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WO2009074427A1 - Soupape de commande pour injecteurs - Google Patents

Soupape de commande pour injecteurs Download PDF

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Publication number
WO2009074427A1
WO2009074427A1 PCT/EP2008/065629 EP2008065629W WO2009074427A1 WO 2009074427 A1 WO2009074427 A1 WO 2009074427A1 EP 2008065629 W EP2008065629 W EP 2008065629W WO 2009074427 A1 WO2009074427 A1 WO 2009074427A1
Authority
WO
WIPO (PCT)
Prior art keywords
closing element
switching valve
liquid
damping chamber
sleeve
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.)
Ceased
Application number
PCT/EP2008/065629
Other languages
German (de)
English (en)
Inventor
Matthias Burger
Hans-Christoph Magel
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 WO2009074427A1 publication Critical patent/WO2009074427A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • 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
    • 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
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a switching valve for injectors, in particular for fuel injectors, according to the preamble of claim 1.
  • Fuel injectors are used to supply fuel to combustion chambers of an internal combustion engine.
  • the fuel is injected under high pressure into the combustion chambers.
  • high-pressure accumulator injection systems are used in which the injection pressure is independent of the speed and load of the internal combustion engine.
  • the pollutants resulting from the combustion can be reduced.
  • a significant increase in the injection pressure is necessary.
  • Fuel injectors which can be used at the required pressures, are leak-free. For this purpose, a low-pressure stage is dispensed with. Due to the absence of the low-pressure stage, however, only small needle closing forces are available. This leads to steep maps and thus to a poor Kleinstmengenmen. However, this disadvantage can be compensated with very fast switching valves.
  • a control valve for a fast-switching fuel injection valve is known for example from DE 10 2007 028 485.
  • a pressure chamber is limited by a control sleeve which is movably mounted in its longitudinal direction.
  • the control sleeve has on a front side on a sealing surface, with which it cooperates with a valve seat which is formed on a valve body.
  • a recess in the side of the valve body facing the pressure chamber is formed in the valve body.
  • the control sleeve and the recess in the valve body are designed so that a deformation of the control sleeve and valve body by the pressure in the pressure chamber to no or only very little movement between the valve seat and the sealing surface of the control sleeve leads.
  • fast-switching valves have the disadvantage that due to a bounce characteristic waviness occur.
  • On the one hand results in a bouncing of the closing element due to a hard stop in conjunction with a fast closing element.
  • the hard hit results from the bouncing of metal on metal.
  • these bumpers which occur when the closing element opens, have a negative influence on the function of the fuel injector and generally lead to large lift / stroke spreads.
  • solenoid-operated switching valves a squish gap is formed at the upper stroke stop between armature and magnet, which dampens the stop and thus reduces bouncing.
  • such a nip can not be attached to the valve seat due to its sealing functions in order to reduce the impact of the closing element in the valve seat.
  • An inventively designed switching valve for injectors in particular for fuel injectors, comprises a closing element with which a control chamber for actuating an injection valve member is pressure-relieved.
  • the closing element is driven by a magnetic actuator comprising a magnet assembly and an armature.
  • the closing element is guided in a sleeve accommodated in a stationary manner in the injector, wherein the sleeve has a diameter widening and the closing element has a collar and the collar is guided in the diameter widening, so that a damping space is enclosed by the sleeve and the closing element such that the volume of the sleeve Damping space when opening the switching valve increases and is reduced again when closing.
  • the damping chamber is filled with liquid. Due to the increase in volume when opening the switching valve, the pressure in the damping chamber drops to the vapor pressure and the liquid begins to boil at a constant pressure and evaporate. When the switching valve closes again and thereby reduces the volume of the damping chamber, the liquid condenses again. At the moment in which the closing element closes the switching valve by the closing element strikes, the damping chamber is again completely filled with liquid. Further movement of the closing element in the direction of the valve seat leads to a further volume reduction of the damping space and thus to a strong pressure increase. By this, the movement of the closing element is damped and a large part of the impact energy is absorbed by the liquid in the damping chamber. The energy with which the closing element strikes the valve seat is reduced and as a result a bouncing or sitting avoided. Furthermore, a swing through, which is due to the elasticity of the closing element and the valve seat, avoided.
  • the closing element is guided on a guide pin.
  • the closing element has an annular sealing surface or sealing edge and a constant over its entire length inner diameter in which the guide pin is guided, on. Due to the constant inner diameter pressure forces act in the interior of the closing element only in the radial direction. The closing element is pressure balanced. Due to the pressure equalization even small valve closing forces are sufficient to lead to a switching of the switching valve. A quick switching is possible through this.
  • the guide pin preferably has an upper and a lower guide on which the closing element is guided. Furthermore, a leakage collection space surrounds the guide pin between the upper guide and the lower guide. Via the lower guide, which acts as a leakage gap, liquid can pass from the high-pressure region of the injector into the leakage collection space.
  • the pressure in the Leckagesammeiraum is adjusted so that the liquid in the Leckagesammeiraum is free of gas.
  • the damping chamber is preferably connected via a channel in the closing element with the Leckagesammeiraum. Through the channel of the damping chamber can be filled with liquid. Due to the pressure of the liquid in Leckagesammeiraum and the liquid in the damping chamber with the switching valve is closed gas.
  • the adjustment of the pressure in the Leckagesammeiraum is carried out by a leakage gap on the upper guide. This is adjusted so that it acts as a throttle and thereby the pressure in the Leckagesammeiraum can be adjusted.
  • the cross-section of the channel through which the damping chamber is connected to the Leckagesammeiraum is preferably selected so that the channel acts as a throttle, so that no liquid flows from the Leckagesammeiraum in the damping chamber with open switching valve. This ensures that the liquid volume in the damping chamber does not change when the switching valve is open and the movement of the closing element is not dampened by an excessive amount of liquid in the damping chamber before the sealing edge of the closing element strikes in the valve seat. The subsequent flow of liquid from the Leckagesammeiraum in the damping chamber is avoided with appropriate cross-section also due to the short switching times of the switching valve. If a lifting drift occurs, eg due to seat wear, this can be compensated by the switching valve according to the invention. Since the damping chamber is filled when the switching valve is closed, between two closing operations of the switching valve is always exactly the amount of liquid contained in the damping chamber, which is required to dampen the movement of the closing element and thus prevent bouncing when fully closing the switching valve.
  • the invention further relates to a method for driving a switching valve for injectors, in particular for fuel injectors, wherein the switching valve comprises a closing element, which is guided in a sleeve, and the sleeve has a diameter extension and the closing element has a collar.
  • the collar is guided in the diameter widening, so that a damping space is enclosed by the sleeve and the closing element, which is completely filled with liquid when the switching valve is closed.
  • the liquid in the damping chamber When opening the switching valve, the liquid in the damping chamber at least partially evaporated at constant pressure and the condensed liquid is condensed again, so that at the time of impact, the entire liquid is condensed and at least a portion of the impaction pulse is absorbed by the liquid in the damping chamber , By absorbing the impact pulse through the liquid in the damping chamber of the closing pulse is destroyed, thus preventing bouncing of the closing element. By preventing bouncing of the closing element and the seat wear is significantly reduced or even completely prevented.
  • the damping chamber is preferably filled with liquid from a leak collecting chamber when the switching valve is closed.
  • Advantage of filling the damping chamber with liquid from the Leckagesammeiraum is that the Leckagesammeiraum is generally in hydraulic communication with a high pressure region of the injector and thus in the Leckagesammeiraum a higher pressure than in the low pressure region of the injector. In this way it is ensured that the liquid entering the damping chamber is free of gas bubbles.
  • the single FIGURE shows a schematic representation of a fuel injector with a switching valve designed according to the invention.
  • the single FIGURE shows a schematic representation of a fuel injector with a switching valve designed according to the invention.
  • a fuel injector 1 comprises an injection valve member 3, with which at least one, not shown here injection port for injecting fuel into a combustion chamber of an internal combustion engine can be released or closed.
  • the injection valve member 3 is guided in a valve piece 5 and delimited with an upper end face 7 a control chamber 9.
  • the control chamber 9 is filled via an inlet throttle 11 with fuel under system pressure.
  • the inlet throttle 11 connects the control chamber 9 with an annular space 13, which surrounds the valve piece 5 and in turn is connected to a high-pressure accumulator, not shown here, via an inlet channel 15.
  • the control chamber 9 In order to release the at least one injection opening, the control chamber 9 is depressurized.
  • a switching valve 17 opens, whereby a connection from a flow channel 19 is released to a fuel return line 21 and fuel can flow out of the control chamber 9.
  • the pressure in the control chamber 9 decreases and the injection valve member 3 rises from its valve seat and releases the injection port.
  • a throttle element 23 is formed in the outlet channel 19.
  • the switching valve closes the connection from the outlet channel 19 to the return line 21.
  • fuel under system pressure flows into the control chamber 9, the pressure in the control chamber 9 increases. Due to the increasing pressure force, the injection valve member 3 is placed back in his seat and closes the at least one injection port.
  • the closing movement of the injection valve member 3 is supported by a spring element 25.
  • the spring element 25 is preferably designed as a helical spring compression spring.
  • valve piece 5 in which the injection valve member 3 is guided, is mounted in the injector housing 29 with a valve clamping nut 27.
  • the switching valve 17, with which the opening and closing of the fuel injector for injecting fuel into the combustion chamber of the internal combustion engine is controlled, includes a closing element 31.
  • the closing element 31 has a sealing edge 33 which is placed in a valve seat 35 for closing.
  • the switching valve 17 is pressure balanced.
  • the sealing edge 33 is annular.
  • the closing element 31 has a constant inner diameter 37. In this way, the pressure of the under system pressure fuel acts only in the radial direction on the closing element 31. Thus act on opposite surfaces on the closing element 31 always only the same pressure forces.
  • the closing element 31 is pressure balanced.
  • a guide pin 39 In order to avoid that the closing element 31 tilts or slips in the radial direction, this is guided on a guide pin 39.
  • the guide pin ends with a lower end face 41 above the drainage channel 19 and thus delimits, together with the closing element 31, a pressure chamber 43. With the side opposite the pressure chamber 43, the guide pin 39 rests against the injector housing. A displacement of the guide pin 39 is avoided in that it is pressed against the injector housing with a spring element 45.
  • the spring element 45 is preferably designed as a compression spring coil spring. With one side, the spring element 45 acts against an end face on an extension 47 of the guide pin and with another side on the closing element 31. By the spring force of the spring element 45 on the closing element 31 this is provided with closed switching valve 17 in the valve seat 35.
  • the closure member 31 is further connected to an armature 49.
  • the armature 49 cooperates with a magnet assembly 51 through which the switching valve 17 is actuated.
  • the magnet assembly 51 generally includes a solenoid 53 and a core 55 that surrounds the coil 53.
  • the switching valve 17 To start the injection process, the switching valve 17 must be opened.
  • the coil 53 is energized.
  • a magnetic field is formed by which the armature 49 is attracted and moves in the direction of the magnet assembly 51. Since the armature 49 is connected to the closing element 31, this also pulls the closing element 31 upwards.
  • the closing element 31 rises from the valve seat 35 and releases a connection from the outlet channel 19 via a low-pressure chamber 57 into the return line 21. A bouncing of the armature 49 is thereby avoided that between the armature 49 and the magnet assembly 51, a nip 59 is formed.
  • the nip 59 is filled with fuel contained in the low-pressure chamber 57.
  • the fuel in the nip 59 is compressed, thus damping the movement of the armature 49. Due to the released connection from the outlet channel 19 via the low-pressure chamber 57 to the return line 21, fuel flows out of the control chamber 9. The pressure in the control chamber 9 decreases. As a result, the force acting on the upper end face 7 of the injection valve member 3 compressive force is reduced. The injection valve member 3 is lifted out of its seat and thus releases the at least one injection opening of the fuel injector 1. Fuel is injected into a combustion chamber of the internal combustion engine.
  • the injection valve member 3 must be put back in its seat to close the injection port.
  • the switching valve 17 must close the connection from the outlet channel 19 into the return 21.
  • the energization of the coil 53 is terminated, the magnetic field coincides.
  • the closing element 31 Due to the spring force of the spring element 45, which acts on the closing element 31, the closing element 31 is moved in the direction of the valve seat 35 until the sealing edge 33 is in the valve seat 35.
  • fuel under system pressure flows from the annular space 13 into the control chamber 9.
  • the pressure in the control chamber 9 increases and thus also the pressure force acting on the upper end face 7 of the injection valve member 3.
  • the injection valve member 3 Due to the increasing pressure force on the upper end face 7 of the injection valve member 3, the injection valve member 3 is placed back in his seat and thus closes the at least one injection port.
  • the injection process is finished.
  • the closing element 31 is guided in a sleeve 61.
  • the sleeve 61 has an L-shaped extension 63.
  • a collar 65 is formed, which is guided on a guide 67 in the region of the extension 63 of the inner diameter of the sleeve 61.
  • the damping chamber 69 is filled with liquid when the switching valve 17 is closed.
  • the Leckagesammeiraum 73 encloses in the embodiment shown here, the guide pin 39 between an upper guide 75 and a lower guide 77. At the upper guide 75 and the lower guide 77, the closing element 31 is guided.
  • At least one passage 79 is formed in the sleeve 61.
  • the sleeve 61 is fixed in the injector housing 29. accepted.
  • the sleeve 61 is fixedly connected to the valve piece 5, which is screwed in the injector 29.
  • the connection of the sleeve 61 with the valve piece 5 can be done for example by a non-positive or positive connection.
  • the coil 53 is energized and it forms a magnetic field.
  • the armature 49 is attracted and moved in the direction of the magnet assembly 51.
  • the sealing edge 33 lifts out of the valve seat 35 and releases a connection from the outlet channel 19 into the return line 21 via the passage 79 and the low-pressure chamber 57.
  • the volume of the damping chamber 69 increases when the switching valve 17 is opened. As a result, the pressure in the damping chamber 69 drops, whereby the vapor pressure of the liquid in the damping chamber 69 falls below. The liquid in the damping chamber evaporates. During the evaporation process, the pressure in the damping chamber 69 remains constant.
  • the cross section of the channel 71 is designed so that during the opening operation of the switching valve 17 no liquid flows into the damping chamber 69.
  • the injection times in particular when the injector is used as a fuel injector for an internal combustion engine, so short that an optionally flowing over the channel 71 amount of liquid is negligible.
  • the guides 67 and 81 in which the closing element 31 is guided in the sleeve 61, also act in a sealing manner, so that no fluid enters the damping chamber 69 via the guides 67 and 81.
  • the switching valve 17 is closed again.
  • the energization of the coil 53 is released and the magnetic field collapses.
  • the closing element 31 with the armature 49 moves again in the direction of the valve seat 53. This movement is assisted by the spring element 45 acting as a closing spring.
  • the low pressure in the damping chamber 69 also assists in the closing movement of the closing element 31.
  • the movement of the closing element 31 reduces the volume of the damping chamber 69 again.
  • the previously evaporated liquid condenses again.
  • the entire liquid in the damping chamber 69 is also condensed again. Since the liquid is substantially incompressible, the volume of the damping chamber 69 will not shrink further and the liquid will take a Much of the kinetic energy of the closing element 31. As a result, a rebounding of the closing element 31 is prevented.
  • High-pressure ranges are the ranges in which system-pressure fuel is contained. These are in particular the inlet channel 15, the annular space 13, the control chamber 9 and the pressure chamber 43.
  • the upper guide 75 is designed such that a pressure prevails in the leakage collection chamber 73 which is higher
  • the pressure in the leak collection chamber 73 is preferably so high that the liquid in the leak collection chamber is gas-free. Due to the pressure difference between the Leckagesammeiraum 73 and the low-pressure chamber 57, the liquid flows through the first channel 71 in the damping chamber 69.
  • the guide 67 also acts as a throttle gap, passes through the liquid from the damping chamber 69 in the low-pressure chamber 57. Since the pressure in the damping chamber 69 is higher than in the low-pressure chamber 57, however, the damping chamber 69 is always completely filled with liquid. As a result of the complete filling of the damping chamber 69, the zero stroke of the damping chamber 69 acting as damper is automatically set before the switching valve 17 is actuated when the switching valve 17 is closed. The damper is force-free. This also ensures that the hydraulic stop, which results from the sudden change in pressure at the time when the liquid is completely condensed in the damping chamber 69, always works properly. Even if a stroke drift occurs, the hydraulic stop will not act until it reaches the zero stroke, i. when the sealing edge 33 strikes the valve seat 35.

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  • 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 de commande pour des injecteurs, en particulier pour des injecteurs de carburant (1), comprenant un obturateur (31) qui permet la décompression d'une chambre de commande (9) pour l'actionnement d'un organe de soupape d'injection (3). L'obturateur (31) est commandé par un actionneur magnétique comprenant un module magnétique (51) et un induit (49). L'obturateur (31) est guidé dans un manchon (61) reçu fixement dans l'injecteur. Le manchon (61) présente un élargissement de diamètre (63) et l'obturateur (31) présente un collet (65), et le collet (65) est guidé dans l'élargissement de diamètre (63), de sorte que le manchon (61) et l'obturateur (31) entourent une chambre d'amortissement (69) de telle sorte que le volume de la chambre d'amortissement (69) augmente lors de l'ouverture de la soupape de commande (17), et diminue à nouveau lors de sa fermeture.
PCT/EP2008/065629 2007-12-10 2008-11-17 Soupape de commande pour injecteurs Ceased WO2009074427A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710059263 DE102007059263A1 (de) 2007-12-10 2007-12-10 Schaltventil für Injektoren
DE102007059263.0 2007-12-10

Publications (1)

Publication Number Publication Date
WO2009074427A1 true WO2009074427A1 (fr) 2009-06-18

Family

ID=40428265

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/065629 Ceased WO2009074427A1 (fr) 2007-12-10 2008-11-17 Soupape de commande pour injecteurs

Country Status (2)

Country Link
DE (1) DE102007059263A1 (fr)
WO (1) WO2009074427A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009045623A1 (de) * 2009-10-13 2011-04-14 Robert Bosch Gmbh Kraftstoff-Injektor
DE102013227063A1 (de) * 2013-12-23 2015-06-25 Robert Bosch Gmbh Kraftstoffinjektor
DE102014226258A1 (de) * 2014-12-17 2016-06-23 Robert Bosch Gmbh Kraftstoffinjektor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007128613A1 (fr) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Injecteur de carburant comportant une soupape de commande à compensation de pression
WO2008148643A1 (fr) * 2007-06-04 2008-12-11 Robert Bosch Gmbh Injecteur
EP2022977A1 (fr) * 2007-07-30 2009-02-11 C.R.F. Società Consortile per Azioni Servovanne à compensation de pression pour un injecteur de carburant d'un moteur à combustion interne

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007128613A1 (fr) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Injecteur de carburant comportant une soupape de commande à compensation de pression
WO2008148643A1 (fr) * 2007-06-04 2008-12-11 Robert Bosch Gmbh Injecteur
EP2022977A1 (fr) * 2007-07-30 2009-02-11 C.R.F. Società Consortile per Azioni Servovanne à compensation de pression pour un injecteur de carburant d'un moteur à combustion interne

Also Published As

Publication number Publication date
DE102007059263A1 (de) 2009-06-18

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