EP1546545B8 - Unite pompe-buse et procede pour reguler la durete de zones d'appui d'une soupape de commande - Google Patents

Unite pompe-buse et procede pour reguler la durete de zones d'appui d'une soupape de commande

Info

Publication number
EP1546545B8
EP1546545B8 EP03750345A EP03750345A EP1546545B8 EP 1546545 B8 EP1546545 B8 EP 1546545B8 EP 03750345 A EP03750345 A EP 03750345A EP 03750345 A EP03750345 A EP 03750345A EP 1546545 B8 EP1546545 B8 EP 1546545B8
Authority
EP
European Patent Office
Prior art keywords
hardness
areas
pump
contact areas
nozzle unit
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
EP03750345A
Other languages
German (de)
English (en)
Other versions
EP1546545A1 (fr
EP1546545B1 (fr
Inventor
Maximilian Kronberger
Christoph Hamann
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.)
Continental Mechatronic Germany GmbH and Co KG
Original Assignee
Siemens VDO Mechatronic GmbH and Co KG
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 Siemens VDO Mechatronic GmbH and Co KG filed Critical Siemens VDO Mechatronic GmbH and Co KG
Publication of EP1546545A1 publication Critical patent/EP1546545A1/fr
Application granted granted Critical
Publication of EP1546545B1 publication Critical patent/EP1546545B1/fr
Publication of EP1546545B8 publication Critical patent/EP1546545B8/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals
    • F02M2200/9061—Special treatments for modifying the properties of metals used for fuel injection apparatus, e.g. modifying mechanical or electromagnetic properties

Definitions

  • the invention relates to a pump-nozzle unit for supplying fuel to a combustion chamber of an internal combustion engine, with a control and / or controllable fuel pump, which comprises a control valve with a valve needle which is deflected by a piezo actuator, the comparatively small stroke of the Piezo actuator is increased by a mechanical translation device to the extent necessary for deflecting the valve needle.
  • the invention relates to a method for adjusting the hardness of at least some arilage areas of a control valve for a pump-nozzle unit for supplying fuel into a combustion chamber of an internal combustion engine that come into contact with a mechanical translation device, the mechanical translation device being provided for one by one to increase a comparatively small stroke caused by a piezo actuator to a level necessary for deflecting a valve needle of the control valve.
  • Pump-nozzle units are used to supply fuel into a combustion chamber of an internal combustion engine.
  • This can be, for example, a pump-nozzle unit with a control and / or controllable fuel pump, a fuel injection nozzle that has a nozzle needle that can be moved back and forth between a closed position and an opening division, a first pressure chamber that is separated from the fuel pump can be filled with fuel under a first pressure, a second pressure chamber, with fuel in the second pressure chamber under a second pressure having a closing exerts force on the nozzle needle, and a third pressure chamber, which communicates with the first pressure chamber, fuel in the third pressure chamber under a third pressure exerting an opening force on the nozzle needle.
  • Pump-nozzle units are used in particular in connection with pressure-controlled injection systems.
  • An essential feature of a pressure-controlled injection system is that the fuel injection nozzle opens as soon as an opening force that is at least influenced by the currently prevailing pressures is exerted on the nozzle needle.
  • Such pressure-controlled injection systems are used for fuel metering, fuel conditioning, shaping the injection process and sealing the fuel supply against the combustion chamber of the internal combustion engine.
  • the time course of the volume flow during the injection can be controlled in an advantageous manner. This can have a positive impact on the performance, fuel consumption and pollutant emissions of the engine.
  • the fuel pump and the fuel injection nozzle are generally designed as an integrated component.
  • at least one pump-nozzle unit is provided, which is usually installed in the cylinder head.
  • the fuel pump u typically includes a fuel pump piston that can be moved back and forth in a fuel pump cylinder and is driven by a camshaft of the internal combustion engine either directly via a tappet or indirectly via rocker arms.
  • the section of the fuel pump cylinder which usually forms the first pressure chamber can be connected to a low-pressure fuel region via a control valve, wherein when the control valve is open, fuel is drawn into the first pressure chamber from the low-pressure fuel region and is pushed back into the low-pressure fuel region from the first pressure chamber when the control valve is still open.
  • the fuel pump piston compresses the fuel in the first pressure chamber and thus builds up pressure.
  • the control valve in the form of a solenoid valve.
  • solenoid valves usually have a relatively long response time, which is due in particular to the fact that the magnet armature of a solenoid valve cannot be accelerated as quickly as desired due to the inertia forces which are dependent on its mass.
  • the build-up of the magnetic field to generate the attractive force also requires time.
  • a pump-nozzle unit equipped with a solenoid valve is known for example from EP 0 277 939 B1.
  • Piezo actuators of a suitable size can only produce a comparatively short stroke. It has therefore already been proposed to provide a mechanical transmission device which increases the comparatively small stroke caused by the piezo actuator to a level necessary for deflecting the valve needle of the control valve.
  • the mechanical transmission device can be formed, for example, by one or more levers.
  • the contact areas of the control valve which come into contact with the mechanical transmission device are loaded with very high pressures and are therefore subject to high wear, although the control valve body forming the contact areas is generally hardened, for example with the aid of an air hardening process.
  • Another problem is that hardening processes that lead to higher hardness also make the material brittle increase. In the case of control valves in which high pressures prevail, this has an adverse effect on the pressure resistance.
  • the object of the invention is to further develop the generic pump-nozzle units and the generic methods in such a way that the susceptibility to wear of the contact areas of the control valve coming into contact with the mechanical transmission device is reduced without adversely affecting the pressure resistance of the control valve.
  • the pump-nozzle unit according to the invention builds on the generic state of the art in that contact areas of the control valve that come into contact with the translation device at least partially have a higher hardness than areas adjacent to these contact areas. This solution makes it possible to optimize the strength of the control valve both with regard to the pressure resistance and the susceptibility to wear of the system areas.
  • the hardness of the areas adjacent to the system areas with higher hardness is set by an air hardening process.
  • Air hardening processes are characterized by the fact that the heated steel is slowly cooled in the air in order to create a martensite of high hardness form. It is desirable to produce a martensite structure that is at least as good as martensite structure that can be produced by oil or salt bath hardening processes.
  • steel compositions can be used, for example, which comprise silicon, manganese and molybdenum in connection with chromium and different carbon contents.
  • the hardness of the contact areas with higher hardness is set by a laser hardening process.
  • the laser hardening process has been applied to material that has already been hardened by an air hardening process.
  • the air hardening process enables the material to be hardened to 680 HV with normal cooling conditions, for example, without the material properties being adversely affected in terms of pressure resistance.
  • the hardness of the system areas can then be increased to, for example, 800 HV using laser beam processes.
  • a laser with a rectangular beam can advantageously be used for hardening, it being possible for the abutment areas to be hardened to be brought briefly to the austenitizing temperature in order to then generate the high hardness, for example after the laser beam has been switched off, by self-quenching.
  • Diode lasers in particular high-power diode lasers, have a very good electrical efficiency (for example a factor of 10 compared to the Nd: YAG laser). They can be realized with an extremely compact design (for example factor 0.1 compared to the C0 2 laser).
  • the material already hardened by an air hardening process is "Ovako 677".
  • the "Ovako 677" steel offered by the company Ovako has better hardening capacity with slow cooling in open air than, for example, a normal DIN 100 Cr 6 steel with fast oil hardening.
  • Another preferred development of the pump nozzle unit according to the invention provides that the contact areas with higher hardness and the areas adjacent to these contact areas are formed in one piece.
  • the system areas with higher hardness have a hardness in the range from 760 HV to 850 HV.
  • a particularly preferred range in this connection extends from 760 HV to 780 HV.
  • the areas adjacent to the plant areas with higher hardness have a hardness in the range from 600 HV to 750 HV.
  • a particularly preferred range extends from 650 HV to 720 HV.
  • the bearing areas with higher hardness are at least partially reground. Good results are achieved, for example, when approximately 50 ⁇ m of the material is ground off.
  • the contact areas with higher hardness have a depth of approximately 0.2 mm.
  • the method according to the invention builds on the generic state of the art in that the contact areas of the control valve that come into contact with the translation device are at least partially post-hardened such that their hardness is higher than the hardness of areas adjacent to these contact areas.
  • the hardness of the areas adjacent to the plant areas with higher hardness was set by an air hardening process.
  • embodiments of the method according to the invention are considered advantageous in which it is provided that that the hardness of the system areas with higher hardness is set by a laser hardening process.
  • the laser hardening process is applied to material already hardened by an air hardening process.
  • the material which has already been hardened by an air hardening method is “Ovako 677”.
  • the contact regions are integrally formed with higher hardness and the areas adjacent to these system areas.
  • the system areas with higher hardness have a hardness in the range from 760 HV to 850 HV, preferably in the range from 760 HV to 780 HV.
  • the areas adjacent to the plant areas with higher hardness have a hardness in the range from 600 HV to 750 HV, preferably in the range from 650 HV to 720 HV.
  • An advantageous development of the method according to the invention provides that the system areas with higher hardness are at least partially reground.
  • the method according to the invention can provide that the contact areas with higher hardness are formed with a depth of approximately 0.2 mm.
  • the hardness of the system areas with higher hardness is set by a diode laser hardening method, the diode laser being operated as a function of an output signal from at least one photodiode which emitted radiation recorded.
  • the emitted radiation can be used to determine the current surface temperature, for example, so that it can be used as a feedback variable, which enables the actuator for the laser diodes to be controlled in such a way that controlled cooling and / or cooling is achieved by switching off the laser becomes.
  • the emitted radiation is thermal radiation.
  • embodiments of the method according to the invention are considered to be particularly advantageous, in which it is provided that the hardness of the system areas with higher hardness is set by a diode laser hardening method, the diode laser being operated as a function of an output signal from at least one photodiode, which detects reflected radiation , Reflected radiation can also be can be used to control and / or regulate the laser diodes.
  • the reflected radiation is laser radiation.
  • An essential basic idea of the invention is to meet the requirements placed on the control valve housing by choosing a material with a lower basic hardness instead of a starting material with a high basic hardness, which material is subsequently hardened by means of a laser beam, in particular in the system areas, which with the mechanical translation device come into contact.
  • FIG. 1 shows a schematic embodiment of a pump-nozzle unit according to the invention, in which the method according to the invention was applied;
  • FIG. 2 shows a schematic partial sectional view of a first embodiment of a control valve which can be used with the pump-nozzle unit according to FIG. 1;
  • Figure 3 is a schematic partial sectional view of a second embodiment of a control valve, which also can be used with the pump-nozzle unit according to Figure 1.
  • FIG. 1 shows schematically a pump-nozzle unit.
  • the pump-nozzle unit shown for supplying fuel 10 to a combustion chamber 12 of an internal combustion engine has a fuel pump 14-22.
  • a fuel pump piston 14 can be moved back and forth in a fuel pump cylinder 16.
  • the fuel pump piston 14 is driven directly or indirectly via a camshaft, not shown, of the internal combustion engine.
  • the compression space of the fuel pump cylinder 16 forms a first pressure space 28.
  • the first pressure space 28 is connected to a piezo control valve 22 via a fuel line 20.
  • the piezo control valve 22 serves to either close the fuel line 20 or to connect it to a low-pressure fuel region 18 from which fuel 10 can be drawn.
  • the pump-nozzle unit shown further comprises a total of 24 designated fuel injection nozzle which has a nozzle needle 46 which can be moved back and forth between a closed position and an open position.
  • a pressure pin 26 can, in relation to the illustration in FIG. 1, in particular exert a downward force on the nozzle needle 46.
  • an adjusting disk 40 is provided, which is guided in a second pressure chamber 30 , fuel 10 in the second pressure chamber 30 under a second pressure p 30 being pressed downward via the pressure pin 26, based on the illustration in FIG directed closing force exerts on the nozzle needle 46.
  • the adjusting disk 40 is preferably sealed only so strongly with respect to the second pressure chamber 30 that the second pressure p 30 has already been reduced again before the start of a new injection cycle.
  • a further closing force which is also directed downward, is exerted by a first spring 36 on the pressure pin 26 and thus the nozzle needle 46, the first spring 36 being arranged in the second pressure chamber 30 and having its rear end supported on the adjusting disk 40.
  • a section of the nozzle needle 46 which has a shoulder 44, is surrounded by a third pressure chamber 32, which communicates with the first pressure chamber 28 via a connecting line 42.
  • a third pressure p 32 is built up in the third pressure chamber 32 as a function of the throttling action of the connecting line 42 and , if appropriate, further throttling devices, not shown, depending on the first pressure p 28 prevailing in the first pressure chamber 28.
  • the nozzle needle 46 assumes its open position as long as there is a difference between the opening force caused by the third pressure p 32 and the sum of the force generated by the second pressure p 30 Closing force and the closing force generated by the first spring 36 exceeds a predetermined value.
  • the nozzle opening pressure can thus be influenced via the second pressure p 30 in the second pressure chamber 30.
  • a pressure limiting and holding valve 34 can be provided between the first pressure chamber 28 and the second pressure chamber 30.
  • FIG. 2 shows a schematic partial sectional view of a first embodiment of a control valve which can be used with the pump-nozzle unit according to FIG. 1.
  • the control valve shown in FIG. 2 is a so-called I-valve, that is to say a valve that closes in the direction of flow from the high-pressure area to the low-pressure area of the control valve.
  • the piezo control valve 22 shown has a valve needle 48 which can be moved into the illustrated first end position for closing the piezo control valve 22 and into a second end position for fully opening the piezo control valve 22, which is related to the
  • valve needle 48 When the valve needle 48 is in its illustrated first end position, a valve disk 64 provided on the valve needle 48 interacts with a valve seat 62 on the housing side. As a result, the low-pressure fuel region 18 becomes one
  • the piezo control valve 22 has a piezo actuator or a piezo element 76.
  • the piezo element 76 When the piezo element 76 is actuated appropriately, it exerts a force on a pressure piece 54 via an end face 78.
  • the pressure piece 54 in turn transmits the force generated by the piezo element 76 to a first lever 56 and a second lever 58, the first lever at 56 and the second lever 58 are provided to effect a force transmission and to increase the valve needle stroke.
  • the first lever 56 and the second lever 58 abut a second axial end surface 72 of the valve needle 48 in order to transmit the translated force generated by the piezo element 76 to the valve needle 48.
  • the translated force generated by the suitably controlled piezo element 76, which acts on the valve needle 48, is greater than an opposite force, which is generated by a second spring 66 and is exerted on a first axial end face 70 of the valve needle 48 via a spring pressure piece 68.
  • the low-pressure fuel region 18 is connected to an exhaust chamber 50, which is also connected via a compensating bore 52 to an actuator chamber 74 located in front of the piezo element 76. This actuator chamber 74 is connected to a return 60 via which fuel can flow back from the actuator chamber 74.
  • the first lever 56 and the second lever 58 which form the mechanical transmission device, come into contact with areas 80, 82 of the control valve housing which have been post-hardened with the aid of a diode laser in such a way that they have a hardness in the range from 760 HV to 780 HV exhibit.
  • the areas 52 of the control valve housing adjacent to the contact areas 80, 82 with higher hardness are formed in one piece with the contact areas 80, 82 (the different hatching only serves to identify the post-hardened areas).
  • the areas 52 adjacent to the system areas 80, 82 have a hardness of 650 HV to 720 HV set by an air hardening process.
  • the steel "Ovako 677" offered by the Ovako company is particularly preferred as the material for the control valve housing.
  • the depth of the contact areas 80, 82 is approximately 0.2 mm, the surface coming into contact with the levers 56, 58 Chen the system areas 80, 82 are reground by a material removal of about 50 microns.
  • FIG. 3 shows a schematic partial sectional view of a second embodiment of a control valve, which can also be used with the pump-nozzle unit according to FIG. 1.
  • the control valve shown in FIG. 3 is a so-called A valve, that is to say a valve which closes in the opposite direction to the flow from the high pressure area to the low pressure area.
  • a valve that is to say a valve which closes in the opposite direction to the flow from the high pressure area to the low pressure area.
  • Such A valves often offer greater security against undesired jamming of the valve needle.
  • the piezo control valve 22 shown has a valve needle 48 which can be moved into the first end position shown for closing the piezo control valve 22 and into a second end position for fully opening the piezo control valve 22, which in relation to the illustration can be seen in FIG is shifted to the right.
  • the piezo control valve 22 has a piezo actuator or a piezo element 76.
  • the piezo actuator 76 When the piezo actuator 76 is actuated appropriately, the end face 78 exerts a force on a first lever 56 and a second lever 58, the first lever 56 and the second lever 58 forming the mechanical transmission device.
  • the first lever 56 and the second lever 58 rest against a second axial end surface 72 of the valve needle 48 in order to apply the translated force generated by the piezo element 76 to the valve. transfer needle 48.
  • the translated force generated by the suitably controlled piezo actuator 76 which acts on the valve needle 48, is greater than an opposite force, which is generated by a second spring 66 and is exerted on a first axial end face 70 of the valve needle 48.
  • the contact areas 80, 82 which come into contact with the mechanical transmission device formed by the first lever 56 and the second lever 58, are post-hardened with the aid of a laser beam. For the rest, reference is made to the description of FIG. 2.
  • the invention can be summarized as follows:
  • the invention relates to a pump-nozzle unit for supplying fuel into a combustion chamber of an internal combustion engine, with a control and / or controllable fuel pump, which comprises a control valve with a valve needle, which is provided by a Piezo actuator is deflected, the comparatively small stroke of the piezo actuator from a mechanical transmission device to that necessary for deflecting the valve needle
  • control valve housing be made from a material with a comparatively lower basic hardness, for example from Ovako 677, and post-harden the contact areas 80, 82 of the control valve 22 by means of a laser.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

La présente invention concerne une unité pompe-buse qui sert à alimenter en carburant (10) une chambre de combustion (12) d'un moteur à combustion interne, et comprend une pompe à carburant (14-22) commandable et/ou réglable, qui comprend une soupape de commande (22) dotée d'une tige de soupape (48) qui est actionnée par un actionneur piézo-électrique (76), la plus petite course de l'actionneur piézo-électrique (76) étant augmentée par un système de conversion mécanique (56, 58) pour prendre la valeur nécessaire à l'actionnement de la tige de soupape (48). Pour ne pas altérer la résistance à la compression du boîtier de la soupape de commande, tout en mettant à disposition des zones d'appui (80, 82) plus résistantes à l'usure en contact avec le système de conversion mécanique (56, 58), le boîtier de soupape de commande est constitué d'un matériau qui a une rigidité de base plus faible, par exemple Ovako 677, et un recuit au laser de ces zones d'appui (80, 82) de la soupape de commande (22) est réalisé.
EP03750345A 2002-09-12 2003-09-12 Unite pompe-buse et procede pour reguler la durete de zones d'appui d'une soupape de commande Expired - Lifetime EP1546545B8 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10242376 2002-09-12
DE2002142376 DE10242376A1 (de) 2002-09-12 2002-09-12 Pumpe-Düse-Einheit und Verfahren zur Einstellung der Härte von Anlagebereichen eines Steuerventils
PCT/DE2003/003027 WO2004027252A1 (fr) 2002-09-12 2003-09-12 Unite pompe-buse et procede pour reguler la durete de zones d'appui d'une soupape de commande

Publications (3)

Publication Number Publication Date
EP1546545A1 EP1546545A1 (fr) 2005-06-29
EP1546545B1 EP1546545B1 (fr) 2007-06-13
EP1546545B8 true EP1546545B8 (fr) 2007-08-01

Family

ID=31895881

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03750345A Expired - Lifetime EP1546545B8 (fr) 2002-09-12 2003-09-12 Unite pompe-buse et procede pour reguler la durete de zones d'appui d'une soupape de commande

Country Status (4)

Country Link
EP (1) EP1546545B8 (fr)
JP (1) JP2005538306A (fr)
DE (2) DE10242376A1 (fr)
WO (1) WO2004027252A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006031567A1 (de) 2006-07-07 2008-01-10 Siemens Ag Einspritzsystem und Verfahren zum Herstellen eines Einspritzsystems
DE102006042601A1 (de) 2006-09-11 2008-03-27 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2523759B2 (ja) * 1987-02-04 1996-08-14 フエスト − アルピネ オウトモチブ ゲゼルシャフト ミットベシュレンクテル ハフツンク 燃料噴射ノズル
DE4008153A1 (de) * 1990-03-14 1991-09-19 Rexroth Mannesmann Gmbh Fremdkraftbetaetigtes, insbesondere magnetkraftbetaetigtes sitzventil
DE4035589A1 (de) * 1990-11-06 1992-05-07 Gerhard Mangold Verfahren zum haerten metallischer werkstoffe
US5271226A (en) * 1992-04-24 1993-12-21 The United States Of America, As Represented By The Secretary Of Commerce High speed, amplitude variable thrust control
DE4426006A1 (de) * 1994-07-22 1996-01-25 Bosch Gmbh Robert Ventilnadel für ein elektromagnetisch betätigbares Ventil und Verfahren zur Herstellung
DE19726991A1 (de) * 1997-06-25 1999-01-07 Bosch Gmbh Robert Ventil und Verfahren zur Herstellung eines Ventilsitzes für ein Ventil
US6607178B1 (en) * 1997-09-29 2003-08-19 Siemens Aktiengesellschaft Thrust device, fuel injection valve having such a device, and method for manufacturing a thrust transfer element
DE19801612C1 (de) * 1998-01-17 1999-06-02 Robby Dipl Phys Ebert Vorrichtung zur großflächigen Bearbeitung von Werkstücken mittels Laserstrahlen unter Vakuum
DE19833461A1 (de) * 1998-07-24 2000-01-27 Bosch Gmbh Robert Elektromagnetisch betätigbares Ventil
DE10008542A1 (de) * 2000-02-24 2001-09-06 Bosch Gmbh Robert Einspritzeinrichtung
DE10104617A1 (de) * 2001-02-02 2002-08-08 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten

Also Published As

Publication number Publication date
DE10242376A1 (de) 2004-03-25
EP1546545A1 (fr) 2005-06-29
DE50307485D1 (de) 2007-07-26
JP2005538306A (ja) 2005-12-15
EP1546545B1 (fr) 2007-06-13
WO2004027252A1 (fr) 2004-04-01

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