chamber via the orifice.
2 . 前記制御圧室が前記環伏突部内に形成されている請求の範囲第 1項記載の 燃料噴射弁。 2. The fuel injection valve according to claim 1, wherein the control pressure chamber is formed in the annular protrusion.
3 . 前記インジェクタハウジング内には前記高圧燃料を外部から挿入するため の燃料通路と、 前記シールプレー 卜の前記ォリフィスに対向する高圧燃料室とが 形成されており、 前記燃料通路内の高圧燃料が前記高圧燃料室を介して前記ォリ フィスに供給される請求の範囲第 2項記載の燃料噴射弁。 3. A fuel passage through which the high-pressure fuel is inserted from the outside and a high-pressure fuel chamber facing the orifice of the seal plate are formed in the injector housing, and the high-pressure fuel in the fuel passage is formed therein. 3. The fuel injection valve according to claim 2, wherein the fuel is supplied to the orifice via the high-pressure fuel chamber.
4 . 前記環伏突部内に、 前記制御圧室と前記オリフィスとを連通させる通路が 形成されている請求の範囲第 3項記載の燃料噴射弁。 4. The fuel injection valve according to claim 3, wherein a passage for communicating the control pressure chamber and the orifice is formed in the annular protrusion.
5 . 前記シールプレートの上下面には、 前記オリフィスの周辺及び前記シール プレー卜の内周部と外周部の一部を残して座繰加工が施されている請求の範囲第 1項、 第 2項、 第 3項又は 4項記載の燃料噴射弁。 5. The upper and lower surfaces of the seal plate are subjected to a counterboring process except for a periphery of the orifice and a part of an inner peripheral portion and an outer peripheral portion of the seal plate. Item 5. The fuel injection valve according to item 3 or 4.
6 . 前記シールプレー卜に位置決め用の孔が設けられている請求の範囲第 1項 第 2項、 第 3項、 第 4項又は 5項記載の燃料噴射弁。 6. The fuel injection valve according to claim 1, wherein a positioning hole is provided in the seal plate.
PCT/JP2005/010532 2004-06-03 2005-06-02 Fuel injection valve WO2005119047A1 (en)

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JP2005344622A (en) 2005-12-15
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KR20070037612A (en) 2007-04-05

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