EP1366282A1 - Soupape d'injection - Google Patents

Soupape d'injection

Info

Publication number
EP1366282A1
EP1366282A1 EP01985327A EP01985327A EP1366282A1 EP 1366282 A1 EP1366282 A1 EP 1366282A1 EP 01985327 A EP01985327 A EP 01985327A EP 01985327 A EP01985327 A EP 01985327A EP 1366282 A1 EP1366282 A1 EP 1366282A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve control
chamber
spring plate
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Withdrawn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
EP01985327A
Other languages
German (de)
English (en)
Inventor
Patrick Mattes
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 EP1366282A1 publication Critical patent/EP1366282A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • 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
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention is based on an injection valve, in particular an injection valve for an internal combustion engine, according to the type defined in more detail in the preamble of claim 1.
  • Such an injection valve which is known from practice, is used in particular in connection with common-rail accumulator injection systems for diesel combustion engines.
  • a valve control piston which as a rule forms a structural unit with the nozzle needle, is at least partially enclosed by a space which is connected to a high-pressure connection via a so-called high-pressure supply line and contains fuel.
  • a nozzle needle forming a structural unit with the valve control piston interacts with a correspondingly designed valve seat.
  • a combustion chamber of the internal combustion engine leading opening of the injection valve the fuel injection into the combustion chamber can be controlled.
  • the position of the valve control piston and thus that of the nozzle needle is determined by means of a valve-like valve control module which has, for example, a piezoelectric actuator unit.
  • valve control piston In the case of the injection valve of the type mentioned in the introduction, in which the self-valve-shaped valve control module interacts with two valve seats, the translation between the valve control piston and the valve control module takes place via a valve control chamber arranged between the two, which via an inlet throttle and the high-pressure supply line with one with one Common high-pressure accumulator (common rail) is connected to the high-pressure connection and is connected to the valve control module via an outlet throttle and is connected to the free end, ie connects to the end of the valve control piston facing away from the nozzle needle.
  • Common high-pressure accumulator common rail
  • This structure enables a targeted pressure build-up and pressure reduction in the valve control chamber, triggered by means of the valve control module, described below.
  • valve closing member of the valve control module which interacts, for example, with two valve seats
  • the pressure prevailing in the valve control chamber can be released via the outlet throttle.
  • the valve control piston thus moves in the direction of the valve control module, as a result of which the combustion chamber of the internal combustion engine ne leading opening is released and fuel is injected into the combustion chamber.
  • the pressure in the valve control chamber increases so that the valve control piston and thus the nozzle needle are moved into the closed position. So that the nozzle needle is pressed into its seat, so that the injection valve is sealed off from the combustion chamber and no fuel gets into the latter.
  • the injection valve according to the invention with the features according to the preamble of patent claim 1, which has means for filling the valve control chamber via the first inlet channel with the inlet throttle and the second outlet channel with the outlet throttle, has the advantage that the pressure increased considerably faster in the valve control chamber than in the above-described injection valve according to the prior art, since the valve control chamber is filled not only via the inlet channel but also via the outlet channel if necessary. This in turn means that the valve control piston and thus the nozzle needle are moved into their closed position considerably faster. This also reduces the so-called specimen scatter, ie a larger number of usable parts can be produced with the same manufacturing tolerances.
  • the filling of the valve control chamber via the outlet throttle and the inlet throttle results in flatter quantity characteristics of the injection valve or a reduction in the tolerances in the injection quantity.
  • the injection valve according to the invention also leads to an improvement in the small quantity capacity, i.e. the ability to inject the smallest amounts of fuel into the combustion engine in a controlled manner.
  • the means for filling the valve control chamber are designed such that the spring plate is designed to be displaceable, at least in regions, in the axial direction of the valve.
  • the displacement that takes place when the actuator unit is actuated is preferably carried out by means of the valve closing element, which establishes a connection between the valve chamber and the high-pressure supply line, so that the pressure prevailing in the high-pressure supply line is via both the inlet channel having the inlet throttle and the outlet channel having the outlet throttle , which opens into the valve chamber, acts in the valve control chamber. In this way, a large amount of fluid can be introduced into the valve control chamber in a simple manner.
  • connection which can be established by means of the valve closing member between the valve chamber and the high pressure supply line is designed as an annular gap which is arranged between the spring plate and the valve body region which laterally delimits the valve chamber.
  • This annular gap preferably has a height of 5 to 10 ⁇ m.
  • a line for relieving the valve chamber which generally leads to a fuel tank, can have a return throttle.
  • Figure 1 shows a region of a first embodiment of an injection valve according to the invention relevant to the invention in longitudinal section
  • Figure 2 shows an alternative embodiment of an injection valve according to the invention in a representation corresponding to Figure 1.
  • the embodiment shown in Figure 1 shows a fuel injection valve 1, which is provided for installation in an internal combustion engine of a motor vehicle, not shown here, and is designed as a common rail injector for the injection of preferably diesel fuel.
  • the fuel injection valve 1 comprises, as essential structural units, a nozzle module 2 and a valve control module 3.
  • the nozzle module 2 comprises a valve control piston 4, which is in operative connection with a nozzle needle, not shown here, which controls an opening leading to a combustion chamber of the internal combustion engine, or with the latter forms a structural unit.
  • valve control piston 4 The position of the valve control piston 4 and thus that of the nozzle needle is regulated via the pressure level in a valve control chamber 5 which connects to the free end face 6 of the valve control piston 4 and which is arranged via an inlet channel 7 in which a so-called inlet throttle 8 is arranged is connected to a fuel supply channel 9.
  • the fuel supply channel 9 is connected to a high-pressure accumulator common to several injection valves, a so-called common rail.
  • the fuel guided in the fuel supply channel 9 can thus be under a pressure of up to 1.5 kbar.
  • a spring plate 21 In the nozzle module 2, in which the valve control piston 4 is arranged, a spring plate 21 is also arranged, in which the free end of the valve control piston 4 is guided and which delimits the valve control chamber 5.
  • the spring plate 21 is supported by a spring 22 on a support 23, which in turn is connected to the valve control piston 4.
  • the inlet channel 7 is radially aligned and an outlet channel 24 is axially arranged, in which a so-called outlet throttle 25 is formed and which connects the valve control chamber 5 to a valve chamber 18 of the valve control module 3.
  • the drain channel 24 is released or closed via a valve closing member 14 arranged in the valve chamber 18.
  • the spring plate 21 lies with its end facing the valve closing member 14 against a body 12 of the valve control module 3 and is designed to be axially movable.
  • a valve member 10 cooperating with the valve closing member 14 is actuated via an actuator, not shown here, for example designed as a piezoelectric actuator Unit controlled, which is arranged on the side of the valve control piston 4 and thus facing away from the combustion chamber of the valve member 10.
  • the piezoelectric actuator acts on a first piston 11, which is assigned to the valve member 10 and is referred to as an actuating piston.
  • the valve member 10 is arranged axially displaceably in a longitudinal bore of a valve body 12 and comprises, in addition to the actuating piston 11, a second piston 13, a so-called actuating piston, which serves to actuate the valve closing member 14.
  • the actuating piston 13 itself is actuated via a hydraulic transmission, which acts as a hydraulic chamber
  • the hydraulic translation causes the actuating piston 13 to make a stroke which is increased by the ratio of the piston diameters when the actuating piston 11 of larger diameter is moved a certain distance by means of the piezoelectric actuator.
  • the valve closing member 14 acts with a first valve seat
  • first valve seat 16 as a ball seat and the second valve seat
  • valve chamber 18, in which the valve closing member 14 is arranged is separated from a so-called drain chamber 19 by means of the valve closing member 14 interacting with the first valve seat 16, which in turn serves to relieve the drain chamber 19 and the valve chamber 18
  • Return channel 20 branches off to a force not shown here Fabric storage tank leads.
  • a return throttle can be arranged in the return duct 20.
  • the exemplary embodiment shown in FIG. 2 also represents an injection valve 50, in which, for reasons of clarity, the same reference numerals as in FIG. 1 are used for functionally identical components.
  • the injection valve 50 differs from the injection valve according to FIG. 1 in that it does not have a one-part, but a two-part spring plate 21.
  • This consists of an annular wall area 30, in which the inlet channel 7 leading from the high-pressure supply channel 9 to the valve control chamber 5 with the inlet throttle 8 is arranged, and of a plate-shaped base area 31, which is rather by means of a biasing spring 32, which is located on the end face 6 of the valve control piston 4, is pressed against the valve body region 12 of the valve control module 3 when the actuator is not actuated.
  • the outlet channel 24 connecting the valve control chamber 5 to the valve chamber 18 is with the outlet throttle
  • This construction enables only the plate-shaped base area 31 of the spring plate to be displaced in the direction of the valve control piston 4 and thus in the direction of the axis of the injection valve 50 when the piezoelectric actuator is actuated, whereas the annular wall area 30 of the spring plate remains stationary.
  • Valve body region 12 of the valve control module 3 has a gap designated by “s” in FIG. 2, through which fuel under high pressure and guided in the high-pressure supply channel 9 can flow in the direction of the plate-shaped base region 31.
  • the valve closing member 14 which is embodied here as a hemisphere, is located on the first valve seat 16 assigned to it Via the inlet anal 7, the valve control chamber 5 and the outlet channel 24 with the outlet throttle 25 acting on the valve closing member 14, prevailing in the high-pressure supply channel 9, high pressure or rail pressure against the valve seat 16 designed here as a ball seat.
  • the valve closing member 14 is thus in its first blocking position.
  • the injection valve 1 or 50 is to be opened, that is to say if the injection nozzle which is closed by means of the nozzle needle (not shown here) is to be opened, a voltage is applied to the piezoelectric actuator, " whereupon the latter suddenly changes in the axial direction, ie in the direction of the actuating piston 11
  • the actuating piston 11 is thereby displaced in the direction of the actuating piston 13.
  • This releases one via the hydraulic chamber 15 mediated displacement of the actuating piston 13 in the direction of the valve control piston 4.
  • the valve closing member 14 is also moved in the direction of the valve control piston 4, to the extent that the circular area of the valve closing member 14 rests against the bottom area of the one-piece spring plate 21 (FIG.
  • valve closing member 14 If the valve closing member 14 is not in contact with either the first valve seat 16 or the second valve seat 17, fuel located in the valve chamber 18 flows into the outlet chamber 19 and from there via the return channel 20 into the fuel storage tank.
  • the valve control chamber 5 is relieved via the outlet channel 24, in which the outlet throttle 25 is arranged, so that the pressure in the latter is reduced and the valve control piston 4 is displaced in the direction of the valve control module 3.
  • the opening leading to the combustion chamber of the internal combustion engine is released, so that fuel under high pressure and guided in the high-pressure supply duct 9 is injected into the combustion chamber.
  • the actuating piston 11 is retracted in the direction of the actuator, as a result of which the pressure prevailing in the hydraulic chamber 15 is reduced and the valve closing member and thus the actuating piston 13 are likewise moved in the direction of the piezoelectric actuator. until the valve closing member 14 comes to rest in the first valve seat 16. In the transitional period, the pressure prevailing in the valve control chamber 18 is reduced again, as a result of which the valve control chamber is relieved and the nozzle needle opens.
  • the invention can be used not only in the Cornmon Rail injectors described here as a preferred field of application, but also in general in fuel injectors, if appropriate also those with a so-called single-seat actuator.

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)

Abstract

L'invention concerne une soupape d'injection comprenant au moins un module d'injection (2) qui comporte un piston (4) de commande de soupape coopérant avec une aiguille d'injection et une chambre (5) de commande de soupape délimitée par une rondelle élastique (21) et un côté frontal (6) du piston (4) de commande de soupape. Ladite chambre est en liaison avec une conduite d'alimentation haute pression (9) par l'intermédiaire d'un canal d'amenée (7) et elle est en liaison active, par l'intermédiaire d'un canal de sortie (24), avec un module (3) de commande de soupape se présentant sous la forme d'une soupape actionné par une unité d'actionnement piézo-électrique, ledit module comprenant au moins un élément (14) de fermeture de soupape disposé dans une chambre (18) de soupape et coopérant avec au moins un siège de soupape (16, 17). L'aiguille d'injection est ouverte par une réduction de pression provoquée par le module (3) de commande de soupape dans la chambre (5) de commande de soupape par l'intermédiaire du canal de sortie (24) et elle est fermée par remplissage de la chambre (5) de commande de soupape. Pour permettre une fermeture rapide de l'aiguille d'injection, cette soupape d'injection comprend des moyens pour remplir la chambre (5) de commande de soupape par l'intermédiaire du canal d'amenée (7) et du canal de sortie (24).
EP01985327A 2001-01-05 2001-12-21 Soupape d'injection Withdrawn EP1366282A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10100390 2001-01-05
DE10100390A DE10100390A1 (de) 2001-01-05 2001-01-05 Einspritzventil
PCT/DE2001/004860 WO2002053904A1 (fr) 2001-01-05 2001-12-21 Soupape d'injection

Publications (1)

Publication Number Publication Date
EP1366282A1 true EP1366282A1 (fr) 2003-12-03

Family

ID=7669875

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01985327A Withdrawn EP1366282A1 (fr) 2001-01-05 2001-12-21 Soupape d'injection

Country Status (5)

Country Link
US (1) US20030141472A1 (fr)
EP (1) EP1366282A1 (fr)
JP (1) JP2004517254A (fr)
DE (1) DE10100390A1 (fr)
WO (1) WO2002053904A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10043625C2 (de) * 2000-09-05 2003-03-27 Bosch Gmbh Robert Hydraulisch übersetztes Ventil
DE10122245A1 (de) * 2001-05-08 2002-12-12 Bosch Gmbh Robert Leckagereduzierter druckgesteuerter Kraftstoffinjektor
JP2005529264A (ja) * 2002-02-22 2005-09-29 シーアールティー コモン レールテクノロジーズ エージー 内燃機関用燃料噴射バルブ
DE10250720A1 (de) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Einspritzventil
JP4019934B2 (ja) * 2002-12-26 2007-12-12 株式会社デンソー 制御弁および燃料噴射弁
DE10315489B3 (de) * 2003-04-04 2004-08-26 Robert Bosch Gmbh Kraftstoffinjektor mit Druckübersetzer und in ein Düsenmodul integriertem Dämpfungskolben
DE502004008540D1 (de) * 2003-08-22 2009-01-08 Ganser Hydromag Pilotventil gesteuertes brennstoffeinspritzventil
ATE447104T1 (de) * 2005-04-14 2009-11-15 Ganser Hydromag Brennstoffeinspritzventil
CH697562B1 (de) * 2005-08-09 2008-11-28 Ganser Hydromag Brennstoffeinspritzventil.
WO2007098621A1 (fr) * 2006-03-03 2007-09-07 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs A combustion interne
CN101818711B (zh) * 2010-06-03 2012-02-08 无锡开普动力有限公司 电控喷油器的喷射阀
DE102017101999A1 (de) * 2017-02-01 2018-08-02 Firma L'orange Gmbh Kraftstoff-Einspritzinjektor für eine Brennkraftmaschine
WO2020260285A1 (fr) 2019-06-25 2020-12-30 Ganser Hydromag Ag Soupape d'injection de carburant pour des moteurs à combustion interne

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0426205B1 (fr) * 1985-12-02 1993-07-21 Marco Alfredo Ganser Dispositif de commande d'injecteurs de combustible actionnés électro-hydrauliquement
EP0807757A1 (fr) * 1994-06-06 1997-11-19 Ganser-Hydromag Ag Injecteur de combustible pour moteur à combustion interne
US5732679A (en) * 1995-04-27 1998-03-31 Isuzu Motors Limited Accumulator-type fuel injection system
DE19516565C2 (de) * 1995-05-05 1998-07-30 Orange Gmbh Einspritzventil einer Brennkraftmaschine
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
DE19743640A1 (de) * 1997-10-02 1999-04-08 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19936669A1 (de) * 1999-08-04 2001-02-22 Bosch Gmbh Robert Common-Rail-Injektor
US6499467B1 (en) * 2000-03-31 2002-12-31 Cummins Inc. Closed nozzle fuel injector with improved controllabilty

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02053904A1 *

Also Published As

Publication number Publication date
WO2002053904A1 (fr) 2002-07-11
US20030141472A1 (en) 2003-07-31
JP2004517254A (ja) 2004-06-10
DE10100390A1 (de) 2002-07-25

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