EP1552136B1 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine Download PDF

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Publication number
EP1552136B1
EP1552136B1 EP03740027A EP03740027A EP1552136B1 EP 1552136 B1 EP1552136 B1 EP 1552136B1 EP 03740027 A EP03740027 A EP 03740027A EP 03740027 A EP03740027 A EP 03740027A EP 1552136 B1 EP1552136 B1 EP 1552136B1
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EP
European Patent Office
Prior art keywords
valve
fuel injection
valve element
injection device
pressure
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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
Application number
EP03740027A
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German (de)
French (fr)
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EP1552136A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—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
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0061—Single actuator acting on two or more valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine, comprising a housing, with a recess provided in the housing, with at least two in the recess coaxially arranged valve elements, which cooperate with a respective valve seat and which each have at least one corresponding fuel outlet opening assigned.
  • Such a fuel injection device is known from DE 40 23 223 A1.
  • a fuel injection nozzle for internal combustion engines is shown.
  • Two valve pins are arranged coaxially with each other. Both valve needles each have a pressure surface.
  • the pressure surfaces of the valve needles each delimit a pressure chamber, which is in each case connected to a flow channel, through which the fuel pressure space can flow.
  • the pressure surfaces are aligned so that at a Pressing the valve needles in each case lift off from their assigned seat and thereby release corresponding outlet openings at the end of the injector.
  • the valve needles can be controlled independently of each other via the two independent flow channels.
  • EP 1 069 308 A2 further describes a fuel injection device with two valve elements, which are both stroke-controlled and independently operable by a common valve device.
  • WO 02/42637 A1 discloses a fuel injection device with a lifting and a pressure-controlled valve element.
  • Object of the present invention is to develop a fuel injection device for an internal combustion engine of the type mentioned so that it is as simple and compact builds.
  • the fuel injection device according to the invention requires for operation only a common valve device with which all valve elements can be controlled at least indirectly. It therefore builds comparatively compact. Furthermore, since a comparatively small number of parts is required, their manufacture is also inexpensive. Due to the fact that the common valve device provided according to the invention has three switching positions, high flexibility is achieved Operation of the fuel injection device according to the invention possible.
  • the fuel injection device therefore, on the one hand, is compact and, on the other hand, enables an emission and consumption-optimized operation of the internal combustion engine.
  • a flow restrictor is arranged in the flow path between the control chamber of the hydraulically switchable valve device and the common valve device.
  • valve element pressure-controlled and the other valve element work stroke-controlled.
  • the respective advantages of pressure-controlled or stroke-controlled valve elements can be combined in a single fuel injection device.
  • a pressure-controlled valve element in particular in a partial load operation of the internal combustion engine, has a particularly favorable injection characteristic.
  • the control of the pressure-controlled valve element is simplified in that the pressure-controlled valve element is arranged radially outwardly of the stroke-controlled valve element.
  • control chamber of the pressure-controlled valve element is connected to the hydraulically switchable valve device.
  • a fuel system as a whole bears the reference numeral 10. It comprises a fuel tank 12, from which an electric fuel pump 14 conveys the fuel into a low-pressure fuel line 16.
  • the low-pressure fuel line 16 leads to a high-pressure fuel pump 18.
  • This is a piston pump which is driven by a camshaft (not shown) of the internal combustion engine to which the fuel system 10 belongs.
  • the high-pressure fuel pump 18 delivers into a fuel rail 20 ("rail") in which the fuel is stored under high pressure.
  • a plurality of injectors 22 are connected, which inject the fuel directly into them associated combustion chambers 24 of the internal combustion engine.
  • the operation of the internal combustion engine and the fuel system 10 is controlled and regulated by a control and regulating device 26.
  • the injectors 22 are controlled by the control and regulating device 26. From the injectors 22 in each case a line 28 leads back to the fuel tank 12th
  • FIG. 2 An area of one of the injectors 22 is shown in detail in FIG. 2:
  • the injector 22 comprises a two-part housing with an upper part 30 and a lower part 32.
  • the housing 30, 32 has a recess 34, in which inter alia a first elongated valve element 36 is present. Its lower end in FIG. 2 is conically tapered and cooperates with a valve seat 38 (cf., FIG. 3) in the lower part 32 of the housing.
  • a second valve element 40 Coaxial to the first Valve element 36 and radially outside of this, a second valve element 40 is provided, the conical tip also cooperates with a valve seat 42 in the lower part 32 of the housing.
  • the first valve element 36 is acted upon by a compression spring 44, one end of which is supported on a shoulder (without reference numeral) in the upper part 30 of the housing, in the direction of the valve seat 38.
  • the second valve element 40 is acted upon by a compression spring 46 in the direction of the corresponding valve seat 42 out.
  • the compression spring 46 is not supported directly on a shoulder in the recess 34 in the upper part 30 of the housing, but on an intermediate ring 48th
  • the recess 34 in the lower part 32 of the housing comprises a blind hole 50, from which a plurality of outlet openings 52 leads to the outside. Through these outlet openings 52 of the fuel, as will be explained below in more detail, with open first valve element 36 and 40 open second valve element. Outlet openings 54 serve analogously to the outlet of the fuel when only the second valve element 40 is lifted from the second valve seat 42. Again, this will be more detailed below.
  • a common valve device 56 is provided, which is arranged in the upper region of the upper part 34 of the housing. This comprises a hemispherically shaped valve element 58, which is arranged in a switching chamber 60. Via a plunger 62, the valve element 60 of a piezoelectric actuator 64 shown only symbolically in various switch positions are adjusted.
  • valve element 58 In the rest position, the valve element 58 is pressed by a compression spring 66 against a valve seat 68. When the valve element 58 bears against the valve seat 68, the connection from the switching chamber 60 via a channel 70 to a low-pressure connection 72 (see also FIG. The low-pressure port 72 is in turn connected to the return line 28, which leads back to the fuel tank 12.
  • a channel 74 leads to a control chamber 76.
  • the upper end of the first valve element 36 with a pressure surface 78 also opens into the control chamber 76.
  • a flow throttle 80 is present in the channel 74. From the radial boundary wall (without reference numeral) of the switching chamber 60 performs a fluid connection (without reference numeral) via a flow restrictor 82 to a control chamber 84 of a hydraulically actuated switching valve 86th
  • the hydraulically actuable switching valve 86 also includes a switching chamber 88, in which a valve element 90 is arranged.
  • the valve element 90 is generally cylindrical with a switching portion 92 having a circular cylindrical diameter, a transition portion 94 which is formed as a constriction, and a circular cylindrical guide portion 96.
  • One end of a compression spring 98 is supported on a closure member 100 from. The other end of the compression spring 98 acts on the valve element 90 in the direction of the control chamber 84.
  • annular groove 102 is present in the peripheral wall of the switching chamber 88. This is connected on the one hand via a channel 104 with a high-pressure port 106 (see also Figure 1). This in turn leads to the fuel manifold 20. On the other hand, a channel 108 via a flow restrictor 110 from the annular groove 102 to the control chamber 76, with which the movement of the first valve element 36 is controlled. From that portion of the peripheral wall of the switching chamber 88, which is approximately in the region of the constricted transition portion 94 of the valve element 90, a channel 112 leads to an annular space 114 in the lower region of the second valve element 40th
  • the circumferential wall of the switching chamber 88 forms a valve seat 116 for a switching edge 118 of the valve element 90.
  • the switching edge 118 is formed between the switching section 92 and the transition section 94.
  • a further channel 120 In the switching portion 92 of the valve member 90 extends obliquely to the longitudinal axis of the valve element 90, a further channel 120. This includes a flow restrictor 122, and it connects the annular groove 102 with the control chamber 84. Also to mention is still a leakage channel 124, of the recess 34 in Upper part 30 of the housing leads to a leakage connection 126.
  • the injector 22 shown in Figures 1 to 3 operates as follows:
  • the valve element 38 of the common valve device 56 bears against the upper valve seat 68 in FIG.
  • the switching chamber 60 of the common valve device 56 in the control chamber 76 of the first valve element 36, and in the control chamber 84 of the hydraulically operated switching valve 86 is thus the on High pressure port 106 present high pressure.
  • the valve element 92 of the hydraulically actuated switching valve 86 is pressed with the switching edge 118 against the valve seat 116. That region of the switching chamber 88 which lies at the level of the transition section 94 is thus separated from the high-pressure port 106. Therefore, there is a comparatively low pressure in him.
  • the second valve element 40 can therefore be pressed by the spring 46 against the valve seat 42.
  • valve element 58 of the common valve device 56 can be brought by the actuator 64 via the plunger 62 in a second switching position in which it rests against the lower boundary wall of the switching chamber 60 in FIG.
  • the switching chamber 60 is now connected via the channel 70 to the low pressure port 72.
  • the high pressure can escape from the control chamber 84 of the hydraulically actuatable switching valve 86 via the flow throttle 82.
  • the valve element 90 of the hydraulically actuatable switching valve 86 is now moved in the direction of the control chamber 84, so that the switching edge 118 lifts from the valve seat 116.
  • the fuel present under high pressure in the annular groove 102 can now flow via the channel 112 into the annular space 114.
  • the high fuel pressure which also rests on the high-pressure port 106.
  • the second valve element 40 is moved against the action of the compression spring 46 upwards, so that it is released from the valve seat 42.
  • the fuel present under high pressure in the annular space 114 can flow through the outlet openings 54 to the outside.
  • valve element 58 of the common valve device 56 closes the channel 74 to the control chamber 76 in this second switching position, there continues to be a high fuel pressure which presses the first valve element 36 downward over the pressure surface 78 in FIG.
  • a high fuel pressure now rests on the region of the conical lower end surface of the valve element 36 that is located radially outside of the valve seat 38, the first valve element 36 is pressed further against the valve seat 38 due to the downward force on the pressure surface 78 in FIG. Therefore, no fuel can escape through the outlet openings 52.
  • the valve element 58 of the common valve device 56 can be brought by the actuator 64 in a third, middle switching position. In this it is neither on the valve seat 68 nor on the lower end wall of the switching chamber 60 in Figure 2. Thus, as in the second switching position, the switching chamber 60 is connected to the low pressure port 72. In addition, however, the fuel can now flow from the control chamber 76 via the channel 74 and the flow restrictor 80 into the switching chamber 60 and on to the low-pressure connection 72. As a result, the pressure in the control chamber 76 decreases to such an extent that the valve element 36 is lifted off the valve seat 38 by the high pressure applied radially outward from the valve seat 38 of the conical end surface. When the valve element 58 of the common valve device 56 is thus in the middle third switching position, fuel is discharged from the injector 22 both through the outlet openings 54 and through the outlet openings 52.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a fuel injection device (22) for an internal combustion engine, comprising a housing (30, 32). Said housing comprises a cavity (34) containing two valve elements (36, 40) which are arranged in a coaxial manner in relation to each other. Said elements cooperate with a corresponding valve seat (38, 42). The valve elements (36, 40) are associated with corresponding fuel outlets (52, 54). The aim of the invention is to produce said fuel injection device (22) with a compact structure. As a result, a common valve device (56) is provided, comprising at least three switch positions in order to influence the position of the valve elements (36, 40).

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine, mit einem Gehäuse, mit einer in dem Gehäuse vorhandenen Ausnehmung, mit mindestens zwei in der Ausnehmung koaxial zueinander angeordneten Ventilelementen, welche jeweils mit einem entsprechenden Ventilsitz zusammenarbeiten und denen jeweils mindestens eine entsprechende Kraftstoff-Austrittsöffnung zugeordnet ist.The invention relates to a fuel injection device for an internal combustion engine, comprising a housing, with a recess provided in the housing, with at least two in the recess coaxially arranged valve elements, which cooperate with a respective valve seat and which each have at least one corresponding fuel outlet opening assigned.

Eine derartige Kraftstoff-Einspritzvorrichtung ist aus der DE 40 23 223 A1 bekannt. In dieser ist eine KraftstoffEinspritzdüse für Brennkraftmaschinen gezeigt. Zwei Ventilnadeln sind koaxial zueinander angeordnet. Beide Ventilnadeln weisen jeweils eine Druckfläche auf. Die Druckflächen der Ventilnadeln begrenzen jeweils einen Druckraum, welcher jeweils mit einem Strömungskanal verbunden ist, durch den Kraftstoff Druckraum strömen kann. Die Druckflächen sind dabei so ausgerichtet, dass bei einer Druckbeaufschlagung die Ventilnadeln jeweils von dem ihnen zugeordneten Sitz abheben und hierdurch entsprechende Austrittsöffnungen am Ende der Einspritzdüse freigeben. Über die beiden voneinander unabhängigen Strömungskanäle können die Ventilnadeln unabhängig voneinander angesteuert werden.Such a fuel injection device is known from DE 40 23 223 A1. In this, a fuel injection nozzle for internal combustion engines is shown. Two valve pins are arranged coaxially with each other. Both valve needles each have a pressure surface. The pressure surfaces of the valve needles each delimit a pressure chamber, which is in each case connected to a flow channel, through which the fuel pressure space can flow. The pressure surfaces are aligned so that at a Pressing the valve needles in each case lift off from their assigned seat and thereby release corresponding outlet openings at the end of the injector. The valve needles can be controlled independently of each other via the two independent flow channels.

Die EP 1 069 308 A2 beschreibt ferner eine Kraftstoff-Einspritzvorrichtung mit zwei Ventilelementen, welche beide hubgesteuert und unabhängig voneinander durch eine gemeinsame Ventileinrichtung betätigbar sind. Die WO 02/42637 A1 offenbart eine Kraftstoff-Einspritzvorrichtung mit einem hub- und einem druckgesteuerten Ventilelement.EP 1 069 308 A2 further describes a fuel injection device with two valve elements, which are both stroke-controlled and independently operable by a common valve device. WO 02/42637 A1 discloses a fuel injection device with a lifting and a pressure-controlled valve element.

Aufgabe der vorliegenden Erfindung ist es, eine Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine der eingangs genannten Art so weiterzubilden, dass sie möglichst einfach und kompakt baut.Object of the present invention is to develop a fuel injection device for an internal combustion engine of the type mentioned so that it is as simple and compact builds.

Diese Aufgabe wird durch eine Kraftstoff-Einspritzvorrichtung mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a fuel injection device having the features of claim 1.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoff-Einspritzvorrichtung benötigt für den Betrieb nur noch eine gemeinsame Ventileinrichtung, mit der alle Ventilelemente wenigstens mittelbar angesteuert werden können. Sie baut daher vergleichsweise kompakt. Da ferner eine vergleichsweise geringe Anzahl an Teilen erforderlich ist, ist auch ihre Herstellung preiswert. Dadurch, dass die erfindungsgemäß vorgesehene gemeinsame Ventileinrichtung drei Schaltstellungen aufweist, ist eine hohe Flexibilität im Betrieb der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung möglich.The fuel injection device according to the invention requires for operation only a common valve device with which all valve elements can be controlled at least indirectly. It therefore builds comparatively compact. Furthermore, since a comparatively small number of parts is required, their manufacture is also inexpensive. Due to the fact that the common valve device provided according to the invention has three switching positions, high flexibility is achieved Operation of the fuel injection device according to the invention possible.

Durch die Verwendung einer hydraulisch schaltbaren Ventileinrichtung, deren Schaltstellung von der gemeinsamen Ventileinrichtung beeinflusst wird, können hohe Kraftstoffdrücke realisiert werden, ohne dass die gemeinsame Ventileinrichtung besonders komplex und/oder teuer baut. Gleichzeitig werden dennoch geringe Leckagen innerhalb der Kraftstoff-Einspritzvorrichtung realisiert.By using a hydraulically switchable valve device whose switching position is influenced by the common valve device, high fuel pressures can be realized without the common valve device is particularly complex and / or expensive builds. At the same time small leaks are nevertheless realized within the fuel injection device.

Vorteilhafte Weiterbildungen der Erfindung sind in Unteransprüchen angegeben.Advantageous developments of the invention are specified in subclaims.

In einer ersten Weiterbildung der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung wird vorgeschlagen, dass in einer ersten Schaltstellung der gemeinsamen Ventileinrichtung beide Ventilelemente am Ventilsitz anliegen, in einer zweiten Schaltstellung eines der beiden Ventilelemente von seinem Ventilsitz abgehoben ist, und in einer dritten Schaltstellung beide Ventilelemente von ihren Ventilsitzen abgehoben sind.In a first development of the fuel injection device according to the invention, it is proposed that in a first switching position of the common valve device both valve elements abut the valve seat, in a second switching position of the two valve elements is lifted from its valve seat, and in a third switching position both valve elements of their valve seats are lifted off.

In diesem Fall werden von der gemeinsamen Ventileinrichtung sämtliche wesentlichen Schaltzustände einer Kraftstoff-Einspritzvorrichtung mit zwei Ventilelementen abgedeckt. Die Kraftstoff-Einspritzvorrichtung baut daher zum Einen kompakt und ermöglicht zum Anderen einen emissions- und verbrauchsoptimalen Betrieb der Brennkraftmaschine.In this case, all essential switching states of a fuel injection device with two valve elements are covered by the common valve device. The fuel injection device therefore, on the one hand, is compact and, on the other hand, enables an emission and consumption-optimized operation of the internal combustion engine.

Vorgeschlagen wird auch, dass im Strömungsweg zwischen dem Hochdruckanschluss und dem Steuerraum der hydraulisch schaltbaren Ventileinrichtung eine Strömungsdrossel angeordnet ist. Hierdurch kann die Schließcharakteristik der hydraulisch schaltbaren Ventileinrichtung, und somit letztlich die Schließcharakteristik des zweiten Ventilelements, beeinflusst werden.It is also proposed that in the flow path between the high pressure port and the control chamber of the hydraulic switchable valve device is arranged a flow restrictor. As a result, the closing characteristic of the hydraulically switchable valve device, and thus ultimately the closing characteristic of the second valve element, can be influenced.

Analog hierzu wird auch vorgeschlagen, dass im Strömungsweg zwischen dem Steuerraum der hydraulisch schaltbaren Ventileinrichtung und der gemeinsamen Ventileinrichtung eine Strömungsdrossel angeordnet ist. Durch diese wird die Öffnungscharakteristik der hydraulisch schaltbaren Ventileinrichtung und somit auch die Öffnungscharakteristik des zweiten Ventilelements beeinflusst. Dies ermöglicht vor allem auch eine Optimierung des Verbrennungsgeräuschs der Brennkraftmaschine.Analogously, it is also proposed that a flow restrictor is arranged in the flow path between the control chamber of the hydraulically switchable valve device and the common valve device. By this, the opening characteristic of the hydraulically switchable valve device and thus also the opening characteristic of the second valve element is influenced. Above all, this also makes it possible to optimize the combustion noise of the internal combustion engine.

Optimal ist es auch, wenn das eine Ventilelement druckgesteuert und das andere Ventilelement hubgesteuert arbeiten. In diesem Falle können die jeweiligen Vorteile druckgesteuerter bzw. hubgesteuerter Ventilelemente in einer einzigen Kraftstoff-Einspritzvorrichtung kombiniert werden. So weist beispielsweise ein druckgesteuertes Ventilelement insbesondere in einem Teillastbetrieb der Brennkraftmaschine eine besonders günstige Einspritzcharakteristik auf.It is also optimal if one valve element pressure-controlled and the other valve element work stroke-controlled. In this case, the respective advantages of pressure-controlled or stroke-controlled valve elements can be combined in a single fuel injection device. For example, a pressure-controlled valve element, in particular in a partial load operation of the internal combustion engine, has a particularly favorable injection characteristic.

Die Ansteuerung des druckgesteuerten Ventilelements wird dadurch vereinfacht, dass das druckgesteuerte Ventilelement radial außen von dem hubgesteuerten Ventilelement angeordnet ist.The control of the pressure-controlled valve element is simplified in that the pressure-controlled valve element is arranged radially outwardly of the stroke-controlled valve element.

In Weiterbildung hierzu ist es wiederum von Vorteil, wenn der Steuerraum des druckgesteuerten Ventilelements mit der hydraulisch schaltbaren Ventileinrichtung verbunden ist.In a further development, it is again advantageous if the control chamber of the pressure-controlled valve element is connected to the hydraulically switchable valve device.

Die Vorteile der hydraulisch schaltbaren Ventileinrichtung im Hinblick auf geringe Leckagen bei gleichzeitig hohem Druck sind in Verbindung mit der Ansteuerung eines druckgesteuerten Ventilelements besonders prägnant.The advantages of the hydraulically switchable valve device with regard to low leaks and high pressure at the same time are particularly concise in connection with the actuation of a pressure-controlled valve element.

In einer weiteren Ausgestaltung der Kraftstoff-Einspritzvorrichtung wird auch vorgeschlagen, dass in einer Endstellung der gemeinsamen Ventileinrichtung der Steuerraum des hubgesteuerten Ventilelements und der Steuerraum der hydraulisch schaltbaren Ventileinrichtung nur mit dem Hochdruckanschluss verbunden sind. In dieser Schaltstellung der gemeinsamen Ventileinrichtung sind beide Ventilelemente in ihrer geschlossenen Position, also in Anlage an dem jeweiligen Ventilsitz.In a further embodiment of the fuel injection device is also proposed that in an end position of the common valve means of the control chamber of the stroke-controlled valve element and the control chamber of the hydraulically switchable valve means are connected only to the high pressure port. In this switching position of the common valve device, both valve elements are in their closed position, that is, in contact with the respective valve seat.

Zeichnungdrawing

Nachfolgend wird ein besonders bevorzugtes Ausführungsbeispiel der vorliegenden Erfindung unter Bezugnahme auf die beiliegende Zeichnung im Detail erläutert. In der Zeichnung zeigen:

Figur 1
eine schematische Darstellung eines Kraftstoffsystems einer Brennkraftmaschine mit mehreren Kraftstoff-Einspritzvorrichtungen;
Figur 2
einen teilweisen Schnitt durch eine der Kraftstoff-Einspritzvorrichtungen von Figur 1; und
Figur 3
eine vergrößerte Darstellung eines Bereichs der Kraftstoff-Einspritzvorrichtung von Figur 2.
Hereinafter, a particularly preferred embodiment of the present invention will be explained in detail with reference to the accompanying drawings. In the drawing show:
FIG. 1
a schematic representation of a fuel system of an internal combustion engine having a plurality of fuel injection devices;
FIG. 2
a partial section through one of the fuel injectors of Figure 1; and
FIG. 3
an enlarged view of a portion of the fuel injection device of Figure 2.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 trägt ein Kraftstoffsystem insgesamt das Bezugszeichen 10. Es umfasst einen Kraftstoffbehälter 12, aus dem eine elektrische Kraftstoffpumpe 14 den Kraftstoff in eine Niederdruck-Kraftstoffleitung 16 fördert. Die Niederdruck-Kraftstoffleitung 16 führt zu einer Hochdruck-Kraftstoffpumpe 18. Bei dieser handelt es sich um eine Kolbenpumpe, welche von einer Nockenwelle (nicht dargestellt) der Brennkraftmaschine, zu der das Kraftstoffsystem 10 gehört, angetrieben wird. Die Hochdruck-Kraftstoffpumpe 18 fördert in eine Kraftstoff-Sammelleitung 20 ("Rail"), in der der Kraftstoff unter hohem Druck gespeichert ist.In FIG. 1, a fuel system as a whole bears the reference numeral 10. It comprises a fuel tank 12, from which an electric fuel pump 14 conveys the fuel into a low-pressure fuel line 16. The low-pressure fuel line 16 leads to a high-pressure fuel pump 18. This is a piston pump which is driven by a camshaft (not shown) of the internal combustion engine to which the fuel system 10 belongs. The high-pressure fuel pump 18 delivers into a fuel rail 20 ("rail") in which the fuel is stored under high pressure.

An die Kraftstoff-Sammelleitung 20 sind mehrere Injektoren 22 angeschlossen, die den Kraftstoff direkt in ihnen zugeordnete Brennräume 24 der Brennkraftmaschine einspritzen. Der Betrieb der Brennkraftmaschine und des Kraftstoffsystems 10 wird von einem Steuer- und Regelgerät 26 gesteuert und geregelt. Insbesondere werden auch die Injektoren 22 von dem Steuer- und Regelgerät 26 angesteuert. Von den Injektoren 22 führt jeweils eine Leitung 28 zurück zum Kraftstoffbehälter 12.To the fuel manifold 20 a plurality of injectors 22 are connected, which inject the fuel directly into them associated combustion chambers 24 of the internal combustion engine. The operation of the internal combustion engine and the fuel system 10 is controlled and regulated by a control and regulating device 26. In particular, the injectors 22 are controlled by the control and regulating device 26. From the injectors 22 in each case a line 28 leads back to the fuel tank 12th

Ein Bereich eines der Injektoren 22 ist in Figur 2 im Detail dargestellt:An area of one of the injectors 22 is shown in detail in FIG. 2:

Der Injektor 22 umfasst ein zweiteiliges Gehäuse mit einem Oberteil 30 und einem Unterteil 32. Im Gehäuse 30, 32 ist eine Ausnehmung 34 vorhanden, in der unter anderem ein erstes längliches Ventilelement 36 vorhanden ist. Dessen in Figur 2 unteres Ende ist konisch spitz zulaufend und arbeitet mit einem Ventilsitz 38 (vgl. Figur 3) im Unterteil 32 des Gehäuses zusammen. Koaxial zu dem ersten Ventilelement 36 und radial außen von diesem ist ein zweites Ventilelement 40 vorhanden, dessen ebenfalls konische Spitze mit einem Ventilsitz 42 im Unterteil 32 des Gehäuses zusammenarbeitet.The injector 22 comprises a two-part housing with an upper part 30 and a lower part 32. The housing 30, 32 has a recess 34, in which inter alia a first elongated valve element 36 is present. Its lower end in FIG. 2 is conically tapered and cooperates with a valve seat 38 (cf., FIG. 3) in the lower part 32 of the housing. Coaxial to the first Valve element 36 and radially outside of this, a second valve element 40 is provided, the conical tip also cooperates with a valve seat 42 in the lower part 32 of the housing.

Das erste Ventilelement 36 wird von einer Druckfeder 44, deren eines Ende sich an einem Absatz (ohne Bezugszeichen) im Oberteil 30 des Gehäuses abstützt, in Richtung zum Ventilsitz 38 hin beaufschlagt. Analog hierzu wird das zweite Ventilelement 40 von einer Druckfeder 46 in Richtung zum entsprechenden Ventilsitz 42 hin beaufschlagt. Die Druckfeder 46 stützt sich dabei nicht unmittelbar an einem Absatz in der Ausnehmung 34 im Oberteil 30 des Gehäuses ab, sondern an einem Zwischenring 48.The first valve element 36 is acted upon by a compression spring 44, one end of which is supported on a shoulder (without reference numeral) in the upper part 30 of the housing, in the direction of the valve seat 38. Analogously, the second valve element 40 is acted upon by a compression spring 46 in the direction of the corresponding valve seat 42 out. The compression spring 46 is not supported directly on a shoulder in the recess 34 in the upper part 30 of the housing, but on an intermediate ring 48th

Die Ausnehmung 34 im Unterteil 32 des Gehäuses umfasst ein Sackloch 50, von dem eine Mehrzahl von Austrittsöffnungen 52 nach außen führt. Durch diese Austrittsöffnungen 52 tritt der Kraftstoff, wie weiter unten noch stärker im Detail ausgeführt werden wird, bei geöffnetem ersten Ventilelement 36 und geöffnetem zweiten Ventilelement 40 aus. Austrittsöffnungen 54 dienen analog hierzu zum Austritt des Kraftstoffs dann, wenn nur das zweite Ventilelement 40 vom zweiten Ventilsitz 42 abgehoben ist. Auch dies wird weiter unten noch stärker im Detail ausgeführt werden.The recess 34 in the lower part 32 of the housing comprises a blind hole 50, from which a plurality of outlet openings 52 leads to the outside. Through these outlet openings 52 of the fuel, as will be explained below in more detail, with open first valve element 36 and 40 open second valve element. Outlet openings 54 serve analogously to the outlet of the fuel when only the second valve element 40 is lifted from the second valve seat 42. Again, this will be more detailed below.

Für die Betätigung der beiden Ventilelemente 36 und 40 ist eine gemeinsame Ventileinrichtung 56 vorgesehen, die im oberen Bereich des Oberteils 34 des Gehäuses angeordnet ist. Diese umfasst ein halbsphärisch geformtes Ventilelement 58, welches in einer Schaltkammer 60 angeordnet ist. Über einen Stößel 62 kann das Ventilelement 60 von einem nur symbolisch dargestellten Piezoaktor 64 in verschiedene Schaltstellungen verstellt werden.For the actuation of the two valve elements 36 and 40, a common valve device 56 is provided, which is arranged in the upper region of the upper part 34 of the housing. This comprises a hemispherically shaped valve element 58, which is arranged in a switching chamber 60. Via a plunger 62, the valve element 60 of a piezoelectric actuator 64 shown only symbolically in various switch positions are adjusted.

In der Ruhestellung wird das Ventilelement 58 von einer Druckfeder 66 gegen einen Ventilsitz 68 gedrückt. Wenn das Ventilelement 58 am Ventilsitz 68 anliegt, ist die Verbindung von der Schaltkammer 60 über einen Kanal 70 zu einem Niederdruckanschluss 72 (vgl. auch Figur 1) unterbrochen. Der Niederdruckanschluss 72 ist wiederum mit der Rückleitung 28 verbunden, die zum Kraftstoffbehälter 12 zurückführt.In the rest position, the valve element 58 is pressed by a compression spring 66 against a valve seat 68. When the valve element 58 bears against the valve seat 68, the connection from the switching chamber 60 via a channel 70 to a low-pressure connection 72 (see also FIG. The low-pressure port 72 is in turn connected to the return line 28, which leads back to the fuel tank 12.

Von der in Figur 2 unteren Stirnwand der Schaltkammer 60 führt ein Kanal 74 zu einem Steuerraum 76. In den Steuerraum 76 mündet auch das in Figur 2 obere Ende des ersten Ventilelements 36 mit einer Druckfläche 78. In dem Kanal 74 ist eine Strömungsdrossel 80 vorhanden. Von der radialen Begrenzungswand (ohne Bezugszeichen) der Schaltkammer 60 führt eine Fluidverbindung (ohne Bezugszeichen) über eine Strömungsdrossel 82 zu einem Steuerraum 84 eines hydraulisch betätigbaren Schaltventils 86.From the lower end wall of the switching chamber 60 in FIG. 2, a channel 74 leads to a control chamber 76. The upper end of the first valve element 36 with a pressure surface 78 also opens into the control chamber 76. A flow throttle 80 is present in the channel 74. From the radial boundary wall (without reference numeral) of the switching chamber 60 performs a fluid connection (without reference numeral) via a flow restrictor 82 to a control chamber 84 of a hydraulically actuated switching valve 86th

Das hydraulisch betätigbare Schaltventil 86 umfasst ebenfalls eine Schaltkammer 88, in der ein Ventilelement 90 angeordnet ist. Das Ventilelement 90 ist insgesamt zylindrisch mit einem Schaltabschnitt 92, der kreiszylindrischen Durchmesser hat, einem Übergangsabschnitt 94, der wie eine Einschnürung ausgebildet ist, und einem kreiszylindrischen Führungsabschnitt 96. Ein Ende einer Druckfeder 98 stützt sich an einem Verschlussteil 100 ab. Das andere Ende der Druckfeder 98 beaufschlagt das Ventilelement 90 in Richtung zum Steuerraum 84 hin.The hydraulically actuable switching valve 86 also includes a switching chamber 88, in which a valve element 90 is arranged. The valve element 90 is generally cylindrical with a switching portion 92 having a circular cylindrical diameter, a transition portion 94 which is formed as a constriction, and a circular cylindrical guide portion 96. One end of a compression spring 98 is supported on a closure member 100 from. The other end of the compression spring 98 acts on the valve element 90 in the direction of the control chamber 84.

In der Umfangswand der Schaltkammer 88 ist eine Ringnut 102 vorhanden. Diese ist zum Einen über einen Kanal 104 mit einem Hochdruckanschluss 106 (vgl. auch Figur 1) verbunden. Dieser führt wiederum zur Kraftstoff-Sammelleitung 20. Zum Anderen führt ein Kanal 108 über eine Strömungsdrossel 110 von der Ringnut 102 zum Steuerraum 76, mit dem die Bewegung des ersten Ventilelements 36 gesteuert wird. Von jenem Abschnitt der Umfangswand der Schaltkammer 88, welcher ungefähr im Bereich des eingeschnürten Übergangsabschnittes 94 des Ventilelements 90 liegt, führt ein Kanal 112 zu einem Ringraum 114 im unteren Bereich des zweiten Ventilelements 40.In the peripheral wall of the switching chamber 88, an annular groove 102 is present. This is connected on the one hand via a channel 104 with a high-pressure port 106 (see also Figure 1). This in turn leads to the fuel manifold 20. On the other hand, a channel 108 via a flow restrictor 110 from the annular groove 102 to the control chamber 76, with which the movement of the first valve element 36 is controlled. From that portion of the peripheral wall of the switching chamber 88, which is approximately in the region of the constricted transition portion 94 of the valve element 90, a channel 112 leads to an annular space 114 in the lower region of the second valve element 40th

In Figur 2 rechts von der Ringnut 102 bildet die Umfangswand der Schaltkammer 88 einen Ventilsitz 116 für eine Schaltkante 118 des Ventilelements 90. Die Schaltkante 118 ist zwischen dem Schaltabschnitt 92 und dem Übergangsabschnitt 94 gebildet. Im Schaltabschnitt 92 des Ventilelements 90 verläuft schräg zur Längsachse des Ventilelements 90 ein weiterer Kanal 120. Dieser umfasst eine Strömungsdrossel 122, und er verbindet die Ringnut 102 mit dem Steuerraum 84. Zu erwähnen ist ferner noch ein Leckagekanal 124, der von der Ausnehmung 34 im Oberteil 30 des Gehäuses zu einem Leckageanschluss 126 führt.In FIG. 2, to the right of the annular groove 102, the circumferential wall of the switching chamber 88 forms a valve seat 116 for a switching edge 118 of the valve element 90. The switching edge 118 is formed between the switching section 92 and the transition section 94. In the switching portion 92 of the valve member 90 extends obliquely to the longitudinal axis of the valve element 90, a further channel 120. This includes a flow restrictor 122, and it connects the annular groove 102 with the control chamber 84. Also to mention is still a leakage channel 124, of the recess 34 in Upper part 30 of the housing leads to a leakage connection 126.

Der in den Figuren 1 bis 3 dargestellte Injektor 22 arbeitet folgendermaßen:The injector 22 shown in Figures 1 to 3 operates as follows:

In der ersten Ruheschaltstellung liegt das Ventilelement 38 der gemeinsamen Ventileinrichtung 56 am in Figur 2 oberen Ventilsitz 68 an. In der Schaltkammer 60 der gemeinsamen Ventileinrichtung 56, im Steuerraum 76 des ersten Ventilelements 36, und im Steuerraum 84 des hydraulisch betätigten Schaltventils 86 liegt somit der am Hochdruckanschluss 106 vorliegende hohe Druck an. Hierdurch wird das Ventilelement 92 des hydraulisch betätigten Schaltventils 86 mit der Schaltkante 118 gegen den Ventilsitz 116 gedrückt. Jener Bereich der Schaltkammer 88, der auf Höhe des Übergangsabschnitts 94 liegt, ist also vom Hochdruckanschluss 106 getrennt. Daher herrscht in ihm ein vergleichsweise niedriger Druck. Das gleiche gilt für den Kanal 112 und den Ringraum 114. Das zweite Ventilelement 40 kann daher von der Feder 46 gegen den Ventilsitz 42 gedrückt werden.In the first closed-switch position, the valve element 38 of the common valve device 56 bears against the upper valve seat 68 in FIG. In the switching chamber 60 of the common valve device 56, in the control chamber 76 of the first valve element 36, and in the control chamber 84 of the hydraulically operated switching valve 86 is thus the on High pressure port 106 present high pressure. As a result, the valve element 92 of the hydraulically actuated switching valve 86 is pressed with the switching edge 118 against the valve seat 116. That region of the switching chamber 88 which lies at the level of the transition section 94 is thus separated from the high-pressure port 106. Therefore, there is a comparatively low pressure in him. The same applies to the channel 112 and the annular space 114. The second valve element 40 can therefore be pressed by the spring 46 against the valve seat 42.

Dadurch, dass im Steuerraum 76 und somit auch an der Druckfläche 78 ein hoher Kraftstoffdruck anliegt, gleichzeitig jedoch im Sackloch 50 ein niedriger Druck (Brennraumdruck) herrscht, wird auch das Ventilelement 36 gegen den Ventilsitz 38 gedrückt. In dieser ersten Schaltstellung der gemeinsamen Ventileinrichtung 56, in der das Ventilelement 58 am Ventilsitz 68 anliegt, ist also der Injektor 22 geschlossen und es tritt kein Kraftstoff aus den Austrittsöffnungen 52 und 54 aus.The fact that in the control chamber 76 and thus also on the pressure surface 78, a high fuel pressure is applied, but at the same time in the blind hole 50, a low pressure (combustion chamber pressure) prevails, and the valve element 36 is pressed against the valve seat 38. In this first switching position of the common valve device 56, in which the valve element 58 rests against the valve seat 68, that is, the injector 22 is closed and there is no fuel from the outlet openings 52 and 54 from.

Das Ventilelement 58 der gemeinsamen Ventileinrichtung 56 kann vom Aktor 64 über den Stößel 62 in eine zweite Schaltstellung gebracht werden, in der es an der in Figur 2 unteren Begrenzungswand der Schaltkammer 60 anliegt. Die Schaltkammer 60 ist nun über den Kanal 70 mit dem Niederdruckanschluss 72 verbunden. Über die Strömungsdrossel 82 kann somit der hohe Druck aus dem Steuerraum 84 des hydraulisch betätigbaren Schaltventils 86 entweichen. Durch die Druckfeder 98 wird nun das Ventilelement 90 des hydraulisch betätigbaren Schaltventils 86 in Richtung zum Steuerraum 84 bewegt, so dass die Schaltkante 118 vom Ventilsitz 116 abhebt.The valve element 58 of the common valve device 56 can be brought by the actuator 64 via the plunger 62 in a second switching position in which it rests against the lower boundary wall of the switching chamber 60 in FIG. The switching chamber 60 is now connected via the channel 70 to the low pressure port 72. Thus, the high pressure can escape from the control chamber 84 of the hydraulically actuatable switching valve 86 via the flow throttle 82. By the compression spring 98, the valve element 90 of the hydraulically actuatable switching valve 86 is now moved in the direction of the control chamber 84, so that the switching edge 118 lifts from the valve seat 116.

Der unter hohem Druck in der Ringnut 102 vorhandene Kraftstoff kann nun über den Kanal 112 in den Ringraum 114 strömen. An einem radial außerhalb des Ventilsitzes 42 gelegenen Bereich der in Figur 2 unteren konischen Endfläche des Ventilelements 40 liegt nun der hohe Kraftstoffdruck an, der auch am Hochdruckanschluss 106 anliegt. Durch diesen wird das zweite Ventilelement 40 entgegen der Beaufschlagung durch die Druckfeder 46 nach oben bewegt, so dass es vom Ventilsitz 42 freikommt. Somit kann der unter hohem Druck im Ringraum 114 vorhandene Kraftstoff durch die Austrittsöffnungen 54 nach außen strömen.The fuel present under high pressure in the annular groove 102 can now flow via the channel 112 into the annular space 114. At a radially outwardly of the valve seat 42 located region of the lower conical end surface of the valve element 40 in Figure 2 is now the high fuel pressure, which also rests on the high-pressure port 106. By this, the second valve element 40 is moved against the action of the compression spring 46 upwards, so that it is released from the valve seat 42. Thus, the fuel present under high pressure in the annular space 114 can flow through the outlet openings 54 to the outside.

Da das Ventilelement 58 der gemeinsamen Ventileinrichtung 56 in dieser zweiten Schaltstellung dem Kanal 74 zum Steuerraum 76 hin verschließt, herrscht in diesem weiterhin ein hoher Kraftstoffdruck, der das erste Ventilelement 36 über die Druckfläche 78 in Figur 2 nach unten drückt. Obwohl nun an dem radial außen vom Ventilsitz 38 gelegenen Bereich der konischen unteren Endfläche des Ventilelements 36 ein hoher Kraftstoffdruck anliegt, wird aufgrund der in Figur 2 nach unten gerichteten Kraftresultierenden der Druckfläche 78 das erste Ventilelement 36 weiter gegen den Ventilsitz 38 gedrückt. Durch die Austrittsöffnungen 52 kann daher weiterhin kein Kraftstoff austreten.Since the valve element 58 of the common valve device 56 closes the channel 74 to the control chamber 76 in this second switching position, there continues to be a high fuel pressure which presses the first valve element 36 downward over the pressure surface 78 in FIG. Although a high fuel pressure now rests on the region of the conical lower end surface of the valve element 36 that is located radially outside of the valve seat 38, the first valve element 36 is pressed further against the valve seat 38 due to the downward force on the pressure surface 78 in FIG. Therefore, no fuel can escape through the outlet openings 52.

Damit auch während der Bewegung des Ventilelements 58 der gemeinsamen Ventileinrichtung 56 von der ersten in die zweite Schaltstellung der Druck im Steuerraum 76 nicht so weit abfällt, dass das Ventilelement vom Ventilsitz 38 abhebt, wird durch die Strömungsdrossel 80 das Abströmen des Kraftstoffes aus dem Steuerraum 76 verzögert.So that during the movement of the valve element 58 of the common valve device 56 from the first to the second switching position, the pressure in the control chamber 76 does not drop so far that the valve element lifts off from the valve seat 38, the outflow of the fuel from the control chamber 76 through the flow restrictor 80th delayed.

Das Ventilelement 58 der gemeinsamen Ventileinrichtung 56 kann vom Aktor 64 auch in eine dritte, mittlere Schaltstellung gebracht werden. In dieser liegt es weder am Ventilsitz 68 noch an der in Figur 2 unteren Stirnwand der Schaltkammer 60 an. Somit ist, wie bei der zweiten Schaltstellung, die Schaltkammer 60 mit dem Niederdruckanschluss 72 verbunden. Zusätzlich kann jedoch nun der Kraftstoff aus dem Steuerraum 76 über den Kanal 74 und die Strömungsdrossel 80 in die Schaltkammer 60 und weiter zum Niederdruckanschluss 72 abströmen. Hierdurch sinkt der Druck im Steuerraum 76 so weit ab, dass das Ventilelement 36 von dem am radial außen vom Ventilsitz 38 der konischen Endfläche anliegenden hohen Druck vom Ventilsitz 38 abgehoben wird. Wenn sich das Ventilelement 58 der gemeinsamen Ventileinrichtung 56 also in der mittleren dritten Schaltstellung befindet, wird vom Injektor 22 Kraftstoff sowohl durch die Austrittsöffnungen 54 als auch durch die Austrittsöffnungen 52 abgegeben.The valve element 58 of the common valve device 56 can be brought by the actuator 64 in a third, middle switching position. In this it is neither on the valve seat 68 nor on the lower end wall of the switching chamber 60 in Figure 2. Thus, as in the second switching position, the switching chamber 60 is connected to the low pressure port 72. In addition, however, the fuel can now flow from the control chamber 76 via the channel 74 and the flow restrictor 80 into the switching chamber 60 and on to the low-pressure connection 72. As a result, the pressure in the control chamber 76 decreases to such an extent that the valve element 36 is lifted off the valve seat 38 by the high pressure applied radially outward from the valve seat 38 of the conical end surface. When the valve element 58 of the common valve device 56 is thus in the middle third switching position, fuel is discharged from the injector 22 both through the outlet openings 54 and through the outlet openings 52.

Claims (7)

  1. Fuel injection device (22) for an internal combustion engine, with a housing (30, 32), with a recess (34) present in the housing (30, 32), and with at least two valve elements (36, 40) which are arranged coaxially to one another in the recess (34) and in each case cooperate with a corresponding valve seat (38, 42) and which are assigned in each case at least one corresponding fuel outlet orifice (52, 54), characterized in that it comprises, as a common valve device (56), a 3/3-way valve (56) which influences the position of the valve elements (36, 40) and is connected to a low-pressure connection (72), to a control space (76) of the first valve element (36) and to a control space (84) of a hydraulically switchable valve device (86) which, in turn, is connected to a control space (114) of the second valve element (40) and to a high-pressure connection (106).
  2. Fuel injection device (22) according to Claim 1, characterized in that, in a first switching position of the common valve device (56), both valve elements (36, 40) bear against the valve seat (52, 54), in a second switching position one of the two valve elements (40) is lifted off from its valve seat (54), and, in a third switching position, both valve elements (36, 40) are lifted off from their valve seats (52, 54).
  3. Fuel injection device (22) according to one of the preceding claims, characterized in that a flow throttle (122) is arranged in the flow path between the high-pressure connection (106) and the control space (84) of the hydraulically switchable valve device (86).
  4. Fuel injection device (22) according to one of the preceding claims, characterized in that a flow throttle (82) is arranged in the flow path between the control space (84) of the hydraulically switchable valve device (86) and the common valve device (56).
  5. Fuel injection device (22) according to one of the preceding claims, characterized in that one valve element (40) operates by pressure control and the other valve element operates (36) by stroke control.
  6. Fuel injection device (22) according to Claim 5, characterized in that the pressure-controlled valve element (40) is arranged radially on the outside of the stroke-controlled valve element (36).
  7. Fuel injection device (22) according to Claim 5 or 6, characterized in that, in one end position of the common valve device (56), the control space (76) of the stroke-controlled valve element (36) and the control space (84) of the hydraulically switchable valve device (86) are connected only to the high-pressure connection (106).
EP03740027A 2002-10-09 2003-05-23 Fuel injection device for an internal combustion engine Expired - Lifetime EP1552136B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10246973 2002-10-09
DE10246973A DE10246973A1 (en) 2002-10-09 2002-10-09 Fuel injector for internal combustion engine has at least two co-axially disposed valve elements and common valve unit which has at least three selectable positions and which influences position of valve elements
PCT/DE2003/001677 WO2004033891A1 (en) 2002-10-09 2003-05-23 Fuel injection device for an internal combustion engine

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EP1552136A1 EP1552136A1 (en) 2005-07-13
EP1552136B1 true EP1552136B1 (en) 2006-08-23

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EP (1) EP1552136B1 (en)
CN (1) CN1688805A (en)
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DE10335211A1 (en) * 2003-08-01 2005-02-17 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
DE102004002090A1 (en) * 2004-01-15 2005-08-04 Robert Bosch Gmbh Injector and associated operating method
DE602006008377D1 (en) 2005-04-28 2009-09-24 Delphi Tech Inc injection
EP1717435B1 (en) * 2005-04-28 2009-08-12 Delphi Technologies, Inc. Injection nozzle
DE602005009334D1 (en) * 2005-05-03 2008-10-09 Delphi Tech Inc Device for a fuel injection valve with switchable operating modes
DE102006020634B4 (en) * 2006-05-04 2008-12-04 Man Diesel Se Injection injector for internal combustion engines
JP4245639B2 (en) * 2007-04-13 2009-03-25 トヨタ自動車株式会社 Fuel injection valve for internal combustion engine
US8905059B2 (en) 2012-07-20 2014-12-09 Caterpillar Inc. Diesel fuel leakage control system for a dual fuel injector
DE102013210036A1 (en) * 2013-05-29 2014-12-04 Robert Bosch Gmbh High pressure pump for a fuel injection system
WO2023166139A1 (en) * 2022-03-03 2023-09-07 Ganser-Hydromag Ag Fuel injection valve for internal combustion engines
US20240068408A1 (en) * 2022-08-26 2024-02-29 Collins Engine Nozzles, Inc. Proportional force modification of passive spool for control of secondary nozzle circuits
US11970977B2 (en) 2022-08-26 2024-04-30 Hamilton Sundstrand Corporation Variable restriction of a secondary circuit of a fuel injector
US11913382B1 (en) 2022-08-26 2024-02-27 Hamilton Sundstrand Corporation Variable restriction of a fuel circuit of a fuel nozzle
US11970976B2 (en) 2022-08-26 2024-04-30 Hamilton Sundstrand Corporation Variable restriction of fuel nozzle with an auxiliary circuit
US11913381B1 (en) * 2022-08-26 2024-02-27 Hamilton Sundstrand Corporation Force modification of passive spool for control of secondary nozzle circuits

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EP1041272B1 (en) * 1999-04-01 2004-10-27 Delphi Technologies, Inc. Fuel injector
GB9916464D0 (en) * 1999-07-14 1999-09-15 Lucas Ind Plc Fuel injector
DE10058130A1 (en) * 2000-11-22 2002-05-23 Bosch Gmbh Robert Fuel injection system for internal combustion engine has high pressure collection chamber in which fuel is held under high pressure and at least one fuel injection valve connected to the collection chamber
US20060060673A1 (en) * 2000-11-22 2006-03-23 Gerhard Mack Injector with separately controllable injector needles
DE10058153A1 (en) * 2000-11-22 2002-06-06 Bosch Gmbh Robert Injection nozzle with separately controllable nozzle needles
US6557776B2 (en) * 2001-07-19 2003-05-06 Cummins Inc. Fuel injector with injection rate control
US6705543B2 (en) * 2001-08-22 2004-03-16 Cummins Inc. Variable pressure fuel injection system with dual flow rate injector
US6725838B2 (en) * 2001-10-09 2004-04-27 Caterpillar Inc Fuel injector having dual mode capabilities and engine using same

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DE10246973A1 (en) 2004-04-22
CN1688805A (en) 2005-10-26
US7267096B2 (en) 2007-09-11
EP1552136A1 (en) 2005-07-13
DE50304778D1 (en) 2006-10-05
WO2004033891A1 (en) 2004-04-22
US20060144964A1 (en) 2006-07-06

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