EP2267295A2 - Fuel injector - Google Patents
Fuel injector Download PDFInfo
- Publication number
- EP2267295A2 EP2267295A2 EP10160976A EP10160976A EP2267295A2 EP 2267295 A2 EP2267295 A2 EP 2267295A2 EP 10160976 A EP10160976 A EP 10160976A EP 10160976 A EP10160976 A EP 10160976A EP 2267295 A2 EP2267295 A2 EP 2267295A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- piston
- stop
- chamber
- fuel injector
- 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- Withdrawn
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- 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 relates to a fuel injector according to the preamble of claim 1.
- a fuel injector of the aforementioned type is for example made DE 103 22 672 A1 known.
- the stroke of the piezo actuator is transmitted via a hydraulic coupler to a valve element of a control valve which controls a control chamber of the nozzle needle by the control chamber is connected to open the nozzle needle with a relatively pressureless low pressure / return system.
- the control valve When the control valve is closed, the control chamber is filled via an inlet throttle with the system pressure of the common rail and the nozzle needle is placed in the nozzle needle seat.
- the piezo actuator To open the valve seat of the control valve, the piezo actuator must press against the pressure prevailing in the valve chamber a valve pin of the control valve from the valve seat.
- valve element comprises a valve pin and a valve pin axially guided valve sleeve, which are arranged in a valve chamber.
- the valve sleeve separates with a sealing surface a low-pressure space, which is exposed to the valve pin with an end face, against the highly pressurized valve chamber hydraulically.
- the valve chamber is connected to a control chamber to which the nozzle needle is exposed.
- the control chamber is connected via the valve seat of the control valve to the low-pressure / return system, so that an outflow volume can flow out of the control chamber into the low-pressure / return system via an outlet throttle.
- the effluent from the control chamber outflow volume flows through the valve chamber in the direction of the hydraulic coupler surrounding low pressure space, past the valve seat of the valve element.
- the invention has the advantage that with a defined stroke stop of the valve piston of the hydraulic coupler unit acting on the valve element of the control valve Aktorhub is delimited. As a result, a defined outlet geometry is realized at the valve seat between a valve chamber of the valve element and a low-pressure chamber of the hydraulic coupler unit, whereby a defined throttling of the outflow volume from the valve chamber is made possible. In addition, an improvement of the control and regulation behavior of the fuel injector is achieved because the Aktorschwingisme occurring in the controlled state are minimized.
- a defined outflow of Abströmvolumens from the valve chamber in the low-pressure space is achieved by at least one overflow connection between the valve chamber and the low-pressure space is present, which is effective in the stop position and at a valve pin seated by the valve seat.
- the defined throttling of the outflow volume from the valve space leads to the avoidance or reduction of cavitating flows, which occur in particular in the vicinity of the valve seat.
- annular surface is formed on the control valve side end of the valve piston, which forms a counter surface for the stop.
- the stop is formed by a valve body formed on the plane stop surface, such that in the stop position, the annular surface of the valve piston rests substantially on the planar stop surface.
- a conical circumferential surface is formed on the control valve-side end of the valve piston, which forms a counter surface for the stop.
- the stop is formed by a valve body formed on the conical abutment surface, such that in a stop position, the conical Outer surface of the valve piston rests substantially on the conical abutment surface of the valve body.
- the overflow connection is formed by slot-shaped or gap-shaped overflow channels on an end face of the valve piston and / or on the stop face of the valve body. Expediently, four slot-shaped or gap-shaped overflow channels arranged at right angles and directed radially to the center are provided.
- FIG. 1 shows a part of a fuel injector in longitudinal section with an actuator element 10, a hydraulic coupler unit 11, a control valve 12 and an injection valve 13.
- the actuator element 10 may be, for example, a piezo actuator, but also an electromagnetic actuator.
- the actuator element 10 and the hydraulic coupler unit 11 are accommodated in an injector body 14.
- a valve body 15, a throttle plate 16 and a nozzle body 17 adjoin the injector body 14.
- the said bodies are clamped by means of a hydraulic nozzle nut 18 hydraulically tight.
- a nozzle needle pressure chamber 19 is formed, which is supplied via a high pressure line 21 to the system pressure of a common rail.
- a nozzle needle 20 is arranged, at one end of a control chamber 22 a control chamber 23 separates from the nozzle needle pressure chamber 19.
- the hydraulic coupler unit 11 comprises a coupler body 25, in which a coupler piston 26 and a valve piston 27 are axially guided. Between the coupler piston 26 and the valve piston 27, a coupler gap 28 is formed, which is filled with fuel.
- the valve piston 27 is designed with a conical pressure piece 29 which engages in a cone-shaped overflow opening 31 formed on the valve body 15. Between the pressure piece 29 and the overflow 31, a flow gap 32 is present. Axially in alignment with the overflow opening 31, a passage 33 is arranged in the valve body 15 and leads into a valve space 34 for the control valve 12.
- the control valve 12 comprises a valve pin 40, on which a valve sleeve 41 is biased by means of a valve spring 42.
- the valve pin 40 has a mushroom-shaped or valve-shaped element 44, which cooperates with a valve seat 45 formed adjacent to the passage 33.
- the valve sleeve 41 encloses a low pressure chamber 47, which is constantly connected via a hydraulic connecting channel 48 to the low pressure / return system. Outside the valve sleeve 41, the valve chamber 34 is connected via a drain line 51 to the control chamber 23 of the nozzle needle 20.
- the control valve 12 is shown in FIG FIG. 1 shown in the closed state, in which the valve seat member 44 rests against the valve seat 45.
- a gap is present between the pressure piece 29 of the valve piston 27 and a support bolt of the valve seat element 44, so that the closing pressure of the valve spring 33 acts both on the valve sleeve 41 and on the valve seat element 44.
- An additional closing force acts on the valve seat element 44 by the pressure prevailing in the valve chamber 34 of the control chamber 23 in the closed state of the nozzle needle 20.
- the actuator element 12 is actuated and the stroke of the actuator element 12 via the coupler piston 26, the coupler gap 28 and the valve piston 27 transmitted to the valve pin 40, whereby the valve seat member 44 lifts off from the valve seat 45 and the valve chamber 34 with a hydraulic Coupler unit 11 surrounding low pressure space 30 connects.
- the low pressure space 30 is connected to the low pressure / return system.
- the pressure in the control chamber 23 is lowered and the nozzle needle 20 is lifted from the nozzle needle seat, not shown, and the fuel with the in the Pin pressure chamber 19 prevailing rail pressure (system pressure) injected into the combustion chamber of an internal combustion engine.
- a mating surface 61 formed on the valve piston 27 of the hydraulic coupling unit 11 acts on a stop 64 formed on the valve body 15, whereby the stroke of the valve piston 27 and thus the stroke of the actuator element 10 acting on the valve pin 40 is limited becomes.
- the pressure piece 29 of the valve piston 27 in this case has an end face 63 which presses against an adjacent further end face 66 of the valve pin 40.
- overflow connections 65 are formed, which form a defined hydraulic throttle of the outflow volume between the valve space 34 and the low pressure space 30.
- the abutment 64 is carried out by a planar abutment surface 64.1 arranged on the valve body 15 and formed by a plane surface running perpendicular to the center line of the valve piston 27 on the valve body 15.
- a planar abutment surface 64.1 arranged on the valve body 15 and formed by a plane surface running perpendicular to the center line of the valve piston 27 on the valve body 15.
- annular surface 61.1 designed as a mating surface 61 for the stop surface 64.1.
- the valve seat member 44 is lifted from the valve seat 45.
- slot-shaped or gap-shaped overflow channels 65.1 are formed, which are open on the annular surface 61.1 and on the outer circumferential surface of the valve piston 27.
- FIG. 2a In the opened state of the control valve 12, the overflow channels 65. 1 ensure a defined throttling of the outflow volume between the valve space 34 and the low-pressure space 30
- FIG. 2a illustrated embodiment of the slot or slit-shaped overflow channels 65, it is also conceivable, the annular Run counter-surface 61.1 continuously and incorporate the transfer channels 65.1 in the stop surface 64.1 of the valve body 15.
- the stop 64 is formed by a conical abutment surface 64.2 formed by the conical section 31 of the valve body 15.
- the mating surface 61 for this purpose forms a conical mantle surface 61.2 formed on the pressure piece 29.
- slot-shaped or slot-shaped transfer channels 65.2 are incorporated in the conical jacket surface 61.2.
- FIG. 3a in which, for example, four slot-shaped or gap-shaped transfer channels 65.2 are shown.
- the transfer channels 65.2 in the conical abutment surface 64.2 of the valve body 15.
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
Description
Die Erfindung betrifft einen Kraftstoffinjektor nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injector according to the preamble of claim 1.
Ein Kraftstoffinjektor der vorstehend genannten Art ist beispielsweise aus
Zur Reduzierung der Öffnungskraft wurde in
Die Erfindung hat den Vorteil, dass mit einem definierten Hubanschlag des Ventilkolbens der hydraulischen Kopplereinheit der auf das Ventilelement des Steuerventils wirkende Aktorhub abgegrenzt wird. Dadurch wird am Ventilsitz zwischen einem Ventilraum des Ventilelements und einem Niederdruckraum der hydraulischen Kopplereinheit eine definierte Abströmgeometrie realisiert, wodurch eine definierte Drosselung des Abströmvolumens aus dem Ventilraum ermöglicht wird. Außerdem wird eine Verbesserung des Ansteuerungs- und Regelungsverhaltens des Kraftstoffinjektors erzielt, weil die im angesteuerten Zustand auftretenden Aktorschwingungen minimiert werden.The invention has the advantage that with a defined stroke stop of the valve piston of the hydraulic coupler unit acting on the valve element of the control valve Aktorhub is delimited. As a result, a defined outlet geometry is realized at the valve seat between a valve chamber of the valve element and a low-pressure chamber of the hydraulic coupler unit, whereby a defined throttling of the outflow volume from the valve chamber is made possible. In addition, an improvement of the control and regulation behavior of the fuel injector is achieved because the Aktorschwingungen occurring in the controlled state are minimized.
Vorteilhafte Weiterbildungen und Verbesserungen der Erfindung werden durch die Maßnahmen der Unteransprüche erreicht.Advantageous developments and improvements of the invention are achieved by the measures of the subclaims.
Eine definierte Abströmung des Abströmvolumens aus dem Ventilraum in den Niederdruckraum wird erreicht, indem mindestens eine Überströmverbindung zwischen dem Ventilraum und dem Niederdruckraum vorhanden ist, die in der Anschlagposition und bei einem vom Ventilsitz abgedrückten Ventilbolzen wirksam ist. Die definierte Drosselung des Abströmvolumens aus dem Ventilraum führt zur Vermeidung bzw. Reduzierung von kavitierenden Strömungen, die insbesondere in der Umgebung des Ventilsitzes auftreten.A defined outflow of Abströmvolumens from the valve chamber in the low-pressure space is achieved by at least one overflow connection between the valve chamber and the low-pressure space is present, which is effective in the stop position and at a valve pin seated by the valve seat. The defined throttling of the outflow volume from the valve space leads to the avoidance or reduction of cavitating flows, which occur in particular in the vicinity of the valve seat.
Bei einer ersten Ausführungsform ist am steuerventilseitigen Ende des Ventilkolbens eine Ringfläche ausgebildet, die eine Gegenfläche für den Anschlag bildet. Der Anschlag ist dabei von einer am Ventilkörper ausgebildeten planen Anschlagfläche gebildet, derart, dass in der Anschlagposition die Ringfläche des Ventilkolbens im Wesentlichen auf der planen Anschlagfläche aufliegt.In a first embodiment, an annular surface is formed on the control valve side end of the valve piston, which forms a counter surface for the stop. The stop is formed by a valve body formed on the plane stop surface, such that in the stop position, the annular surface of the valve piston rests substantially on the planar stop surface.
Bei einer zweiten Ausführungsform ist am steuerventilseitigen Ende des Ventilkolbens eine kegelförmige Mantelfläche ausgebildet, die eine Gegenfläche für den Anschlag bildet. Der Anschlag ist von einer am Ventilkörper ausgebildeten kegelförmig Anschlagfläche gebildet, derart, dass in einer Anschlagposition die kegelförmige Mantelfläche des Ventilkolbens im Wesentlichen auf der kegelförmigen Anschlagfläche des Ventilkörpers aufliegt.In a second embodiment, a conical circumferential surface is formed on the control valve-side end of the valve piston, which forms a counter surface for the stop. The stop is formed by a valve body formed on the conical abutment surface, such that in a stop position, the conical Outer surface of the valve piston rests substantially on the conical abutment surface of the valve body.
Die Überströmverbindung ist durch schlitz- oder spaltförmige Überströmkanäle an einer Endfläche des Ventilkolbens und/oder an der Anschlagfläche des Ventilkörpers ausgebildet. Zweckmäßigerweise sind vier rechtwinklig angeordnete und radial zum Zentrum gerichtete schlitz- bzw. spaltförmige Überströmkanäle vorgesehen.The overflow connection is formed by slot-shaped or gap-shaped overflow channels on an end face of the valve piston and / or on the stop face of the valve body. Expediently, four slot-shaped or gap-shaped overflow channels arranged at right angles and directed radially to the center are provided.
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description.
Es zeigen:
-
Figur 1 eine Schnittdarstellung durch einen Teil eines Kraftstoffinjektors nach dem in der Beschreibungseinleitung zitierten Stand der Technik, -
Figur 2 eine Schnittdarstellung durch ein Steuerventil gemäß einem ersten Ausführungsbeispiel -
Figur 2a eine Ansicht eines Ventilkolbens gemäß Linie II-II inFigur 2 , -
Figur 3 eine Schnittdarstellung durch ein Steuerventil gemäß einem zweiten Ausführungsbeispiel und -
Figur 3a eine Ansicht eines Ventilkolbens gemäß Linie III-III inFigur 3 .
-
FIG. 1 a sectional view through a portion of a fuel injector according to the cited in the introduction of the prior art, -
FIG. 2 a sectional view through a control valve according to a first embodiment -
FIG. 2a a view of a valve piston according to line II-II inFIG. 2 . -
FIG. 3 a sectional view through a control valve according to a second embodiment and -
FIG. 3a a view of a valve piston according to line III-III inFIG. 3 ,
Im Düsenkörper 17 ist ein Düsennadeldruckraum 19 ausgebildet, der über eine Hochdruckleitung 21 mit dem Systemdruck eines Common-Rails versorgt wird. Im Düsennadeldruckraum 19 ist eine Düsennadel 20 angeordnet, an deren einen Ende eine Steuerraumhülse 22 einen Steuerraum 23 vom Düsennadeldruckraum 19 trennt. Die hydraulische Kopplereinheit 11 umfasst einen Kopplerkörper 25, in dem ein Kopplerkolben 26 und ein Ventilkolben 27 axial geführt sind. Zwischen dem Kopplerkolben 26 und dem Ventilkolben 27 ist ein Kopplerspalt 28 ausgebildet, der mit Kraftstoff gefüllt ist. Der Ventilkolben 27 ist mit einem kegelförmigem Druckstück 29 ausgeführt, das in eine am Ventilkörper 15 ausgebildete kegelförmige Überströmöffnung 31 eingreift. Zwischen dem Druckstück 29 und der Überströmöffnung 31 ist ein Strömungsspalt 32 vorhanden. Axial fluchtend zur Überströmöffnung 31 ist im Ventilkörper 15 ein Durchgang 33 angeordnet, der in einen Ventilraum 34 für das Steuerventil 12 führt.In the
Das Steuerventil 12 umfasst einen Ventilbolzen 40, an dem eine Ventilhülse 41 mittels einer Ventilfeder 42 vorgespannt ist. Der Ventilbolzen 40 weist ein pilz- bzw. kegelförmiges Ventilsitzelement 44 auf, das mit einem am Durchgang 33 angrenzend ausgebildeten Ventilsitz 45 zusammenwirkt. Die Ventilhülse 41 umschließt einen Niederdruckraum 47, der ständig über einen hydraulischen Verbindungskanal 48 an das Niederdruck/Rücklaufsystem angeschlossen ist. Außerhalb der Ventilhülse 41 ist der Ventilraum 34 über ein Ablaufleitung 51 mit dem Steuerraum 23 der Düsenadel 20 verbunden.The
Das Steuerventil 12 ist bei der Darstellung in
Zum Öffnen der Düsennadel 20 wird das Aktorelement 12 betätigt und der Hub des Aktorelements 12 über den Kopplerkolben 26, den Kopplerspalt 28 und den Ventilkolben 27 auf den Ventilbolzens 40 übertragen, wodurch das Ventilsitzelement 44 vom Ventilsitz 45 abhebt und der Ventilraum 34 mit einem die hydraulische Kopplereinheit 11 umgebenden Niederdruckraum 30 verbindet. Der Niederdruckraum 30 ist dabei an das Niederdruck/Rücklaufsystem angeschlossen. Dadurch wird der Druck im Steuerraum 23 abgesenkt und die Düsennadel 20 wird vom nicht dargestellten Düsennadelsitz abgehoben und der Kraftstoff mit dem im Nadeldruckraum 19 herrschenden Rail-Druck (Systemdruck) in den Brennraum einer Brennkraftmaschine eingespritzt.To open the
Bei den Ausführungsbeispielen in
Die detaillierte Ausbildung des Anschlages 64 und der Überströmverbindung 65 wird in den
Beim Ausführungsbeispiel in
Die nähere Darstellung dazu geht aus
Beim Ausführungsbeispiel in
Die nähere Darstellung dazu geht aus
Claims (8)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200910027187 DE102009027187A1 (en) | 2009-06-25 | 2009-06-25 | fuel injector |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2267295A2 true EP2267295A2 (en) | 2010-12-29 |
EP2267295A3 EP2267295A3 (en) | 2013-03-06 |
Family
ID=42937240
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10160976A Withdrawn EP2267295A3 (en) | 2009-06-25 | 2010-04-26 | Fuel injector |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2267295A3 (en) |
DE (1) | DE102009027187A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011086297A1 (en) | 2011-11-14 | 2013-05-16 | Robert Bosch Gmbh | Fuel injector for injecting fuel in combustion chamber of internal combustion engine e.g. diesel-powered fuel-ignition engine, has sealing sleeve and valve pin with pivot points provided at different distance relative to throttle plate |
DE102011086335A1 (en) | 2011-11-15 | 2013-05-16 | Robert Bosch Gmbh | Fuel injection valve used as common-rail injector for fuel injection system of diesel engine, has intermediate element with throttle that connects actuator module unit with module in inner space |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10322672A1 (en) | 2003-05-20 | 2004-12-09 | Robert Bosch Gmbh | Valve for controlling liquids |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10019767A1 (en) * | 2000-04-20 | 2001-10-31 | Bosch Gmbh Robert | Valve for controlling liquids |
DE102006027484A1 (en) * | 2006-06-14 | 2007-12-20 | Robert Bosch Gmbh | Fuel injector for an internal combustion motor, with a common rail fuel injection system, has the armature of the magnetic setting unit in the equalizing zone with the control piston pressure surface to reduce injector height |
DE102007042466B3 (en) * | 2007-09-06 | 2009-04-09 | Continental Automotive Gmbh | Injection system with reduced switching leakage and method of manufacturing an injection system |
DE102008040637A1 (en) | 2008-07-23 | 2010-01-28 | Robert Bosch Gmbh | Fuel injection valve device |
-
2009
- 2009-06-25 DE DE200910027187 patent/DE102009027187A1/en not_active Withdrawn
-
2010
- 2010-04-26 EP EP10160976A patent/EP2267295A3/en not_active Withdrawn
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10322672A1 (en) | 2003-05-20 | 2004-12-09 | Robert Bosch Gmbh | Valve for controlling liquids |
Also Published As
Publication number | Publication date |
---|---|
EP2267295A3 (en) | 2013-03-06 |
DE102009027187A1 (en) | 2010-12-30 |
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