EP1772618B1 - Common rail injector - Google Patents

Common rail injector Download PDF

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Publication number
EP1772618B1
EP1772618B1 EP06123003A EP06123003A EP1772618B1 EP 1772618 B1 EP1772618 B1 EP 1772618B1 EP 06123003 A EP06123003 A EP 06123003A EP 06123003 A EP06123003 A EP 06123003A EP 1772618 B1 EP1772618 B1 EP 1772618B1
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EP
European Patent Office
Prior art keywords
nozzle
spring
space
pressure
injector
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP06123003A
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German (de)
French (fr)
Other versions
EP1772618A1 (en
Inventor
Dieter Kienzler
Patrick Mattes
Wolfgang Stoecklein
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Application filed by Robert Bosch GmbH filed Critical 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/006—Springs assisting hydraulic closing force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting

Definitions

  • the invention relates to a common rail injector for injecting fuel in a common rail injection system of an internal combustion engine having an injector housing with a fuel inlet communicating with a central fuel high pressure accumulator outside the injector housing and with a pressure space inside the injector housing. is injected from the high-pressure fuel in response to the position of a control valve, which ensures that in a longitudinal bore of the injector axially against the biasing force of a nozzle spring, which is accommodated in a nozzle spring chamber, movable back and forth nozzle needle lifts from a seat when the pressure in the pressure chamber is greater than the pressure in a control chamber, which is connected via an inlet throttle with the fuel inlet.
  • a high-pressure pump delivers the fuel into the central high-pressure accumulator, which is referred to as a common rail.
  • high pressure lines lead to the individual injectors, which are assigned to the engine cylinders.
  • the injectors are controlled individually by the engine electronics.
  • the rail pressure is in the pressure chamber and on the control valve. When the control valve opens, high-pressure fuel passes past the nozzle needle lifted against the biasing force of the nozzle spring in the combustion chamber.
  • An injector of a pump-nozzle unit in which a control chamber sleeve is guided on the nozzle needle, which separates a control chamber from a high-pressure nozzle spring chamber.
  • the sleeve is held by a nozzle spring arranged in the nozzle spring in contact with the injector, so that the control chamber is separated from the nozzle spring chamber.
  • the fuel inlet in a pressure chamber which is exposed to the nozzle needle with a pressure shoulder acting in the opening direction, takes place through the nozzle spring chamber.
  • the nozzle spring is supported directly on an integrally formed on the nozzle needle collar.
  • the object of the invention is to provide a common rail injector, which ensures a good closing behavior at a high nozzle needle speed.
  • the object is in a common rail injector for injecting fuel in a common rail injection system of an internal combustion engine having an injector with a fuel inlet, which communicates with a central fuel high pressure accumulator outside the injector and with a pressure chamber inside the injector , from the with High-pressure fuel is injected in response to the position of a control valve, which ensures that in a longitudinal bore of the injector axially against the biasing force of a nozzle spring, which is accommodated in a nozzle spring space, reciprocally movable nozzle needle lifts from a seat when the Pressure in the pressure chamber is greater than the pressure in a control chamber, which is connected via an inlet throttle with the fuel inlet, achieved in that the control chamber is limited by a sleeve which can be combined under sealing effect at the combustion chamber distal end of the nozzle needle, without the volume of the control chamber depends on the installation space of the nozzle spring.
  • the injection time and the injection timing can be set exactly.
  • the control chamber can be made very small, resulting in a fast response of the injector according to the invention.
  • the maximum achievable nozzle needle speed In order to get higher nozzle needle speeds, which is especially important when needle closing, the nozzle needle diameter must be reduced. For a closing speed of 1 m / sec, a needle diameter of less than 3.5 mm is necessary with an acceptable control quantity. This is technically very complicated and therefore expensive.
  • the nozzle needle diameter can be chosen freely and is not dependent on the dimensions of the nozzle spring. Compared to conventional jet needles, the length can be significantly reduced, which contributes to a precise stroke stop.
  • the invention is characterized in that a step is formed on the nozzle needle, which forms a stop for a spring plate and that the Düsennadelhub and the Düsenfedervorschreib by means of spacer elements are adjustable between the spring plate and the stop for the spring plate or between the Nozzle spring and the abutments are arranged for the nozzle spring.
  • a step is formed on the nozzle needle, which forms a stop for a spring plate and that the Düsennadelhub and the Düsenfedervorschreib by means of spacer elements are adjustable between the spring plate and the stop for the spring plate or between the Nozzle spring and the abutments are arranged for the nozzle spring.
  • a particular embodiment of the invention is characterized in that a biting edge is formed on the surface of the sleeve, which is in contact with the injector housing. It is thereby achieved that the control chamber formed in the interior of the sleeve remains separated from the nozzle spring chamber surrounding the sleeve.
  • Another particular embodiment of the invention is characterized in that the inner diameter of the sleeve smaller than the guide diameter on the nozzle needle.
  • the inner diameter of the sleeve and the corresponding outer diameter on the nozzle needle can be made much smaller than in conventional injectors.
  • Another particular embodiment of the invention is characterized in that the nozzle needle is guided between the nozzle spring chamber and the pressure chamber. This provides the advantage that the nozzle needle guide no longer has a sealing function. This reduces the quality requirements of the guide, which leads to savings in production. Because there is the same pressure on both sides of the guide, there is no longer any pilot leakage.
  • Another particular embodiment of the invention is characterized in that the nozzle spring chamber communicates via a bore with the pressure chamber. As a result, the complete circumference of the nozzle needle can be used for guidance purposes.
  • a further particular embodiment of the invention is characterized in that at least one flat surface is formed on the nozzle needle between the nozzle spring chamber and the pressure chamber, past which fuel can pass from the nozzle spring chamber into the pressure chamber.
  • inlet throttle is integrated into the nozzle needle, the sleeve or the injector housing.
  • the inlet throttle is used to pressure surges during operation prevent.
  • Another particular embodiment of the invention is characterized in that the sleeve has a collar at its end remote from the combustion chamber.
  • the collar forms a first abutment for the nozzle spring.
  • Another particular embodiment not according to the present invention is characterized in that in the nozzle needle a circumferential groove is recessed, in which a retaining ring is supported, which forms a stop for a spring plate.
  • the outer diameter of the nozzle needle in the control chamber and the guide diameter of the nozzle needle between the nozzle spring chamber and the pressure chamber can be the same size. This is in the manufacturing, e.g. by lapping, an advantage.
  • Another particular embodiment not according to the present invention is characterized in that the retaining ring is in two parts and is fixed in the assembled state by the spring plate. As a result, a release of the spring plate is prevented during operation in a simple manner.
  • Another particular embodiment of the invention is characterized in that the Düsennadelhub is defined by the distance between the sleeve and the spring plate.
  • This purely mechanical Düsennadelhubendanschlag provides the advantage that the Düsennadelhub is exactly reproducible. As a result, the course of injection can be reliably shaped. So-called hydraulic bonding is avoided.
  • Another particular embodiment not according to the present invention is characterized in that the Düsennadelhub is defined by the distance between the combustion chamber remote end face of the nozzle needle and the injector.
  • This embodiment has the advantage that it is particularly easy to implement in terms of manufacturing technology.
  • Another particular embodiment not according to the present invention is characterized in that in the combustion chamber remote end face of the nozzle needle and / or in the opposite surface of the injector housing recesses are provided whose dimensions are adapted to the volume of the control chamber.
  • the nozzle needle stroke stop In order to achieve the most linear quantity characteristic diagram possible during operation of the injector, it makes sense not to design the nozzle needle stroke stop purely hydraulically. In a purely hydraulic Düsennadelhubanschlag it may happen that the nozzle needle in the open position on a pressure pad "floats". This can lead to vibrations of the nozzle needle. The oscillations in turn result in non-linear quantity maps. Since this is a dynamic movement, there is a greater tolerance dependency.
  • the vibrations of the nozzle needle may depend on the inlet and the outlet throttle, the friction of the nozzle needle guide, the control chamber volume, etc.
  • a vibration of the nozzle needle is indeed avoided, but it is a slightly larger tax amount required. This has an unfavorable effect on the efficiency of the injector.
  • a "semi-hydraulic" stop is created. The flow cross-section remaining at the stop is just chosen so large that avoids oscillation of the nozzle needle, but the control amount at the end stop as far as possible In this case, it is advantageous that the injector according to the invention has no leakage, ie no return quantity is generated without activation of the injector.
  • Another particular embodiment not according to the present invention is characterized in that in the combustion chamber remote end face of the nozzle needle at least one axial bore is provided which is in communication with at least one radial bore in the nozzle needle.
  • This embodiment has the advantage that it is insensitive to mechanical shrinkage, i. the flow cross section does not change over the service life.
  • the injector housing 1 comprises a nozzle body 2, which projects with its lower free end into the combustion chamber of the internal combustion engine to be supplied. With its upper, combustion chamber remote end face of the nozzle body 2 is clamped by means of a clamping nut 5 axially against a valve body 3 and an injector 4.
  • an axial guide bore 6 is recessed.
  • a nozzle needle 8 is guided axially displaceable.
  • a sealing surface is formed, which cooperates with a sealing seat which is formed on the nozzle body 2.
  • the nozzle needle 8 has three regions with different diameters d1, d2 and d3.
  • the diameter d2 is the largest and serves to guide the nozzle needle 8 in the nozzle body 2.
  • the diameter d1 is the smallest. In the section with the
  • Diameter d1 is a collar 16 with a flat 17 formed on its outer peripheral surface.
  • the collar 16 forms a second guide for the nozzle needle 1.
  • the flattening 17 in the collar 16 is a flow connection allows in the longitudinal direction of the nozzle needle 1 from one side of the collar 16 to the other side.
  • the diameter d3 is larger than the diameter dl but smaller than the diameter d2.
  • the diameter d3 is also referred to as the control diameter.
  • the nozzle needle 8 is biased by means of a nozzle spring 19 against the nozzle needle seat in the region of the injection holes 10 and 11.
  • the nozzle spring 19 is arranged in a nozzle spring chamber 20, in which a fuel inlet 21 opens.
  • a fuel inlet 21 is supplied from a (not shown) rail with fuel, which is acted upon by high pressure.
  • the high-pressure fuel from the nozzle spring chamber 20 passes into a pressure chamber 24.
  • the pressure chamber 24 is connected via an annular space 25 with the spray holes 10 and 11 in connection, when the nozzle needle 1 against the biasing force of the nozzle spring 19 lifted from its seat is.
  • a step results on the nozzle needle 8, which forms a stop for a spring plate 26.
  • the biasing force of the nozzle spring 19 is transmitted to the nozzle needle 8.
  • the other end of the nozzle spring 19 is supported on a collar 27, which is formed on a sleeve 28.
  • the inner diameter of the sleeve 28 is slightly larger than the control diameter d3 of the nozzle needle B.
  • the dimensions of the diameters are selected so that the sleeve 28 is displaceable relative to the nozzle needle 8 under sealing action.
  • the biasing force of the nozzle spring 19 the sleeve 28 is pressed with a biting edge 29 against the valve body 3.
  • a control chamber 30 provided in the interior of the sleeve 28, which is delimited by the end face of the nozzle needle 8 remote from the combustion chamber, is sealed off from the nozzle spring chamber 20.
  • the control chamber 30 is connected via an inlet throttle 31 with the nozzle spring chamber 20.
  • the control chamber 30 is connected via an outlet throttle 32 with a (not shown) discharge space in connection.
  • the connection of the control chamber 30 with the discharge chamber depends on the position of a control valve member 33.
  • FIG. 2 illustrated second embodiment corresponds largely to the in Fig. 1 illustrated first embodiment.
  • the same reference numerals will be used to designate like parts.
  • a flattening 36 is formed in the portion of the nozzle needle 8 with the diameter d2.
  • the flattening 36 provides a connection between the nozzle spring chamber 20 and the pressure chamber 24. Otherwise, there are no differences between the two embodiments.
  • FIG. 3 illustrated third non-inventive embodiment differs from the second embodiment in that the inlet throttle is not disposed in the sleeve 28.
  • the inlet throttle in the form of holes of different orientations and different dimensions can be integrated into the nozzle needle 8.
  • the inlet throttle can also be integrated in the valve body 3.
  • the spring plate 26 is not supported directly on the nozzle needle 8, but only indirectly via a resilient retaining ring 42 having a rectangular cross-section.
  • the retaining ring 42 is formed slotted.
  • a two-part retaining ring 46 can be used instead of a one-piece, clip-on retaining ring.
  • the retaining ring 46 consists of two ring halves, which are placed in the associated groove in the nozzle needle 8 and fixed by means of the spring plate 26.
  • the stroke is not, as in the in Fig. 1 illustrated embodiment, limited by the distance H1 of the combustion chamber remote end face of the nozzle needle 8 and the opposite surface of the valve body 3, but by the distance H2 between the sleeve 28 and the spring plate 26.
  • the stroke H2 can be adjusted by a spacer 51.
  • the spacer 51 is arranged for this purpose between the shoulder, which results from the difference in diameter between d2 and d3, and the spring plate 26.
  • the spring biasing force of the nozzle spring 19 can be adjusted by means of a spacer 50.
  • the spacer 50 between the nozzle spring 19 and the collar 27 of the sleeve 28 is arranged.
  • two grooves 55 and 56 are arranged crosswise in the end face 54 of the nozzle needle 8.
  • a purely mechanical stop of the needle nozzle is realized. If the dimensions of the grooves 54 and 55 are adapted to the injector, this can become a "semi-hydraulic stop". The one at the stop remaining breakthrough cross-section is just chosen so large that a vibration of the nozzle needle 8 Although avoided, the control amount at the end stop but is lowered as much as possible.
  • a throttle bore 58 is arranged parallel to the longitudinal axis of the nozzle needle 8 in the end face 54 of the nozzle needle 8.
  • the throttle bore 58 opens into a bore 59 which extends transversely to the longitudinal axis of the nozzle needle 8.
  • the bore 59 is a blind bore, which is open to the combustion chamber distant, frustoconical end of the nozzle needle 8 out.
  • a groove 61 is recessed instead of in the combustion chamber remote end face 54 of the nozzle needle 8 in the opposite surface 62 of the valve body 3.
  • the groove 61 has the same function as the grooves 54 and 55 in which in the 8 and 9 illustrated embodiment.

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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)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Seats For Vehicles (AREA)
  • Platform Screen Doors And Railroad Systems (AREA)

Abstract

The injector has an injector housing (1) with a fuel feed connected to a central high pressure fuel reservoir and an internal pressure chamber. A reciprocally movable nozzle needle movable axially against a spring force is raised from as eat if the pressure in the pressure chamber exceeds that in a control chamber connected via a feed choke to the fuel feed. The control chamber (30) is bounded by a sleeve (28) that can be moved into contact with the injector housing under the sealing effect of the end of the needle (8) remote from the combustion chamber and with the aid of the nozzle spring (19).

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Common-Rail-Injektor zur Einspritzung von Kraftstoff in einem Common-Rail-Einspritzsystem einer Brennkraftmaschine, der ein Injektorgehäuse mit einem Kraftstoffzulauf aufweist, der mit einem zentralen Kraftstoffhochdruckspeicher außerhalb des Injektorgehäuses und mit einem Druckraum innerhalb des Injektorgehäuses in Verbindung steht, aus dem mit Hochdruck beaufschlagter Kraftstoff in Abhängigkeit von der Stellung eines Steuerventils eingespritzt wird, das dafür sorgt, dass eine in einer Längsbohrung des Injektors axial gegen die Vorspannkraft einer Düsenfeder, die in einem Düsenfederraum aufgenommen ist, hin und her bewegbare Düsennadel von einem Sitz abhebt, wenn der Druck in dem Druckraum größer als der Druck in einem Steuerraum ist, der über eine Zulaufdrossel mit dem Kraftstoffzulauf verbunden ist.The invention relates to a common rail injector for injecting fuel in a common rail injection system of an internal combustion engine having an injector housing with a fuel inlet communicating with a central fuel high pressure accumulator outside the injector housing and with a pressure space inside the injector housing. is injected from the high-pressure fuel in response to the position of a control valve, which ensures that in a longitudinal bore of the injector axially against the biasing force of a nozzle spring, which is accommodated in a nozzle spring chamber, movable back and forth nozzle needle lifts from a seat when the pressure in the pressure chamber is greater than the pressure in a control chamber, which is connected via an inlet throttle with the fuel inlet.

In Common-Rail-Einspritzsystemen fördert eine Hochdruckpumpe den Kraftstoff in den zentralen Hochdruckspeicher, der als Common-Rail bezeichnet wird. Von dem Hochdruckspeicher führen Hochdruckleitungen zu den einzelnen Injektoren, die den Motorzylindern zugeordnet sind. Die Injektoren werden einzeln von der Motorelektronik angesteuert. Der Raildruck steht in dem Druckraum und an dem Steuerventil an. Wenn das Steuerventil öffnet, gelangt mit Hochdruck beaufschlagter Kraftstoff an der gegen die Vorspannkraft der Düsenfeder abgehobenen Düsennadel vorbei in den Verbrennungsraum.In common-rail injection systems, a high-pressure pump delivers the fuel into the central high-pressure accumulator, which is referred to as a common rail. From the high pressure accumulator high pressure lines lead to the individual injectors, which are assigned to the engine cylinders. The injectors are controlled individually by the engine electronics. The rail pressure is in the pressure chamber and on the control valve. When the control valve opens, high-pressure fuel passes past the nozzle needle lifted against the biasing force of the nozzle spring in the combustion chamber.

Bei herkömmlichen Injektoren, wie sie beispielsweise aus der DE 197 24 637 Al oder der DE 197 32 802 AI bekannt sind, kommen relativ lange Düsennadeln zum Einsatz. Im Betrieb wirken auf die Düsennadel infolge der hohen Drücke und der schnellen Lastwechsel sehr große Kräfte. Diese Kräfte führen dazu, dass die Düsennadel in Längsrichtung gedehnt und gestaucht wird. Das wiederum hat zur Folge, dass der Düsennadelhub in Abhängigkeit von der auf die Düsennadel wirkenden Kräfte variiert.In conventional injectors, such as those from the DE 197 24 637 Al or the DE 197 32 802 AI are known, relatively long nozzle needles are used. In operation, very large forces act on the nozzle needle as a result of the high pressures and the rapid load changes. These forces cause the nozzle needle to be stretched and compressed in the longitudinal direction. This in turn has the consequence that the nozzle needle stroke varies depending on the forces acting on the nozzle needle forces.

Aus US 4,572,433 A ist ein Injektor einer Pumpe-Düse-Einheit bekannt, bei dem an der Düsennadel eine Steuerraumhülse geführt ist, die einen Steuerraum von einem mit Hochdruck beaufschlagten Düsenfederraum trennt. Die Hülse wird von einer im Düsenfederraum angeordneten Düsenfeder in Anlage an das Injektorgehäuse gehalten, so dass der Steuerraum vom Düsenfederraum getrennt ist. Der Kraftstoffzulauf in einem Druckraum, dem die Düsennadel mit einer in Öffnungsrichtung wirkenden Druckschulter ausgesetzt ist, erfolgt durch den Düsenfederraum. Die Düsenfeder stützt sich dabei unmittelbar an einem an der Düsennadel angeformten Bund ab.Out US 4,572,433 A An injector of a pump-nozzle unit is known, in which a control chamber sleeve is guided on the nozzle needle, which separates a control chamber from a high-pressure nozzle spring chamber. The sleeve is held by a nozzle spring arranged in the nozzle spring in contact with the injector, so that the control chamber is separated from the nozzle spring chamber. The fuel inlet in a pressure chamber, which is exposed to the nozzle needle with a pressure shoulder acting in the opening direction, takes place through the nozzle spring chamber. The nozzle spring is supported directly on an integrally formed on the nozzle needle collar.

Aufgabe der Erfindung ist es, einen Common-Rail-Injektor zu schaffen, der bei einer hohen Düsennadelgeschwindigkeit ein gutes Schließverhalten gewährleistet.The object of the invention is to provide a common rail injector, which ensures a good closing behavior at a high nozzle needle speed.

Offenbarung der ErfindungDisclosure of the invention

Die Aufgabe ist bei einem Common-Rail-Injektor zur Einspritzung von Kraftstoff in einem Common-Rail-Einspritzsystem einer Brennkraftmaschine, der ein Injektorgehäuse mit einem Kraftstoffzulauf aufweist, der mit einem zentralen Kraftstoffhochdruckspeicher außerhalb des Injektorgehäuses und mit einem Druckraum innerhalb des Injektorgehäuses in Verbindung steht, aus dem mit Hochdruck beaufschlagter Kraftstoff in Abhängigkeit von der Stellung eines Steuerventils eingespritzt wird, das dafür sorgt, dass eine in einer Längsbohrung des Injektors axial gegen die Vorspannkraft einer Düsenfeder, die in einem Düsenfederraum aufgenommen ist, hin und her bewegbare Düsennadel von einem Sitz abhebt, wenn der Druck in dem Druckraum größer als der Druck in einem Steuerraum ist, der über eine Zulaufdrossel mit dem Kraftstoffzulauf verbunden ist, dadurch gelöst, dass der Steuerraum von einer Hülse begrenzt ist, die unter Dichtwirkung an dem brennraumfernen Ende der Düsennadel kombiniert werden können, ohne dass das Volumen des Steuerraums von dem Bauraum der Düsenfeder abhängt. Deshalb ist es möglich, eine Düsenfeder mit einer hohen Federsteifigkeit einzubauen, die ein gutes Schließen der Düsennadel gewährleistet. Dadurch können die Einspritzzeit und der Einspritzzeitpunkt exakt festgelegt werden. Außerdem kann der Steuerraum sehr klein ausgeführt werden, was zu einem schnellen Ansprechverhalten des erfindungsgemäßen Injektors führt. Weiterhin besteht ein Zusammenhang zwischen der maximal erreichbaren Düsennadelgeschwindigkeit und dem Düsennadeldurchmesser. Um zu höheren Düsennadelgeschwindigkeiten zu kommen, was besonders beim Nadelschließen wichtig ist, muss der Düsennadeldurchmesser reduziert werden. Für eine Schließgeschwindigkeit von 1 m/sec ist bei einer akzeptablen Steuermenge ein Nadeldurchmesser von unter 3,5 mm nötig. Das ist technisch sehr aufwendig und daher teuer. Gemäß der vorliegenden Erfindung kann der Düsennadeldurchmesser frei gewählt werden und ist nicht abhängig von den Abmessungen der Düsenfeder. Im Vergleich zu herkömmlichen Düsennadeln kann die Länge erheblich reduziert werden, was zu einem exakten Hubanschlag beiträgt.The object is in a common rail injector for injecting fuel in a common rail injection system of an internal combustion engine having an injector with a fuel inlet, which communicates with a central fuel high pressure accumulator outside the injector and with a pressure chamber inside the injector , from the with High-pressure fuel is injected in response to the position of a control valve, which ensures that in a longitudinal bore of the injector axially against the biasing force of a nozzle spring, which is accommodated in a nozzle spring space, reciprocally movable nozzle needle lifts from a seat when the Pressure in the pressure chamber is greater than the pressure in a control chamber, which is connected via an inlet throttle with the fuel inlet, achieved in that the control chamber is limited by a sleeve which can be combined under sealing effect at the combustion chamber distal end of the nozzle needle, without the volume of the control chamber depends on the installation space of the nozzle spring. Therefore, it is possible to install a nozzle spring with a high spring stiffness, which ensures a good closing of the nozzle needle. As a result, the injection time and the injection timing can be set exactly. In addition, the control chamber can be made very small, resulting in a fast response of the injector according to the invention. Furthermore, there is a relationship between the maximum achievable nozzle needle speed and the nozzle needle diameter. In order to get higher nozzle needle speeds, which is especially important when needle closing, the nozzle needle diameter must be reduced. For a closing speed of 1 m / sec, a needle diameter of less than 3.5 mm is necessary with an acceptable control quantity. This is technically very complicated and therefore expensive. According to the present invention, the nozzle needle diameter can be chosen freely and is not dependent on the dimensions of the nozzle spring. Compared to conventional jet needles, the length can be significantly reduced, which contributes to a precise stroke stop.

Die Erfindung ist dadurch gekennzeichnet, dass an der Düsennadel eine Stufe ausgebildet ist, die einen Anschlag für einen Federteller bildet und dass der Düsennadelhub und die Düsenfedervorspannung mit Hilfe von Distanzelementen einstellbar sind, die zwischen dem Federteller und dem Anschlag für den Federteller bzw. zwischen der Düsenfeder und den Widerlagern für die Düsenfeder angeordnet sind. Dadurch kann das Schließverhalten des Injektors verbessert werden.The invention is characterized in that a step is formed on the nozzle needle, which forms a stop for a spring plate and that the Düsennadelhub and the Düsenfedervorspannung by means of spacer elements are adjustable between the spring plate and the stop for the spring plate or between the Nozzle spring and the abutments are arranged for the nozzle spring. As a result, the closing behavior of the injector can be improved.

Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass an der Fläche der Hülse, die sich in Anlage an dem Injektorgehäuse befindet, eine Beißkante ausgebildet ist. Dadurch wird erreicht, dass der im Inneren der Hülse ausgebildete Steuerraum von dem die Hülse umgebenden Düsenfederraum getrennt bleibt.A particular embodiment of the invention is characterized in that a biting edge is formed on the surface of the sleeve, which is in contact with the injector housing. It is thereby achieved that the control chamber formed in the interior of the sleeve remains separated from the nozzle spring chamber surrounding the sleeve.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Innendurchmesser der Hülse kleiner als der Führungsdurchmesser an der Düsennadel ist. Je kleiner das Steuerraumvolumen gewählt werden kann, desto reaktionsfreudiger ist der Injektor. Gemäß der vorliegenden Erfindung können der Innendurchmesser der Hülse und der entsprechende Außendurchmesser an der Düsennadel viel kleiner ausgeführt werden als bei herkömmlichen Injektoren.Another particular embodiment of the invention is characterized in that the inner diameter of the sleeve smaller than the guide diameter on the nozzle needle. The smaller the control chamber volume can be chosen, the more responsive the injector is. According to the present invention, the inner diameter of the sleeve and the corresponding outer diameter on the nozzle needle can be made much smaller than in conventional injectors.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Düsennadel zwischen dem Düsenfederraum und dem Druckraum geführt ist. Das liefert den Vorteil, dass der Düsennadelführung keine Dichtfunktion mehr zukommt. Damit werden die Anforderungen an die Qualität der Führung geringer, was zu Einsparungen in der Fertigung führt. Weil auf beiden Seiten der Führung der gleiche Druck herrscht, tritt keine Führungsleckage mehr auf.Another particular embodiment of the invention is characterized in that the nozzle needle is guided between the nozzle spring chamber and the pressure chamber. This provides the advantage that the nozzle needle guide no longer has a sealing function. This reduces the quality requirements of the guide, which leads to savings in production. Because there is the same pressure on both sides of the guide, there is no longer any pilot leakage.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Düsenfederraum über eine Bohrung mit dem Druckraum in Verbindung steht. Dadurch kann der komplette Umfang der Düsennadel zu Führungszwecken benutzt werden.Another particular embodiment of the invention is characterized in that the nozzle spring chamber communicates via a bore with the pressure chamber. As a result, the complete circumference of the nozzle needle can be used for guidance purposes.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass an der Düsennadel zwischen dem Düsenfederraum und dem Druckraum mindestens eine ebene Fläche ausgebildet ist, an der vorbei Kraftstoff von dem Düsenfederraum in den Druckraum gelangen kann. Diese Ausführungsart bietet insbesondere in Bezug auf die Hochdruckfestigkeit Vorteile.A further particular embodiment of the invention is characterized in that at least one flat surface is formed on the nozzle needle between the nozzle spring chamber and the pressure chamber, past which fuel can pass from the nozzle spring chamber into the pressure chamber. This embodiment offers particular advantages in terms of high pressure resistance.

Weitere besondere Ausführungsarten der Erfindung sind dadurch gekennzeichnet, dass die Zulaufdrossel in die Düsennadel, die Hülse oder das Injektorgehäuse integriert ist. Die Zulaufdrossel dient dazu, Druckstöße im Betrieb zu verhindern.Further special embodiments of the invention are characterized in that the inlet throttle is integrated into the nozzle needle, the sleeve or the injector housing. The inlet throttle is used to pressure surges during operation prevent.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Hülse an ihrem brennraumfernen Ende einen Bund aufweist. Der Bund bildet ein erstes Widerlager für die Düsenfeder.Another particular embodiment of the invention is characterized in that the sleeve has a collar at its end remote from the combustion chamber. The collar forms a first abutment for the nozzle spring.

Eine weitere besondere Ausführungsart nicht nach der vorliegenden Erfindung ist dadurch gekennzeichnet, dass in der Düsennadel eine Umfangsnut ausgespart ist, in der sich ein Haltering abstützt, der einen Anschlag für einen Federteller bildet. Bei dieser Ausführungsart können der Außendurchmesser der Düsennadel im Steuerraum und der Führungsdurchmesser der Düsennadel zwischen dem Düsenfederraum und dem Druckraum gleich groß sein. Das ist bei der Fertigung, z.B. durch Läppen, von Vorteil.Another particular embodiment not according to the present invention is characterized in that in the nozzle needle a circumferential groove is recessed, in which a retaining ring is supported, which forms a stop for a spring plate. In this embodiment, the outer diameter of the nozzle needle in the control chamber and the guide diameter of the nozzle needle between the nozzle spring chamber and the pressure chamber can be the same size. This is in the manufacturing, e.g. by lapping, an advantage.

Eine weitere besondere Ausführungsart nicht nach der vorliegenden Erfindung ist dadurch gekennzeichnet, dass der Haltering zweiteilig ist und in zusammengebautem Zustand durch den Federteller fixiert wird. Dadurch wird in einfacher Art und Weise ein Lösen des Federtellers im Betrieb verhindert.Another particular embodiment not according to the present invention is characterized in that the retaining ring is in two parts and is fixed in the assembled state by the spring plate. As a result, a release of the spring plate is prevented during operation in a simple manner.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Düsennadelhub durch den Abstand zwischen der Hülse und dem Federteller definiert ist. Dieser rein mechanische Düsennadelhubendanschlag liefert den Vorteil, dass der Düsennadelhub exakt reproduzierbar ist. Dadurch kann der Einspritzverlauf zuverlässig geformt werden. Ein sogenanntes hydraulisches Kleben wird vermieden.Another particular embodiment of the invention is characterized in that the Düsennadelhub is defined by the distance between the sleeve and the spring plate. This purely mechanical Düsennadelhubendanschlag provides the advantage that the Düsennadelhub is exactly reproducible. As a result, the course of injection can be reliably shaped. So-called hydraulic bonding is avoided.

Eine weitere besondere Ausführungsart nicht nach der vorliegenden Erfindung ist dadurch gekennzeichnet, dass der Düsennadelhub durch den Abstand zwischen der brennraumfernen Stirnfläche der Düsennadel und dem Injektorgehäuse definiert ist. Diese Ausführungsart hat den Vorteil, dass sie fertigungstechnisch besonders einfach zu realisieren ist.Another particular embodiment not according to the present invention is characterized in that the Düsennadelhub is defined by the distance between the combustion chamber remote end face of the nozzle needle and the injector. This embodiment has the advantage that it is particularly easy to implement in terms of manufacturing technology.

Eine weitere besondere Ausführungsart nicht nach der vorliegenden Erfindung ist dadurch gekennzeichnet, dass in der brennraumfernen Stirnfläche der Düsennadel und/oder in der gegenüberliegenden Fläche des Injektorgehäuses Ausnehmungen vorgesehen sind, deren Abmessungen an das Volumen des Steuerraums angepasst sind. Um im Betrieb des Injektors ein möglichst lineares Mengenkennfeld zu erzielen, ist es sinnvoll, den Düsennadelhubanschlag nicht rein hydraulisch auszuführen. Bei einem rein hydraulischen Düsennadelhubanschlag kann es vorkommen, dass die Düsennadel in der geöffneten Stellung auf einem Druckpolster "schwebt". Das kann zu Schwingungen der Düsennadel führen. Die Schwingungen wiederum ergeben nichtlineare Mengenkennfelder. Da es sich hierbei um eine dynamische Bewegung handelt, ergibt sich eine größere Toleranzabhängigkeit. Die Schwingungen der Düsennadel können abhängen von der Zulauf- und der Ablaufdrossel, der Reibung der Düsennadelführung, dem Steuerraumvolumen usw.. Bei einem rein mechanischen Anschlag wird eine Schwingung der Düsennadel zwar vermieden, allerdings ist dafür eine etwas größere Steuermenge erforderlich. Das wirkt sich ungünstig auf den Wirkungsgrad des Injektors aus. Durch die Ausnehmungen, die z.B. die Form von Kreuzschlitzen haben können, wird ein " "halbhydraulischer" Anschlag geschaffen. Der beim Anschlag verbleibende Durchflussquerschnitt wird gerade so groß gewählt, dass eine Schwingung der Düsennadel zwar vermieden, die Steuermenge beim Endanschlag jedoch so weit wie möglich abgesenkt wird. Hierbei ist von Vorteil, dass der erfindungsgemäße Injektor keine Leckage hat, d.h. ohne Ansteuerung des Injektors wird keine Rücklaufmenge erzeugt.Another particular embodiment not according to the present invention is characterized in that in the combustion chamber remote end face of the nozzle needle and / or in the opposite surface of the injector housing recesses are provided whose dimensions are adapted to the volume of the control chamber. In order to achieve the most linear quantity characteristic diagram possible during operation of the injector, it makes sense not to design the nozzle needle stroke stop purely hydraulically. In a purely hydraulic Düsennadelhubanschlag it may happen that the nozzle needle in the open position on a pressure pad "floats". This can lead to vibrations of the nozzle needle. The oscillations in turn result in non-linear quantity maps. Since this is a dynamic movement, there is a greater tolerance dependency. The vibrations of the nozzle needle may depend on the inlet and the outlet throttle, the friction of the nozzle needle guide, the control chamber volume, etc. In a purely mechanical stop a vibration of the nozzle needle is indeed avoided, but it is a slightly larger tax amount required. This has an unfavorable effect on the efficiency of the injector. Through the recesses, which may have the shape of Phillips, for example, a "semi-hydraulic" stop is created.The flow cross-section remaining at the stop is just chosen so large that avoids oscillation of the nozzle needle, but the control amount at the end stop as far as possible In this case, it is advantageous that the injector according to the invention has no leakage, ie no return quantity is generated without activation of the injector.

Eine weitere besondere Ausführungsart nicht nach der vorliegenden Erfindung ist dadurch gekennzeichnet, dass in der brennraumfernen Stirnfläche der Düsennadel mindestens eine axiale Bohrung vorgesehen ist, die mit mindestens einer radialen Bohrung in der Düsennadel in Verbindung steht. Diese Ausführungsart hat den Vorteil, dass sie unempfindlich gegen mechanisches Einlaufen ist, d.h. der Durchflussquerschnitt verändert sich über die Lebensdauer nicht.Another particular embodiment not according to the present invention is characterized in that in the combustion chamber remote end face of the nozzle needle at least one axial bore is provided which is in communication with at least one radial bore in the nozzle needle. This embodiment has the advantage that it is insensitive to mechanical shrinkage, i. the flow cross section does not change over the service life.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Abbildung 7 ein Ausführungsbeispiel der Erfindung im Einzelnen beschrieben sind. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein.Further advantages, features and details of the invention will become apparent from the following description, with reference to the Figure 7 an embodiment of the invention are described in detail. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination.

Zeichnungdrawing

In der Zeichnung zeigen:

  • Figur 1 ein erstes nicht erfindungsgemässes Ausführungsbeispiel im Längsschnitt durch den Injektor mit einer Bohrung zwischen dem Düsenfederraum und dem Druckraum;
  • Figur 2 ein zweites nicht erfindungsgemässes Ausführungsbeispiel im Längsschnitt durch den Injektor mit einer Abflachung an der Düsennadel zwischen dem Düsenfederraum und dem Druckraum;
  • Figur 3 ein weiteres nicht erfindungsgemässes Ausführungsbeispiel im Längsschnitt durch den Injektor, wobei die Zulaufdrossel in die Düsennadel oder in das Injektorgehäuse integriert ist;
  • Figur 4 ein weiteres nicht erfindungsgemässes Ausführungsbeispiel im Längsschnitt durch den Injektor, wobei der Führungsdurchmesser gleich dem Steuerdurchmesser ist;
  • Figur 5 eine Variante des in Fig. 4 dargestellten Ausführungsbeispiels mit einem zweiteiligen Haltering;
  • Figur 6 die Ansicht eines Schnitts entlang der Linie VI-VI in Fig. 5;
  • Figur 7 ein weiteres erfindungsgemässes Ausführungsbeispiel im Längsschnitt durch den Injektor mit Distanzelementen zur Einstellung des Düsennadelhubs und der Düsenfedervorspannkraft;
  • Figur 8 ein weiteres Ausführungsbeispiel im Längsschnitt durch den Injektor mit Kreuznuten in der brennraumfernen Stirnfläche der Düsennadel;
  • Figur 9 die brennraumferne Stirnfläche der Düsennadel aus Fig. 8 in der Draufsicht;
  • Fig. 10 ein weiteres Ausführungsbeispiel im Längsschnitt durch den Injektor mit Bohrungen in der brennraumfernen Stirnfläche; und
  • Fig. 11 ein weiteres Ausführungsbeispiel im Längsschnitt durch den Injektor mit einer Nut in dem Injektorgehäuse.
In the drawing show:
  • FIG. 1 a first embodiment not according to the invention in longitudinal section through the injector with a bore between the nozzle spring chamber and the pressure chamber;
  • FIG. 2 a second non-inventive embodiment in longitudinal section through the injector with a flattening on the nozzle needle between the nozzle spring chamber and the pressure chamber;
  • FIG. 3 a further non-inventive embodiment in longitudinal section through the injector, wherein the inlet throttle is integrated into the nozzle needle or in the injector;
  • FIG. 4 a further non-inventive embodiment in longitudinal section through the injector, wherein the guide diameter is equal to the control diameter;
  • FIG. 5 a variant of in Fig. 4 illustrated embodiment with a two-part retaining ring;
  • FIG. 6 the view of a section along the line VI-VI in Fig. 5 ;
  • FIG. 7 a further embodiment according to the invention in longitudinal section through the injector with spacer elements for adjusting the nozzle needle stroke and the Düsenfedervorspannkraft;
  • FIG. 8 a further embodiment in longitudinal section through the injector with cross grooves in the combustion chamber remote end face of the nozzle needle;
  • FIG. 9 the combustion chamber remote end face of the nozzle needle Fig. 8 in the plan view;
  • Fig. 10 a further embodiment in longitudinal section through the injector with holes in the combustion chamber remote end face; and
  • Fig. 11 a further embodiment in longitudinal section through the injector with a groove in the injector.

Beschreibungdescription

Das in Fig. 1 im Längsschnitt dargestellte erste Ausführungsbeispiel des nicht erfindungsgemäßen Injektors weist ein insgesamt mit 1 bezeichnetes Injektorgehäuse auf. Das Injektorgehäuse 1 umfasst einen Düsenkörper 2, der mit seinem unteren freien Ende in den Brennraum der zu versorgenden Brennkraftmaschine ragt. Mit seiner oberen, brennraumfernen Stirnfläche ist der Düsenkörper 2 mittels einer Spannmutter 5 axial gegen einen Ventilkörper 3 und einen Injektorkörper 4 verspannt.This in Fig. 1 in longitudinal section shown first embodiment of the injector not according to the invention has a generally designated 1 injector. The injector housing 1 comprises a nozzle body 2, which projects with its lower free end into the combustion chamber of the internal combustion engine to be supplied. With its upper, combustion chamber remote end face of the nozzle body 2 is clamped by means of a clamping nut 5 axially against a valve body 3 and an injector 4.

In dem Düsenkörper 2 ist eine axiale Führungsbohrung 6 ausgespart. In der Führungsbohrung 6 ist eine Düsennadel 8 axial verschiebbar geführt. An der Spitze 9 der Düsennadel 8 ist eine Dichtfläche ausgebildet, die mit einem Dichtsitz zusammenwirkt, der an dem Düsenkörper 2 ausgebildet ist. Wenn sich die Spitze 9 der Düsennadel 8 mit ihrer Dichtfläche in Anlage an dem Dichtsitz befindet, sind zwei Spritzlöcher 10 und 11 in dem Düsenkörper 2 verschlossen. Wenn die Düsennadelspitze 9 von ihrem Sitz abhebt, wird mit Hochdruck beaufschlagter Kraftstoff durch die Spritzlöcher 10 und 11 in den Brennraum der Brennkraftmaschine eingespritzt.In the nozzle body 2, an axial guide bore 6 is recessed. In the guide bore 6, a nozzle needle 8 is guided axially displaceable. At the tip 9 of the nozzle needle 8, a sealing surface is formed, which cooperates with a sealing seat which is formed on the nozzle body 2. When the tip 9 of the nozzle needle 8 is in contact with the sealing seat with its sealing surface, two spray holes 10 and 11 in the nozzle body 2 are closed. When the nozzle needle tip 9 lifts off its seat, high pressure fuel is injected through the injection holes 10 and 11 into the combustion chamber of the engine.

Ausgehend von der Spitze 9 weist die Düsennadel 8 drei Bereiche mit unterschiedlichen Durchmessern d1, d2 und d3 auf. Der Durchmesser d2 ist am größten und dient zur Führung der Düsennadel 8 in dem Düsenkörper 2. Der Durchmesser d1 ist am kleinsten. In dem Abschnitt mit demStarting from the tip 9, the nozzle needle 8 has three regions with different diameters d1, d2 and d3. The diameter d2 is the largest and serves to guide the nozzle needle 8 in the nozzle body 2. The diameter d1 is the smallest. In the section with the

Durchmesser d1 ist ein Bund 16 mit einer Abflachung 17 an seiner äußeren Umfangsfläche ausgebildet. Der Bund 16 bildet eine zweite Führung für die Düsennadel 1. Durch die Abflachung 17 in dem Bund 16 wird eine Strömungsverbindung in Längsrichtung der Düsennadel 1 von der einen Seite des Bundes 16 zur anderen Seite ermöglicht. Der Durchmesser d3 ist größer als der Durchmesser dl, aber kleiner als der Durchmesser d2. Der Durchmesser d3 wird auch als Steuerdurchmesser bezeichnet.Diameter d1 is a collar 16 with a flat 17 formed on its outer peripheral surface. The collar 16 forms a second guide for the nozzle needle 1. The flattening 17 in the collar 16 is a flow connection allows in the longitudinal direction of the nozzle needle 1 from one side of the collar 16 to the other side. The diameter d3 is larger than the diameter dl but smaller than the diameter d2. The diameter d3 is also referred to as the control diameter.

Die Düsennadel 8 ist mit Hilfe einer Düsenfeder 19 gegen den Düsennadelsitz im Bereich der Spritzlöcher 10 und 11 vorgespannt. Die Düsenfeder 19 ist in einem Düsenfederraum 20 angeordnet, in den ein Kraftstoffzulauf 21 mündet. Durch einen Pfeil 22 ist angedeutet, dass der Kraftstoffzulauf 21 aus einem (nicht dargestellten) Rail mit Kraftstoff versorgt wird, der mit Hochdruck beaufschlagt ist. Über eine Bohrung 23 gelangt der mit Hochdruck beaufschlagte Kraftstoff aus dem Düsenfederraum 20 in einen Druckraum 24. Der Druckraum 24 steht über einen Ringraum 25 mit den Spritzlöchern 10 und 11 in Verbindung, wenn die Düsennadel 1 entgegen der Vorspannkraft der Düsenfeder 19 von ihrem Sitz abgehoben ist.The nozzle needle 8 is biased by means of a nozzle spring 19 against the nozzle needle seat in the region of the injection holes 10 and 11. The nozzle spring 19 is arranged in a nozzle spring chamber 20, in which a fuel inlet 21 opens. By an arrow 22 is indicated that the fuel inlet 21 is supplied from a (not shown) rail with fuel, which is acted upon by high pressure. Via a bore 23, the high-pressure fuel from the nozzle spring chamber 20 passes into a pressure chamber 24. The pressure chamber 24 is connected via an annular space 25 with the spray holes 10 and 11 in connection, when the nozzle needle 1 against the biasing force of the nozzle spring 19 lifted from its seat is.

Infolge des Größenunterschiedes zwischen dem Durchmesser d2 und dem Durchmesser d3 ergibt sich an der Düsennadel 8 eine Stufe, die einen Anschlag für einen Federteller 26 bildet. Über den Federteller 26 wird die Vorspannkraft der Düsenfeder 19 auf die Düsennadel 8 übertragen. Das andere Ende der Düsenfeder 19 stützt sich an einem Bund 27 ab, der an einer Hülse 28 ausgebildet ist. Der Innendurchmesser der Hülse 28 ist geringfügig größer als der Steuerdurchmesser d3 der Düsennadel B. Die Abmessungen der Durchmesser sind so gewählt, dass die Hülse 28 relativ zu der Düsennadel 8 unter Dichtwirkung verschiebbar ist. Infolge der Vorspannkraft der Düsenfeder 19 wird die Hülse 28 mit einer Beißkante 29 gegen den Ventilkörper 3 gedrückt. Dadurch wird ein im Inneren der Hülse 28 vorgesehener Steuerraum 30, der durch die brennraumferne Stirnfläche der Düsennadel 8 begrenzt ist, gegenüber dem Düsenfederraum 20 abgedichtet.As a result of the difference in size between the diameter d2 and the diameter d3, a step results on the nozzle needle 8, which forms a stop for a spring plate 26. About the spring plate 26, the biasing force of the nozzle spring 19 is transmitted to the nozzle needle 8. The other end of the nozzle spring 19 is supported on a collar 27, which is formed on a sleeve 28. The inner diameter of the sleeve 28 is slightly larger than the control diameter d3 of the nozzle needle B. The dimensions of the diameters are selected so that the sleeve 28 is displaceable relative to the nozzle needle 8 under sealing action. As a result of the biasing force of the nozzle spring 19, the sleeve 28 is pressed with a biting edge 29 against the valve body 3. As a result, a control chamber 30 provided in the interior of the sleeve 28, which is delimited by the end face of the nozzle needle 8 remote from the combustion chamber, is sealed off from the nozzle spring chamber 20.

Der Steuerraum 30 ist über eine Zulaufdrossel 31 mit dem Düsenfederraum 20 verbunden. Außerdem steht der Steuerraum 30 über eine Ablaufdrossel 32 mit einem (nicht dargestellten) Entlastungsraum in Verbindung. Die Verbindung des Steuerraums 30 mit dem Entlastungsraum hängt von der Stellung eines Steuerventilgliedes 33 ab.The control chamber 30 is connected via an inlet throttle 31 with the nozzle spring chamber 20. In addition, the control chamber 30 is connected via an outlet throttle 32 with a (not shown) discharge space in connection. The connection of the control chamber 30 with the discharge chamber depends on the position of a control valve member 33.

Der in Fig. 1 dargestellte Injektor funktioniert wie folgt:The in Fig. 1 illustrated injector works as follows:

Über den Kraftstoffzulauf 21 gelangt mit Hochdruck beaufschlagter Kraftstoff in den Düsenfederraum 20. Von dort gelangt der mit Hochdruck beaufschlagte Kraftstoff einerseits über die Zulaufdrossel 31 in den Steuerraum 30 und andererseits über die Bohrung 23 in den Druckraum 24. Die Durchmesserverhältnisse sind in bekannter Weise so gewählt, dass sich die Düsennadel 8 infolge des Hochdruckes in dem Steuerraum 30 mit ihrer Spitze 9 in Anlage an dem Düsennadelsitz befindet. Wenn das Steuerventilglied 33 öffnet, wird der Steuerraum 30 druckentlastet, und die Düsennadelspitze 9 hebt von ihrem Sitz ab. Dann wird so lange mit Hochdruck beaufschlagter Kraftstoff durch die Spritzlöcher 10 und 11 in den Brennraum der Brennkraftmaschine eingespritzt, bis das Steuerventilglied 33 wieder schließt. Das hat dann zur Folge, dass der Druck in dem Steuerraum 30 wieder ansteigt und die Düsennadel 8 mit ihrer Spitze 9 wieder gegen den zugehörigen Düsennadelsitz gedrückt wird.From the fuel inlet 21 passes under high pressure acted upon fuel in the nozzle spring chamber 20. From there passes the high-pressure fuel on the one hand via the inlet throttle 31 into the control chamber 30 and the other via the bore 23 into the pressure chamber 24. The diameter ratios are chosen in a known manner in that, as a result of the high pressure in the control chamber 30, the nozzle needle 8 is in contact with the nozzle needle seat with its tip 9. When the control valve member 33 opens, the control chamber 30 is depressurized and the nozzle needle tip 9 lifts off its seat. Then, as long as high-pressure fuel is injected through the injection holes 10 and 11 in the combustion chamber of the internal combustion engine until the control valve member 33 closes again. This has the consequence that the pressure in the control chamber 30 rises again and the nozzle needle 8 is pressed with its tip 9 again against the associated nozzle needle seat.

Das in Fig. 2 dargestellte zweite nicht erfindungsgemässe Ausführungsbeispiel entspricht weitestgehend dem in Fig. 1 dargestellten ersten Ausführungsbeispiel. Der Einfachheit halber werden zur Bezeichnung gleicher Teile dieselben Bezugszeichen verwendet. Außerdem wird, um Wiederholungen zu vermeiden, auf die vorstehende Beschreibung des ersten Ausführungsbeispiels verwiesen. Im Folgenden wird nur auf die Unterschiede zwischen den beiden Ausführungsbeispielen eingegangen. Bei der ausführlichen Beschreibung der in den Fig. 3 - 11 dargestellten Ausführungsbeispiele wird analog vorgegangen.This in Fig. 2 illustrated second embodiment not according to the invention corresponds largely to the in Fig. 1 illustrated first embodiment. For simplicity, the same reference numerals will be used to designate like parts. In addition, in order to avoid repetition, reference is made to the above description of the first embodiment. The following will only focus on the differences between the two embodiments received. In the detailed description of the in the Fig. 3 - 11 illustrated embodiments will proceed analogously.

Bei dem in Fig. 2 dargestellten zweiten Ausführungsbeispiel fehlt eine Verbindungsbohrung zwischen dem Düsenfederraum 20 und dem Druckraum 24. Stattdessen ist in dem Abschnitt der Düsennadel 8 mit dem Durchmesser d2 eine Abflachung 36 ausgebildet. Die Abflachung 36 sorgt für eine Verbindung zwischen dem Düsenfederraum 20 und dem Druckraum 24. Ansonsten gibt es keine Unterschiede zwischen den beiden Ausführungsbeispielen.At the in Fig. 2 illustrated second embodiment is missing a connecting hole between the nozzle spring chamber 20 and the pressure chamber 24. Instead, a flattening 36 is formed in the portion of the nozzle needle 8 with the diameter d2. The flattening 36 provides a connection between the nozzle spring chamber 20 and the pressure chamber 24. Otherwise, there are no differences between the two embodiments.

Das in Fig. 3 dargestellte dritte nicht erfindungsgemässe Ausführungsbeispiel unterscheidet sich von dem zweiten Ausführungsbeispiel dadurch, dass die Zulaufdrossel nicht in der Hülse 28 angeordnet ist. Bei 38 ist in Fig. 3 angedeutet, dass die Zulaufdrossel in Form von Bohrungen unterschiedlicher Ausrichtungen und unterschiedlicher Abmessungen in die Düsennadel 8 integriert sein kann. Bei 39 ist angedeutet, dass die Zulaufdrossel auch in dem Ventilkörper 3 integriert sein kann.This in Fig. 3 illustrated third non-inventive embodiment differs from the second embodiment in that the inlet throttle is not disposed in the sleeve 28. At 38 is in Fig. 3 indicated that the inlet throttle in the form of holes of different orientations and different dimensions can be integrated into the nozzle needle 8. Indicated at 39 is that the inlet throttle can also be integrated in the valve body 3.

Bei dem in Fig. 4 dargestellten vierten nicht erfindungsgemässen Ausführungsbeispiel stützt sich der Federteller 26 nicht direkt auf der Düsennadel 8 ab, sondern nur indirekt über einen federnden Haltering 42 mit einem rechteckförmigen Querschnitt. Um ein Einsetzen des Halterings 42 in eine in der Düsennadel 8 ausgebildete Umfangsnut zu ermöglichen, ist der Haltering 42 geschlitzt ausgebildet.At the in Fig. 4 illustrated fourth non-inventive embodiment, the spring plate 26 is not supported directly on the nozzle needle 8, but only indirectly via a resilient retaining ring 42 having a rectangular cross-section. In order to allow insertion of the retaining ring 42 in a formed in the nozzle needle 8 circumferential groove, the retaining ring 42 is formed slotted.

In den Fig. 5 und 6 ist dargestellt, dass statt eines einteiligen, aufklipsbaren Halterings auch ein zweiteiliger Haltering 46 verwendet werden kann. Der Haltering 46 besteht aus zwei Ringhälften, die in die zugehörige Nut in der Düsennadel 8 gelegt und mit Hilfe des Federtellers 26 fixiert werden.In the FIGS. 5 and 6 It is shown that instead of a one-piece, clip-on retaining ring, a two-part retaining ring 46 can be used. The retaining ring 46 consists of two ring halves, which are placed in the associated groove in the nozzle needle 8 and fixed by means of the spring plate 26.

Bei dem in Fig. 7 dargestellten erfindungsgemässen Ausführungsbeispiel wird der Hub nicht, wie bei dem in Fig. 1 dargestellten Ausführungsbeispiel, durch den Abstand H1 der brennraumfernen Stirnfläche der Düsennadel 8 und der gegenüberliegenden Fläche des Ventilkörpers 3 begrenzt, sondern durch den Abstand H2 zwischen der Hülse 28 und dem Federteller 26. In Fig. 7 ist außerdem zu sehen, dass der Hub H2 durch eine Distanzscheibe 51 eingestellt werden kann. Die Distanzscheibe 51 ist zu diesem Zweck zwischen dem Absatz, der sich durch die Durchmesserdifferenz zwischen d2 und d3 ergibt, und dem Federteller 26 angeordnet. Darüber hinaus kann die Federvorspannkraft der Düsenfeder 19 mit Hilfe einer Distanzscheibe 50 eingestellt werden. Zu diesem Zweck ist die Distanzscheibe 50 zwischen der Düsenfeder 19 und dem Bund 27 der Hülse 28 angeordnet. Durch diese Einstellmöglichkeiten kann ein hydraulisches Kleben bzw. eine vollständige Druckbeaufschlagung der Düsennadel 8 in dem Steuerraum 30 unterbunden werden. Daraus resultiert ein besseres Schließverhalten des Injektors.At the in Fig. 7 illustrated inventive embodiment, the stroke is not, as in the in Fig. 1 illustrated embodiment, limited by the distance H1 of the combustion chamber remote end face of the nozzle needle 8 and the opposite surface of the valve body 3, but by the distance H2 between the sleeve 28 and the spring plate 26. In Fig. 7 is also seen that the stroke H2 can be adjusted by a spacer 51. The spacer 51 is arranged for this purpose between the shoulder, which results from the difference in diameter between d2 and d3, and the spring plate 26. In addition, the spring biasing force of the nozzle spring 19 can be adjusted by means of a spacer 50. For this purpose, the spacer 50 between the nozzle spring 19 and the collar 27 of the sleeve 28 is arranged. These adjustment options can prevent hydraulic sticking or complete pressurization of the nozzle needle 8 in the control chamber 30. This results in a better closing behavior of the injector.

Bei den in den Fig. 8 - 11 dargestellten nicht erfindungsgemässen Ausführungsbeispielen ergibt sich der Düsennadelhub, wie bei dem in Fig. 1 dargestellten Ausführungsbeispiel, aus dem Abstand H1 zwischen der Düsennadel 8 und dem Ventilkörper 3. Um zu verhindern, dass die Düsennadel 8 in der geöffneten Stellung auf einem Druckpolster schwebt, werden die folgenden Lösungsvorschläge bereitgestellt:In the in the Fig. 8 - 11 not illustrated embodiments according to the invention results in the Düsennadelhub, as in the in Fig. 1 illustrated embodiment, from the distance H1 between the nozzle needle 8 and the valve body 3. In order to prevent the nozzle needle 8 floats in the open position on a pressure pad, the following solution proposals are provided:

Bei dem in den Fig. 8 und 9 dargestellten Ausführungsbeispiel sind in der Stirnfläche 54 der Düsennadel 8 zwei Nuten 55 und 56 kreuzweise angeordnet. Dadurch wird ein rein mechanischer Anschlag der Nadeldüse realisiert. Wenn die Abmessungen der Nuten 54 und 55 an den Injektor angepasst werden, kann daraus ein "halbhydraulischer Anschlag" werden. Der beim Anschlag verbleibende Durchbruchsquerschnitt wird gerade so groß gewählt, dass eine Schwingung der Düsennadel 8 zwar vermieden, die Steuermenge beim Endanschlag jedoch so weit wie möglich abgesenkt wird.In the in the 8 and 9 illustrated embodiment, two grooves 55 and 56 are arranged crosswise in the end face 54 of the nozzle needle 8. As a result, a purely mechanical stop of the needle nozzle is realized. If the dimensions of the grooves 54 and 55 are adapted to the injector, this can become a "semi-hydraulic stop". The one at the stop remaining breakthrough cross-section is just chosen so large that a vibration of the nozzle needle 8 Although avoided, the control amount at the end stop but is lowered as much as possible.

Bei dem in Fig. 10 dargestellten Ausführungsbeispiel ist in der Stirnfläche 54 der Düsennadel 8 eine Drosselbohrung 58 parallel zur Längsachse der Düsennadel 8 angeordnet. Die Drosselbohrung 58 mündet in eine Bohrung 59, die sich quer zur Längsachse der Düsennadel 8 erstreckt. Bei der Bohrung 59 handelt es sich um eine Sackbohrung, die zu dem brennraumfernen, kegelstumpfartigen Ende der Düsennadel 8 hin geöffnet ist. Dieses Ausführungsbeispiel hat den Vorteil, dass es unempfindlich gegen mechanisches Einlaufen ist.At the in Fig. 10 illustrated embodiment, a throttle bore 58 is arranged parallel to the longitudinal axis of the nozzle needle 8 in the end face 54 of the nozzle needle 8. The throttle bore 58 opens into a bore 59 which extends transversely to the longitudinal axis of the nozzle needle 8. When the bore 59 is a blind bore, which is open to the combustion chamber distant, frustoconical end of the nozzle needle 8 out. This embodiment has the advantage that it is insensitive to mechanical shrinkage.

Bei dem in Fig. 11 dargestellten Ausführungsbeispiel ist eine Nut 61 anstatt in der brennraumfernen Stirnfläche 54 der Düsennadel 8 in der gegenüberliegenden Fläche 62 des Ventilkörpers 3 ausgespart. Die Nut 61 hat die gleiche Funktion wie die Nuten 54 und 55 bei dem in den Fig. 8 und 9 dargestellten Ausführungsbeispiel.At the in Fig. 11 illustrated embodiment, a groove 61 is recessed instead of in the combustion chamber remote end face 54 of the nozzle needle 8 in the opposite surface 62 of the valve body 3. The groove 61 has the same function as the grooves 54 and 55 in which in the 8 and 9 illustrated embodiment.

Claims (9)

  1. Common-rail injector for the injection of fuel in a common-rail injection system of an internal combustion engine, the said common-rail injector having an injector housing (1) with a fuel inflow (21) which is connected to a central high-pressure fuel accumulator outside the injector housing (1) and to a pressure space (24) inside the injector housing (1), out of which pressure space fuel acted upon with high pressure is injected as a function of the position of a control valve (33) which ensures that a nozzle needle (8), movable to and fro in a longitudinal bore (6) of the injector axially counter to the prestressing force of a nozzle spring (19) received in a nozzle-spring space (20), lifts off from a seat when the pressure in the pressure space (24) is higher than the pressure in a control space (30) which is connected to the fuel inflow via an inflow throttle (31, 38, 39), the control space (30) being delimited by a sleeve (28) which is displaceable under sealing action at that end of the nozzle needle (8) remote from the combustion space and which is held in bearing contact against the injector housing (1) with the aid of a spring (19), the sleeve (28) being held in bearing contact against the injector housing (1) by the nozzle spring (19), the sleeve (28) being arranged in the nozzle-spring space (20), and the fuel inflow (21) into the pressure space (24) taking place through the nozzle-spring space (20), characterized in that on the nozzle needle (8) a step is formed which forms a stop for a spring plate (26), and in that the nozzle-needle stroke (H2) and the nozzle-spring prestress can be set with the aid of spacer elements (50, 51) which are arranged between the spring plate (26) and the stop for the spring plate and between the nozzle spring (19) and the abutments for the nozzle spring (19) respectively.
  2. Common-rail injector according to Claim 1, characterized in that a biting edge (29) is formed on that face of the sleeve (28) which is in bearing contact against the injector housing (1).
  3. Common-rail injector according to one of the preceding claims, characterized in that the inside diameter (d3) of the sleeve (28) is smaller than the guide diameter (d2) of the nozzle needle (8).
  4. Common-rail injector according to one of the preceding claims, characterized in that the nozzle needle (8) is guided between the nozzle-spring space (20) and the pressure space (24).
  5. Common-rail injector according to Claim 4, characterized in that the nozzle-spring space (20) is connected to the pressure space (24) via a bore (23) in the injector housing (1).
  6. Common-rail injector according to Claim 4, characterized in that at least one plane face (36) is formed on the nozzle needle (8) between the nozzle-spring space (20) and the pressure space (24), past which plane face fuel can pass from the nozzle-spring space (20) into the pressure space (24).
  7. Common-rail injector according to one of the preceding claims, characterized in that the inflow throttle (31, 38, 39) is integrated into the sleeve (28), the nozzle needle (8) or the injector housing (1).
  8. Common-rail injector according to one of the preceding claims, characterized in that the sleeve (28) has a collar (27) at its end remote from the combustion space.
  9. Common-rail injector according to one of Claims 1 to 8, characterized in that the nozzle-needle stroke (H2) is defined by the distance between the sleeve (28) and the spring plate (26).
EP06123003A 1999-08-04 2000-08-02 Common rail injector Expired - Lifetime EP1772618B1 (en)

Applications Claiming Priority (2)

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DE19936668A DE19936668A1 (en) 1999-08-04 1999-08-04 Common rail injector
EP00958210A EP1117920B1 (en) 1999-08-04 2000-08-02 Common rail injector

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EP1772618A1 EP1772618A1 (en) 2007-04-11
EP1772618B1 true EP1772618B1 (en) 2008-11-05

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US (1) US6705551B1 (en)
EP (2) EP1117920B1 (en)
JP (1) JP4746230B2 (en)
KR (1) KR20010075570A (en)
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CZ (1) CZ20011135A3 (en)
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JP4746230B2 (en) 2011-08-10
DE50014113D1 (en) 2007-04-12
DE19936668A1 (en) 2001-02-22
KR20010075570A (en) 2001-08-09
ATE413526T1 (en) 2008-11-15
EP1117920A1 (en) 2001-07-25
US6705551B1 (en) 2004-03-16
WO2001011222A1 (en) 2001-02-15
ATE355455T1 (en) 2006-03-15
DE50015444D1 (en) 2008-12-18
EP1117920B1 (en) 2007-02-28
EP1772618A1 (en) 2007-04-11
CZ20011135A3 (en) 2002-01-16
JP2003506622A (en) 2003-02-18

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