EP2286080A1 - Injecteur de carburant à siège perforé - Google Patents

Injecteur de carburant à siège perforé

Info

Publication number
EP2286080A1
EP2286080A1 EP09757357A EP09757357A EP2286080A1 EP 2286080 A1 EP2286080 A1 EP 2286080A1 EP 09757357 A EP09757357 A EP 09757357A EP 09757357 A EP09757357 A EP 09757357A EP 2286080 A1 EP2286080 A1 EP 2286080A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injector
injection
armature
control valve
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Withdrawn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
EP09757357A
Other languages
German (de)
English (en)
Inventor
Wilhelm Christ
Thomas Pauer
Werner Teschner
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 EP2286080A1 publication Critical patent/EP2286080A1/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Withdrawn legal-status Critical Current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
    • F02M63/004—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
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves

Definitions

  • the invention is based on known fuel injectors for supplying combustion chambers of self-igniting internal combustion engines with fuel. For this purpose, both stroke-controlled and pressure-controlled injection systems can be used. In addition to pump-nozzle units, pump-line-nozzle units, fuel injection systems are also used as fuel injection systems. Storage injection systems (common rail systems) advantageously make it possible to adapt the injection pressure to the load and speed of the internal combustion engine.
  • a fuel injector In accumulator injection systems, a fuel injector is generally pressurized with pressurized fuel from a high pressure accumulator (common rail).
  • the fuel injector has an actuator, by means of which the injection process is controlled.
  • the present invention particularly relates to common rail systems, but in principle also an application to other types of fuel injectors is possible.
  • Fuel injectors generally have a valve body in which an injection valve member is mounted axially displaceable.
  • an injection valve member is mounted axially displaceable.
  • one or more injection openings are provided at the lower, the combustion chamber facing the end of the valve body, which are closed or opened by the injection valve member, that are separated from the fuel supply or connected thereto.
  • blind-hole nozzles In blind-hole nozzles remains after injection in a so-called blind hole below the injection valve member, a small amount of fuel.
  • the at least one injection valve opening usually branches off in the region of this blind hole.
  • blind hole nozzles as described for example in DE 196 34 933 Al in various Although embodiments are described, while having the advantage of increased long-term stability and good controllability, but sometimes lead to an increased emissions problem. So remains in the blind hole after injection usually a small remainder of fuel, so that the blind hole has a high Schadvolumen. If this fuel evaporates, the hydrocarbon emission generally increases.
  • valve covered orifices In the case of seat-hole nozzles, which are often referred to as "valve covered orifices", the injection opening is closed by the valve sealing surface of the injection valve member in a closed state of the fuel injector and are covered so that evaporation of fuel can be avoided.
  • seat hole nozzles lead to strong pressure fluctuations in the injection system even at absolutely constant injection pressure. For example, cavitations frequently occur in the region of the needle seat and in a residual volume below the injection valve member, which cavities can lead to rapidly changing, greatly varying inlet conditions for the flow through the injection openings and thus to different injection jet properties. In addition, fluctuations in the position of the injection valve member are noticeable in asymmetric flows in these injection valve types, which also leads to a non-uniform injection jet pattern.
  • the invention is based on the recognition that the properties of fuel injectors with seat hole nozzles can be significantly improved if the actuator control of the fuel injectors is made uniform.
  • pressure fluctuations such as the pressure fluctuations caused by the described cavitations, can lead to a feedback to the actuator, which in turn can adversely affect the injection process.
  • an actuator must be used, which acts on the injection valve member such that it quickly releases the openable cross-section and thus a fast-switching valve provides.
  • a fast-switching valve By such a fast-switching valve, the use of a seat hole nozzle is possible, and it can be the emission advantages of such seat hole nozzles realize at the same time high stability of the injection process.
  • a basic idea of the present invention is therefore that the fast-opening properties which are required for seat-hole nozzles can be realized, in particular, by means of force-balanced or pressure-balanced actuators.
  • a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine which has at least one injection valve member axially displaceably mounted in a valve body for releasing and closing at least one injection opening.
  • this fuel injector may be a fuel injector for a storage injection system.
  • the fuel injector is designed according to the seat hole nozzle principle.
  • the valve body has at least one valve seat surface, in particular at least one conical valve seat surface, at an end facing the combustion chamber.
  • valve seat surfaces may also be provided, for example stepped valve seat surfaces or the like.
  • tapering refers to a surface with an angle different from 0 ° to the injector axis, in particular an angle between 0 ° and 90 °, for example between 10 ° and 80 °.
  • the at least one injection opening is wholly or partly provided in this conical valve seat surface.
  • the injection valve member in turn has at least one valve sealing surface, in particular at least one conical valve sealing surface, which closes the injection opening in a closed state of the fuel injector.
  • valve sealing surfaces may in turn be provided instead of or in addition to conical valve sealing surfaces.
  • the at least one valve sealing surface in the closed state of the fuel injector rest on the valve seat surface, wherein the at least one injection port is directly in contact with the valve sealing surface and thus is closed by the latter.
  • the at least one valve sealing surface and the at least one valve seat surface may at least partially have the same cone angle in the region of the at least one injection opening, so that the valve sealing surface rests flush on the valve seat surface in the region of the injection opening. In this way, as described above, even in the closed state of the fuel injector no evaporation of Hydrocarbons from an optionally present below the injection valve member space or a bore occur.
  • a control valve is furthermore provided, which is designed to be force-balanced and / or pressure-balanced.
  • This control valve is used for hydraulic actuation of the injection valve member.
  • This control can be done for example via one or more control chambers, for example by means of the control valve by opening the control valve causes a pressure relief of the control chamber and thus a stroke of the injection valve member can be effected.
  • the control valve is designed according to the invention force or pressure balanced. Accordingly, the control valve is arranged such that substantially no net axial hydraulic force acts on the control valve in a closed state of the control valve. In particular, it should not be possible to exert an axial force in the closed state of the control valve on the control valve or an actuator of the control valve in a hydraulic fluid, for example fuel, which is present between the control valve and the injection valve member.
  • the injection valve member may have one, two or more (eg, conical) valve sealing surfaces. At least one of these valve sealing surfaces is intended to find a correspondence in the at least one (for example conical) valve seat surface, so that, as described above, the at least one injection opening is closed in the closed state of the fuel injector. If at least two conical valve seat surfaces are provided, then it is particularly preferred if these two conical valve sealing surfaces have different cone angles. In this regard, reference may be made, for example, to the embodiments constructed according to the VCO principle of DE 196 34 933 A1. At least one step and / or at least one groove can be provided between the at least two valve sealing surfaces.
  • the at least one control valve may in particular comprise at least one actuator. It is particularly preferred if the control valve has at least one solenoid valve. This solenoid valve may in turn have at least one armature, on which a sealing surface may be formed. This sealing surface should be adjustable to close the control valve in a valve seat.
  • the anchor in turn should be movable between an upper and a lower stroke stop.
  • the armature without armature guide is designed.
  • control valve in particular the solenoid valve, preferably be designed such that this in the closed state of the control valve no hydraulic surface perpendicular to the axial direction, ie the direction of the longitudinal extent of the fuel injector or the injection valve member , having. Slight bevelled edges can be neglected, provided that they are small compared to, for example, a spring force of a spring element provided in the actuator, for example a helical valve spring.
  • a bore may be provided in the armature.
  • This bore which can be configured for example as a central, concentric bore relative to the axis of the fuel injector, can serve to receive a push rod.
  • This push rod which is preferably not connected to the armature, but which is preferably mounted slidably in the armature, or the bore, can serve to absorb axial pressure forces.
  • the push rod may be fixedly mounted at its upper end and at a lower end of a control chamber or a hole to assign a control chamber with an end face. This push rod thus serves by means of, for example, said end face for receiving axial pressure forces, whereas the armature and thus the solenoid valve are not acted upon by hydraulic forces, provided that the solenoid valve is in its closed state.
  • the anchor can, as proposed in DE 10 2006 021 736 Al, further comprise at least one resilient guide lip.
  • This resilient guide lip can rest for example on the lower stroke stop on a support surface, so that the armature is aligned.
  • the guide lip and the sealing surface on the armature and the bearing surface and the valve seat of the control valve can be ground in particular at the same height, which considerably simplifies the manufacturing process of the solenoid valve.
  • the diameter of the push rod is at least approximately equal to an inner diameter of the valve seat.
  • the push rod be mounted sealingly in the bore in the anchor, so that between the push rod and the armature escape of pressure is prevented.
  • the closed state of the fuel injector is defined such that in this closed state, the at least one Einspritzöffhung is closed by the injection valve member, whereas in an open state of the fuel injector, the Einspritzöffhung is released.
  • the closed state of the control valve corresponds to a state in which the control valve is pressed into the valve seat, so that the armature is located in the lower stroke stop. In the open state of the control valve, however, the armature is in the upper stroke stop, so that, for example, a control chamber can be pressure relieved.
  • the erfmdungsconcee fuel injector can be driven in principle inverse or non-inverse, with the non-inverse control is preferred due to the simple control.
  • the non-inverse control when the magnet is energized, the at least one injection opening is released and fuel is injected into the combustion chamber of the internal combustion engine. By energizing the magnet, however, the armature is lifted from the valve seat, so that a pressure relief can take place, and the injection process is triggered.
  • the proposed fuel injector in one or more of the embodiments described above thus has the advantage over conventional fuel injectors of reduced pollutant emission while maintaining high stability and reliability.
  • the fuel injector is comparatively easy to manufacture and differs in the manufacturing cost is not or only slightly different from conventional, corresponding to the prior art Rraftstoff ⁇ njektoren.
  • Figure 1 is a fragmentary sectional view of a control valve of a fuel injector according to the invention
  • Figure 2 is a fragmentary sectional view of one end of an injection valve member of the inventive fuel injector.
  • FIGS. 1 and 2 various regions of a fuel injector 110 according to the invention are shown by way of example. 1 shows a detail of the fuel injector, in which a control valve 112 is shown as an example, whereas FIG. 2 shows a section of a nozzle region of the fuel injector 110.
  • FIG. 1 shows a detail of the fuel injector, in which a control valve 112 is shown as an example
  • FIG. 2 shows a section of a nozzle region of the fuel injector 110.
  • the control valve 112 according to FIG. 1 can be combined with other types of nozzle areas, and the configuration of the nozzle area according to FIG. 2 with other types of control valves 112 according to the invention.
  • the fuel injector 110 has a valve body 114, which may have a modular design, for example.
  • the valve body 114 has an injector axis 116.
  • a needle chamber 118 is arranged, which extends parallel to the injector axis 116.
  • an injection valve member 120 is received and movably mounted parallel to the injector axis 116.
  • the injection valve member 120 may be guided at one or more locations within the needle chamber 118.
  • the valve body 114 has a conical valve seat surface 122 in the end region of the needle chamber 118 at its lower region, which is assigned to the combustion chamber when used in an internal combustion engine. In the region of this valve seat surface 122, at least one injection opening 124 is provided, wherein usually a plurality of such injection openings 124 are present.
  • the injection valve member 120 has a conical valve sealing surface 126 at its lower end. 2, which may correspond to one or more of the exemplary embodiments listed in DE 196 34 933 A1, is divided into two parts and has a first valve sealing surface 128 and a second valve sealing surface 130.
  • the first valve sealing surface 128, which is arranged below the second valve sealing surface 130 is adapted from its cone angle to the cone angle of the valve seat surface 122.
  • the second valve sealing surface 130 has a smaller cone angle.
  • a step 132 is arranged with a groove 134. In this way, an annular space 136 is formed in the region of the groove 134.
  • the arrangement shown has the advantage that it has a particular low wear.
  • the first valve sealing surface 128 contacts the wall of the valve body 114 in the region of the injection opening 124 and closes the injection opening 124.
  • the valve sealing surface 126 lifts from the valve seat surface 122, and fuel from the needle chamber 118 can flow to the injection port 124 and be injected from there into the combustion chamber.
  • the injection valve member 120 is acted upon by a nozzle spring, not shown in the figures, with a spring force in the closing direction 138. Via a hydraulic surface, which is also not shown, this spring force counteracts a hydraulic force through the fuel, wherein the spring force usually exceeds the hydraulic force.
  • the injection valve member 120 has at its upper end a control piston 140 and / or is connected to such a control piston 140. Also, this control piston 140 is mounted in the axial direction movable in the needle chamber 118 and / or in a separate control piston chamber. The movement of the control piston 140 takes place in the embodiment shown in Figure 1, which corresponds for example to an embodiment of DE 10 2006 021 736 Al, hydraulically.
  • the control piston 140 opens with its side facing away from the injection valve member 120 in a control chamber 142. Via an inlet throttle 144, the control chamber 142 is connected to a fuel inlet 146. As a result, fuel under system pressure can flow into the control chamber 142.
  • an outlet throttle 148 of the control chamber 142 is relieved.
  • the outlet throttle 148 is hydraulically connected to a return, not shown in Figure 1.
  • the outlet throttle 148 can be closed by means of the control valve 112.
  • the control valve 112 comprises a solenoid valve 150.
  • other types of actuators can be used, for example piezo actuators, which can be operated according to the invention pressure-balanced.
  • FIG. 1 shows a closed state of the control valve 112, in which the inlet throttle 144 is hydraulically separated from the return flow by the control valve 112 by means of the control valve 112.
  • a bore 158 is formed in the armature 154.
  • a push rod 160 is added. So that no axial pressure forces act on the armature 154 when the solenoid valve 150 is closed, the diameter of the bore 158 is substantially equal to the inner diameter of the sealing surface 152.
  • Another object of the push rod 160 is to seal the bore 158 against leakage currents. For this reason, preferably the push rod 160 and the bore 158 are made in a tight guide play.
  • an elastic guide lip 162 is disposed on the armature 154.
  • the upper stroke stop of the armature 154 is formed by an annular surface 164 which is designed as a lower end face of a stroke stop sleeve 166.
  • a bore 168 is formed in the Hubantschshülse 166, in which a spring element 170 is received.
  • the spring element 170 is preferably a helical spring designed as a compression spring, which is supported on one side by the armature 154 and on the other side by a disk 172.
  • the disk 172 is placed against an end face 174 of the bore 168.
  • the solenoid valve 150 includes a magnet 176 received in a magnetic core 178.
  • the valve seat 156 and a support surface 182, on which the elastic guide lip 162 rests when the armature 154 is located at the lower stroke stop, are ground to a height.
  • the support of the elastic guide lip 162, which rests on the support surface 182, and the sealing surface 152 are ground on the armature 154 to a height.
  • the stroke of the armature 154 is limited by the Hubanschlaghülse 166.
  • the armature 154 and the magnetic core 178 are enclosed by a sleeve 184, by the axial extent of the stroke is determined.
  • the stroke stop sleeve 166 with an end face 186 on the sleeve 184 is located for this purpose.
  • the inlet throttle 144, the outlet throttle 148 and the valve seat 156 and the bearing surface 182 are formed on a valve piece 188, which is part of the valve body 114 and which is accommodated in an injector 190. Also, the injector 190 is the part of the valve body 114.
  • the attachment of the valve member 188 in the injector housing 190 by means of a valve clamping screw 192.
  • a bore 194 is formed in this for each pin 180.
  • the pins 180 are each enclosed by a lower disk 196, an upper disk 198 and a sealing ring 200 located therebetween.
  • the attachment of the Hubanschlagshülse 166 on the injector 190 takes place in the embodiment shown here by means of a clamping nut 202nd
  • the injection process can be made to DE 10 2006 021 736 Al extensively.
  • the magnet 176 of the solenoid valve 150 is energized to start the injection process, so that the armature 154 is lifted off its valve seat 156.
  • the control chamber 142 is pressure-relieved via the outlet throttle 148, as a result of which the control piston 140 and the injection valve member 120, driven by the hydraulic force of the fuel, can move upwards.
  • the injection valve member 120 is lifted at its lower end with its valve sealing surface 126 from the valve seat surface 122, and the injection ports 124 are released.
  • the energization of the solenoid valve 150 is interrupted so that the spring element 170 presses the armature 154 back into the valve seat 156.
  • the control chamber 142 is refilled with fuel via the inlet throttle 144 so that the control piston 140 and the injection valve member 120 move downwards again, whereby the injection openings 124 are again fired via the valve sealing surface 126.
  • a control valve 112 may be provided with an inverse drive, so with a control in which, for example, when energized Magnet 176, the at least one injection port 120 is closed.
  • control valve 112 in the closed state is pressure balanced.
  • no axial hydraulic forces act on the control valve 112 or the armature 154 of the control valve 112.
  • an additional closing element for closing the outlet throttle 148 can be dispensed with.
  • the mass of the moving components can be minimized, and it can be shorter switching times realize.

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 un injecteur de carburant (110), destiné à injecter du carburant dans une chambre de combustion d'une machine à combustion interne. L'injecteur de carburant (110) possède au moins un obturateur de soupape d'injection (120) monté coulissant axialement dans un corps de soupape (114) afin de libérer et de fermer au moins une ouverture d'injection (124). Le corps de soupape (114), à une extrémité tournée vers la chambre de combustion, possède au moins une surface de siège de soupape (122). L'ouverture d'injection (124) est ménagée dans la surface de siège de soupape (122). L'obturateur de soupape d'injection (120) possède au moins une surface d'obturation de soupape (126, 128, 130). La surface d'obturation de soupape (126, 128, 130), dans la position de fermeture de l'injecteur de carburant (110), obture l'ouverture d'injection (124). L'injecteur de carburant (110) possède en outre au moins une soupape de commande (112) pour commander hydrauliquement l'obturateur de soupape d'injection (120). La soupape de commande (112) est configurée pour que, dans la position de fermeture de la soupape de commande (112), essentiellement aucune force hydraulique axiale ne s'applique à la soupape de commande (112).
EP09757357A 2008-06-02 2009-04-21 Injecteur de carburant à siège perforé Withdrawn EP2286080A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810002146 DE102008002146A1 (de) 2008-06-02 2008-06-02 Kraftstoffinjektor mit Sitzlochdüse
PCT/EP2009/054730 WO2009146974A1 (fr) 2008-06-02 2009-04-21 Injecteur de carburant à siège perforé

Publications (1)

Publication Number Publication Date
EP2286080A1 true EP2286080A1 (fr) 2011-02-23

Family

ID=41021026

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09757357A Withdrawn EP2286080A1 (fr) 2008-06-02 2009-04-21 Injecteur de carburant à siège perforé

Country Status (3)

Country Link
EP (1) EP2286080A1 (fr)
DE (1) DE102008002146A1 (fr)
WO (1) WO2009146974A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106704065A (zh) * 2017-01-18 2017-05-24 哈尔滨工程大学 一种带有刻沟的谐振式电控喷油器
GB2559560B (en) * 2017-02-08 2020-06-17 Delphi Tech Ip Ltd Control valve arrangement for a dual fuel injector

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19634933B4 (de) 1996-08-29 2007-06-06 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
ATE413527T1 (de) * 2004-06-30 2008-11-15 Fiat Ricerche Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine
DE102006021736A1 (de) 2006-05-10 2007-11-15 Robert Bosch Gmbh Kraftstoffinjektor mit druckausgeglichenem Steuerventil
DE102006050032A1 (de) * 2006-10-24 2008-04-30 Robert Bosch Gmbh Injektor mit einem eine konische Hubanschlagfläche aufweisenden Steuerventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009146974A1 *

Also Published As

Publication number Publication date
WO2009146974A1 (fr) 2009-12-10
DE102008002146A1 (de) 2009-12-03

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