EP1507082B1 - Fuel injection system for combustion engine - Google Patents
Fuel injection system for combustion engine Download PDFInfo
- Publication number
- EP1507082B1 EP1507082B1 EP04015171A EP04015171A EP1507082B1 EP 1507082 B1 EP1507082 B1 EP 1507082B1 EP 04015171 A EP04015171 A EP 04015171A EP 04015171 A EP04015171 A EP 04015171A EP 1507082 B1 EP1507082 B1 EP 1507082B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- control
- fuel injection
- space
- 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.)
- Expired - Lifetime
Links
- 239000000446 fuel Substances 0.000 title claims description 54
- 238000002347 injection Methods 0.000 title claims description 37
- 239000007924 injection Substances 0.000 title claims description 37
- 238000002485 combustion reaction Methods 0.000 title claims description 8
- 238000007789 sealing Methods 0.000 claims description 13
- 230000005540 biological transmission Effects 0.000 description 4
- 238000004891 communication Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 239000002828 fuel tank Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
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
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0028—Valves characterised by the valve actuating means hydraulic
- F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
-
- 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
- F02M47/025—Hydraulically 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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
-
- 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
- F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
- F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
Definitions
- the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1.
- a fuel injection device for internal combustion engines of this type is known from EP 1 176 306 A2 known, in which for controlling a fuel injection valve, a servo control circuit is provided with a control valve having a longitudinally displaceable in a bore control piston, which controlled by a solenoid valve as a switching valve, the pressure control of the fuel injection valve realized.
- the control valve in this case has a first valve seat, which limits a first pressure chamber, and designed as a slide seal second valve seat, which limits a second pressure chamber on.
- the fuel injection device is designed without an intermediate pressure accumulator and fuel injection valve intermediate pressure booster.
- a fuel injection device for internal combustion engines with a pressure booster for pressure amplification is known in which a 3/2-valve is used to control the injector.
- a 3/2-valve is used to control the injector.
- Such, designed as servo valves 3/2 valves generally have an electromagnetically or piezoelectrically controlled switching valve and a control valve with a control piston, which is controlled by the switching valve.
- Such control valves which are constructed in seat slide version, have to control a large return flow of the pressure booster device.
- the fuel injection device with the characterizing features of claim 1 has the advantage that a proportional to the switching pressure force acts on the valve body from the outside, so that the forces acting at the critical points of the control piston and the valve body pressure forces are compensated and thereby in the control valve acting deformation forces can be kept low.
- the proportional force is generated by the applied pressure in the fuel line, which is supplied for example by a fuel pump and is present as system pressure.
- no high notch stresses occur in the bore intersections of the valve body.
- the wear on the control edges of valve seats is reduced. The occurring stresses remain well below the fatigue strength values, which simplifies the manufacturing processes to be used and allows less expensive materials to be used. This makes it possible to provide a cheaper fuel injection device.
- An expedient embodiment is that leads from the annulus a transverse bore in the cooperating with the control valve valve pressure chamber. About this transverse bore of the pressure equalization between inner chambers of the control valve and an outer chamber formed by an annular space takes place.
- the invention is for driving suitable fuel injection devices with a pressure booster, wherein the control edges of the control piston alternately allow a connection of a differential pressure chamber of the pressure booster to a high pressure line in communication with the high pressure chamber or a connection to a connected to a return line low pressure system.
- a fuel injection device is shown with a fuel injector 1, which is connected via a fuel line 3 with a high-pressure fuel source 5.
- the high-pressure fuel source 5 comprises several elements not shown, such as fuel tank, a high-pressure pump and a high-pressure line, for example, a known common rail system, wherein the pump provides up to 1600 bar high fuel pressure via the high pressure line.
- the fuel injector 1 shown has a fuel injection valve 10, which projects with injection openings 11 in a combustion chamber of an internal combustion engine.
- the fuel injection valve 10 has a closing piston 12 with a pressure shoulder 13, which is surrounded by a pressure chamber 14.
- the closing piston 12 is guided at an end facing away from the combustion chamber in a guide region 15, to which a closing pressure chamber 16 connects.
- the closing piston 12 is biased by a closing spring 17 in the closing direction.
- the pressure booster device 20 has a booster piston 21 which is mounted in a spring-loaded manner by means of a return spring 18 and has a first partial piston 22 and a smaller diameter partial piston 23.
- the partial pistons 22, 23 are each assigned a corresponding, stepped diameter-shaped cylinder 24, so that the smaller-diameter partial piston 23 in the cylinder 24 separates a high pressure chamber 25 from a rear space 26 liquid-tight.
- the larger diameter first partial piston 22, which is guided in the cylinder portion of the cylinder 24 with the larger diameter, also separates the back space 26 of a pressure transmission chamber 27 from liquid-tight.
- a return spring 18 is arranged, which is biased to produce a corresponding return movement for the booster piston 21 between a spring holder 28 and a ring member 29.
- the fuel injector 1 has an electro-hydraulic servo-valve 90, which comprises a hydraulic control valve 30 and an electrically controllable switching valve 40, wherein the control of an electromagnetic or piezoelectric actuator 41 takes place.
- the switching valve 40 has an actuator piston 42 connected to the actuator 41, which is guided in an actuator bore 43.
- the actuator piston 42 separates with an actuator-side sealing seat 44 an actuator-side leakage chamber 45 from an actuator-side annular space 46 liquid-tight.
- the control valve 30 it is also possible to form the control valve 30 as a directly controlled valve.
- the actuator 41 is directly connected to the control piston 70, so that the switching movement of the actuator 41 is transmitted directly to the control piston (30) and the switching movement of the actuator 41 performs the stroke movement of the control piston 70.
- the control valve 30 has a valve body 31 with a receptacle 39 for a socket 80.
- a stepped bore 32 is formed, which opens into a control chamber 33 and at the opposite end into a connecting space 36.
- a valve chamber 34 and a valve pressure chamber 35 are formed by the stepped bore 32.
- a control piston 70 is guided axially displaceable.
- the control piston 70 is also stepped with a first piston portion 71 and a second piston portion 72 executed, wherein the first piston portion 71 has a larger piston diameter than the second piston portion 72.
- the face of the The first piston section 71 forms a first pressure surface 78.
- the stepped design of the control piston 70 creates an annular surface between the first piston section 71 and the second piston section 72, which acts as a second pressure surface 79.
- the first pressure surface 78 is larger than the second pressure surface 79.
- On the control piston 70 a first control edge 73 and a second control edge 74 are further formed.
- the sleeve 80 is surrounded in the receptacle 39 by an annular space 82 which is pressure-tightly sealed with a cover 83 and a seal 84 on the valve body 31.
- the annular space 82 communicates with the fuel line 3 (rail), so that the pressure supplied by the fuel pump 5 as a system pressure in the annular space 82 is applied and thereby the sleeve 80 is acted upon by the voltage applied to the fuel line 3 system pressure.
- a transverse bore 85 is attached, which connects the annular space 82 with the valve pressure chamber 35. From the annular space 82 further leads a connecting bore 55 to the pressure transmission chamber 27.
- the first piston portion 71 performs a further connecting line 57, which connects the control chamber 33 via an inlet throttle 56 with the valve pressure chamber 35.
- the system pressurized fuel line 3 is connected to the annular space 82.
- a connecting channel 37 is formed, which connects the valve pressure chamber 35 with the first control edge 73 upstream valve chamber 34 in the switching position shown.
- a sealing edge 75 is executed, which cooperates with the second control edge 74 and forms with this according to a second switching position of the control valve 30 described later, a sealing surface.
- pressure booster 20 To connect the individual components injection valve 10, pressure booster 20, control valve 30 and switching valve 40, are used pressure lines, which are integrated, for example, in the fuel injector 1.
- the pressure chamber 14 of the fuel injection valve 10 is connected to a first pressure line 51 to the high-pressure chamber 25 of the pressure booster 20.
- a second pressure line 52 leads to the rear space 26 of the pressure booster 20.
- the hydraulic pressure of the high-pressure fuel source 5 is on the High pressure line 3 and the connecting hole 55 in the pressure booster chamber 27 of the pressure booster 20 performed.
- the pressure transmission chamber 27 is characterized by the transverse bore 85 with the valve pressure chamber 35 of the control valve 30 in conjunction.
- a return space line 58 connects the rear space 26 of the pressure booster 20 with the valve chamber 34 of the control valve 30.
- connection space 36 of the control valve 30 From the connection space 36 of the control valve 30 performs a first return line 61 via a not shown in the drawing low-pressure system in a likewise not shown fuel tank.
- the control chamber 33 of the control valve 30 is connected by means of a control line 59 via an outlet throttle 64 with the actuator-side annular space 46 of the switching valve 40.
- a second return line 62 leads out of the actuator-side leakage chamber 45 of the switching valve 40 into the low-pressure or return system.
- the return lines 61, 62 may also be formed as a common return system.
- FIG. 2 A second embodiment starts FIG. 2 out.
- the same components of the fuel injector 1 are provided with the same reference numerals.
- the peculiarities of the embodiment according to FIG. 2 in comparison to the embodiment in FIG. 1 is that the sleeve 80 is made of several parts.
- the socket 80 has a valve chamber bushing 91, a setting bush 92 and a valve plate 93.
- the valve chamber liner 91 has substantially the same function as the one-piece liner 80 of the embodiment in FIG FIG. 1 , By adjoining the valve chamber bush 91 axially adjusting bushing 92, it is possible to adjust the position of the cooperating with the second control edge 74 sealing edge 75.
- the adjusting bush 92 having different thicknesses can be provided as a selection group.
- the valve plate 93 is optionally provided, if a direct sealing on the valve body 31 at the seat of the first control edge 73 for material reasons is not possible. In this case, the valve plate 93 would be made of a material suitable for the formation of a valve seat necessary for the second control edge 74.
- the operation of the fuel injector 1 is as shown below: At the beginning of the injection process is due to the constant pressure in the high-pressure accumulator 5 the voltage applied in the pressure booster 27 pressure on the back room line 58 in the back room 26 and via the second pressure line 52 and the connecting line 53 in the high-pressure chamber 25th and from there via the first pressure line 51 in the pressure chamber 14.
- the actuator 41 of the switching valve 40 which is a solenoid valve in the present embodiment, is energized so that the actuator piston 42 closes the control line 59, which is in communication with the control chamber 33 of the control valve 30, against the actuator-side leakage chamber 45 which is in communication with the second return line 62 ,
- the same pressure prevails in the control chamber 33 as in the annular space 82 communicating with the pressure transmission chamber 27 via the further connecting line 57.
- the first die edge 73 is pressed against the sealing seat by the high pressure acting on the first pressure surface 78.
- the connecting chamber 36 and thus the first return line 61 is decoupled from the high pressure or system pressure.
- the injection valve 10 is closed.
- the opening stroke of the closing piston 12 of the injection valve 10 is initiated by lifting the actuator piston 42 from the actuator-side sealing seat 44 due to a corresponding energization of the actuator 41, so that the control chamber 33 is connected to the actuator-side annular space 46 and the actuator-side leakage chamber 55.
- the flow resistances of the inlet throttle 56 and the outlet throttle 64 are dimensioned such that the pressure in the control chamber 33 drops and the control piston 70 lifts off from the sealing seat of the first control edge 73.
- the pressure in the pressure booster chamber 27 acts on the second, smaller pressure surface 79, so that it continues its opening movement and closes the valve pressure chamber 35 to the valve chamber 34 with the second control edge 74 and blocks the high pressure to the connecting space 36.
- the rear space 26 is connected to the first return line 61 via the back-room line 58, the valve chamber 34 and the connecting space 36. Accordingly, the pressure prevailing in the rear space 26 of the pressure booster 20 high pressure on the return line 61 is released and the pressure in the rear chamber 26 drops. As a result, the pressure booster device 20 is activated and the lower effective area afflicted second partial piston 23 compresses the fuel in the high pressure chamber 25, so that in the pressure chamber 14 connected to the high pressure chamber 25 in the opening direction of the pressure shoulder 13 acting pressure force increases and the closing piston 12, the injection openings eleventh releases. As long as the back space 26 is depressurized, the remains Pressure booster 20 activates and compresses the fuel in the high-pressure chamber 25th
- the switching valve 40 is returned to its initial position. This separates the back space 26 from the first return line 61 and connects it again to the supply pressure of the high-pressure fuel source 5. As a result, the pressure in the high-pressure chamber 25 drops to system pressure, whereby system pressure is likewise applied again in the pressure chamber 14.
- the provision of the closing piston 12 is supported by the closing pressure chamber 16 arranged in the closing spring 17 and realized by the also applied via the second pressure line 52 system pressure. After pressure equalization of the pressure booster piston 21 is returned by the return spring 18 in its initial position, the high-pressure chamber 25 is filled via the connecting line 53 from the high-pressure fuel source 5.
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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 Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection device for internal combustion engines according to the preamble of
Eine Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen dieser Art ist aus der
Aus der
Aus der
Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass eine dem zu schaltenden Druck proportionale Kraft von außen auf den Ventilkörper einwirkt, so dass die an den kritischen Stellen des Steuerkolbens und des Ventilkörpers wirkenden Druckkräfte kompensiert werden und dadurch die im Steuerventil wirkenden Verformungskräfte gering gehalten werden können. Die proportionale Kraft wird dabei von dem in der Kraftstoffleitung anliegenden Druck erzeugt, der beispielsweise von einer Kraftstoffpumpe geliefert wird und als Systemdruck vorliegt. Dadurch treten keine hohen Kerbspannungen in den Bohrungsverschneidungen des Ventilkörpers auf. Außerdem wird der Verschleiß an den Steuerkanten von Schiebersitzen reduziert. Die auftretenden Spannungen bleiben deutlich unter den Dauerfestigkeitswerten, wodurch die einzusetzenden Fertigungsverfahren vereinfacht und kostengünstigere Werkstoffe eingesetzt werden können. Dadurch ist die Bereitstellung einer kostengünstigeren Kraftstoffeinspritzeinrichtung möglich.The fuel injection device according to the invention with the characterizing features of
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Kraftstoffeinspritzeinrichtung möglich.The measures listed in the dependent claims advantageous refinements and improvements of the main claim fuel injector are possible.
Eine zweckmäßige Ausführungsform besteht darin, dass von dem Ringraum eine Querbohrung in die mit dem Steuerkolben zusammenwirkende Ventildruckraum führt. Über diese Querbohrung erfolgt der Druckausgleich zwischen Innenkammern des Steuerventils und einer vom einem Ringraum gebildeten Außenkammer. Die Erfindung ist zur Ansteuerung von Kraftstoffeinspritzeinrichtungen mit einem Druckverstärker geeignet, wobei die Steuerkanten des Steuerkolbens wechselweise eine Zuschaltung eines Differenzdruckraumes des Druckverstärkers zu einem mit der Hochdruckleitung in Verbindung stehenden Hochdruckraum oder eine Zuschaltung zu einem an eine Rücklaufleitung angeschlossenen Niederdrucksystem ermöglichen.An expedient embodiment is that leads from the annulus a transverse bore in the cooperating with the control valve valve pressure chamber. About this transverse bore of the pressure equalization between inner chambers of the control valve and an outer chamber formed by an annular space takes place. The invention is for driving suitable fuel injection devices with a pressure booster, wherein the control edges of the control piston alternately allow a connection of a differential pressure chamber of the pressure booster to a high pressure line in communication with the high pressure chamber or a connection to a connected to a return line low pressure system.
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- einen schematischen Aufbau einer Kraftstoffeinspritzeinrichtung gemäß einem ersten Ausführungsbeispiel und
- Figur 2
- eine schematischen Aufbau einer Kraftstoffeinspritzeinrichtung gemäß einem zweiten Ausführungsbeispiel.
- FIG. 1
- a schematic structure of a fuel injection device according to a first embodiment and
- FIG. 2
- a schematic structure of a fuel injection device according to a second embodiment.
In
Der Kraftstoffinjektor 1 gemäß
Weiterhin verfügt der Kraftstoffinjektor 1 über ein elektrohydraulisches Servo-Ventil 90, das ein hydraulisches Steuerventil 30 und ein elektrisch ansteuerbares Schaltventil 40 umfasst, wobei die Ansteuerung von einem elektromagnetischen oder piezoelektrischen Aktor 41 erfolgt. Das Schaltventil 40 weist einen mit dem Aktor 41 verbundenen Aktorkolben 42 auf, der in einer Aktorbohrung 43 geführt ist. Der Aktorkolben 42 trennt mit einem aktorseitigen Dichtsitz 44 einen aktorseitigen Leckraum 45 von einem aktorseitigen Ringraum 46 flüssigkeitsdicht ab. Es ist aber genauso möglich, das Steuerventil 30 als direkt gesteuertes Ventil auszubilden. Dazu ist der Aktor 41 direkt mit dem Steuerkolben 70 verbunden, so dass die Schaltbewegung des Aktors 41 direkt auf den Steuerkolben (30) übertragen wird und die Schaltbewegung des Aktors 41 die Hubbewegung des Steuerkolbens 70 ausführt.Furthermore, the
Das Steuerventil 30 weist einen Ventilkörper 31 mit einer Aufnahme 39 für eine Buchse 80 auf. In der Buchse 80 ist eine Stufenbohrung 32 ausgebildet, die in einen Steuerraum 33 und am gegenüberliegenden Ende in einen Verbindungsraum 36 mündet. Zwischen dem Steuerraum 33 und Verbindungsraum 36 wird von der Stufenbohrung 32 eine Ventilkammer 34 und ein Ventildruckraum 35 ausgebildet. In der Stufenbohrung 32 des Steuerventils 30 ist axial verschiebbar ein Steuerkolben 70 geführt. Der Steuerkoben 70 ist ebenfalls gestuft mit einem ersten Kolbenabschnitt 71 und einem zweiten Kolbenabschnitt 72 ausgeführt, wobei der erste Kolbenabschnitt 71 einen größeren Kolbendurchmesser als der zweite Kolbenabschnitt 72 aufweist. Die Stirnfläche des ersten Kolbenabschnitts 71 bildet eine erste Druckfläche 78. Durch die gestufte Ausführung des Steuerkolbens 70 entsteht zwischen dem ersten Kolbenabschnitt 71 und dem zweiten Kolbenabschnitt 72 eine Ringfläche, die als zweite Druckfläche 79 wirkt. Die erste Druckfläche 78 ist dabei größer als die zweite Druckfläche 79. Am Steuerkolben 70 sind ferner eine erste Steuerkante 73 und eine zweite Steuerkante 74 ausgebildet.The
Die Buchse 80 ist in der Aufnahme 39 von einem Ringraum 82 umgeben, der mit einer Abdeckung 83 und einer Dichtung 84 am Ventilkörper 31 druckdicht verschlossen ist. Der Ringraum 82 steht mit der Kraftstoffleitung 3 (Rail) in Verbindung, so dass der von der Kraftstoffpumpe 5 gelieferte Druck als Systemdruck im Ringraum 82 anliegt und dadurch die Buchse 80 mit dem in der Kraftstoffleitung 3 anliegenden Systemdruck beaufschlagt ist. In der Buchse 80 ist eine Querbohrung 85 angebracht, die den Ringraum 82 mit dem Ventildruckraum 35 verbindet. Vom Ringraum 82 führt weiterhin eine Verbindungsbohrung 55 zum Druckübersetzungsraum 27. Durch den ersten Kolbenabschnitt 71 führt eine weitere Verbindungsleitung 57, die den Steuerraum 33 über eine Zulaufdrossel 56 mit dem Ventildruckraum 35 verbindet. An den Ringraum 82 ist die systemdruckbeaufschlagte Kraftstoffleitung 3 angeschlossen.The
Am zweiten Kolbenabschnitt 72 ist ein Verbindungskanal 37 ausgebildet, der in der gezeigten Schaltstellung den Ventildruckraum 35 mit der der ersten Steuerkante 73 vorgelagerten Ventilkammer 34 verbindet. An der Stufenbohrung 32 ist eine Dichtkante 75 ausgeführt, die mit der zweiten Steuerkante 74 zusammenwirkt und mit dieser gemäß einer später beschriebenen zweiten Schaltstellung des Steuerventils 30 eine Dichtfläche ausbildet.At the
Zur Verbindung der einzelnen Komponenten Einspritzventil 10, Druckübersetzungseinrichtung 20, Steuerventil 30 und Schaltventil 40, dienen Druckleitungen, die beispielsweise in den Kraftstoffinjektor 1 integriert sind. Der Druckraum 14 des Kraftstoffeinspritzventils 10 ist mit einer erste Druckleitung 51 mit dem Hochdruckraum 25 der Druckübersetzungseinrichtung 20 verbunden. Vom Schließdruckraum 16 des Einspritzventils 10 führt eine zweite Druckleitung 52 zum Rückraum 26 der Druckübersetzungseinrichtung 20. Zusätzlich existiert eine Verbindungsleitung 53 mit Drossel zwischen Schließdruckraum 16 und Hochdruckraum 25. Der hydraulische Druck der Kraftstoffhochdruckquelle 5 wird über die Hochdruckleitung 3 und die Verbindungsbohrung 55 in den Druckübersetzungsraum 27 der Druckübersetzungseinrichtung 20 geführt. Der Druckübersetzungsraum 27 steht dadurch über die Querbohrung 85 mit dem Ventildruckraum 35 des Steuerventils 30 in Verbindung. Eine Rückraumleitung 58 verbindet den Rückraum 26 der Druckübersetzungseinrichtung 20 mit der Ventilkammer 34 des Steuerventils 30.To connect the individual
Vom Verbindungsraum 36 des Steuerventils 30 führt eine erste Rücklaufleitung 61 über ein nicht in der Zeichnung dargestelltes Niederdrucksystem in einen ebenfalls nicht dargestellten Kraftstofftank zurück. Der Steuerraum 33 des Steuerventils 30 ist mittels einer Steuerleitung 59 über eine Ablaufdrossel 64 mit dem aktorseitigen Ringraum 46 des Schaltventils 40 verbunden. Schließlich führt eine zweite Rücklaufleitung 62 aus dem aktorseitigen Leckraum 45 des Schaltventils 40 heraus in das Niederdruck- bzw. Rücklaufsystem hinein. Die Rücklaufleitungen 61, 62 können jedoch auch als ein gemeinsames Rücklaufsystem ausgebildeten sein.From the
Ein zweites Ausführungsbeispiel geht aus
Die Funktionsweise des Kraftstoffinjektors 1 ist wie im Folgenden dargestellt: Zu Beginn des Einspritzvorgangs liegt durch den konstanten Druck im Hochdruckspeicher 5 der im Druckübersetzungsraum 27 anliegende Druck über die Rückraumleitung 58 auch im Rückraum 26 und über die zweite Druckleitung 52 und die Verbindungsleitung 53 im Hochdruckraum 25 und von dort über die erste Druckleitung 51 im Druckraum 14 an. Der Aktor 41 des Schaltventils 40, das im vorliegenden Ausführungsbeispiel ein Magnetventil ist, ist so bestromt, dass der Aktorkolben 42 die mit dem Steuerraum 33 des Steuerventils 30 in Verbindung stehende Steuerleitung 59 gegen den mit der zweiten Rücklaufleitung 62 in Verbindung stehenden aktorseitigen Leckraum 45 verschließt. Dadurch herrscht im Steuerraum 33 der gleiche Druck wie in dem über die weitere Verbindungsleitung 57 mit dem Druckübersetzungsraum 27 in Verbindung stehenden Ringraum 82. Durch den auf die erste Druckfläche 78 wirkenden Hochdruck wird die erste Sterkante 73 gegen den Dichtsitz gepresst. Dadurch ist die Verbindungskammer 36 und damit die ersten Rücklaufleitung 61 vom Hochdruck bzw. Systemdruck entkoppelt. Das Einspritzventil 10 ist geschlossen.The operation of the
Die Öffnungshubbewegung des Schließkolbens 12 des Einspritzventils 10 wird dadurch eingeleitet, indem aufgrund einer entsprechenden Bestromung des Aktors 41 der Aktorkolben 42 vom aktorseitigen Dichtsitz 44 abhebt, so dass der Steuerraum 33 mit dem aktorseitigen Ringraum 46 und dem aktorseitigen Leckraum 55 verbunden wird. Die Durchflusswiderstände der Zulaufdrossel 56 und der Ablaufdrossel 64 sind so bemessen, dass der Druck im Steuerraum 33 abfällt und der Steuerkolben 70 von dem Dichtsitz der ersten Steuerkante 73 abhebt. Gleichzeitig wirkt der Druck im Druckübersetzungsraum 27 auf die zweite, kleinere Druckfläche 79, so dass dieser seine Öffnungsbewegung fortsetzt und mit der zweiten Steuerkante 74 den Ventildruckraum 35 zur Ventilkammer 34 hin schließt und den Hochruck zum Verbindungsraum 36 hin sperrt. Dadurch wird der Rückraum 26 über die Rückraumleitung 58, die Ventilkammer 34 und den Verbindungsraum 36 mit der ersten Rücklaufleitung 61 verbunden. Dementsprechend wird der im Rückraum 26 der Druckübersetzungseinrichtung 20 herrschende Hochdruck über die Rücklaufleitung 61 entspannt und der Druck im Rückraum 26 fällt ab. Dadurch wird die Druckübersetzungseinrichtung 20 aktiviert und der mit geringerer Wirkfläche behaftete zweite Teilkolben 23 verdichtet den Kraftstoff im Hochdruckraum 25, so dass in dem mit dem Hochdruckraum 25 verbundenen Druckraum 14 die in Öffnungsrichtung an der Druckschulter 13 angreifende Druckkraft ansteigt und der Schließkolben 12 die Einspritzöffnungen 11 freigibt. So lange der Rückraum 26 druckentlastet ist, bleibt die Druckübersetzungseinrichtung 20 aktiviert und verdichtet den Kraftstoff im Hochdruckraum 25.The opening stroke of the
Zum Beenden des Einspritzvorganges wird das Schaltventil 40 wieder in seine Ausgangsstellung überführt. Dies trennt den Rückraum 26 von der ersten Rücklaufleitung 61 und verbindet ihn wieder mit dem Versorgungsdruck der Kraftstoffhochdruckquelle 5. Dadurch fällt der Druck im Hochdruckraum 25 auf Systemdruck ab, wodurch im Druckraum 14 ebenfalls wieder Systemdruck anliegt. Die Rückstellung des Schließkolbens 12 wird dabei durch die im Schließdruckraum 16 angeordnete Schließfeder 17 unterstützt und durch den ebenfalls über die zweite Druckleitung 52 anliegenden Systemdruck realisiert. Nach dem Druckausgleich wird der Druckübersetzerkolben 21 durch die Rückstellfeder 18 in seine Ausgangslage zurückgestellt, wobei der Hochdruckraum 25 über die Verbindungsleitung 53 aus der Kraftstoffhochdruckquelle 5 befüllt wird.To end the injection process, the switching
- 11
- Kraftstoffinjektorfuel injector
- 33
- KraftstoffleitungFuel line
- 55
- KraftstoffhochdruckquelleHigh-pressure fuel source
- 1010
- KraftstoffeinspritzventilFuel injection valve
- 1111
- EinspritzöffnungInjection port
- 1212
- Schließkolbenclosing piston
- 1313
- Druckschulterpressure shoulder
- 1414
- Druckraumpressure chamber
- 1515
- Führungsbereichguide region
- 1616
- SchließdruckraumClosing pressure chamber
- 1717
- Schließfederclosing spring
- 1818
- RückstellfederReturn spring
- 2020
- DruckübersetzungseinrichtungPressure booster device
- 2121
- ÜbersetzerkolbenBooster piston
- 2222
- erster Teilkolbenfirst part piston
- 2323
- zweiter Teilkolbensecond partial piston
- 2424
- Zylindercylinder
- 2525
- HochdruckraumHigh-pressure chamber
- 2626
- Rückraumbackcourt
- 2727
- DruckübersetzungsraumPressure boosting chamber
- 2828
- Federhalterpenholder
- 2929
- Ringelementring element
- 3030
- Steuerventilcontrol valve
- 3131
- SteuerventilkörperControl valve body
- 3232
- Bohrungdrilling
- 3333
- Steuerraumcontrol room
- 3434
- Ventilkammervalve chamber
- 3535
- VentildruckraumValve pressure chamber
- 3535
- Verbindungsraumcommunication space
- 3636
- Verbindungskanalconnecting channel
- 3939
- Aufnahmeadmission
- 4040
- Schaltventilswitching valve
- 4141
- Aktoractuator
- 4242
- Aktorkolbenactuator piston
- 4343
- Aktorbohrungactuator bore
- 4444
- aktorseitiger DichtsitzActuator-side sealing seat
- 4545
- aktorseitiger Leckraumactuator-side leakage space
- 4646
- aktorseitiger Ringraumactuator-side annulus
- 5151
- erste Druckleitungfirst pressure line
- 5252
- zweite Druckleitungsecond pressure line
- 5353
- Verbindungsleitungconnecting line
- 5555
- Verbindungsbohrungconnecting bore
- 5656
- Zulaufdrosselinlet throttle
- 5757
- weitere Verbindungsleitungfurther connection line
- 5858
- RückraumleitungBackcourt line
- 5959
- Steuerleitungcontrol line
- 6161
- erste Rücklaufleitungfirst return line
- 6262
- zweite Rücklaufleitungsecond return line
- 6464
- Ablaufdrosseloutlet throttle
- 7070
- Steuerkolbenspool
- 7171
- erster Kolbenabschnittfirst piston section
- 7272
- zweiter Kolbenabschnittsecond piston section
- 7373
- erste Steuerkantefirst control edge
- 7474
- zweite Steuerkantesecond control edge
- 7575
- Dichtkantesealing edge
- 7878
- erste Druckflächefirst printing surface
- 7979
- zweite Druckflächesecond printing surface
- 8080
- BuchseRifle
- 8282
- Ringraumannulus
- 8383
- Abdeckungcover
- 8484
- Dichtungpoetry
- 8585
- Querbohrungcross hole
- 9090
- Servo-VentilServo-valve
- 9191
- VentilkammerbuchseValve chamber socket
- 9292
- Einstellbuchseadjusting bush
- 9393
- Ventilplattevalve plate
Claims (7)
- Fuel injection device for internal combustion engines having a fuel injection valve (10) which is connected to a high-pressure source, having a control valve (30) which has a valve body (31) with a control piston (70) which is arranged in a longitudinally movable fashion, and having a pressure boosting device (20) which has a rear space (26), which interacts with a pressure boosting piston (21), a pressure boosting space (27) and a high-pressure space (25), with it being possible for the rear space (26) to be activated by the control valve (30) such that a pressure boost which acts on the fuel injection valve (10) takes place by means of a pressure change in the rear space (26), with the control piston (70), in a first valve position, separating a pressurized valve chamber (34) from a return- or low-pressure system, with the valve chamber (34) being relieved of pressure to the return system, and an actuation of the fuel injection valve (10) thereby being initiated, when the control piston (70) is in a second valve position, with the control piston (70) being guided in a sleeve (80) which is acted on, at least partially within the valve body (31), with pressure from the outside, and with the sleeve (80) being inserted in a pressure-tight manner into a receptacle (39) of the valve body (31), characterized in that the sleeve (80) in the valve body (31) is surrounded at least partially by an annular space (82) which is connected to the high-pressure source (5) and is permanently connected to the pressure boosting space (27) by means of a connecting bore (55).
- Fuel injection device according to Claim 1, characterized in that a transverse bore (85) is formed on the sleeve (80), which transverse bore (85) produces a hydraulic connection from the annular space (82) to a valve pressure space (35).
- Fuel injection device according to one of Claims 1 or 2, characterized in that the sleeve (80) is of multi-part design and has at least two partial sleeves (91, 92) situated axially in series.
- Fuel injection device according to Claim 3, characterized in that the axial position of the first partial sleeve (91) in the valve body (31) can be set by means of the thickness of the second partial sleeve (92).
- Fuel injection device according to Claim 3 or 4, characterized in that the first partial sleeve (91) encloses a pressurizable valve pressure space (35) and has a sealing edge (75) which interacts with a control edge (74) on the control piston (70), and in that the axial position of the sealing edge (75) with respect to the control edge (74) can be set by means of the axial extent of the second partial sleeve (92).
- Fuel injection device according to Claim 3, characterized in that a third partial sleeve (93) is provided, on which a valve seat is formed by means of a first control edge (73) formed on the control piston (70).
- Fuel injection device according to Claim 1, characterized in that the control valve (30) interacts with a switching valve (40) such that the control valve (30) and the switching valve (40) form a servo-valve unit (90).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10337574A DE10337574A1 (en) | 2003-08-14 | 2003-08-14 | Fuel injection device for internal combustion engines |
DE10337574 | 2003-08-14 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1507082A1 EP1507082A1 (en) | 2005-02-16 |
EP1507082B1 true EP1507082B1 (en) | 2008-07-30 |
Family
ID=33560336
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04015171A Expired - Lifetime EP1507082B1 (en) | 2003-08-14 | 2004-06-29 | Fuel injection system for combustion engine |
Country Status (3)
Country | Link |
---|---|
US (1) | US6915785B2 (en) |
EP (1) | EP1507082B1 (en) |
DE (2) | DE10337574A1 (en) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10315016A1 (en) * | 2003-04-02 | 2004-10-28 | Robert Bosch Gmbh | Fuel injector with a leak-free servo valve |
EP1613856B1 (en) * | 2003-04-02 | 2008-07-09 | Robert Bosch Gmbh | Fuel injector provided with a pressure transmitter controlled by a servo valve |
FI117805B (en) * | 2003-06-17 | 2007-02-28 | Waertsilae Finland Oy | Arrangement in the fuel supply system |
DE10333697A1 (en) * | 2003-07-24 | 2005-02-24 | Robert Bosch Gmbh | Fuel injector |
DE10333696A1 (en) * | 2003-07-24 | 2005-02-24 | Robert Bosch Gmbh | Fuel injector |
DE10333695A1 (en) * | 2003-07-24 | 2005-03-03 | Robert Bosch Gmbh | Fuel injector |
DE10352736A1 (en) * | 2003-11-12 | 2005-07-07 | Robert Bosch Gmbh | Fuel injector with direct needle injection |
DE102004017304A1 (en) * | 2004-04-08 | 2005-10-27 | Robert Bosch Gmbh | Servo valve controlled fuel injector |
DE102004022270A1 (en) * | 2004-05-06 | 2005-12-01 | Robert Bosch Gmbh | Fuel injector for internal combustion engines with multi-stage control valve |
DE102004028521A1 (en) * | 2004-06-11 | 2005-12-29 | Robert Bosch Gmbh | Fuel injector with multipart injection valve member and with pressure booster |
JP2006090176A (en) * | 2004-09-22 | 2006-04-06 | Denso Corp | Injector |
JP4003770B2 (en) * | 2004-10-01 | 2007-11-07 | トヨタ自動車株式会社 | Fuel injection device |
JP4305394B2 (en) * | 2005-01-25 | 2009-07-29 | 株式会社デンソー | Fuel injection device for internal combustion engine |
JP4459183B2 (en) * | 2006-03-16 | 2010-04-28 | 株式会社デンソー | Injector |
US7568632B2 (en) | 2006-10-17 | 2009-08-04 | Sturman Digital Systems, Llc | Fuel injector with boosted needle closure |
DE102007001363A1 (en) * | 2007-01-09 | 2008-07-10 | Robert Bosch Gmbh | Injector for injecting fuel into combustion chambers of internal combustion engines |
CN108397325A (en) * | 2018-02-09 | 2018-08-14 | 中国第汽车股份有限公司 | A kind of common-rail injector throttling control valve |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5687693A (en) * | 1994-07-29 | 1997-11-18 | Caterpillar Inc. | Hydraulically-actuated fuel injector with direct control needle valve |
US6119960A (en) * | 1998-05-07 | 2000-09-19 | Caterpillar Inc. | Solenoid actuated valve and fuel injector using same |
DE19908418C1 (en) * | 1999-02-26 | 2000-10-26 | Siemens Ag | Control valve for diesel engine fuel injection system |
DE19951004A1 (en) * | 1999-10-22 | 2001-04-26 | Bosch Gmbh Robert | Hydraulic regulator esp. for fuel injector for motor vehicles has hydraulic converter between actor and valve member, to reverse actor movement |
DE19951554A1 (en) * | 1999-10-26 | 2001-05-10 | Bosch Gmbh Robert | Fuel injector with integrated flow limitation |
US6283441B1 (en) * | 2000-02-10 | 2001-09-04 | Caterpillar Inc. | Pilot actuator and spool valve assembly |
DE10031278A1 (en) * | 2000-06-27 | 2002-01-17 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
DE10036578A1 (en) * | 2000-07-27 | 2002-02-07 | Bosch Gmbh Robert | Fuel injection unit for internal combustion engine has slide valve formed by cylindrical end section of control valve element and constructed as throttling section and protruding into first overflow oil chamber |
US6749130B2 (en) * | 2000-12-08 | 2004-06-15 | Caterpillar Inc | Check line valve faster venting method |
US6655602B2 (en) * | 2001-09-24 | 2003-12-02 | Caterpillar Inc | Fuel injector having a hydraulically actuated control valve and hydraulic system using same |
US20040099246A1 (en) * | 2002-11-22 | 2004-05-27 | Caterpillar Inc. | Fuel injector with multiple control valves |
-
2003
- 2003-08-14 DE DE10337574A patent/DE10337574A1/en not_active Withdrawn
-
2004
- 2004-06-29 DE DE502004007716T patent/DE502004007716D1/en not_active Expired - Lifetime
- 2004-06-29 EP EP04015171A patent/EP1507082B1/en not_active Expired - Lifetime
- 2004-08-04 US US10/910,346 patent/US6915785B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
EP1507082A1 (en) | 2005-02-16 |
US20050035212A1 (en) | 2005-02-17 |
US6915785B2 (en) | 2005-07-12 |
DE10337574A1 (en) | 2005-03-10 |
DE502004007716D1 (en) | 2008-09-11 |
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