EP1752653A1 - Soupape d"injection de carburant - Google Patents

Soupape d"injection de carburant Download PDF

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Publication number
EP1752653A1
EP1752653A1 EP05748484A EP05748484A EP1752653A1 EP 1752653 A1 EP1752653 A1 EP 1752653A1 EP 05748484 A EP05748484 A EP 05748484A EP 05748484 A EP05748484 A EP 05748484A EP 1752653 A1 EP1752653 A1 EP 1752653A1
Authority
EP
European Patent Office
Prior art keywords
fuel
pressure
injector
valve body
orifice
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP05748484A
Other languages
German (de)
English (en)
Inventor
Natsuki Bosch Automotive Systems Corp. HOSOYA
Kenichi Bosch Automotive Systems Corp. KUBO
Kiyoshi Bosch Automotive Systems Corp MATSUZAKI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Corp
Original Assignee
Bosch Corp
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 Corp filed Critical Bosch Corp
Publication of EP1752653A1 publication Critical patent/EP1752653A1/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • 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 injector.
  • Fig. 4 is a view for explaining the constitution of a conventional fuel injector.
  • the fuel injector 1 is used for injecting and supplying a high-pressure fuel which is stored in the inside of a common rail 12 into the inside of a cylinder of a diesel internal combustion engine not shown in the drawing.
  • Fuel F in the inside of a fuel tank 10 is pressurized by a fuel pump 11, and the pressurized fuel is stored in the inside of the common rail 12 as the high-pressure fuel.
  • the fuel injector 1 includes an injector housing 2, a nozzle body 3, a nozzle needle 4, a valve piston 5, a valve body 6, a back-pressure control part 7 and a connecting rod 8.
  • the nozzle body 3 is mounted on a distal end portion of the injector housing 2 using a nozzle nut 9, while the connecting rod 8 is mounted on an upper portion of the injector housing 2.
  • a fuel passage 13 is formed in the fuel injector valve 1 in a state that the fuel passage 13 extends to the nozzle body 3 through the injector housing 2 from the connecting rod 8, and a fuel reservoir 14 is formed in a state that the fuel reservoir 14 faces a pressure-receiving portion 4A of the nozzle needle 4 in an opposed manner. Further, in the injector housing 2, a fuel return passage 15 is formed in a state that the fuel return passage 15 is branched from the fuel passage 13 in the vicinity of the connecting rod 8 and is communicated with a low fuel pressure portion through the back-pressure control part 7.
  • the nozzle body 3 is configured such that an injection hole 16 is closed by seating a distal end portion of the nozzle needle 4 on a seat portion 17 which is communicated with the injection hole 16, and the injection hole 16 is opened by lifting the nozzle needle 4 from the seat portion 17. Due to such a constitution, it is possible to start or stop the fuel injection.
  • a nozzle spring 18 for biasing the nozzle needle 4 in the direction that the nozzle needle 4 is seated on the seat portion 17 is provided, and the valve piston 5 is slidably inserted into a sliding hole 2A formed in the injector housing 2 and a sliding hole 6A formed in the valve body 6.
  • Fig. 5 is an enlarged cross-sectional view of respective essential parts of the valve body 6 and the back pressure control part 7.
  • a pressure-controlling chamber 19 is formed in the valve body 6, and a distal end portion of the valve piston 5 is allowed to face the pressure-controlling chamber 19 from below.
  • the pressure-controlling chamber 19 is communicated with an introduction-side orifice 20 which is formed in the valve body 6.
  • the introduction-side orifice 20 is configured to be communicated with the fuel passage 13 by way of a pressure introduction chamber 21 which is formed between the valve body 6 and the injector housing 2 so as to allow the supply of an introduced pressure from the common rail 12 to the pressure-controlling chamber 19.
  • a seal member 22 made of a resin material, a rubber material, copper or other soft material is provided to a lower end portion of the pressure introduction chamber 21, a seal member 22 made of a resin material, a rubber material, copper or other soft material is provided.
  • the seal member 22 interrupts the communication between the pressure introduction chamber 21 which constitutes a high-fuel-pressure side and a gap 28 which is formed between the injector housing 2 and the valve body 6 and constitutes a low-fuel-pressure side.
  • the pressure-controlling chamber 19 is also communicated with an open/close orifice 23, and the open/close orifice 23 can be opened or closed by a valve ball 24 of the back-pressure control part 7.
  • a pressure-receiving area of a top portion 5A of the valve piston 5 in the pressure-controlling chamber 19 is set larger than a pressure-receiving area of the pressure-receiving portion 4A of the nozzle needle 4(see, Fig. 4).
  • the back-pressure control part 7 includes a magnet 25, an armature 27, the valve ball 24 which is integrally formed with the armature 27, and the pressure-controlling chamber 19.
  • the magnet 25 attracts the armature 27 against a biasing force of the valve spring 26 so as to lift the valve ball 24 from the open/close orifice 23 thus releasing a pressure inside the pressure-controlling chamber 19 to the fuel return passage 15 side.
  • the high-pressure fuel from the common rail 12 acts on the pressure receiving portion 4A of the nozzle needle 4 arranged in the inside of the fuel reservoir 14 by way of the fuel passage 13 from the connecting rod 8 and, at the same time, also acts on the top portion 5A of the valve piston 5 arranged in the inside of the pressure-controlling chamber 19 by way of the pressure introduction chamber 21 and the introduction-side orifice 20.
  • the nozzle needle 4 receives the back pressure of the pressure-controlling chamber 19 by way of the valve piston 5 and is seated on the seat portion 17 of the nozzle body 3 together with the biasing force of the nozzle spring 18 thus closing the injection hole 16.
  • the high pressure in the inside of the pressure-controlling chamber 19 passes through the fuel return passage 15 byway of the open/close orifice 23 and returns to the fuel tank 10 and hence, the high pressure which acts on the top portion 5A of the valve piston 5 in the pressure-controlling chamber 19 is released and hence, the nozzle needle 4 is lifted from the seat portion 17 by the high pressure which acts on the pressure-receiving portion 4A against the biasing force of the nozzle spring 18 whereby the injection hole 16 is opened thus enabling the injection of the fuel.
  • the pressure introduction chamber 21 is positioned at an inlet portion leading to the pressure controlling chamber 19 which controls an injection amount and an injection pressure of the fuel from the injection hole 16 and hence, a fuel pressure inside the pressure introduction chamber 21 is substantially equal to the injection pressure whereby a high pressure which is substantially equal to the injection pressure acts on the seal member 22.
  • valve piston 5 As shown in Fig. 5, between the valve piston 5 and the valve body 6, it is necessary to provide a clearance which allows the axial slide movement of the valve piston 5 which is integrally moved with the nozzle needle 4 therein.
  • the gap 28 is provided also between the injector housing 2 and the valve body 6 as a slight clearance.
  • JP-A-2003-28021 discloses an injector having the constitution which can prevent a seal member from being pushed out to a low-pressure side by providing a metal backup ring to the low-pressure side (a gap side) of the seal member.
  • a fastening stress of a fastening nut 40 is applied to a valve-body large-diameter portion 361 and hence, a seat surface which is constituted of an open/close orifice 365 and a valve ball 371 tends to be deformed so as to be displaced in the injector magnet direction by receiving a fastening stress.
  • the seat surface is moved thus giving rise to a drawback that an injector lift amount is changed so that an error occurs in an injection amount.
  • the introduction-side orifice 20 is designed to extend toward a control chamber 19 perpendicular to the injector axis direction and hence, a large-diameter portion of a valve body is set at a position which avoids the introduction-side orifice 20. Accordingly, a thickness of the valve body in the injector axis direction is restricted thus giving rise to a drawback that a large-diameter portion of the valve body is liable to be easily deformed when a fastening stress is applied to the large-diameter portion.
  • the technical feature of the present invention for overcoming the above-mentioned tasks lies in that, in a fuel injector in which a valve body which allows a valve piston to be slidably inserted therein is arranged in the inside of an injector housing, one end of the valve piston is arranged to face a control pressure chamber formed in the inside of the valve body, and a high-pressure fuel is supplied to the inside of the control pressure chamber from the injector housing, in the inside of the injector housing, on an annular stepped portion which is configured to be aligned with an injector axis, a large-diameter portion of the valve body which forms the control pressure chamber therein and corresponds to the annular stepped portion is seated by way of a seal plate in which an orifice parallel to the injector axis is formed, and high pressure fuel supplied from the injector housing side is supplied to the inside of the control pressure chamber through an oil passage formed in the inside of the large-diameter portion by way of the orifice.
  • the orifice plate which functions as the seal plate as well as the high-pressure-fuel introducing orifice is sandwiched by the valve body and the injector housing, it is possible to increase a thickness in the injector axial direction of the valve-body large-diameter portion and hence, the deformation of the valve-body large-diameter portion attributed to a fastening stress generated by a fastening nut can be suppressed whereby the irregularities of an injector injection amount can be lowered.
  • Fig. 1 is a view showing one embodiment of a fuel injector according to the present invention
  • Fig. 2 is an enlarged view of an essential part shown in Fig. 1.
  • a fuel injector 30 includes an injector housing 32, a nozzle body 33, a nozzle needle 34, a valve piston 35, a valve body 36, a back pressure control portion 37, and an inlet connector 38.
  • a nozzle body 33 is mounted on a distal end portion of the injector housing 32 using a nozzle nut 39, and the inlet connector 38 is mounted on an upper portion of the injector housing 32.
  • the fuel injector 30 serves also, in the same manner as the fuel injector 1 shown in Fig. 4 and Fig. 5, to supply a high pressure fuel which is stored in the inside of a common rail into the inside of a cylinder of a diesel internal combustion engine not shown in the drawing.
  • a fuel passage 38A which extends to a nozzle body 33 from the inlet connector 38 is formed, and a fuel reserving chamber 33A is formed such that the fuel reserving chamber 33A faces a pressure receiving portion 34A of a nozzle needle 34. Since the constitution of the nozzle portion has the known constitution substantially equal to the constitution shown in Fig. 4, the detailed explanation of the constitution is omitted.
  • the valve body 36 is a member which includes a large-diameter portion 361 and a small-diameter portion 362 and has an approximately cylindrical shape as a whole.
  • a valve body accommodating chamber 321 formed in the inside of the injector housing 32 the valve body 36 is accommodated coaxially with the injector housing 32.
  • a slide hole 363 which opens at a small-diameter-portion-362 side is formed in the valve body 36, while a rear end portion 351 of a valve piston 35 is inserted in the slide hole 363 in an axially slidable manner while maintaining an oil sealed state.
  • the slide hole 363 extends to the inside of the large-diameter portion 361 and a control pressure chamber 364 is formed in the inside of the large-diameter portion 361 opposite to an opening end of the slide hole 363, wherein one end of the valve piston 35 faces the control pressure chamber 364.
  • the control pressure chamber 364 is also communicated with an open/close orifice 365, while the open/close orifice 365 can be opened or closed by a valve ball 371 of the back pressure control portion 37.
  • a pressure receiving area of a top portion 35A of the valve piston 35 in the control pressure chamber 364 is set larger than a pressure receiving area of a pressure receiving portion 34A (Fig. 1) of the nozzle needle 34.
  • the back pressure control portion 37 is configured such that the back pressure control portion 37 includes a magnet 372, an armature 373, and a valve ball 371 which is integrally formed with the armature 373, wherein in response to the supply of a drive signal to the magnet 372, the magnet 372 attracts the armature 373 against a biasing force of the valve spring 374 so as to lift the valve ball 371 from the open/close orifice 365 thus releasing a pressure of the control pressure chamber 364 to a low fuel pressure side by way of a fuel return flow passage not shown in the drawing.
  • a back pressure of the nozzle needle 34 can be controlled by way of the valve piston 35 thus controlling the lifting of the nozzle needle 34. Since the constitution of the back pressure control for the above-mentioned fuel injection control per se is known, the further detailed explanation of the constitution is omitted.
  • the valve body accommodating chamber 321 which accommodates the valve body 36 defines a space of a size and a shape which correspond to a size and a shape of the valve body 36.
  • the valve body 36 is accommodated in the inside of the valve body accommodating chamber 321 such that an annular projecting portion 361A of a large-diameter portion 361 is seated on the annular stepped portion 321A by way of a seal plate 50.
  • valve body 36 which is accommodated in the inside of the valve body accommodating chamber 321 is pushed into the inside of the valve body accommodating chamber 321 by the fastening nut 40 and hence, the seal plate 50 is hermetically sandwiched between an upper surface 321Aa of the annular stepped portion 321A and a lower surface 361Aa of the annular projection portion 361A thus establishing a state in which an oil sealed state between the upper surface 321Aa and the lower surface 361Aa is held favorably.
  • the seal plate 50 is an annular member having an orifice 501 and is made of an iron-based metal material which contains chromium. Further, spot facing is applied to upper and lower surfaces of the seal plate 50 for stabilizing a sealing performance except for a periphery of the orifice 501, and a portion of an inner peripheral portion and a portion of an outer peripheral portion of the seal plate 50.
  • Numerals 502, 503 indicate positioning holes. With the use of these holes 502, 503, it is possible to easily arrange the seal plate 50 between the injector housing 32 and the valve body 36 such that the orifice 501 faces the fuel supply passage 38A in an opposed manner.
  • An axis of the orifice 501 is arranged parallel to the injector axis of the fuel injector 30.
  • a high-pressure fuel supply chamber 41 is formed in the annular stepped portion 321A in the inside of the injector housing 32 such that the high-pressure fuel supply chamber 41 faces the orifice 501 in an opposed manner, wherein a high-pressure fuel supplied from the inlet connector 38 is introduced into the high-pressure fuel supply chamber 41 through the fuel passage 38A.
  • a passage 42 which has one end thereof communicated with the control pressure chamber 364 and another end thereof opened at a lower surface 361Aa such that the another end faces the orifice 501 in an opposed manner is formed.
  • the fuel injector is configured such that the high-pressure fuel from the inlet connector 38 is supplied to the control pressure chamber 364 through the orifice 501 formed in the seal plate 50 and hence, it is unnecessary to temporarily reserve the high-pressure fuel between the injector housing 32 and the valve body 36 whereby the fuel is directly supplied to the valve body 36 side from the injector housing 32 side through the orifice 501.
  • the seal plate 50 is hermetically brought into contact with the upper surface 321Aa of the annular stepped portion 321A and the lower surface 361Aa of the annular projection portion 361A thus establishing a state in which an oil sealed state between the upper surface 321Aa and the lower surface 361Aa is favorably held. Accordingly, the high-pressure fuel in the inside of the high-pressure fuel supply chamber 41 is supplied to the inside of the control pressure chamber 364 without generating the leaking of the high-pressure fuel between the valve body 36 and the injector housing 32.
  • control pressure chamber 364 is formed in the inside of the large-diameter portion 361 of the valve body 36, even when the high-pressure fuel is fully filled in the inside of the control pressure chamber 364, the deformation of the large-diameter portion 361 can be suppressed to a small value due to a large wall thickness of the large-diameter portion 361. As a result, it is possible to reduce the deformation of the whole valve body 36 to a small value and hence, it is possible to provide the smooth sliding movement of the valve piston 35 in the inside of the slide hole 363 and, at the same time, the adjustment of performance is facilitated.
  • the fuel injector 30 is constituted in the above-mentioned manner, it is possible to increase the thickness in the injector axis direction of the large-diameter portion 361 of the valve body 36.
  • the valve body 36 is fastened to the injector housing 32 using the fastening nut 40, the deformation of the large-diameter portion 361 of the valve body 36 attributed to the fastening stress can be suppressed and hence, the irregularities of the injector injection amount can be reduced.
  • the passage 42 and the control pressure chamber 364 are formed in the inside of the large-diameter portion 361, the deformation of the valve body 36 attributed to the supply of the high-pressure fuel can be effectively suppressed thus realizing the fuel injector 30 of high performance.
  • the deformation of the large-diameter portion of the valve body can be suppressed and hence, the irregularities of the injection amount can be reduced whereby the present invention is useful in the improvement of the fuel injector.
EP05748484A 2004-06-03 2005-06-02 Soupape d"injection de carburant Withdrawn EP1752653A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004165707A JP4087817B2 (ja) 2004-06-03 2004-06-03 燃料噴射弁
PCT/JP2005/010527 WO2005119046A1 (fr) 2004-06-03 2005-06-02 Soupape d’injection de carburant

Publications (1)

Publication Number Publication Date
EP1752653A1 true EP1752653A1 (fr) 2007-02-14

Family

ID=35462968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05748484A Withdrawn EP1752653A1 (fr) 2004-06-03 2005-06-02 Soupape d"injection de carburant

Country Status (4)

Country Link
EP (1) EP1752653A1 (fr)
JP (1) JP4087817B2 (fr)
CN (1) CN1969121A (fr)
WO (1) WO2005119046A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005344622A (ja) * 2004-06-03 2005-12-15 Bosch Corp 燃料噴射弁
EP1867867B1 (fr) * 2006-06-15 2010-08-25 C.R.F. Società Consortile per Azioni Injecteur de carburant
DE102007044357A1 (de) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Steuerventil für ein Kraftstoffeinspritzventil
JP4716142B2 (ja) * 2008-09-16 2011-07-06 株式会社デンソー 燃料噴射装置
JP6395218B2 (ja) * 2014-12-23 2018-09-26 ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング 燃料噴射システムに組み込まれるコンポーネント、及び、燃料噴射システム

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH495504A (de) * 1968-08-28 1970-08-31 Sopromi Soc Proc Modern Inject Brennstoff-Einspritzventil mit elektromagnetischer Betätigung
AT378242B (de) * 1981-07-31 1985-07-10 Berchtold Max Prof Kraftstoffeinspritzanlage fuer brennkraftmaschinen, insbesondere dieselmotoren
JP3849067B2 (ja) * 1995-03-30 2006-11-22 ボッシュ株式会社 燃料噴射ポンプ
JP3755143B2 (ja) * 1996-11-21 2006-03-15 株式会社デンソー 蓄圧式燃料噴射装置
JP3781061B2 (ja) * 1995-12-21 2006-05-31 株式会社デンソー 燃料噴射装置
DE19937677C2 (de) * 1999-08-10 2003-06-26 Siemens Ag Einspritzventil mit verbesserter Dichtflächenanordnung
DE10102233A1 (de) * 2001-01-19 2002-07-25 Bosch Gmbh Robert Kraftstoffhochdrucksystem für Brennkraftmaschinen
JP3567374B2 (ja) 2001-07-16 2004-09-22 株式会社ボッシュオートモーティブシステム 燃料噴射弁のシール構造
JP3864328B2 (ja) * 2001-11-02 2006-12-27 ボッシュ株式会社 燃料噴射弁の燃料通路シール構造
JP2005344622A (ja) * 2004-06-03 2005-12-15 Bosch Corp 燃料噴射弁

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005119046A1 *

Also Published As

Publication number Publication date
JP4087817B2 (ja) 2008-05-21
JP2005344623A (ja) 2005-12-15
WO2005119046A1 (fr) 2005-12-15
CN1969121A (zh) 2007-05-23

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