EP0096312B1 - Kraftstoff-Einspritzdüse für Brennkraftmaschinen - Google Patents

Kraftstoff-Einspritzdüse für Brennkraftmaschinen Download PDF

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Publication number
EP0096312B1
EP0096312B1 EP83105257A EP83105257A EP0096312B1 EP 0096312 B1 EP0096312 B1 EP 0096312B1 EP 83105257 A EP83105257 A EP 83105257A EP 83105257 A EP83105257 A EP 83105257A EP 0096312 B1 EP0096312 B1 EP 0096312B1
Authority
EP
European Patent Office
Prior art keywords
valve needle
damping
stroke
fuel
return spring
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.)
Expired - Lifetime
Application number
EP83105257A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0096312A1 (de
Inventor
Dietrich Dipl.-Ing. Trachte
Helmut Ing. Grad. Giess
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
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Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0096312A1 publication Critical patent/EP0096312A1/de
Application granted granted Critical
Publication of EP0096312B1 publication Critical patent/EP0096312B1/de
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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

Definitions

  • the one controlling the opening cross section Valve needle coupled to a damping device.
  • the damping device which has a damping chamber formed by a piston and a cylinder and can be acted upon by a throttle, is designed in such a way that the damping already before Is made ineffective at the end of the opening stroke of the valve needle.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that a damping of the opening movement of the valve needle and the spraying time which largely corresponds to the requirements is automatically set at each operating point of the internal combustion engine.
  • damping always takes place immediately at the beginning of the opening stroke of the valve needle.
  • the mutually movable parts of the damping device consisting of cylinder and piston always return to their starting position when the valve needle closes.
  • the invention is based on the knowledge that the time between two injection processes becomes shorter with increasing speed and that there is a greater stroke of the valve needle with larger injection quantities.
  • the time of activation of the damping means for the next opening stroke of the valve needle is delayed compared to the time of the beginning of this opening stroke, the greater the previous valve needle stroke was and ever shorter the time between successive strokes, ie the greater the speed of the internal combustion engine.
  • the valve needle can therefore perform an undamped partial stroke at the beginning of an opening stroke, the length of which is automatically matched to the respective operating parameters of the internal combustion engine.
  • the damping effect can be changed by shifting the start of damping from the start of injection. It is thereby achieved that the entire duration of an injection process at high speed and a large quantity can be shortened even further compared to an arrangement with initial damping of the valve needle, although a long spraying duration is maintained at low speed / quantity.
  • the duration of an injection process can be made so short that when the injection system is adapted to the operating conditions, the injection duration can be changed within further limits than before.
  • the arrangement could also be such that the damping remains effective over the entire opening stroke of the valve needle in the lower speed and load range or only in the critical point of idling. In some cases it could also be advisable to delay the damping means a minimum, i.e. to provide a minimum free stroke of the valve needle, which is present in all operating points of the internal combustion engine.
  • the piston of the damping device is formed by the inlet-side end section of the valve needle 26 and serves as a cylinder a cap attached to this end section.
  • FIG. 1 shows an injection nozzle for a diesel internal combustion engine in longitudinal section
  • FIGS. 2 to 4 show functional diagrams of the sequence of movements of the valve needle 26 and the cap 48 of the injection nozzle according to FIG. 1 belonging to a damping device, specifically FIG. 2 in principle, FIG. 3 at low speed - / Load range and Figure 4 in the high speed / load range of an internal combustion engine.
  • the injection nozzle according to FIG. 1 has a nozzle body 10 which is clamped to a nozzle holder 14 by a union nut 12.
  • a sleeve 16 Arranged between the nozzle body 10 and the nozzle holder 14 is a sleeve 16 which has an inwardly directed shoulder 18 which divides a chamber 20 from a chamber 22 of larger diameter inside the injection nozzle.
  • a valve seat 24 is formed in the nozzle body 10 and a valve needle 26 is displaceably mounted, the sealing cone 27 of which is pressed against the valve seat 24 by a closing spring 28.
  • the closing spring 28 is supported on the nozzle body 10 and engages via a flange part 30 on a support disk 32, which in turn is supported on a shoulder 34 det valve needle 26.
  • an inlet bore 36 is formed, which opens into the chamber 20, which is connected to the chamber 22 via an opening 38 surrounded by the shoulder 18. From this, a bore 40 in the nozzle body 10 leads into an annular space 42, which is formed between the central bore wall of the nozzle body 10 and the circumference of a section 44 of the valve needle 26 with a reduced diameter and extends up to the valve seat 24. Between the flange part 30 and the nozzle body 10 there is a distance hg in the illustrated closed position, which corresponds to the total stroke of the valve needle 26. The valve needle 26 is displaced outward in the opening direction by the fuel pressure against the closing spring 28 until the flange part 30 strikes the nozzle body 10. When the valve closes, the closing spring 28 returns the valve needle 26 inward to the closed position shown.
  • a piston-shaped extension 46 adjoins the shoulder 34 of the valve needle 26, which extends through the opening 38 and projects into the chamber 20.
  • the diameter of the piston-shaped extension 46 corresponds to the guide diameter of the valve needle 26.
  • a cap 48 is placed on the extension 46, which has a bottom 50, a jacket part 52 and a flange edge 54.
  • a return spring 56 engages on the cap 48, which surrounds the jacket part 52 and presses the flange edge 54 against the collar of the sleeve 16.
  • transverse slots 58 are provided, through which the fuel can always pass from the chamber 20 into the chamber 22, even when the valve needle is closed.
  • a damping chamber 60 is formed in the cap 48 between the end face of the projection 46 and the base 50, which is connected to the flow path of the fuel in a throttled manner via a throttle bore 62 in the base 50.
  • the projection 46 covers the transverse slots 58 in the axial direction by the path h "which is greater than the total stroke hg of the valve needle 26.
  • the path h i could also be smaller by a minimal amount than the total stroke hg, so that there is still a small undamped partial stroke at the end of an opening stroke of the valve needle 26.
  • the throttle bore 62 could also be partially or completely replaced by a corresponding radial play between the cap 48 and the shoulder 46.
  • the piston-shaped extension 46 of the valve needle 26 and the cap 48 simultaneously form the means for damping the valve needle movement and a time-displacement element, which makes the beginning of the damping dependent on the speed and the size of the valve needle stroke.
  • the damping effect and the time-displacement function are determined by appropriate coordination of the return spring 56 with the throttle bore 62 and others, the inflow and outflow of the fuel into the damping chamber 60 and parameters determining it.
  • the closing stroke of the valve needle 26 is to begin, at which the cap 48 is pushed from the first end position E i to the second end position E2.
  • the cap 48 travels a path ag which, as already mentioned, is somewhat smaller than the total stroke hg of the valve needle 26.
  • the closing stroke is currently point t 2 ended. From then on, the cap 48 begins to move back under the influence of the return spring 56 at a predetermined speed, which is shown in the diagram as the angle a.
  • a new opening stroke of valve needle 26 begins at time t 3. If, as shown in FIG. 2, cap 48 has not yet reached its first end position again at time t 3 , it moves into this end position at approximately the same speed as valve needle 26 returned. It then reaches the first end position at time t 4 . From then on, the cap 48 is held by the shoulder 18 against a further movement in the opening direction of the valve needle 26, as a result of which the damping means described become effective again. This can be seen in the diagram in that the stroke curve has a break point K at time t4. From time t 4 the valve needle 26 is transferred to the stroke end position at a damped, ie at a reduced speed, whereupon the game described is repeated.
  • FIGS. 3 and 4 illustrate that the damping device according to the invention adapts itself automatically to the various operating states of the internal combustion engine.
  • the internal combustion engine runs at low speed and low load, so that the cap 48 reaches its first end position before the start of the next opening stroke.
  • the damping is effective over the entire opening stroke of the valve needle 26.
  • Figure 4 shows an operating state in which the internal combustion engine is running at high speed under high load, in which a large valve needle stroke also occurs. In this case, the next opening stroke begins before the cap 48 has returned to its first end position.
  • the break point K of the stroke curve h of the valve needle 26 has moved further towards the end of the stroke than in the operating state according to FIG. 2, so that a smaller part of the opening movement of the valve needle 26 is damped.
  • FIG. 4 also makes it clear that the break point K moves towards the end of the opening of the valve needle, the faster the injection processes follow one another and the greater the valve needle stroke.
  • the cap 48 is centered on the valve needle 26 and has a sufficiently large radial play with respect to the nozzle holder 14 so that the valve needle 26 can work without jamming.
  • the return spring 56 extends in part over the cap 48 so that in this embodiment the means for partially damping the opening stroke of the valve needle 26 take up little space in the axial direction of the injection nozzle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP83105257A 1982-06-07 1983-05-27 Kraftstoff-Einspritzdüse für Brennkraftmaschinen Expired - Lifetime EP0096312B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19823221442 DE3221442A1 (de) 1982-06-07 1982-06-07 Kraftstoff-einssritzduese fuer brennkraftmaschinen
DE3221442 1982-06-07

Publications (2)

Publication Number Publication Date
EP0096312A1 EP0096312A1 (de) 1983-12-21
EP0096312B1 true EP0096312B1 (de) 1990-12-19

Family

ID=6165535

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83105257A Expired - Lifetime EP0096312B1 (de) 1982-06-07 1983-05-27 Kraftstoff-Einspritzdüse für Brennkraftmaschinen

Country Status (4)

Country Link
US (1) US4747545A (enExample)
EP (1) EP0096312B1 (enExample)
JP (1) JPS593165A (enExample)
DE (2) DE3221442A1 (enExample)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3408579A1 (de) * 1983-04-02 1984-10-04 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3405161A1 (de) * 1984-02-14 1985-08-22 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
JPS6128331A (ja) * 1984-06-29 1986-02-08 株式会社北陸地所 アワビ育成礁
US5472013A (en) * 1994-07-18 1995-12-05 Outboard Marine Corporation Fuel injection nozzle
US5485818A (en) * 1995-02-22 1996-01-23 Navistar International Transportation Corp. Dimethyl ether powered engine
US5954487A (en) * 1995-06-23 1999-09-21 Diesel Technology Company Fuel pump control valve assembly
US6113012A (en) * 1998-06-25 2000-09-05 Caterpillar Inc. Rate shaped fuel injector with internal dual flow rate office
US6158419A (en) * 1999-03-10 2000-12-12 Diesel Technology Company Control valve assembly for pumps and injectors
US6089470A (en) * 1999-03-10 2000-07-18 Diesel Technology Company Control valve assembly for pumps and injectors
DE10006111A1 (de) * 2000-02-11 2001-08-30 Bosch Gmbh Robert Kraftstoffeinspritzventil
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
WO2004076898A1 (de) * 2003-02-26 2004-09-10 Bosch Rexroth Ag Direktgesteuertes druckbegrenzungsventil
DE102004005451A1 (de) * 2004-02-04 2005-08-25 Robert Bosch Gmbh Kraftstoffeinspritzsystem für Brennkraftmaschinen
US9879645B2 (en) 2016-02-18 2018-01-30 Caterpillar Inc. Control valve bounce limiting mechanism for fuel injectors

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2621015A (en) * 1945-05-28 1952-12-09 Edward Valves Inc Valve construction
US2621016A (en) * 1946-04-15 1952-12-09 Edward Valves Inc Valve construction
GB736794A (en) * 1952-05-13 1955-09-14 David William Edgar Kyle Improvements in liquid fuel injection equipment for internal combustion engines
GB1110102A (en) * 1963-11-26 1968-04-18 Ruston & Hornsby Ltd Improvements in fuel injection equipment for internal combustion engines
IT1059704B (it) * 1975-04-19 1982-06-21 Cav Ltd Unita di ugello di iniezione di combustibile
DE2741634A1 (de) * 1976-09-18 1978-03-23 Lucas Industries Ltd Kraftstoffeinspritzduese
BR7909000A (pt) * 1979-04-13 1981-03-31 Caterpillar Tractor Co Injetor de combustivel
JPS6029674Y2 (ja) * 1979-09-03 1985-09-06 株式会社デンソー 燃料噴射弁
DE3105686A1 (de) * 1981-02-17 1982-09-02 Robert Bosch Gmbh, 7000 Stuttgart "kraftstoffeinspritzduese"
DE3120060A1 (de) * 1981-05-20 1982-12-09 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3220398A1 (de) * 1982-01-26 1983-07-28 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen

Also Published As

Publication number Publication date
US4747545A (en) 1988-05-31
EP0096312A1 (de) 1983-12-21
JPS593165A (ja) 1984-01-09
JPH0429873B2 (enExample) 1992-05-20
DE3221442A1 (de) 1983-12-08
DE3382065D1 (de) 1991-01-31

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