EP1387937B1 - Kraftstoffeinspritzventil für brennkraftmaschinen mit einem druckschwingungen reduzierenden dämpfungsraum - Google Patents

Kraftstoffeinspritzventil für brennkraftmaschinen mit einem druckschwingungen reduzierenden dämpfungsraum Download PDF

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Publication number
EP1387937B1
EP1387937B1 EP02735006A EP02735006A EP1387937B1 EP 1387937 B1 EP1387937 B1 EP 1387937B1 EP 02735006 A EP02735006 A EP 02735006A EP 02735006 A EP02735006 A EP 02735006A EP 1387937 B1 EP1387937 B1 EP 1387937B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
chamber
fuel injection
housing
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
EP02735006A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1387937A1 (de
Inventor
Walter Egler
Peter Boehland
Sebastian Kanne
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 EP1387937A1 publication Critical patent/EP1387937A1/de
Application granted granted Critical
Publication of EP1387937B1 publication Critical patent/EP1387937B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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
    • F02M61/165—Filtering elements specially adapted in fuel inlets to injector

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, which corresponds to the preamble of claim 1.
  • fuel injectors are known in various embodiments from the prior art.
  • a fuel injection valve is described, which is constantly connected to a high-pressure accumulation chamber in which fuel is provided under high pressure.
  • the fuel injection valve has a housing in which a valve member is longitudinally displaceably arranged in a bore, which controls the opening of at least one injection port by its longitudinal movement, is injected by the fuel from a valve member surrounding the pressure chamber into the combustion chamber of the internal combustion engine.
  • a housing in which a piston-shaped valve member is longitudinally displaceably arranged in a bore, which controls the opening of at least one injection opening with its combustion chamber end facing.
  • the valve member is also surrounded by a pressure chamber, which is connectable by the longitudinal movement of the valve member with the injection openings.
  • the pressure chamber is connected via an inlet channel extending in the housing with a high-pressure fuel source, can be supplied by the fuel under high pressure in the pressure chamber.
  • valve member is acted upon by a mechanical device in the housing of the fuel injection valve, preferably a helical compression spring in the closing direction with a closing force, so that it remains in the closed position in the absence of a corresponding hydraulic counterforce and thus closes the injection openings.
  • a mechanical device in the housing of the fuel injection valve preferably a helical compression spring in the closing direction with a closing force, so that it remains in the closed position in the absence of a corresponding hydraulic counterforce and thus closes the injection openings.
  • pressure oscillations arise in the region of the pressure chamber, in particular at the beginning and end of the injection process, which can lead to mechanical loads and correspondingly continuing oscillations to an indefinite state at the beginning of the next injection and which can impair the quality of the subsequent injections ,
  • an injection valve which has a piston with which the fuel is compressed for injection into the pressure chamber.
  • the compressed fuel is supplied to a storage volume from where the fuel enters the pressure chamber of the injection nozzle.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that quickly successive, precisely defined injection operations are possible. Pressure oscillations that occur in the region of the pressure chamber and thus in the immediate vicinity of the injection openings are damped, so that very quickly after the closing operation of the fuel injection valve in the pressure chamber, a static state is reached again.
  • the pressure chamber is connected via a throttle formed in the housing with a damping chamber formed in the housing. If pressure changes occur in the region of the pressure chamber, as caused, for example, by the opening or closing of the valve member, a higher or lower fuel pressure prevails in the pressure chamber than in the damping chamber.
  • the damping chamber is formed as a trained in the housing of the fuel injection valve blind bore.
  • the blind bore opens directly into the pressure chamber, the throttle preferably being close to the pressure chamber. Due to the design of the damping chamber in the form of a blind bore of the damping chamber in the housing can be easily and inexpensively manufactured.
  • more than one throttle is arranged in the housing, which forms the connection from the damping chamber to the pressure chamber.
  • the valve member is arranged in a valve body, while the damping chamber is formed in a valve holding body, wherein both the valve body and the valve holding body are part of the housing.
  • an intermediate disc is arranged, through which the connection passes from the pressure chamber to the damping chamber.
  • the throttle is arranged so that a replacement of the intermediate disc against an intermediate disc with a modified throttle a slight replacement of the throttle and thus an adaptation of the damping effect to different fuel injection valves is possible without the other construction of the fuel injection valve must be changed.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention, together with the high-pressure fuel supply shown schematically.
  • the fuel injection valve has a housing 12 which includes a valve holding body 15 and a valve body 32.
  • a bore 34 is formed, in which a piston-shaped valve member 35 is arranged longitudinally displaceable.
  • the valve member 35 is sealingly guided in a bore away from the combustion chamber in the bore 34 and tapers to form a pressure shoulder 36 to the combustion chamber.
  • a pressure chamber 37 is formed in the valve body 32 by a radial extension of the bore 34, which continues as a valve member 35 surrounding the annular channel to the combustion chamber end of the bore 34.
  • the valve member 35 controls the opening of at least one injection port 39, which connects the pressure chamber 37 with the combustion chamber of the internal combustion engine.
  • a valve sealing surface 40 is formed at the combustion chamber end of the valve member 35, which cooperates with a formed on the combustion chamber end of the bore 34 valve seat 41.
  • the high pressure port 8 is connected via a high pressure line 7 to a high pressure accumulator 5, in which fuel is present at a predetermined high pressure, the fuel is the high pressure accumulator 5 from a fuel tank 1 via a high pressure pump 2 and a fuel line 4 is supplied.
  • a spring chamber 28 is formed in the valve holding body 15, in which a helical compression spring 30 is arranged.
  • the helical compression spring 30 in this case has a compressive bias and acts with its valve member 35 facing the end of the valve member 35 in the closing direction.
  • a piston bore 27 is formed in the valve holding body, which opens into the spring chamber 28 and in which a piston rod 26 is arranged, which rests with its end facing the combustion chamber on the valve member 35 and the combustion chamber facing away from a control chamber 20 limited.
  • the control chamber 20 is in this case connected via an inlet throttle 19 to the inlet channel 14 and via an outlet throttle 17 with a formed in the valve holding body 15 leakage oil chamber 23 which is connected to a drain oil, not shown in the drawing and thereby constantly has a low pressure.
  • a magnet armature 22 is arranged, which is acted upon by a closing spring 31 in the direction of the control chamber 20 and to which a sealing ball 29 is fixed, which closes the outlet throttle 17.
  • an electromagnet 24 is also arranged, which exerts an attractive force against the force of the closing spring 31 on the armature 22 and moves it away from the control chamber 20, whereby the control chamber 20 is connected to the leakage oil chamber 23 with appropriate energization. If the electromagnet 24 is de-energized, then the armature 22 moves by the force of the closing spring 31 again in the direction of the control chamber 20 and closes with the sealing ball 29, the outlet throttle 17th
  • a damping chamber 46 is formed, which is designed as a blind bore and whose open end is arranged on the valve body 32 facing the end face of the valve holding body 15.
  • the the damping chamber 46 forming blind bore extends parallel to the piston bore 27 and is connected via a valve body 32 formed in the connection 42 with the pressure chamber 37.
  • a throttle 44 is arranged, which is formed by a cross-sectional constriction of the connection 42. If there is a pressure difference between the pressure chamber 37 and the damping chamber 46, fuel can flow from one into the other space via the connection 42 and the throttle 44, thus leading to a pressure equalization.
  • the operation of the fuel injection valve is as follows: Through the connection of the pressure chamber 37 with the high pressure accumulator 5 via the inlet channel 14 and the high pressure line 7 prevails in the pressure chamber 37 is always a high fuel pressure, as it is also maintained in the high-pressure accumulator 5. If an injection takes place, the solenoid 24 is actuated and the armature 22 is in the manner described above, the outlet throttle 17 free. As a result, the fuel pressure in the control chamber 20 decreases, and the hydraulic force to the combustion chamber facing away from the end of the piston rod 26 is reduced, so that the hydraulic force on the pressure shoulder 36 outweighs and the valve member 35 is moved in the opening direction, whereby the injection openings 29 are released.
  • the increase in pressure thus caused leads to a pressure difference between the pressure chamber 37 and damping chamber 46, where at least approximately still prevails the pressure that was present in the pressure chamber 37 before the start of injection.
  • this pressure difference some fuel from the pressure chamber 37 flows through the connection 42 and the throttle 44 in the damping chamber 46 and from there according to the pressure difference between the damping chamber 46 and pressure chamber 37 back into the pressure chamber 37.
  • the throttle 44 friction work must be done , Which dampen these pressure oscillations quickly, so that after a short time in the pressure chamber 37 again a static pressure level is reached. For the subsequent injection thus there is a defined pressure state in the pressure chamber 37, which allows a correspondingly accurate and precise injection.
  • FIG. 2 shows a further embodiment of the fuel injection valve according to the invention is shown in longitudinal section.
  • the damping of the pressure oscillations takes place in this fuel injection valve in the same manner as in the fuel injection valve shown in Figure 1, but the other components and the operation are different.
  • a valve holding body 50 is clamped with the interposition of an intermediate disc 52 by means of a clamping nut 55 against a valve body 54.
  • the valve body 54 has a bore 57 is formed, in which a valve member 60 which is formed piston-shaped, is arranged longitudinally displaceable.
  • the valve member 60 has at its combustion chamber end facing a sealing surface 62 which cooperates with a formed on the combustion chamber end of the bore 57 valve seat 64 and thus controls the opening of at least one arranged in the valve seat 64 injection port 66.
  • a pressure shoulder 61 is formed on the valve member 60, at its height by a cross-sectional widening of the bore 57, a pressure chamber 68 is formed, which is connected via a formed in the valve body 54 of the washer 52 and the valve holding body 50 inlet channel 58 to a high-pressure port 56.
  • the high-pressure connection 56 is connected to a high-pressure fuel source, not shown in the drawing, which can supply fuel under high pressure into the high-pressure connection 56 and through the inlet channel 58 to the pressure chamber 68.
  • valve member 60 Facing away from the combustion chamber, the valve member 60 merges into a spring plate 74, which is arranged in an opening of the intermediate disc 52 and projects into a spring space 70 formed in the valve holding body 50. Between the spring plate 74 and the combustion chamber remote from the end of the spring chamber 70, a closing spring 72 is arranged, which is designed as a helical compression spring and has a compressive bias, so that a closing force is exerted on the valve member 60. In the pressure chamber 68 opens a connection 76 which is connected via a formed in the intermediate disc 52 throttle 78 with a formed in the valve holding body 50 damping chamber 80.
  • the throttle 78 is formed by a cross-sectional reduction of the connection 76, wherein it may also be provided to arrange more than one throttle 78 in the washer 52.
  • the damping chamber 78 is, as already in the embodiment shown in FIG. 1, designed as a blind bore which runs parallel to the longitudinal axis of the spring chamber 70 and the bore 57. The length of the blind bore and thus the volume of the damping chamber 80 can be varied depending on the desired damping effect. If an injection takes place, then fuel is introduced into the high-pressure port 56, so that the fuel flows through the inlet channel 58 to the pressure chamber 68.
  • the design of the throttle 78 in the washer 52 is particularly advantageous because replacement of the washer 52, another throttle 78 can be installed in the connection of the pressure chamber 68 with the damping chamber 80 without further structural changes would be necessary to the fuel injector. Alternatively, however, it may also be provided to arrange the throttle 78 still within the valve body 54, for example directly at the pressure chamber 68.
  • the damping chamber 46 in FIG. 1 or the damping chamber 80 in FIG. 2 is not formed as a blind bore, but as a cavity in the housing of the fuel injection valve, which can be any one Can take shape.
  • the spatial possibilities of the fuel injection valve can be used optimally, without having to make structural changes to the existing functional components.
  • it may be provided to arrange more than one throttle 44, 78 in the connection of the pressure chamber 37, 68 to the damping chamber 46, 80. In this way, an optimal damping behavior of the throttle 44, 78 can be achieved.

Landscapes

  • 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)
EP02735006A 2001-05-05 2002-03-22 Kraftstoffeinspritzventil für brennkraftmaschinen mit einem druckschwingungen reduzierenden dämpfungsraum Expired - Lifetime EP1387937B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10121891A DE10121891A1 (de) 2001-05-05 2001-05-05 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10121891 2001-05-05
PCT/DE2002/001037 WO2002090753A1 (de) 2001-05-05 2002-03-22 Kraftstoffeinspritzventil für brennkraftmaschinen mit einem druckschwingungen reduzierenden dämpfungsraum

Publications (2)

Publication Number Publication Date
EP1387937A1 EP1387937A1 (de) 2004-02-11
EP1387937B1 true EP1387937B1 (de) 2007-08-22

Family

ID=7683740

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02735006A Expired - Lifetime EP1387937B1 (de) 2001-05-05 2002-03-22 Kraftstoffeinspritzventil für brennkraftmaschinen mit einem druckschwingungen reduzierenden dämpfungsraum

Country Status (5)

Country Link
US (1) US7172140B2 (ja)
EP (1) EP1387937B1 (ja)
JP (1) JP4154243B2 (ja)
DE (2) DE10121891A1 (ja)
WO (1) WO2002090753A1 (ja)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10232193A1 (de) * 2002-07-16 2004-02-05 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10352736A1 (de) * 2003-11-12 2005-07-07 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadeleinspritzung
DE102004024926A1 (de) * 2004-05-19 2005-12-15 Volkswagen Mechatronic Gmbh & Co. Kg Pumpe-Düse-Einheit
DE102007025617A1 (de) * 2007-06-01 2008-12-04 Robert Bosch Gmbh Kraftstoffinjektor mit geringem Verschleiß
DE102008012637A1 (de) * 2008-03-05 2009-09-10 Robert Bosch Gmbh Kraftstoffinjektor
US9897058B2 (en) 2009-07-29 2018-02-20 Delphi International Operations S.A.R.L. Fuel injector
ATE552420T1 (de) * 2009-07-29 2012-04-15 Delphi Tech Holding Sarl Kraftstoffeinspritzdüse
AT509877B1 (de) * 2010-11-02 2011-12-15 Bosch Gmbh Robert Vorrichtung zum einspritzen von kraftstoff in den brennraum einer brennkraftmaschine
DE102010064057A1 (de) 2010-12-23 2012-06-28 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
AT512960B1 (de) * 2012-05-22 2014-03-15 Bosch Gmbh Robert Injektor eines modularen Common-Rail-Kraftstoffeinspritzsystems
GB201420051D0 (en) * 2014-11-11 2014-12-24 Delphi International Operations Luxembourg S.�.R.L. Fuel injector
DE102016218669A1 (de) * 2016-09-28 2018-03-29 Robert Bosch Gmbh Haltekörper für einen Kraftstoffinjektor, Kraftstoffinjektor mit Haltekörper sowie Verfahren zur Herstellung eines Haltekörpers
RU2731155C1 (ru) * 2019-07-05 2020-08-31 федеральное государственное бюджетное образовательное учреждение высшего образования "Московский политехнический университет" (Московский Политех) Форсунка с электрогидравлическим управлением
CN114458498B (zh) * 2022-02-24 2022-10-28 哈尔滨工程大学 一种基于节流阻容效应实现高稳定喷射的高压共轨喷油器
CN116006366B (zh) * 2023-03-24 2023-06-09 哈尔滨工程大学 一种基于阻容部件自适应调节实现燃油稳定喷射的电控喷油器
CN116085159B (zh) * 2023-03-31 2023-07-21 哈尔滨工程大学 一种基于多级自调压力耗散实现稳定喷射的共轨喷油器

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3332808A1 (de) 1983-09-12 1985-03-28 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
US5241935A (en) 1988-02-03 1993-09-07 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
US5467754A (en) 1988-02-03 1995-11-21 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
DE4340305C2 (de) * 1993-11-26 1998-02-19 Daimler Benz Ag Kraftstoffeinspritzdüse für eine Brennkraftmaschine
DE4440182C2 (de) 1994-11-10 2003-09-18 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US5752659A (en) * 1996-05-07 1998-05-19 Caterpillar Inc. Direct operated velocity controlled nozzle valve for a fluid injector
GB9906092D0 (en) * 1999-03-18 1999-05-12 Lucas France Fuel injector

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP4154243B2 (ja) 2008-09-24
DE50210758D1 (de) 2007-10-04
JP2004519596A (ja) 2004-07-02
WO2002090753A1 (de) 2002-11-14
DE10121891A1 (de) 2002-11-07
EP1387937A1 (de) 2004-02-11
US20040061002A1 (en) 2004-04-01
US7172140B2 (en) 2007-02-06

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