EP0386445A1 - Injecteur de combustible pour moteurs à combustion interne - Google Patents

Injecteur de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0386445A1
EP0386445A1 EP19900101710 EP90101710A EP0386445A1 EP 0386445 A1 EP0386445 A1 EP 0386445A1 EP 19900101710 EP19900101710 EP 19900101710 EP 90101710 A EP90101710 A EP 90101710A EP 0386445 A1 EP0386445 A1 EP 0386445A1
Authority
EP
European Patent Office
Prior art keywords
closing spring
valve needle
injection
pressure
fuel injection
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Withdrawn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
EP19900101710
Other languages
German (de)
English (en)
Inventor
Karl Dipl.-Ing. Hofmann
Bernhard Dipl.-Ing. Bronkal
Ernst Dipl.-Ing. Brocke
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0386445A1 publication Critical patent/EP0386445A1/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Withdrawn legal-status Critical Current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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/083—Having two or more closing springs acting on injection-valve
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a fuel injection nozzle according to the preamble of the main claim.
  • the second value of the fuel injection pressure at which the valve needle continues to move from the intermediate position is dimensioned and fixed so that the valve needle only reaches the intermediate position in idle and in the lower part-load range, so that the fuel in each case has a is injected for a sufficiently long period of time in the required form or atomization quality.
  • the valve needle movement continues after stopping in the intermediate position, so that there is a pre-injection and a main injection phase in connection with the graduated opening pressure curve and the main injection quantity of the fuel only reaches the combustion chamber of the engine when the ignition of the pre-injected fuel is already initiated.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that the second value of the fuel injection pressure, at which the valve needle is moved from the intermediate position, is no longer constant, but increases when a predetermined pressure is exceeded, so that after that the Valve needle is stopped in the intermediate position in a defined manner and / or is moved out of this in a delayed manner towards the stroke end position.
  • the injection process is stretched into a pre-injection and a main injection phase even at high engine speeds.
  • a design which has been tried and tested in known injection nozzles with two closing springs and a constant opening pressure level results when the first closing spring first acts solely on the valve needle and the second closing spring comes into effect after the valve needle has reached the intermediate position and the additional piston influences the second closing spring.
  • the first closing spring is arranged between the valve needle and the second closing spring and is surrounded by an annular body, by means of which the end of the second closing spring facing the valve needle is supported on a shoulder fixed to the housing until the intermediate position of the valve needle is reached, and if further the end of the first closing spring remote from the valve needle rests on a support member moved with the annular body (FIG. 1). It is thereby achieved that the additional piston acts only on the second closing spring, so that already during the preliminary stroke the valve needle of the additional piston is activated so that a two-stage stroke of the valve needle is ensured even at the highest possible speed of the machine.
  • the desired increase in the second value of the nozzle opening pressure in the higher speed range can be achieved with a particularly small stroke of the additional piston if it acts on both closing springs according to a further proposal of the invention.
  • FIGS. 1-4 each show a partial longitudinal section through one of the exemplary embodiments.
  • the injection nozzle according to FIG. 1 has a nozzle body 10 which, together with an intermediate disk 12, is clamped to a nozzle holder 16 by means of a union nut 14.
  • a valve seat which is no longer shown, is formed in the nozzle body 10 and a valve needle 18 is displaceably mounted, which is acted upon by two differently preloaded closing springs 20, 22 arranged in the nozzle holder 16 in the manner described in more detail below.
  • a pressure chamber is formed which surrounds the valve needle 18 and which is connected on the inlet side via a channel connection 24 in the parts to a fuel connection piece 26 on the nozzle holder 16.
  • valve needle 18 in the In the area of the pressure chamber, the valve needle 18 is provided with a pressure shoulder at the transition to a needle section with a smaller diameter, which, with the guide bore in the nozzle body 10, delimits an annular channel leading from the pressure chamber to the valve seat.
  • the fuel injection pressure acts on the valve needle 18 in the opening direction on the pressure shoulder.
  • the weaker closing spring 20 acts on the valve needle 18 via a pressure piece 28, which is guided in a bush 30, which in turn is slidably mounted in the intermediate disk 12.
  • An annular body 32 which surrounds the closing spring 20, sits on the bushing 30, the upper end edge of which is acted upon by the stronger closing spring 22 via a thrust washer 34 which supports the closing spring 20 and is provided with a hub shoulder 33.
  • the closing spring 22 is supported by a support disk 35 on a shoulder 36 of the nozzle holder 16 which is fixed to the housing and, in the closed position of the valve needle 18, presses the bush 30 via the ring body 32 onto the upper end face 37 of the nozzle body 10.
  • the bushing 30 is provided with two stop shoulders 38 and 40, one of which, 38, with a ring shoulder on the valve needle 18, a preliminary stroke h v and the other, 40, with an inner shoulder of the intermediate disk 12, the total stroke h g of the valve needle 18 limited.
  • a cylinder bore 42 is provided upstream of the closing spring 22, which is connected to the channel connection 24 carrying the injection fuel and merges at an annular shoulder 44 into a narrower bore 46 which leads into the closing spring chamber of the nozzle holder 16.
  • an additional piston 48 is slidably guided, which projects through the bore 46 with a shoulder 49 and is acted upon by a spring 50 which presses it against the support disk 35.
  • the fuel injected The cross section of the additional piston 48 is dimensioned such that the force exerted by it on the support disk 35 overcomes the support force of the closing spring 22 when the engine speed and the fuel injection pressure dependent thereon exceed a predetermined value.
  • the fuel injection pressure rises only to such an extent that it can only overcome the force of the weaker closing spring 20.
  • the valve needle 18 executes a stroke, which is limited by the stop shoulder 38 on the bush 30 and therefore corresponds in size to the preliminary stroke h v .
  • the fuel injection pressure also rises until it finally overcomes the force of the second, stronger closing spring 22.
  • the additional piston 48 is also activated and displaced by a stroke h k by the fuel injection pressure exceeding a predetermined value, the stronger closing spring 22 being compressed and its force being further increased. It is thereby achieved that the valve needle 18 is briefly stopped in the intermediate position or slows out of it into the end-of-stroke position in this area of the operating characteristic map and the main injection quantity is thereby injected with the desired delay. Because the additional piston 48 only on the second closing spring 22 acts, there is still enough time for its activation even in the borderline case to achieve the desired effect.
  • the injection nozzle according to Figure 2 has the same basic structure as that of Figure 1, so that the same or equivalent parts are provided with the same reference number. The difference is that a first closing spring 52, which constantly acts on the valve needle 18, is arranged upstream of a second, stronger closing spring 54, which comes into effect only after the preliminary stroke.
  • the first closing spring 52 is surrounded by a sleeve 56 and acts on the valve needle 18 via a push rod 58 guided in the bushing 30, the closing spring 52 being supported on the bottom of the sleeve 56 and pressing it against a shoulder 60 of the nozzle holder 16 which is fixed to the housing.
  • the second closing spring 54 is supported by a washer 62, which also guides the push rod 58, and the sleeve 56 also on the shoulder 60 fixed to the housing and engages via a thrust member 64 guided on the push rod 58 on the bushing 30, which also supports the forward stroke in this embodiment determines the valve needle 18 and limits its total stroke.
  • an additional piston 48 is acted upon by the fuel injection pressure, but acts here on the two closing springs 52, 54 via the sleeve 56. It is thereby achieved that the increase in the opening pressure stage in the high speed range is achieved by a smaller stroke h k of the additional piston 48 than in the first exemplary embodiment.
  • the injection nozzle according to FIG. 3 differs from that according to FIG. 2 in that the additional piston 48 acts on the two closing springs 52 and 54 in chronological succession.
  • a pressure piece 66 influenced by the additional piston 48 which is slidably arranged in a sleeve 68, by means of which both closing springs 52, 54 are supported on the shoulder 60 fixed to the housing.
  • the sleeve 68 has a first pressure shoulder 70, on which the first closing spring 52 is supported via the pressure piece 66.
  • a second pressure shoulder 72 is formed on the sleeve 68, against which the pressure piece 66 comes to bear under the action of the additional piston 48 when it has traveled a partial stroke h t of its possible total stroke h k after activation.
  • the opening pressure level or the second opening pressure, which moves the valve needle from the intermediate position is increased in two stages, so that an even more differentiated adaptation to the respective application is possible.
  • an additional piston 78 acts solely on the first closing spring 52, which, as in the exemplary embodiments according to FIGS. 2 and 3, constantly acts on the valve needle and determines the first value of the opening pressure.
  • the closing spring 52 is supported on the bottom of a sleeve 80 and the additional piston 78 on a valve seat 82 in a nozzle holder 84, which surrounds a smaller diameter inlet bore 86 in the cylinder chamber of the additional piston 78 and increased by the additional piston 78 until the predetermined one is reached Value of the fuel injection pressure is closed.
  • the stroke h k of the additional piston 78 is determined by the sleeve 80 in cooperation with an inner annular collar 88 of the nozzle holder 84, on which the second closing spring 54, which is not influenced by the additional piston 78, is supported.
  • the design of the additional piston 78 as a valve body has an advantageous effect on the closing process.
  • the additional pistons 48 of the other designs could also be designed as two-stage valve pistons according to FIG. 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP19900101710 1989-03-09 1990-01-29 Injecteur de combustible pour moteurs à combustion interne Withdrawn EP0386445A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19893907569 DE3907569A1 (de) 1989-03-09 1989-03-09 Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3907569 1989-03-09

Publications (1)

Publication Number Publication Date
EP0386445A1 true EP0386445A1 (fr) 1990-09-12

Family

ID=6375885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900101710 Withdrawn EP0386445A1 (fr) 1989-03-09 1990-01-29 Injecteur de combustible pour moteurs à combustion interne

Country Status (3)

Country Link
EP (1) EP0386445A1 (fr)
JP (1) JPH02271064A (fr)
DE (1) DE3907569A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002086305A3 (fr) * 2001-04-21 2003-01-03 Bosch Gmbh Robert Dispositif d'injection de carburant pour moteur a combustion
WO2004055356A1 (fr) * 2002-12-13 2004-07-01 Robert Bosch Gmbh Injecteur de carburant a vitesse d'aiguille commandable

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19641824A1 (de) * 1996-10-10 1998-04-16 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE602006003631D1 (de) * 2006-04-13 2008-12-24 Fiat Ricerche Brennstoffinjektor einer Brennkraftmaschine
JP5551037B2 (ja) * 2010-09-28 2014-07-16 株式会社ディーゼルユナイテッド ガス噴射弁

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2536542A (en) * 1941-12-31 1951-01-02 Cav Ltd Variable valve loading injection nozzle
GB785411A (en) * 1955-02-23 1957-10-30 Saurer Ag Adolph Improvements in and relating to injection nozzles for internal combustion engines
GB808206A (en) * 1954-05-11 1959-01-28 Nylands Verksted Improvements in fuel injection systems for internal combustion engines
GB1284797A (en) * 1970-04-17 1972-08-09 Daimler Benz Ag Improvements relating to fuel-injection nozzle assemblies for internal combustion engines
DE2711393A1 (de) * 1977-03-16 1978-09-21 Bosch Gmbh Robert Kraftstoffeinspritzduese
DE3409924A1 (de) * 1983-03-31 1984-10-11 AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH, Prof. Dr.Dr.h.c. Hans List, Graz Duesenhalter fuer eine kraftstoffeinspritzduese
EP0239259A1 (fr) * 1986-03-21 1987-09-30 General Motors Corporation Buse d'injection de carburant à commande hydraulique à injection en deux phases
DE3712310A1 (de) * 1986-04-11 1987-10-29 Nippon Denso Co In einer kraftstoffeinspritzvorrichtung fuer eine brennkraftmaschine verwendetes kraftstoffeinspritzventil

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1751470A1 (de) * 1968-06-05 1971-07-01 Daimler Benz Ag Duesenhalter fuer Verbrennungsmotoren mit eingebauter Einspritzduese
JPS61171875A (ja) * 1985-01-25 1986-08-02 Mazda Motor Corp デイ−ゼルエンジンの燃料噴射装置
DE8608650U1 (de) * 1986-03-29 1987-07-23 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-Einspritzdüse für Brennkraftmaschinen
DE3637729A1 (de) * 1986-11-05 1988-05-11 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2536542A (en) * 1941-12-31 1951-01-02 Cav Ltd Variable valve loading injection nozzle
GB808206A (en) * 1954-05-11 1959-01-28 Nylands Verksted Improvements in fuel injection systems for internal combustion engines
GB785411A (en) * 1955-02-23 1957-10-30 Saurer Ag Adolph Improvements in and relating to injection nozzles for internal combustion engines
GB1284797A (en) * 1970-04-17 1972-08-09 Daimler Benz Ag Improvements relating to fuel-injection nozzle assemblies for internal combustion engines
DE2711393A1 (de) * 1977-03-16 1978-09-21 Bosch Gmbh Robert Kraftstoffeinspritzduese
DE3409924A1 (de) * 1983-03-31 1984-10-11 AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH, Prof. Dr.Dr.h.c. Hans List, Graz Duesenhalter fuer eine kraftstoffeinspritzduese
EP0239259A1 (fr) * 1986-03-21 1987-09-30 General Motors Corporation Buse d'injection de carburant à commande hydraulique à injection en deux phases
DE3712310A1 (de) * 1986-04-11 1987-10-29 Nippon Denso Co In einer kraftstoffeinspritzvorrichtung fuer eine brennkraftmaschine verwendetes kraftstoffeinspritzventil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002086305A3 (fr) * 2001-04-21 2003-01-03 Bosch Gmbh Robert Dispositif d'injection de carburant pour moteur a combustion
WO2004055356A1 (fr) * 2002-12-13 2004-07-01 Robert Bosch Gmbh Injecteur de carburant a vitesse d'aiguille commandable

Also Published As

Publication number Publication date
DE3907569A1 (de) 1990-09-13
JPH02271064A (ja) 1990-11-06

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