EP2494182B1 - Fuel injection device - Google Patents
Fuel injection device Download PDFInfo
- Publication number
- EP2494182B1 EP2494182B1 EP10759858.3A EP10759858A EP2494182B1 EP 2494182 B1 EP2494182 B1 EP 2494182B1 EP 10759858 A EP10759858 A EP 10759858A EP 2494182 B1 EP2494182 B1 EP 2494182B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- injection device
- fuel injection
- pressure
- combustion chamber
- 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.)
- Not-in-force
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Classifications
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- 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
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- 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 F02M39/00Â -Â 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 F02M39/00Â -Â 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
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- 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 F02M39/00Â -Â 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 F02M39/00Â -Â 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 F02M63/0014Â -Â F02M63/0059
- F02M63/0073—Pressure balanced valves
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- 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 F02M39/00Â -Â 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 F02M39/00Â -Â 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 F02M63/0014Â -Â F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
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- 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 F02M39/00Â -Â 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 F02M39/00Â -Â 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
Definitions
- the invention relates to a fuel injection device for injecting fuel into a combustion chamber of an internal combustion engine, comprising a control valve which comprises a valve piece, in which a valve body for the representation of a valve seat is guided to and fro.
- the object of the invention is to minimize the leakage during operation of a fuel injection device according to the preamble of claim 1.
- a fuel injection device for injecting fuel into a combustion chamber of an internal combustion engine with a control valve comprising a valve piece in which a valve body for showing a valve seat is guided to and fro, achieved by the valve body at one end having combustion chamber remote first contact surface, which is arranged with closed valve seat in a plane with a second, formed on the valve member, contact surface so that the two contact surfaces sealing abut against a common counter surface.
- the inventive arrangement of the two contact surfaces an additional seal is created with the valve seat closed, whereby the leakage during operation of the fuel injection device, especially at high injection pressures, can be significantly reduced. Thereby, the quantity balance of the fuel injection device can be improved.
- the valve seat includes a sealing edge or sealing surface on the valve body sealingly abutting a seal surface or sealing edge of the valve member when the valve seat is closed to interrupt fluid communication between a control chamber and a pressure relief space or return.
- the opening movement of the valve body can be initiated by an actuator of a solenoid valve or by a piezoelectric actuator.
- the closing movement of the valve body is preferably effected by a spring, through which the valve body is biased in its closed position.
- the two contact surfaces are designed as annular surfaces. The two annular surfaces preferably extend in the common plane perpendicular to a longitudinal axis of the fuel injection device. The valve body is reciprocable in the longitudinal direction.
- a preferred embodiment of the fuel injection device is characterized in that the two contact surfaces are provided at a combustion chamber distal end of the valve piece and the valve body.
- the mating surface is provided for example on a stop plate or a stop body or on an actuator.
- the mating surface is preferably also designed as an annular surface.
- a further preferred embodiment of the fuel injection device is characterized in that the valve body is designed to be pressure balanced.
- Pressure balanced design means that the valve body with the valve seat closed in equal parts in the opening direction and closing direction with a control chamber pressure, in particular high pressure, is applied.
- valve body is designed as a valve sleeve, which is biased with the first bearing surface against an armature and comes with its combustion chamber near the end with the valve seat to the valve piece to rest.
- the armature on which preferably the counter surface is provided, cooperates with a magnet, preferably an electromagnet, to open the control valve.
- a further preferred embodiment of the fuel injection device is characterized in that the combustion chamber remote end of the valve sleeve is designed to be closed and has a connection through hole which connects an outflow space in the valve sleeve with an armature space.
- the combustion chamber near the end of the armature is, viewed in longitudinal section, preferably U-shaped.
- the armature is preferably disposed in a pressure relief space communicating with a return.
- Another preferred embodiment of the fuel injection device is characterized in that the armature space is connected via at least one relief through-hole with a return. Through the connection with the return ensures that the armature space with closed valve seat with a return pressure, preferably low pressure, is applied.
- a further preferred embodiment of the fuel injection device is characterized in that the valve body is designed as a valve pin, which is biased with the first contact surface against a stop body or a stop plate and radially within the first contact surface has a Betjans foundedwirk Structure.
- the actuating pressure acting surface is preferably acted upon by a coupler space pressure of a hydraulic coupler which is delimited by an actuator module of a piezoelectric actuator device. Via the hydraulic coupler, a longitudinal movement of the actuator module, which is brought about by an expansion of the piezoelectric actuator device, is transmitted to the valve body in an amplified manner.
- valve pin for the representation of the valve seat has a collar which is movable away from the valve piece for opening the valve seat.
- the opening movement of the valve body caused by the piezoactuator device preferably takes place against the biasing force of a valve spring toward the combustion chamber.
- the collar limits an annular space acted upon by a control chamber pressure, in particular at high pressure, whose end remote from the combustion chamber is delimited by an annular surface of a pressure shoulder which is formed on the valve body.
- a fuel injector 1 also referred to as a fuel injector or fuel injector, is shown in longitudinal section.
- the fuel injection device 1 comprises a holding body 2, a stopper plate or a stopper body 3, a valve piece 4, a throttle plate or throttle disk 5, and a nozzle body 6 abutting each other in this order.
- the components are pressed against each other by a clamping nut 8, which is supported on a shoulder of the nozzle body 6 and is screwed by a thread 9 with the holding body 2.
- a nozzle needle 10 is guided in a central through hole 11 of the nozzle body 6 movable back and forth.
- a combustion chamber near the end of the nozzle needle 10 is arranged in a pressure chamber 12.
- the nozzle needle 10 is through a nozzle spring 13 so biased that a nozzle needle seat 14 is closed at a combustion chamber near the end of the nozzle needle 10.
- the nozzle needle seat 14 comprises a sealing edge formed on the nozzle needle 10 which bears against a conical sealing surface which is formed at the end of the nozzle body 6 remote from the combustion chamber and from which two injection holes 15, 16 emerge which connect the pressure chamber 12 to a combustion chamber 18 of an internal combustion engine.
- the pressure chamber 12 communicates via a high-pressure connection channel 19 with a further pressure chamber 22, which in turn communicates via a high-pressure connection channel 23 and a high-pressure line 24 with a central high-pressure fuel storage 25, which is also referred to as a common rail and is disposed outside of the fuel injection device 1.
- the two pressure chambers 12, 22 in the interior of the fuel injection device 1 are filled from the central high-pressure fuel storage 25 with fuel, which is acted upon by high pressure.
- the nozzle needle seat 14 is opened at the end of the nozzle needle 10 close to the combustion chamber, so that high-pressure fuel is injected from the pressure chamber 12 via the injection holes 15, 16 into the combustion chamber 18.
- the opening movement of the nozzle needle 10 is controlled by the pressure in a control chamber 28 which is limited in a nozzle needle sleeve 27 from the combustion chamber remote end 26 of the nozzle needle 10.
- the control chamber 28 which is also referred to as Düsennadel horrraum, is connected via an inlet channel 30 which is provided with an inlet throttle, with the high-pressure connection channel 23 in connection.
- an outlet throttle 32 is arranged
- the control chamber 28 communicates with a drainage chamber 33, which in turn communicates via a further drainage channel 34 with a valve chamber 35 of a control valve 36.
- the inlet channel 30 and the outlet channel 31 extend through the throttle plate 5.
- the outlet chamber 33 and the outlet channel 34 are formed in the valve piece 4.
- the control valve 36 comprises a valve body 37, which has a collar 38.
- the collar 38 includes a sealing edge or sealing surface, which in the illustrated closed state of the control valve 36 at a sealing surface or sealing edge in Appendix, which is formed on the valve piece 4.
- the collar 38 serves to represent a valve seat 39 which is in the in FIG. 1 shown state is closed.
- the valve body 37 has at its end near the combustion chamber on a stop pin which projects into a spring chamber 40 in which a valve spring 41 is biased against the collar 38 of the valve body 37, that the valve seat 39 remains closed.
- the spring chamber 40 communicates via pressure relief channels 42, 43, 44 with a pressure relief chamber 45 at the combustion chamber remote end of the fuel injection device 1 in connection.
- the pressure relief space 45 is connected via a return line 46, in which a return throttle 47 is arranged, with a return tank 48 in connection.
- the return tank 48 is as well as the pressure relief chamber 45 and the pressure relief channels 42, 43, 44 applied with a return pressure or low pressure, which is significantly smaller than the high pressure in the central high-pressure fuel storage 25 and the pressure chambers 12, 22 inside the fuel injection device 1.
- annular space 50 is formed, which communicates via a pressure relief passage 49 with the pressure relief space 45 in connection.
- a relief groove 51 extends into the valve piece 4.
- the relief groove 51 extends around a guide portion 52 in which the valve body 37 is reciprocally movable.
- the valve body 37 is designed as a valve pin 54, which is guided in a through hole of the valve piece 4 to and fro. By the guidance of the valve pin 54 in the valve piece 4, a leakage path 55 is created, passes through the leakage from the valve chamber 35 of the control valve 36 in the annulus 50, which communicates with the return.
- the guide diameter of the valve body 37 and the valve pin 54 is designated 56.
- a high-pressure pocket 58 is provided in the valve piece 4, which serves to compensate for changes in length of the valve pin 54 by rail pressure changes in the region of a length 59 to the same extent on the valve piece 4.
- a high-pressure-loaded surface 67 on the valve piece 4 must therefore be approximately equal to a high pressure-loaded surface 68 on the valve pin 54.
- the high-pressure bag 58 is arranged so that they no Influence on the function of the control valve 36 has.
- the high-pressure pocket 58 does not overlap with the valve chamber 35 both in the closed and in the open state of the valve seat 39.
- the spatial separation over the guide diameter 56 when opening the control valve 36 a faster degradation of the pressure in the valve chamber 35 and thus a faster pressure reduction in Control room 28 allows. In turn, a faster opening of the nozzle needle 10 can be achieved.
- the combustion chamber remote end of the valve body 37 and the valve pin 54 defines an actuating pressure chamber 60 which communicates via a through hole of the stopper plate 3 with a coupler 61 in communication, which is filled with a hydraulic medium.
- the coupler space 61 is delimited by an actuator body 63, which is also referred to as an actuator module.
- the actuator body 63 is biased by an actuator spring 65 away from the stopper plate 3 against a piezoelectric actuator 64.
- the piezoelectric actuator device 64 When the piezoelectric actuator device 64 is energized, then it expands, whereby the actuator body 63 is moved toward the stop plate 3.
- the pressure in the coupler chamber 61 and the actuating pressure chamber 60 increases at the combustion chamber remote end of the valve body 37 and the valve pin 54.
- the pressure increase in the actuating pressure chamber 60 causes the valve body 37 is moved against the biasing force of the valve spring 41 to the combustion chamber 18, so that the valve seat 39 is opened.
- the length 59 between the valve seat 39 and the end remote from the combustion chamber of the valve piece 4 and the valve body 37 before and after assembly is identical.
- a first abutment surface 71 on the valve body 37 or valve pin 54 is formed radially outside the actuating pressure chamber 60.
- a second abutment surface 72 is formed radially within the annulus 50 on the valve piece 4.
- the two contact surfaces 71, 72 are arranged according to an essential aspect of the invention in a common plane. This arrangement of the two contact surfaces 71, 72 is preferably achieved in that the valve body 37 is inserted into the valve piece 4, and the valve seat 39, for example, by the biasing force of the valve spring 41, is closed.
- both contact surfaces 71, 72 are jointly ground flat.
- FIG. 2 it can be further seen that the two contact surfaces 71, 72 of the valve body 37 and the valve member 4 with the valve seat 39 closed are in close contact with a counter surface 73, which is formed on the stop plate 3.
- the two contact surfaces 71, 72 are formed as well as the counter surface 73 as annular surfaces. In order to prevent an undesirable buildup of pressure by sweat leakage through the sealing bandage 71, 72, 73 in the acted upon with low pressure annulus 50, this is connected via the pressure relief channel 49 to the pressure relief chamber 45.
- the piezoelectric actuator device 64 is energized so that it assumes its longest state.
- the change in length of the piezoelectric actuator 64 leads via the actuator body 63 to an increase in pressure in the coupler space 61.
- the sealing compound 71, 72, 73 is repealed.
- the leakage path 55 is opened.
- the pressure in the high-pressure pocket 58 builds up slowly over the leakage path 55 and over the valve space 35.
- the actuator body 63 is returned by the actuator spring 65, so that the pressure in the coupler chamber 61 and in the actuating pressure chamber 60 drops.
- the valve pin 54 is pulled towards the stop plate 3, whereby the valve seat 39 is closed.
- the pressure in the valve chamber 35 and with a time delay also rises in the high-pressure pocket 58 to the rail pressure level, so that differences in length between the valve body 37 and the valve piece 4 due to rail pressure are compensated.
- a fuel injection device 81 is shown in longitudinal section, the fuel injection device 1 in FIG. 1 similar.
- the fuel injector 81 includes a valve piece 84 that projects into a pressure relief space 85 that communicates with the pressure relief space 45 in FIG. 1 equivalent.
- the valve piece 84 is fixed in a housing of the fuel injection device 81 by means of a valve clamping nut 86.
- the valve piece 84 limits the combustion chamber side, a control chamber 88 which is limited to the combustion chamber through the combustion chamber remote end of a nozzle needle 90.
- the control chamber 88 corresponds to the control room 28 in FIG FIG. 1 ,
- the control chamber 88 communicates with a valve chamber 93 of a control valve 94 via a drain passage 91, in which an outlet throttle 92 is arranged.
- the control valve 94 comprises a valve seat 95, which in FIG. 3 closed and in FIG. 4 is shown open.
- the valve seat 95 is defined by a sealing edge or sealing surface formed on a valve body 98, which comes to bear on a sealing surface or sealing edge of the valve piece 84 when the valve seat 95 is closed.
- the valve body 98 is designed as a valve sleeve whose interior 96 constitutes a drainage space. In the interior or drain space 96 of the valve body 98, a valve spring 97 is arranged, through which the valve body 98 is biased away from the combustion chamber.
- the valve body 98 is guided with a guide diameter 99 in the valve piece 84 movable back and forth.
- the interior or drain space 96 of the valve body 98 communicates via a connection through-hole 100 with an armature space 102, which is bounded by a sleeve-like end of an armature 104.
- the armature 104 is actuated by an electromagnet 105, which can be energized via electrical connection lines 106, 107.
- the armature 104 is biased by an armature spring 108 against the valve member 84 and the valve body 98.
- the combustion chamber near the end of the armature 104 is guided with an armature guide diameter 110 in a sleeve-like end of the valve member 84 movable back and forth.
- relief through holes 111, 112 are provided, which connect the armature space 102 with the pressure relief space 85.
- FIG. 5 it can be seen that the armature space 102 is bounded radially on the outside by a first contact surface 121, which is formed on the valve body 98.
- a second contact surface 122 which is formed on the valve piece 84, slightly spaced from the first bearing surface 121.
- symbols 124 is in FIG. 5 indicated that the two contact surfaces 121, 122, which are both designed as annular surfaces, are machined together, in particular by grinding, processed. The processing takes place with the valve seat 95 closed.
- FIG. 6 the machined state of the two contact surfaces 121, 122 is shown.
- the two contact surfaces 121, 122 together bear against a mating surface 123, which is likewise designed as an annular surface on the armature 104.
- the mating surface 123 is located with the two contact surfaces 121, 122 in a common plane 125.
- the solenoid 105 is energized via the electrical connections 106, 107. As a result, a magnetic force is generated which is greater than the spring force of the armature spring 108 and acts counter to this. By the magnetic force of the electromagnet 105, the armature 104 is attracted. The movement of the armature 104 allows movement of the valve body 98 upwards, that is to the electromagnet 105 back. This movement of the valve body 98 is assisted by the valve spring 97 and causes the valve seat 95 to open, which ideally has a sealing edge with a sealing diameter which corresponds to the guide diameter 99 of the valve body 98.
- the size of the mating surface 123 designed as an annular surface must be made as small as possible. However, a sufficient overlap of the contact surfaces 121, 122 with the counter surface 123 must be ensured so that the sealing effect is not impaired.
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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)
Description
Die Erfindung betrifft eine Kraftstoffeinspritzvorrichtung zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine, mit einem Steuerventil, das ein Ventilstück umfasst, in welchem ein Ventilkörper zur Darstellung eines Ventilsitzes hin und her bewegbar geführt ist.The invention relates to a fuel injection device for injecting fuel into a combustion chamber of an internal combustion engine, comprising a control valve which comprises a valve piece, in which a valve body for the representation of a valve seat is guided to and fro.
Aus der deutschen Offenlegungsschrift
Aus der
Aufgabe der Erfindung ist es, die Leckage im Betrieb einer Kraftstoffeinspritzvorrichtung gemäß dem Oberbegriff des Anspruchs 1 zu minimieren.The object of the invention is to minimize the leakage during operation of a fuel injection device according to the preamble of
Die Aufgabe ist bei einer Kraftstoffeinspritzvorrichtung zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine, mit einem Steuerventil, das ein Ventilstück umfasst, in welchem ein Ventilkörper zur Darstellung eines Ventilsitzes hin und her bewegbar geführt ist, dadurch gelöst, dass der Ventilkörper an einem Ende eine brennraumferne erste Anlagefläche aufweist, die bei geschlossenem Ventilsitz in einer Ebene mit einer zweiten, an dem Ventilstück ausgebildeten, Anlagefläche so angeordnet ist, dass die beiden Anlageflächen dichtend an einer gemeinsamen Gegenfläche anliegen. Durch die erfindungsgemäße Anordnung der beiden Anlageflächen wird bei geschlossenem Ventilsitz eine zusätzliche Abdichtung geschaffen, wodurch die Leckage im Betrieb der Kraftstoffeinspritzvorrichtung, insbesondere bei hohen Einspritzdrücken, deutlich reduziert werden kann. Dadurch kann die Mengenbilanz der Kraftstoffeinspritzvorrichtung verbessert werden. Darüber hinaus kann ein beim Schließen der Kraftstoffeinspritzvorrichtung verursachter Impuls gedämpft werden, ohne dass die Schließzeit maßgeblich reduziert wird. Dadurch können eine unerwünschte Prellneigung und der Verschleiß deutlich reduziert werden. Der Ventilsitz umfasst eine Dichtkante oder Dichtfläche an dem Ventilkörper, die bei geschlossenem Ventilsitz an einer Dichtfläche oder Dichtkante des Ventilstücks dichtend zur Anlage kommt, um eine Fluidverbindung zwischen einem Steuerraum und einem Druckentlastungsraum oder Rücklauf zu unterbrechen. Bei geöffnetem Ventilsitz wird die Verbindung zwischen dem Steuerraum und dem Druckentlastungsraum oder Rücklauf freigegeben. Die Öffnungsbewegung des Ventilkörpers kann durch einen Aktor eines Magnetventils oder durch einen Piezoaktor initiiert werden. Die Schließbewegung des Ventilkörpers wird vorzugsweise durch eine Feder bewirkt, durch welche der Ventilkörper in seine Schließstellung vorgespannt ist. Die beiden Anlageflächen sind als Ringflächen ausgeführt. Die beiden Ringflächen erstrecken sich bevorzugt in der gemeinsamen Ebene senkrecht zu einer Längsachse der Kraftstoffeinspritzvorrichtung. Der Ventilkörper ist in der Längsrichtung hin und her bewegbar.The object is achieved in a fuel injection device for injecting fuel into a combustion chamber of an internal combustion engine with a control valve comprising a valve piece in which a valve body for showing a valve seat is guided to and fro, achieved by the valve body at one end having combustion chamber remote first contact surface, which is arranged with closed valve seat in a plane with a second, formed on the valve member, contact surface so that the two contact surfaces sealing abut against a common counter surface. The inventive arrangement of the two contact surfaces an additional seal is created with the valve seat closed, whereby the leakage during operation of the fuel injection device, especially at high injection pressures, can be significantly reduced. Thereby, the quantity balance of the fuel injection device can be improved. In addition, a pulse caused when closing the fuel injection device can be damped without the closing time being significantly reduced. As a result, an undesirable bounce and wear can be significantly reduced. The valve seat includes a sealing edge or sealing surface on the valve body sealingly abutting a seal surface or sealing edge of the valve member when the valve seat is closed to interrupt fluid communication between a control chamber and a pressure relief space or return. When the valve seat is open, the connection between the control chamber and the pressure relief chamber or return is released. The opening movement of the valve body can be initiated by an actuator of a solenoid valve or by a piezoelectric actuator. The closing movement of the valve body is preferably effected by a spring, through which the valve body is biased in its closed position. The two contact surfaces are designed as annular surfaces. The two annular surfaces preferably extend in the common plane perpendicular to a longitudinal axis of the fuel injection device. The valve body is reciprocable in the longitudinal direction.
Ein bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzvorrichtung ist dadurch gekennzeichnet, dass die beiden Anlageflächen an einem brennraumfernen Ende des Ventilstücks und des Ventilkörpers vorgesehen sind. Die Gegenfläche ist zum Beispiel an einer Anschlagplatte beziehungsweise einem Anschlagkörper oder an einem Aktor vorgesehen. Die Gegenfläche ist vorzugsweise ebenfalls als Ringfläche ausgeführt.A preferred embodiment of the fuel injection device is characterized in that the two contact surfaces are provided at a combustion chamber distal end of the valve piece and the valve body. The mating surface is provided for example on a stop plate or a stop body or on an actuator. The mating surface is preferably also designed as an annular surface.
Ein weiteres bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzvorrichtung ist dadurch gekennzeichnet, dass der Ventilkörper druckausgeglichen ausgeführt ist. Druckausgeglichene Ausführung bedeutet, dass der Ventilkörper bei geschlossenem Ventilsitz zu gleichen Teilen in Öffnungsrichtung und Schließrichtung mit einem Steuerraumdruck, insbesondere Hochdruck, beaufschlagt ist.A further preferred embodiment of the fuel injection device is characterized in that the valve body is designed to be pressure balanced. Pressure balanced design means that the valve body with the valve seat closed in equal parts in the opening direction and closing direction with a control chamber pressure, in particular high pressure, is applied.
Dadurch kann die zum Öffnen des Steuerventils benötigte Kraft deutlich reduziert werden.As a result, the force required to open the control valve can be significantly reduced.
Ein weiteres bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzvorrichtung ist dadurch gekennzeichnet, dass der Ventilkörper als Ventilhülse ausgeführt ist, die mit der ersten Anlagefläche gegen einen Anker vorgespannt ist und die mit ihrem brennraumnahen Ende bei geschlossenem Ventilsitz an dem Ventilstück zur Anlage kommt. Der Anker, an dem vorzugsweise die Gegenfläche vorgesehen ist, wirkt mit einem Magneten, vorzugsweise einem Elektromagneten, zusammen, um das Steuerventil zu öffnen.A further preferred embodiment of the fuel injection device is characterized in that the valve body is designed as a valve sleeve, which is biased with the first bearing surface against an armature and comes with its combustion chamber near the end with the valve seat to the valve piece to rest. The armature, on which preferably the counter surface is provided, cooperates with a magnet, preferably an electromagnet, to open the control valve.
Ein weiteres bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzvorrichtung ist dadurch gekennzeichnet, dass das brennraumferne Ende der Ventilhülse geschlossen ausgeführt ist und ein Verbindungsdurchgangsloch aufweist, das einen Ablaufraum in der Ventilhülse mit einem Ankerraum verbindet. Das brennraumnahe Ende des Ankers ist, im Längsschnitt betrachtet, vorzugsweise U-förmig ausgebildet. Der Anker ist vorzugsweise in einem Druckentlastungsraum angeordnet, der mit einem Rücklauf in Verbindung steht.A further preferred embodiment of the fuel injection device is characterized in that the combustion chamber remote end of the valve sleeve is designed to be closed and has a connection through hole which connects an outflow space in the valve sleeve with an armature space. The combustion chamber near the end of the armature is, viewed in longitudinal section, preferably U-shaped. The armature is preferably disposed in a pressure relief space communicating with a return.
Ein weiteres bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzvorrichtung ist dadurch gekennzeichnet, dass der Ankerraum über mindestens ein Entlastungsdurchgangsloch mit einem Rücklauf verbunden ist. Durch die Verbindung mit dem Rücklauf wird sichergestellt, dass der Ankerraum bei geschlossenem Ventilsitz mit einem Rücklaufdruck, vorzugsweise Niederdruck, beaufschlagt ist.Another preferred embodiment of the fuel injection device is characterized in that the armature space is connected via at least one relief through-hole with a return. Through the connection with the return ensures that the armature space with closed valve seat with a return pressure, preferably low pressure, is applied.
Ein weiteres bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzvorrichtung ist dadurch gekennzeichnet, dass der Ventilkörper als Ventilbolzen ausgeführt ist, der mit der ersten Anlagefläche gegen einen Anschlagkörper oder eine Anschlagplatte vorgespannt ist und radial innerhalb der ersten Anlagefläche eine Betätigungsdruckwirkfläche aufweist. Die Betätigungsdruckwirkfläche ist vorzugsweise mit einem Kopplerraumdruck eines hydraulischen Kopplers beaufschlagt, der durch ein Aktormodul einer Piezoaktoreinrichtung begrenzt wird. Über den hydraulischen Koppler wird eine Längsbewegung des Aktormoduls, die durch eine Ausdehnung der Piezoaktoreinrichtung bewirkt wird, verstärkt auf den Ventilkörper übertragen.A further preferred embodiment of the fuel injection device is characterized in that the valve body is designed as a valve pin, which is biased with the first contact surface against a stop body or a stop plate and radially within the first contact surface has a Betätigungsdruckwirkfläche. The actuating pressure acting surface is preferably acted upon by a coupler space pressure of a hydraulic coupler which is delimited by an actuator module of a piezoelectric actuator device. Via the hydraulic coupler, a longitudinal movement of the actuator module, which is brought about by an expansion of the piezoelectric actuator device, is transmitted to the valve body in an amplified manner.
Ein weiteres bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzvorrichtung ist dadurch gekennzeichnet, dass der Ventilbolzen zur Darstellung des Ventilsitzes einen Bund aufweist, der zum Öffnen des Ventilsitzes von dem Ventilstück weg bewegbar ist. Die durch die Piezoaktoreinrichtung bewirkte Öffnungsbewegung des Ventilkörpers erfolgt vorzugsweise gegen die Vorspannkraft einer Ventilfeder zum Brennraum hin. Der Bund begrenzt bei geschlossenem Ventilsitz einen mit einem Steuerraumdruck, insbesondere mit Hochdruck, beaufschlagten Ringraum, dessen brennraumfernes Ende von einer Ringfläche einer Druckschulter begrenzt wird, die an dem Ventilkörper ausgebildet ist.A further preferred embodiment of the fuel injection device is characterized in that the valve pin for the representation of the valve seat has a collar which is movable away from the valve piece for opening the valve seat. The opening movement of the valve body caused by the piezoactuator device preferably takes place against the biasing force of a valve spring toward the combustion chamber. When the valve seat is closed, the collar limits an annular space acted upon by a control chamber pressure, in particular at high pressure, whose end remote from the combustion chamber is delimited by an annular surface of a pressure shoulder which is formed on the valve body.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung verschiedene Ausführungsbeispiele im Einzelnen beschrieben sind.Further advantages, features and details of the invention will become apparent from the following description in which, with reference to the drawings, various embodiments are described in detail.
Es zeigen:
Figur 1- eine Kraftstoffeinspritzvorrichtung gemäß einem ersten Ausführungsbeispiel mit einer Piezoaktoreinrichtung im Längsschnitt;
- Figur 2
- einen vergrößerten Ausschnitt aus
mit zwei Anlageflächen, die an einer gemeinsamen Gegenfläche anliegen;Figur 1 Figur 3- einen Ausschnitt aus
gemäß einem zweiten Ausführungsbeispiel mit einem Magnetaktor im Längsschnitt bei geschlossenem Ventilsitz;Figur 1 Figur 4- den gleichen Ausschnitt wie in
bei geöffnetem Ventilsitz;Figur 3 Figur 5- einen Ausschnitt aus
mit zwei Anlageflächen vor einer Bearbeitung undFigur 4 Figur 6- den gleichen Ausschnitt wie in
, wobei sich die beiden bearbeiteten Anlageflächen in Anlage an einer gemeinsamen Gegenfläche befinden.Figur 5
- FIG. 1
- a fuel injection device according to a first embodiment with a piezoelectric actuator in longitudinal section;
- FIG. 2
- an enlarged section
FIG. 1 with two contact surfaces, which abut against a common counter surface; - FIG. 3
- a section from
FIG. 1 according to a second embodiment with a magnetic actuator in longitudinal section with the valve seat closed; - FIG. 4
- the same section as in
FIG. 3 with the valve seat open; - FIG. 5
- a section from
FIG. 4 with two contact surfaces before processing and - FIG. 6
- the same section as in
FIG. 5 , wherein the two machined contact surfaces are in contact with a common counter surface.
In
Eine Düsennadel 10 ist in einem zentralen Durchgangsloch 11 des Düsenkörpers 6 hin und her bewegbar geführt. Ein brennraumnahes Ende der Düsennadel 10 ist in einem Druckraum 12 angeordnet. Die Düsennadel 10 ist durch eine Düsenfeder 13 so vorgespannt, dass ein Düsennadelsitz 14 an einem brennraumnahen Ende der Düsennadel 10 verschlossen ist. Der Düsennadelsitz 14 umfasst eine an der Düsennadel 10 ausgebildete Dichtkante, die an einer konischen Dichtfläche anliegt, die am brennraumfernen Ende des Düsenkörpers 6 ausgebildet ist und von der zwei Einspritzlöcher 15, 16 ausgehen, die den Druckraum 12 mit einem Brennraum 18 einer Brennkraftmaschine verbinden. Bei geschlossenem Düsennadelsitz 14 ist die Verbindung zwischen dem Druckraum 12 und dem Brennraum 18 unterbrochen.A
Der Druckraum 12 steht über einen Hochdruckverbindungskanal 19 mit einem weiteren Druckraum 22 in Verbindung, der wiederum über einen Hochdruckverbindungskanal 23 und einer Hochdruckleitung 24 mit einem zentralen Kraftstoffhochdruckspeicher 25 in Verbindung steht, der auch als Common Rail bezeichnet wird und außerhalb der Kraftstoffeinspritzvorrichtung 1 angeordnet ist. Die beiden Druckräume 12, 22 im Inneren der Kraftstoffeinspritzvorrichtung 1 werden aus dem zentralen Kraftstoffhochdruckspeicher 25 mit Kraftstoff befüllt, der mit Hochdruck beaufschlagt ist. Wenn sich die Düsennadel 10 vom Brennraum 18 weg bewegt, dann wird der Düsennadelsitz 14 am brennraumnahen Ende der Düsennadel 10 geöffnet, so dass mit Hochdruck beaufschlagter Kraftstoff aus dem Druckraum 12 über die Einspritzlöcher 15, 16 in den Brennraum 18 eingespritzt wird. Die Öffnungsbewegung der Düsennadel 10 wird über den Druck in einem Steuerraum 28 gesteuert, der in einer Düsennadelhülse 27 vom brennraumfernen Ende 26 der Düsennadel 10 begrenzt wird.The
Der Steuerraum 28, der auch als Düsennadelsteuerraum bezeichnet wird, steht über einen Zulaufkanal 30, der mit einer Zulaufdrossel versehen ist, mit dem Hochdruckverbindungskanal 23 in Verbindung. Über einen Ablaufkanal 31, in dem eine Ablaufdrossel 32 angeordnet ist, steht der Steuerraum 28 mit einem Ablaufraum 33 in Verbindung, der wiederum über einen weiteren Ablaufkanal 34 mit einem Ventilraum 35 eines Steuerventils 36 in Verbindung steht. Der Zulaufkanal 30 und der Ablaufkanal 31 erstrecken sich durch die Drosselplatte 5. Der Ablaufraum 33 und der Ablaufkanal 34 sind in dem Ventilstück 4 ausgebildet.The
Das Steuerventil 36 umfasst einen Ventilkörper 37, der einen Bund 38 aufweist. Der Bund 38 umfasst eine Dichtkante oder Dichtfläche, die sich im dargestellten geschlossenen Zustand des Steuerventils 36 an einer Dichtfläche oder Dichtkante in Anlage befindet, die an dem Ventilstück 4 ausgebildet ist. Der Bund 38 dient zur Darstellung eines Ventilsitzes 39, der in dem in
Der Federraum 40 steht über Druckentlastungskanäle 42, 43, 44 mit einem Druckentlastungsraum 45 am brennraumfernen Ende der Kraftstoffeinspritzvorrichtung 1 in Verbindung. Der Druckentlastungsraum 45 steht über eine Rücklaufleitung 46, in der eine Rücklaufdrossel 47 angeordnet, ist, mit einem Rücklauftank 48 in Verbindung. Der Rücklauftank 48 ist ebenso wie der Druckentlastungsraum 45 und die Druckentlastungskanäle 42, 43, 44 mit einem Rücklaufdruck oder Niederdruck beaufschlagt, der deutlich kleiner als der Hochdruck in dem zentralen Kraftstoffhochdruckspeicher 25 und den Druckräumen 12, 22 im Inneren der Kraftstoffeinspritzvorrichtung 1 ist.The
Zwischen dem Ventilstück 4 und der Anschlagplatte 3 ist ein Ringraum 50 ausgebildet, der über einen Druckentlastungskanal 49 mit dem Druckentlastungsraum 45 in Verbindung steht. Von dem Ringraum 50 erstreckt sich eine Entlastungsnut 51 in das Ventilstück 4. Die Entlastungsnut 51 erstreckt sich um einen Führungsbereich 52 herum, in welchem der Ventilkörper 37 hin und her bewegbar geführt ist. Der Ventilkörper 37 ist als Ventilbolzen 54 ausgeführt, der in einem Durchgangsloch des Ventilstücks 4 hin und her bewegbar geführt ist. Durch die Führung des Ventilbolzens 54 in dem Ventilstück 4 wird eine Leckagepfad 55 geschaffen, über den Leckage aus dem Ventilraum 35 des Steuerventils 36 in den Ringraum 50 gelangt, der mit dem Rücklauf in Verbindung steht. Der Führungsdurchmesser des Ventilskörpers 37 beziehungsweise des Ventilbolzens 54 ist mit 56 bezeichnet.Between the
In dem Führungsbereich 52 ist in dem Ventilstück 4 eine Hochdrucktasche 58 vorgesehen, die dazu dient, Längenänderungen an dem Ventilbolzen 54 durch Raildruckänderungen im Bereich einer Länge 59 im gleichen Maße am Ventilstück 4 zu kompensieren. Eine hochdruckbelastete Fläche 67 am Ventilstück 4 muss daher annähernd gleich einer hochdruckbelasteten Fläche 68 an dem Ventilbolzen 54 sein. Dabei ist die Hochdrucktasche 58 so angeordnet, dass sie keinen Einfluss auf die Funktion des Steuerventils 36 hat. Die Hochdrucktasche 58 überschneidet sich sowohl im geschlossenen als auch im geöffneten Zustand des Ventilsitzes 39 nicht mit dem Ventilraum 35. Durch die räumliche Trennung über den Führungsdurchmesser 56 wird beim Öffnen des Steuerventils 36 ein schnellerer Abbau des Drucks im Ventilraum 35 und somit ein schnellerer Druckabbau im Steuerraum 28 ermöglicht. Dadurch wiederum kann ein schnelleres Öffnen der Düsennadel 10 erreicht werden.In the
Das brennraumferne Ende des Ventilkörpers 37 beziehungsweise des Ventilbolzens 54 begrenzt einen Betätigungsdruckraum 60, der über ein Durchgangsloch der Anschlagplatte 3 mit einem Kopplerraum 61 in Verbindung steht, der mit einem Hydraulikmedium gefüllt ist. Der Kopplerraum 61 wird durch einen Aktorkörper 63 begrenzt, der auch als Aktormodul bezeichnet wird. Der Aktorkörper 63 ist durch eine Aktorfeder 65 von der Anschlagplatte 3 weg gegen eine Piezoaktoreinrichtung 64 vorgespannt. Wenn die Piezoaktoreinrichtung 64 bestromt wird, dann dehnt sie sich aus, wodurch der Aktorkörper 63 auf die Anschlagplatte 3 zu bewegt wird. Dabei erhöht sich der Druck in dem Kopplerraum 61 und dem Betätigungsdruckraum 60 am brennraumfernen Ende des Ventilkörpers 37 beziehungsweise des Ventilbolzens 54. Die Druckerhöhung in dem Betätigungsdruckraum 60 führt dazu, dass der Ventilkörper 37 gegen die Vorspannkraft der Ventilfeder 41 zum Brennraum 18 hin bewegt wird, so dass der Ventilsitz 39 geöffnet wird.The combustion chamber remote end of the
Gemäß einem wesentlichen Aspekt der Erfindung ist die Länge 59 zwischen dem Ventilsitz 39 und dem brennraumfernen Ende des Ventilstücks 4 und des Ventilkörpers 37 vor und nach der Montage identisch. In der vergrößerten Darstellung der
In
Zum Durchführen einer Einspritzung mit der Kraftstoffeinspritzvorrichtung 1 wird die Piezoaktoreinrichtung 64 bestromt, so dass sie ihren längsten Zustand einnimmt. Die Längenänderung der Piezoaktoreinrichtung 64 führt über den Aktorkörper 63 zu einer Druckerhöhung im Kopplerraum 61. Durch die Druckerhöhung wird der Ventilbolzen 54 in einem definierten Übersetzungsverhältnis gegen die Vorspannkraft der Ventilfeder 41 aus dem Ventilsitz 39 gedrückt. Gleichzeitig wird der Dichtverband 71, 72, 73 aufgehoben. Solange sich der Ventilbolzen 54 in seiner Öffnungsstellung befindet, ist der Leckagepfad 55 geöffnet. Der Druck in der Hochdrucktasche 58 baut sich langsam über den Leckagepfad 55 und über den Ventilraum 35 ab. Aus dem Steuerraum 28 entweicht über die Ablaufdrossel 32, den Ablaufkanal 31, den Ablaufraum 33, den Ablaufkanal 34, den Ventilraum 35 und über den geöffneten Ventilsitz 39 Kraftstoff in den Federraum 40 und somit über die Druckentlastungskanäle 42, 43, 44 in den Druckentlastungsraum 45.To perform an injection with the
Um die Einspritzung zu beenden, wird der Aktorkörper 63 durch die Aktorfeder 65 zurückgestellt, so dass der Druck im Kopplerraum 61 und in dem Betätigungsdruckraum 60 absinkt. Dadurch wird der Ventilbolzen 54 zur Anschlagplatte 3 hin gezogen, wodurch der Ventilsitz 39 geschlossen wird. Daraufhin steigt der Druck in dem Ventilraum 35 und zeitverzögert auch in der Hochdrucktasche 58 auf Raildruckniveau an, sodass raildruckbedingte Längenunterschiede zwischen dem Ventilkörper 37 und dem Ventilstück 4 ausgeglichen werden.To end the injection, the
In den
Der Steuerraum 88 steht über einen Ablaufkanal 91, in dem eine Ablaufdrossel 92 angeordnet ist, mit einem Ventilraum 93 eines Steuerventils 94 in Verbindung. Das Steuerventil 94 umfasst einen Ventilsitz 95, der in
In
In
Wenn mit der Kraftstoffeinspritzvorrichtung 81 eine Einspritzung betätigt werden soll, dann wird der Elektromagnet 105 über die elektrischen Anschlüsse 106, 107 bestromt. Dadurch wird eine Magnetkraft erzeugt, die größer als die Federkraft der Ankerfeder 108 ist und entgegengerichtet zu dieser wirkt. Durch die Magnetkraft des Elektromagneten 105 wird der Anker 104 angezogen. Die Bewegung des Ankers 104 ermöglicht eine Bewegung des Ventilkörpers 98 nach oben, das heißt zum Elektromagneten 105 hin. Diese Bewegung des Ventilkörpers 98 wird durch die Ventilfeder 97 unterstützt und bewirkt ein Öffnen des Ventilsitzes 95, der idealerweise eine Dichtkante mit einem Dichtdurchmesser aufweist, der dem Führungsdurchmesser 99 des Ventilkörpers 98 entspricht. Bei geöffnetem Ventilsitz 95 kann eine Absteuermenge aus dem Steuerraum 88 über den Ablaufkanal 91 mit der Ablaufdrossel, den Ventilraum 93, den Ablaufraum 96, das Verbindungsdurchgangsloch 100, den Ankerraum 102 und die Entlastungsdurchgangslöcher 111, 112 in den Druckentlastungsraum 85 entweichen. Das führt zu einem Druckabfall im Steuerraum 88 und somit zu einem Öffnen der Düsennadel 90.If an injection is to be actuated with the fuel injector 81, then the
Wenn die Einspritzung der Kraftstoffeinspritzvorrichtung 81 beendet werden soll, dann wird die Bestromung des Elektromagneten 105 beendet. Durch die Vorspannkraft der Ankerfeder 108 wird der Anker 104 mit dem Ventilkörper 98 entgegen der Vorspannkraft der Ventilfeder 97, die deutlich geringer als die Ankerfederkraft ist, nach unten, das heißt gegen das Ventilstück 84, gedrückt, bis der Ventilsitz 95 geschlossen ist und die Anlageflächen 121, 122 mit der Gegenfläche 123 in der gemeinsamen Ebene 125 angeordnet werden, wie man in
Um bei einer möglichen Druckunterwanderung der Gegenfläche 123 ein Abheben des Ankers 104 und somit der Ventilhülse beziehungsweise dem Ventilkörper 98 zu verhindern, muss die Größe der als Ringfläche ausgeführten Gegenfläche 123 so klein wie möglich gestaltet werden. Allerdings muss eine ausreichende Überdeckung der Anlageflächen 121, 122 mit der Gegenfläche 123 sichergestellt werden, damit die Dichtwirkung nicht beeinträchtigt wird.In order to prevent lift-off of the
Claims (8)
- Fuel injection device for injecting fuel into a combustion chamber (18) of an internal combustion engine, having a control valve (36; 94) which comprises a valve piece (4; 84) in which a valve body (37; 98) is guided so as to be movable back and forth in order to represent a valve seat (39; 95), wherein the valve body (37; 98) has a first contact surface (71; 121) at an end remote from the combustion chamber,
characterized in that,
with the valve seat (39; 95) closed, the first contact surface (71; 121) is arranged in a plane (125) with a second contact surface (72; 122), formed on the valve piece (4; 84), such that the two contact surfaces (71, 72; 121, 122) bear in a sealing manner against a common mating surface (73; 123), wherein the two contact surfaces (71, 72; 121, 122) are embodied as annular surfaces. - Fuel injection device according to one of the preceding claims, characterized in that the two contact surfaces (71, 72; 121, 122) are provided at an end of the valve piece (4; 84) and of the valve body (37; 98) that is remote from the combustion chamber.
- Fuel injection device according to either of the preceding claims, characterized in that the valve body (37; 98) is embodied in a pressure-balanced manner.
- Fuel injection device according to one of the preceding claims, characterized in that the valve body (98) is embodied as a valve sleeve, which is preloaded with the first contact surface (121) against an armature (104) and which comes into abutment against the valve piece (84) with its end facing the combustion chamber with the valve seat (95) closed.
- Fuel injection device according to Claim 4, characterized in that that end of the valve sleeve (98) that is remote from the combustion chamber is embodied in a closed manner and has a connecting through-hole (100), which connects an outflow chamber (96) in the valve sleeve to an armature space (102).
- Fuel injection device according to Claim 5, characterized in that the armature space (102) is connected to a return line via at least one relief through-hole (111, 112).
- Fuel injection device according to one of Claims 1 to 3, characterized in that the valve body (37) is embodied as a valve bolt (54), which is preloaded with the first contact surface (71) against a stop body (3) and, radially inside the first contact surface (71), has an actuating pressure effective area.
- Fuel injection device according to Claim 7, characterized in that, in order to represent the valve seat (39), the valve bolt (54) has a collar (38), which is movable away from the valve piece (4) in order to open the valve seat.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009045995A DE102009045995A1 (en) | 2009-10-26 | 2009-10-26 | Fuel injector |
PCT/EP2010/064068 WO2011051060A1 (en) | 2009-10-26 | 2010-09-23 | Fuel injection device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2494182A1 EP2494182A1 (en) | 2012-09-05 |
EP2494182B1 true EP2494182B1 (en) | 2018-11-21 |
Family
ID=43125604
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP10759858.3A Not-in-force EP2494182B1 (en) | 2009-10-26 | 2010-09-23 | Fuel injection device |
Country Status (5)
Country | Link |
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EP (1) | EP2494182B1 (en) |
CN (1) | CN102597484A (en) |
DE (1) | DE102009045995A1 (en) |
IN (1) | IN2012DN02065A (en) |
WO (1) | WO2011051060A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013045690A1 (en) | 2011-10-01 | 2013-04-04 | Robert Bosch Gmbh | An injection valve resistant to cavitation |
DE102014205517A1 (en) * | 2014-03-25 | 2015-10-01 | Robert Bosch Gmbh | Switching valve for a fuel injector and fuel injector |
DE102014206210A1 (en) * | 2014-04-01 | 2015-10-01 | Robert Bosch Gmbh | fuel injector |
GB2547684A (en) * | 2016-02-26 | 2017-08-30 | Delphi Int Operations Luxembourg Sarl | Fuel injector for a combustion engine |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE10023960A1 (en) * | 2000-05-16 | 2001-11-22 | Bosch Gmbh Robert | Fuel injection device for internal combustion engine has choke gap formed between choke section upstream of valve seat in bore and casing surface |
DE10250720A1 (en) * | 2002-10-31 | 2004-05-13 | Robert Bosch Gmbh | Injector |
US7243902B2 (en) * | 2002-11-08 | 2007-07-17 | Robert Bosch Gmbh | Pressure-compensated, directly controlled valve |
DE102006021741A1 (en) | 2006-05-10 | 2007-11-15 | Robert Bosch Gmbh | Fuel injector with pressure compensated control valve |
DE102006049050A1 (en) * | 2006-10-18 | 2008-04-30 | Robert Bosch Gmbh | Injector for injecting fuel |
DE102007042466B3 (en) * | 2007-09-06 | 2009-04-09 | Continental Automotive Gmbh | Injection system with reduced switching leakage and method of manufacturing an injection system |
-
2009
- 2009-10-26 DE DE102009045995A patent/DE102009045995A1/en not_active Withdrawn
-
2010
- 2010-09-23 EP EP10759858.3A patent/EP2494182B1/en not_active Not-in-force
- 2010-09-23 WO PCT/EP2010/064068 patent/WO2011051060A1/en active Application Filing
- 2010-09-23 CN CN2010800483666A patent/CN102597484A/en active Pending
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2012
- 2012-03-07 IN IN2065DEN2012 patent/IN2012DN02065A/en unknown
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Also Published As
Publication number | Publication date |
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EP2494182A1 (en) | 2012-09-05 |
WO2011051060A1 (en) | 2011-05-05 |
DE102009045995A1 (en) | 2011-06-09 |
IN2012DN02065A (en) | 2015-08-21 |
CN102597484A (en) | 2012-07-18 |
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