EP1392962A1 - Fuel injection device with pressure translation device and pressure translation device - Google Patents

Fuel injection device with pressure translation device and pressure translation device

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Publication number
EP1392962A1
EP1392962A1 EP02742691A EP02742691A EP1392962A1 EP 1392962 A1 EP1392962 A1 EP 1392962A1 EP 02742691 A EP02742691 A EP 02742691A EP 02742691 A EP02742691 A EP 02742691A EP 1392962 A1 EP1392962 A1 EP 1392962A1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
valve
space
injection device
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.)
Granted
Application number
EP02742691A
Other languages
German (de)
French (fr)
Other versions
EP1392962B1 (en
Inventor
Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1392962A1 publication Critical patent/EP1392962A1/en
Application granted granted Critical
Publication of EP1392962B1 publication Critical patent/EP1392962B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive

Definitions

  • the invention is based on one
  • Fuel injection device or a pressure booster device according to the preamble of the independent claims. From DE 199 10 970, fuel injection devices or pressure booster devices are already known, in which a pressure booster piston enables the fuel injection pressure to be increased beyond the value provided by a common rail system by means of filling or emptying a rear space.
  • pressure booster devices have the advantage that, by means of a valve which, depending on the fuel pressure prevailing in the rear area, connects the side of the pressure booster device connected to the high-pressure fuel source directly to the side connected to the fuel injector, it is possible to both fill the rear area with Fuel as well as locking the side of the pressure translation device connected to the injector from the high-pressure fuel source with this one valve without additional components.
  • Another advantage is that the high-pressure chamber of the pressure booster device connected to the fuel injector is not filled via a spring-loaded separate check valve, for example, but via a path that is constantly open in the reset phase. This ensures an improved, in particular faster, resetting of the piston of the pressure transmission device.
  • an additional control of the combination valve by the pressure build-up in the high-pressure space is particularly advantageous, so that, in addition to the pressure drop in the rear space, the pressure build-up in the high-pressure space simultaneously drives the valve body and can thus switch the combination valve particularly quickly.
  • FIG. 1 shows a fuel injection device
  • FIG. 2 shows a pressure booster device in the active state
  • FIG. 3 shows the pressure booster device of a further fuel injection device.
  • FIG. 1 shows a fuel injection device in which an injector 10 is connected to a high-pressure fuel source 60 via a pressure booster device 30.
  • the high-pressure fuel source comprises several elements, not shown, such as a fuel tank, a pump and the high-pressure rail of a common rail system known per se, the pump providing a fuel pressure of up to 1600 bar in the high-pressure rail by injecting fuel from the tank transported the high pressure rail.
  • the injector 10 has a fuel injection valve with a valve member 12 which projects with its injection openings 8 into the combustion chamber 11 of a cylinder of an internal combustion engine.
  • the valve member is surrounded on a pressure shoulder 9 by a pressure chamber 13, which is connected via a high-pressure line 21 to the high-pressure chamber 40 of the pressure transmission device 30.
  • the schematically illustrated valve member protrudes at its end facing away from the combustion chamber into a working chamber 18 which is connected via a throttle 20 to the high-pressure line 21 and via a throttle 19 to a control valve 15 of the injector, the Throttle 20 has a smaller opening cross section than the throttle 19.
  • the control valve 15 is designed as a 2/2-way valve and is closed in the first position; in the second position, it connects the throttle 19 to a low-pressure line 17.
  • the valve member is resiliently mounted via a return spring 14, the return spring pressing the valve member against the injection openings 8.
  • the spring-containing space of the injector injector is connected to a further low-pressure line 16.
  • the pressure transmission device 30 has a spring-mounted piston 36 which separates the high-pressure space 40 connected to the high-pressure line 21 from a space 35 which is connected directly to the high-pressure fuel source 60.
  • the spring 39 used to support the piston is arranged in a rear space 38 of the pressure transmission device 30.
  • the piston 36 has an extension piece 37 which has a smaller diameter than the piston 36 at its end facing the space 35.
  • the rear space 38 can be connected to a low-pressure line 32 via a 2/2-way valve 31.
  • the low-pressure line 32 like the low-pressure lines 16 and 17, leads back to the fuel tank (not shown).
  • the space 35 of the pressure transmission device is connected to the rear space 38 via a throttle 47 integrated as a bore in the piston.
  • a combination valve 50 is integrated in a bore 58 of the piston 36.
  • the bore communicates with space 35.
  • a cylindrical valve body 51 is movably mounted in it.
  • a spring 54 is arranged between the piston 36 and the valve body 51, which in the relaxed state presses the valve body just so far in the direction of the space 35 that the valve space 53 on the one hand has an inlet conduit 52 and which leads to the space 35 as a bore in the piston on the other hand, is connected to a high-pressure chamber line 56 leading to the high-pressure chamber 40 and designed as a bore through the extension piece 37.
  • valve chamber 53 is also located Regardless of the position of the valve body 51 via a bore hole in the piston 36 and at the end of the bore 58 facing the end of the bore 58 into the bore outlet chamber 55 in connection with the rear chamber 38, since the valve body 51 on its side facing the spring 54 has through the spring center extension 57 which, as shown in Figure 2, limits the movement of the valve body as soon as it has closed the lines 52 and 56.
  • the mode of operation of the stroke-controlled injector 10 is known per se from German patent application DE 199 10 970.
  • a high fuel pressure is constantly present at the high-pressure line 21.
  • Fuel passes from the pressure chamber 13 through the injection openings 8 into the combustion chamber 11 as soon as the valve member at its end facing away from the injection openings is briefly relieved of fuel pressure by opening the 2/2-way valve 15 and thus the opening shoulder acting on the pressure shoulder 9 acting force is greater than the sum of spring force (14) and force due to the remaining in the working space 18
  • the pressure of the high-pressure fuel source passes via the inlet line 52 and the high-pressure space line 56 to the high-pressure space 40 and from there to the injector 10 an injection with the pressure of the high-pressure fuel source can take place at any time.
  • the control valve 15 of the injector only has to be actuated, as a result of which the injection valve opens. If an injection with increased pressure is now to take place, then the intensifier control valve 31 is opened so that the pressure in the rear space 38 can drop, as a result of which the combination valve 50 closes. In the closed state, the combi valve 50 closes, as shown in FIG. 2, the high pressure chamber line 56 and the inlet line 52.
  • the fuel to be compressed in the high pressure chamber 40 cannot flow back (check valve function of the combi valve) and the fuel from the chamber 35 only flows in a throttled manner via the throttle 47 into the rear space 38 (filling valve function of the combination valve).
  • the piston 36 is not pressure-balanced and there is a pressure increase in the high-pressure space 40 in accordance with the pressure-area ratio of the space 35 and the high-pressure space 40 Pressure equalization between rooms 35, 38 and 40.
  • the combination valve 50 opens when the pressure in the rear room 38 has reached the pressure in the room 35 minus an opening pressure difference.
  • the opening pressure difference of the combination valve is determined by the spring constant of the spring 54 and the hydraulic pressure surfaces of the valve body to the spaces 35 and 53. In the illustrated embodiment, the hydraulic pressure areas are the same size.
  • Pressure translation device take place. Because the injection can take place at two different pressure levels (rail pressure and translated pressure) and one It is possible to switch on the pressure booster at any time, the injection course can be shaped flexibly. Rectangular, ramp-shaped or "boat" injections with variable length of the boot phase are possible.
  • FIG. 3 shows a further embodiment of the fuel injection device according to the invention.
  • the pressure transmission device arranged between the high-pressure fuel source 60 and the high-pressure line 21 leading to the injector 10 has a piston 36 with an integrated alternative combination valve 70.
  • the valve body 78 of the combination valve 70 is movably mounted in a cylindrical cavity 88 of the piston 36.
  • An inlet line 72 designed as a bore in the piston 36 leads from the space 35 into an annular groove 90 of the cavity 88.
  • the rear space 38 is connected to the cavity 88 via the rear space line 74, regardless of the position of the valve body in the cavity, so that there is always a prevailing in the rear space Can attack fuel pressure on the valve body.
  • a spring 80 is stretched between the wall of the cavity 88 and a shoulder of the valve body 78 in such a way that when forces act predominantly on the valve body in the direction of the spring force, a> liquid exchange between the space 35 and the cavity 88 can take place via the annular groove 90.
  • an elevation 94 of the valve body arranged on the end of the valve body facing away from the spring 80 is pressed against the cavity boundary.
  • a high-pressure chamber line 76 designed as a bore in the piston connects the high-pressure chamber 40 to the part of the cavity 88 located between the pressure surface 92 delimited by the elevation 94 and the piston wall.
  • the combination valve 50 thus has both a pressure surface to the high pressure chamber 40, the pressure surface 92, and a pressure surface to the rear chamber 38, it is closed by a falling pressure in the rear chamber and by an increasing pressure in the high pressure chamber.
  • the opening spring force of the spring 80 defines the opening pressure difference between the rear space and the high pressure space up to which the combination valve is open.
  • the sealing function is for the high-pressure space line 40 through the flat sealing seat surfaces 82 and for the inlet line 72 through the

Landscapes

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

Abstract

Disclosed is a fuel injection device for internal combustion engines, comprising a fuel injector which can be fed by a high-pressure fuel source. A pressure translation device provided with a moveable piston is mounted between the fuel injector and the high-pressure fuel source. The moveable piston separates a chamber which is adjacent to the high-pressure fuel source from a high-pressure chamber connected to the injector. The fuel pressure in the high-pressure chamber can be varied by filling the back chamber of the pressure translation device with fuel or by removing fuel from the back chamber. A valve (50,70) is provided with a valve body (51; 78) which is moveably arranged according to the fuel pressure prevailing in the back chamber (38), whereby the high-pressure chamber (40) can be connected (56, 53, 52; 76, 86, 88, 72) to the chamber (35) via said valve (50; 70). A suitable pressure translation device (30) is also disclosed.

Description

Kraftstoffeinspritzeinrichtuncr mit Druckübersetzunqseinrichtuncr und DruckübersetzungseinrichtuncrFuel injector with pressure booster and pressure booster
Stand der TechnikState of the art
Die Erfindung geht aus von einerThe invention is based on one
Kraftstoffeinspritzeinrichtung beziehungsweise einer Druckübersetzungseinrichtung nach der Gattung der unabhängigen Ansprüche. Aus der DE 199 10 970 sind schon Kraftstoffeinspritzeinrichtungen beziehungsweise Druckübersetzungseinrichtungen bekannt, bei denen ein Druckverstärkerkolben mittels einer Befüllung beziehungsweise einer Entleerung eines Rückraums eine Erhöhung des Kraftstoffeinspritzdrucks über den von einem Common-Rail-System hinaus bereitgestellten Wert ermöglicht,Fuel injection device or a pressure booster device according to the preamble of the independent claims. From DE 199 10 970, fuel injection devices or pressure booster devices are already known, in which a pressure booster piston enables the fuel injection pressure to be increased beyond the value provided by a common rail system by means of filling or emptying a rear space.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzeinrichtung beziehungsweise die erfindungsgemäßeThe fuel injection device according to the invention or the one according to the invention
Druckübersetzungseinrichtung haben demgegenüber den Vorteil, dass mittels eines Ventils, das in Abhängigkeit des im Rückraum herrschenden Kraftstoffdrucks die mit der Kraftstoffhochdruckquelle verbundene Seite der Druckübersetzungseinrichtung direkt mit der mit dem Kraftstoffinjektor verbundenen Seite verbindet, es ermöglicht wird, sowohl eine Befüllung des Rückraums mit Kraftstoff als auch eine Abriegelung der mit dem Injektor verbundenen Seite der Druckübersetzungseinrichtung von der Kraftstoffhochdruckquelle mit diesem einen Ventil ohne zusätzliche Bauteile zu gewährleisten. Als weiterer Vorteil ist anzusehen, dass das Befüllen des mit dem Kraftstoffinjektor verbundenen Hochdruckraums der Druckübersetzungseinrichtung nicht über ein beispielsweise federbelastetes separates Rückschlagventil erfolgt, sondern über einen in der Rückstellphase ständig geöffneten Pfad. Dies gewährleistet ein verbessertes, insbesondere schnelleres Rückstellen des Kolbens der Druckübersetzungseinrichtung .In contrast, pressure booster devices have the advantage that, by means of a valve which, depending on the fuel pressure prevailing in the rear area, connects the side of the pressure booster device connected to the high-pressure fuel source directly to the side connected to the fuel injector, it is possible to both fill the rear area with Fuel as well as locking the side of the pressure translation device connected to the injector from the high-pressure fuel source with this one valve without additional components. Another advantage is that the high-pressure chamber of the pressure booster device connected to the fuel injector is not filled via a spring-loaded separate check valve, for example, but via a path that is constantly open in the reset phase. This ensures an improved, in particular faster, resetting of the piston of the pressure transmission device.
Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der in den unabhängigen Ansprüchen angegebenen Kraftstoffeinspritzeinrichtung beziehungsweise Druckübersetzungseinrichtung möglich.The measures listed in the dependent claims enable advantageous developments and improvements of the fuel injection device or pressure booster device specified in the independent claims.
Vorteilhaft ist ferner eine Integration einer Drossel in den Kolben der Druckübersetzungseinrichtung, so dass keine Leitung mehr am durchmessergrößeren Ende des Kolbens vorbeigeführt werden uss . Dies resultiert in einer noch kompakteren Bauform der Kraftstoffeinspritzeinrichtung beziehungsweise der Druckübersetzungseinrichtung.It is also advantageous to integrate a throttle in the piston of the pressure booster, so that no more lines are led past the larger-diameter end of the piston. This results in an even more compact design of the fuel injection device or the pressure booster device.
Besonders vorteilhaft ist darüber hinaus eine zusätzliche Steuerung des Kombiventils durch den Druckaufbau im Hochdruckraum, so dass neben dem Druckabfall im Rückraum gleichzeitig der Druckaufbau im Hochdruckraum den Ventilkörper antreibt und somit das Kombiventil besonders schnell schalten kann.In addition, an additional control of the combination valve by the pressure build-up in the high-pressure space is particularly advantageous, so that, in addition to the pressure drop in the rear space, the pressure build-up in the high-pressure space simultaneously drives the valve body and can thus switch the combination valve particularly quickly.
Weitere Vorteile ergeben sich durch die weiteren in den weiteren abhängigen Ansprüchen und in der Beschreibung genannten Merkmale. ZeichnungFurther advantages result from the further features mentioned in the further dependent claims and in the description. drawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert . Es zeigen Figur 1 eine Kraf stoffeinspritzeinrichtung, Figur 2 eine Druckübersetzungseinrichtung in aktivem Zustand und Figur 3 die Druckübersetzungseinrichtung einer weiteren Kraftstoffeinspritzeinrichtung.Embodiments of the invention are shown in the drawing and explained in more detail in the following description. FIG. 1 shows a fuel injection device, FIG. 2 shows a pressure booster device in the active state and FIG. 3 shows the pressure booster device of a further fuel injection device.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In Figur 1 ist eine Kraftstoffeinspritzeinrichtung dargestellt, bei der ein Injektor 10 über eine Druckübersetzungseinrichtung 30 mit einer Kraftstoffhochdruckquelle 60 verbunden ist. Die Kraftstoffhochdruckquelle umfasst mehrere nicht näher dargestellte Elemente wie einen Kraftstofftank, eine Pumpe und das Hochdruckrail eines an sich bekannten Common-Rail- Systems, wobei die Pumpe einen bis zu 1600 bar hohen Kraftstoff ruck in dem Hochdruckrail bereitstellt, indem sie Kraftstoff aus dem Tank in das Hochdruckrail befördert. Der Injektor 10 weist ein Kraftstoffeinspritzventil mit einem Ventilglied 12 auf, das mit seinen Einspritzö fnungen 8 in den Brennraum 11 eines Zylinders einer Brennkraftmaschine hineinragt. Das Ventilglied ist an einer Druckschulter 9 von einem Druckraum 13 umgeben, der über eine Hochdruckleitung 21 mit dem Hochdruckraum 40 der Druckübersetzungseinrichtung 30 verbunden ist. Das schematisch dargestellte Ventilglied ragt an seinem dem Brennraum abgewandten Ende in einen Arbeitsraum 18 hinein, der über eine Drossel 20 mit der Hochdruckleitung 21 und über eine Drossel 19 mit einem Steuerventil 15 des Injektors verbunden ist, wobei die Drossel 20 einen kleineren Öffnungsqerschnitt hat als die Drossel 19. Das Steuerventil 15 ist als 2/2-Wege-Ventil ausgeführt und in der ersten Stellung geschlossen; in der zweiten Stellung verbindet es die Drossel 19 mit einer Niederdruckleitung 17. Das Ventilglied ist über eine Rückstellfeder 14 federnd gelagert, wobei die Rückstellfeder das Ventilglied gegen die Einspritzöffnungen 8 drückt. Der die Feder enthaltene Raum des Einspritzventils des Injektors ist mit einer weiteren Niederdruckleitung 16 verbunden. Die Druckübersetzungseinrichtung 30 besitzt einen federnd gelagerten Kolben 36, der den mit der Hochdruckleitung 21 verbundenen Hochdruckraum 40 von einem Raum 35 trennt, der direkt an die Kraftstoffhochdruckquelle 60 angeschlossen ist. Die zur Lagerung des Kolbens verwendete Feder 39 ist in einem Rückraum 38 der Druckübersetzungseinrichtung 30 angeordnet. Der Kolben 36 weist ein Fortsetzungsstück 37 auf, das einen kleineren Durchmesser hat als der Kolben 36 an seinem dem Raum 35 zugewandten Ende. Der Rückraum 38 ist über ein 2/2-Wege-Ventil 31 mit einer Niederdruckleitung 32 verbindbar. Die Niederdruckleitung 32 führt ebenso wie die Niederdruckleitungen 16 und 17 zurück zum nicht näher dargestellten Kraftstofftank. Der Raum 35 der Druckübersetzungseinrichtung ist über eine als Bohrung im Kolben integrierte Drossel 47 mit dem Rückraum 38 verbunden. Neben der Drosselbohrung 47 ist ein Kombiventil 50 in einer Bohrung 58 des Kolben 36 integriert. Die Bohrung steht mit dem Raum 35 in Verbindung. In ihr ist ein zylindrischer Ventilkörper 51 beweglich gelagert. Zwischen dem Kolben 36 und dem Ventilkörper 51 ist eine Feder 54 angeordnet, die im entspannten Zustand den Ventilkörper gerade so weit in Richtung Raum 35 drückt, dass der Ventilraum 53 zum einen mit einer zum Raum 35 führenden, als Bohrung im Kolben ausgeführten Zulaufleitung 52 und zum anderen mit einer zum Hochdruckraum 40 führenden, als Bohrung durch das Fortsetzungsstück 37 ausgeführten Hochdruckraumleitung 56 in Verbindung steht. Der Ventilraum 53 steht darüber hinaus unabhängig von der Stellung des Ventilkörpers 51 über eine als Bohrung im Kolben 36 ausgeführte und am dem Raum 35 abgewandten Ende der Bohrung 58 in die Bohrung einmündende Rückraumleitung 55 mit dem Rückraum 38 in Verbindung, da der Ventilkörper 51 auf seiner der Feder 54 zugewandten Seite einen durch die Federmitte hindurchgehenden Fortsatz 57 besitzt, der, wie in Figur 2 dargestellt, die Bewegung des Ventilkörpers begrenzt, sobald er die Leitungen 52 und 56 verschlossen hat.FIG. 1 shows a fuel injection device in which an injector 10 is connected to a high-pressure fuel source 60 via a pressure booster device 30. The high-pressure fuel source comprises several elements, not shown, such as a fuel tank, a pump and the high-pressure rail of a common rail system known per se, the pump providing a fuel pressure of up to 1600 bar in the high-pressure rail by injecting fuel from the tank transported the high pressure rail. The injector 10 has a fuel injection valve with a valve member 12 which projects with its injection openings 8 into the combustion chamber 11 of a cylinder of an internal combustion engine. The valve member is surrounded on a pressure shoulder 9 by a pressure chamber 13, which is connected via a high-pressure line 21 to the high-pressure chamber 40 of the pressure transmission device 30. The schematically illustrated valve member protrudes at its end facing away from the combustion chamber into a working chamber 18 which is connected via a throttle 20 to the high-pressure line 21 and via a throttle 19 to a control valve 15 of the injector, the Throttle 20 has a smaller opening cross section than the throttle 19. The control valve 15 is designed as a 2/2-way valve and is closed in the first position; in the second position, it connects the throttle 19 to a low-pressure line 17. The valve member is resiliently mounted via a return spring 14, the return spring pressing the valve member against the injection openings 8. The spring-containing space of the injector injector is connected to a further low-pressure line 16. The pressure transmission device 30 has a spring-mounted piston 36 which separates the high-pressure space 40 connected to the high-pressure line 21 from a space 35 which is connected directly to the high-pressure fuel source 60. The spring 39 used to support the piston is arranged in a rear space 38 of the pressure transmission device 30. The piston 36 has an extension piece 37 which has a smaller diameter than the piston 36 at its end facing the space 35. The rear space 38 can be connected to a low-pressure line 32 via a 2/2-way valve 31. The low-pressure line 32, like the low-pressure lines 16 and 17, leads back to the fuel tank (not shown). The space 35 of the pressure transmission device is connected to the rear space 38 via a throttle 47 integrated as a bore in the piston. In addition to the throttle bore 47, a combination valve 50 is integrated in a bore 58 of the piston 36. The bore communicates with space 35. A cylindrical valve body 51 is movably mounted in it. A spring 54 is arranged between the piston 36 and the valve body 51, which in the relaxed state presses the valve body just so far in the direction of the space 35 that the valve space 53 on the one hand has an inlet conduit 52 and which leads to the space 35 as a bore in the piston on the other hand, is connected to a high-pressure chamber line 56 leading to the high-pressure chamber 40 and designed as a bore through the extension piece 37. The valve chamber 53 is also located Regardless of the position of the valve body 51 via a bore hole in the piston 36 and at the end of the bore 58 facing the end of the bore 58 into the bore outlet chamber 55 in connection with the rear chamber 38, since the valve body 51 on its side facing the spring 54 has through the spring center extension 57 which, as shown in Figure 2, limits the movement of the valve body as soon as it has closed the lines 52 and 56.
Die Funktionsweise des hubgesteuerten Injektors 10 ist an sich bereits aus der deutschen Patentanmeldung DE 199 10 970 bekannt. An der Hochdruckleitung 21 liegt ständig ein hoher Kraftstoffdruck an. Kraftstoff gelangt aus dem Druckraum 13 durch die Einspritzöffnungen 8 in den Brennraum 11, sobald das Ventilglied an seinem den Einspritzöffnungen abgewandten Ende durch Öffnen des 2/2-Wege-Ventils 15 kurzzeitig vom Kraftstoffdruck entlastet wird und somit die an der Druckschulter 9 angreifende in Öffnungsrichtung wirkende Kraft größer ist als die Summe von Federkraft (14) und Kraft infolge des im Arbeitsraum 18 verbleibendenThe mode of operation of the stroke-controlled injector 10 is known per se from German patent application DE 199 10 970. A high fuel pressure is constantly present at the high-pressure line 21. Fuel passes from the pressure chamber 13 through the injection openings 8 into the combustion chamber 11 as soon as the valve member at its end facing away from the injection openings is briefly relieved of fuel pressure by opening the 2/2-way valve 15 and thus the opening shoulder acting on the pressure shoulder 9 acting force is greater than the sum of spring force (14) and force due to the remaining in the working space 18
Kraftstoffdrucks . Im Ruhezustand hingegen ist das Ventil 15 geschlossen, das Einspritzventil ist geschlossen und es findet keine Einspritzung statt. Ist auch das Übersetzer- Steuerventil 31 geschlossen, so herrscht im Rückraum 38 der Druck der Kraftstoffhochdruckquelle und die Druckübersetzungseinrichtung 30 ist druckausgeglichen, so dass keine Druckverstärkung stattfindet. Das Kombiventil 50 ist dann geöffnet und der Kolben 36, 37 in seiner Ausgangslage, gekennzeichnet durch ein grosses Volumen des Rückraums 38. Der Druck der Kraftstoffhochdruckquelle kann über das geöffnete Kombiventil 50, die Zulaufleitung 52 und die Rückraumleitung 55 in den Rückraum 38 gelangen. Weiterhin gelangt der Druck der Kraftstoffhochdruckquelle über die Zulaufleitung 52 und die Hochdruckraumleitung 56 zum Hochdruckraum 40 und von dort zum Injektor 10. Somit kann zu jeder Zeit eine Einspritzung mit dem Druck der Kraftstoffhochdruckquelle stattfinden. Hierzu muss lediglich, wie bereits eingangs beschrieben, das Steuerventil 15 des Injektors betätigt werden, wodurch sich das Einspritzventil öffnet. Soll nun eine Einspritzung mit erhöhtem Druck stattfinden, dann wird das Übersetzer- Steuerventil 31 geöffnet, so dass der Druck im Rückraum 38 abfallen kann, wodurch sich das Kombiventil 50 schließt. In geschlossenem Zustand verschließt das Kombiventil 50, wie in Figur 2 dargestellt, die Hochdruckraumleitung 56 und die Zulaufleitung 52. Damit kann der im Hochdruckraum 40 zu komprimierende Kraftstoff nicht zurückfliessen (Rückschlagventil-Funktion des Kombiventils) und der Kraftstoff aus dem Raum 35 strömt nur gedrosselt über die Drossel 47 in den Rückraum 38 (Füllventil-Funktion des Kombiventils) . Infolge der Druckentlastung des Rückraums 38 ist der Kolben 36 nicht druckausgeglichen und es erfolgt im Hochdruckraum 40 eine Druckverstärkung entsprechend dem Druckflächenverhältnis von Raum 35 und Hochdruckraum 40. Wird die Druckübersetzungseinrichtung 30 durch Schließen des Übersetzer-Steuerventils 31 abgeschaltet, dann erfolgt über die Drossel 47 ein Druckausgleich zwischen den Räumen 35, 38 und 40. Das Kombiventil 50 öffnet, wenn der Druck im Rückraum 38 den Druck im Raum 35 abzüglich einer Öffnungsdruckdifferenz erreicht hat. Die Öffnungsdruckdifferenz des Kombiventils ist durch die Federkonstante der Feder 54 und die hydraulischen Druckflächen des Ventilkörpers zu den Räumen 35 und 53 festgelegt. Im dargestellten Ausführungsbeispiel sind die hydraulischen Druckflächen gleich gross. Sobald das Kombiventil geöffnet ist, kann eine schnelle Füllung des Rückraums 38 und des Hochdruckraums 40 und damit eine schnelle Rückstellung des Kolbens derFuel pressure. In the idle state, however, the valve 15 is closed, the injection valve is closed and there is no injection. If the booster control valve 31 is also closed, the pressure of the high-pressure fuel source prevails in the rear space 38 and the pressure booster device 30 is pressure-balanced, so that no pressure amplification takes place. The combination valve 50 is then opened and the piston 36, 37 in its initial position, characterized by a large volume of the rear space 38. The pressure of the high-pressure fuel source can reach the rear space 38 via the opened combination valve 50, the feed line 52 and the rear space line 55. Furthermore, the pressure of the high-pressure fuel source passes via the inlet line 52 and the high-pressure space line 56 to the high-pressure space 40 and from there to the injector 10 an injection with the pressure of the high-pressure fuel source can take place at any time. For this purpose, as already described at the outset, the control valve 15 of the injector only has to be actuated, as a result of which the injection valve opens. If an injection with increased pressure is now to take place, then the intensifier control valve 31 is opened so that the pressure in the rear space 38 can drop, as a result of which the combination valve 50 closes. In the closed state, the combi valve 50 closes, as shown in FIG. 2, the high pressure chamber line 56 and the inlet line 52. The fuel to be compressed in the high pressure chamber 40 cannot flow back (check valve function of the combi valve) and the fuel from the chamber 35 only flows in a throttled manner via the throttle 47 into the rear space 38 (filling valve function of the combination valve). As a result of the pressure relief of the rear space 38, the piston 36 is not pressure-balanced and there is a pressure increase in the high-pressure space 40 in accordance with the pressure-area ratio of the space 35 and the high-pressure space 40 Pressure equalization between rooms 35, 38 and 40. The combination valve 50 opens when the pressure in the rear room 38 has reached the pressure in the room 35 minus an opening pressure difference. The opening pressure difference of the combination valve is determined by the spring constant of the spring 54 and the hydraulic pressure surfaces of the valve body to the spaces 35 and 53. In the illustrated embodiment, the hydraulic pressure areas are the same size. As soon as the combination valve is opened, the back space 38 and the high-pressure space 40 can be filled quickly and thus the piston can be quickly reset
Druckübersetzungseinrichtung erfolgen. Dadurch, dass die Einspritzung mit zwei unterschiedlichen Druckniveaus (Raildruck und übersetzter Druck) stattfinden kann und ein Zuschalten der Druckübersetzungseinrichtung zu jeder Zeit möglich ist, kann eine flexible Formung des Einspritzverlaufs erfolgen. Dabei sind rechteckförmige, rampenförmige oder auch "Boot"-Einspritzungen mit variabler Länge der Bootphase möglich.Pressure translation device take place. Because the injection can take place at two different pressure levels (rail pressure and translated pressure) and one It is possible to switch on the pressure booster at any time, the injection course can be shaped flexibly. Rectangular, ramp-shaped or "boat" injections with variable length of the boot phase are possible.
Figur 3 zeigt eine weitere Ausführungsform der erfindungsgemäßen Kraftstoffeinspritzeinrichtung. Die zwischen der Kraftstoffhochdruckquelle 60 und der zum Injektor 10 führenden Hochdruckleitung 21 angeordnete Druckübersetzungseinrichtung weist einen Kolben 36 mit einem integrierten alternativen Kombiventil 70 auf. Der Ventilkörper 78 des Kombiventils 70 ist in einem zylindrischen Hohlraum 88 des Kolbens 36 beweglich gelagert. Eine als Bohrung im Kolben 36 ausgeführte Zulaufleitung 72 führt vom Raum 35 in eine Ringnut 90 des Hohlraums 88. Der Rückraum 38 ist unabhängig von der Stellung des Ventilkörpers im Hohlraum über die Rückraumleitung 74 mit dem Hohlraum 88 verbunden, so dass ständig ein im Rückraum herrschender Kraftstoffdruck am Ventilkörper angreifen kann. Eine Feder 80 ist so zwischen der Wandung des Hohlraums 88 und einer Schulter des Ventilkörpers 78 gespannt, dass bei überwiegend in Federkraftrichtung auf den Ventilkörper wirkenden Kräften über die Ringnut 90 ein > Flüssigkeitsaustausch zwischen dem Raum 35 und dem Hohlraum 88 stattfinden kann. Dabei wird eine am der Feder 80 abgewandten Ende des Ventilkörpers angeordnete Erhebung 94 des Ventilkörpers gegen die Hohlraumbegrenzung gedrückt. Eine als Bohrung im Kolben ausgeführte Hochdruckraumleitung 76 verbindet den Hochdruckraum 40 mit dem zwischen der von der Erhebung 94 begrenzten Druckfläche 92 und der Kolbenwandung befindlichen Teil des Hohlraums 88. Im entspannten Zustand der Feder 80 steht ferner der Bereich des Hohlraums 88, der von dem der Feder zugewandten Ende des Ventilkörpers 78 begrenzt wird, über eine zentrale Bohrung 86 des Ventilkörpers mit dem Bereich des Hohlraums in Verbindung, der von dem der Feder abgewandten Ende des Ventilkörpers begrenzt wird. Überwiegen die gegen Federkraftrichtung wirkenden Kräfte auf den Ventilkörper, so werden die Flachdichtsitzflächen 82 aufeinandergepresst und die Bohrung 86 verschlossen. Gleichzeitig wird die Ringnut 90 vom restlichen Teil des Hohlraums 88 durch die Schieberdichtkanten 84 verschlossen.FIG. 3 shows a further embodiment of the fuel injection device according to the invention. The pressure transmission device arranged between the high-pressure fuel source 60 and the high-pressure line 21 leading to the injector 10 has a piston 36 with an integrated alternative combination valve 70. The valve body 78 of the combination valve 70 is movably mounted in a cylindrical cavity 88 of the piston 36. An inlet line 72 designed as a bore in the piston 36 leads from the space 35 into an annular groove 90 of the cavity 88. The rear space 38 is connected to the cavity 88 via the rear space line 74, regardless of the position of the valve body in the cavity, so that there is always a prevailing in the rear space Can attack fuel pressure on the valve body. A spring 80 is stretched between the wall of the cavity 88 and a shoulder of the valve body 78 in such a way that when forces act predominantly on the valve body in the direction of the spring force, a> liquid exchange between the space 35 and the cavity 88 can take place via the annular groove 90. In this case, an elevation 94 of the valve body arranged on the end of the valve body facing away from the spring 80 is pressed against the cavity boundary. A high-pressure chamber line 76 designed as a bore in the piston connects the high-pressure chamber 40 to the part of the cavity 88 located between the pressure surface 92 delimited by the elevation 94 and the piston wall. In the relaxed state of the spring 80 there is also the region of the cavity 88 which is different from that of the Spring-facing end of the valve body 78 is limited, via a central bore 86 of the valve body with the area of the cavity in Connection that is limited by the end of the valve body facing away from the spring. If the forces acting against the direction of the spring force predominate on the valve body, the flat sealing seat surfaces 82 are pressed against one another and the bore 86 is closed. At the same time, the annular groove 90 is closed by the remaining part of the cavity 88 by the slide sealing edges 84.
Da das Kombiventil 50 also sowohl eine Druckfläche zum Hochdruckraum 40, die Druckfläche 92, als auch eine Druckfläche zum Rückraum 38 aufweist, wird es durch einen abfallenden Druck im Rückraum und durch einen ansteigenden Druck im Hochdruckraum geschlossen. Die öffnende Federkraft der Feder 80 legt die Öffnungsdruckdifferenz zwischen dem Rückraum und dem Hochdruckraum fest, bis zu der das Kombi entil geöffnet ist. Die Dichtfunktion ist dabei für die Hochdruckraumleitung 40 durch die Flachdichtsitzflächen 82 und für die Zulaufleitung 72 durch dieSince the combination valve 50 thus has both a pressure surface to the high pressure chamber 40, the pressure surface 92, and a pressure surface to the rear chamber 38, it is closed by a falling pressure in the rear chamber and by an increasing pressure in the high pressure chamber. The opening spring force of the spring 80 defines the opening pressure difference between the rear space and the high pressure space up to which the combination valve is open. The sealing function is for the high-pressure space line 40 through the flat sealing seat surfaces 82 and for the inlet line 72 through the
Schieberdichtkanten 84 gewährleistet. Eine Druckverstärkung im Hochdruckraum erfolgt wie im vorhergehend beschriebenen Ausführungsbeispiel bei Öffnung des Übersetzer-Steuerventils 31 zur Druckentlastung des Rückraums 38. Slider sealing edges 84 guaranteed. As in the exemplary embodiment described above, pressure is increased in the high-pressure chamber when the booster control valve 31 is opened to relieve the pressure in the rear chamber 38.

Claims

Ansprüche Expectations
1. Kraf stoffeinspritzeinrichtung für Brennkraftmaschinen mit einem von einer Kraftstoffhochdruckquelle versorgbaren Kraftstoffin ektor, wobei zwischen dem Kraftstoffinjektor und der Kraftstoffhochdruckquelle eine einen beweglichen Kolben aufweisende Druckübersetzungseinrichtung geschaltet ist, wobei der bewegliche Kolben einen an die Kraftstoffhochdruckquelle angeschlossenen Raum von einem mit dem Injektor verbundenen Hochdruckraum trennt, wobei durch Befüllen eines Rückraumes der Druckübersetzungseinrichtung mit Kraftstoff beziehungsweise durch Entleeren des Rückraums von Kraftstoff der Kraftstoffdruck im Hochdruckraum variiert werden kann, dadurch gekennzeichnet, dass ein Ventil (50; 70) mit einem verschiebbar angeordneten Ventilkörper (51; 78) vorgesehen ist, so dass der Hochdruckraum1. fuel injection device for internal combustion engines with a fuel injector that can be supplied by a high-pressure fuel source, wherein a pressure booster device having a movable piston is connected between the fuel injector and the high-pressure fuel source, the movable piston separating a space connected to the high-pressure fuel source from a high-pressure space connected to the injector, wherein the fuel pressure in the high-pressure chamber can be varied by filling a rear space of the pressure transmission device with fuel or by emptying the rear space of fuel, characterized in that a valve (50; 70) with a displaceably arranged valve body (51; 78) is provided, so that the high pressure room
(40) über das Ventil (50; 70) mit dem Raum (35) verbindbar (56, 53, 52; 76, 86, 88, 72) und der Rückraum (38) über das Ventil mit dem Raum (35) verbindbar (55, 53, 52; 74, 88, 72) ist.(40) can be connected to the room (35) via the valve (50; 70) (56, 53, 52; 76, 86, 88, 72) and the rear area (38) can be connected to the room (35) via the valve ( 55, 53, 52; 74, 88, 72).
2. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Ventilkörper (51; 78) in Abhängigkeit von dem im Rückraum (38) herrschenden Kraftstoffdruck verschiebbar angeordnet ist.2. Fuel injection device according to claim 1, characterized in that the valve body (51; 78) is arranged displaceably as a function of the fuel pressure prevailing in the rear space (38).
3. Kraftstoffeinspritzeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Ventil (50; 70) im Kolben (36, 37) integriert ist.3. Fuel injection device according to one of the preceding claims, characterized in that the valve (50; 70) in the piston (36, 37) is integrated.
4. Kraftstoffeinspritzeinrichtung nach Anspruch 3, dadurch gekennzeichnet, dass das Ventil (50; 70) über als im Kolben integrierte Bohrungen ausgeführte Leitungen (52, 55, 56; 72, 74, 76) mit dem Raum (35) , dem Rückraum (38) und dem Hochdruckraum (40) verbunden ist. 4. The fuel injection device according to claim 3, characterized in that the valve (50; 70) via lines (52, 55, 56; 72, 74, 76) designed as bores integrated in the piston with the space (35), the rear space (38 ) and the high pressure chamber (40) is connected.
5. Kraftstoffeinspritzeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Ventilkörper einenends mit dem im Rückraum (38) herrschenden Kraftstoffdruck beaufschlagbar (55) und andernends mit dem im Raum (35) herrschenden Kraftstoffdruck beaufschlagbar ist.5. Fuel injection device according to one of the preceding claims, characterized in that the valve body can be acted upon at one end with the fuel pressure prevailing in the rear space (38) (55) and at the other end with the fuel pressure prevailing in the space (35).
6. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Ventilkörper einenends mit dem im Rückraum (38) herrschenden Kraftstoffdruck beaufschlagbar (74) und andernends über eine Druckfläche (92) mit dem im6. Fuel injection device according to one of claims 1 to 4, characterized in that the valve body can be acted upon at one end with the fuel pressure prevailing in the rear space (38) (74) and at the other end via a pressure surface (92) with the
Hochdruckraum (40) herrschenden Kraftstoffdruck beaufschlagbar (76) ist.High pressure chamber (40) prevailing fuel pressure (76).
7. Kraftstoffeinspritzeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Raum (35) mit dem Rückraum (38) über eine Drossel (47) verbunden ist.7. Fuel injection device according to one of the preceding claims, characterized in that the space (35) with the rear space (38) via a throttle (47) is connected.
8. Kraftstoffeinspritzeinrichtung nach Anspruch 7, dadurch gekennzeichnet, dass die Drossel (47) als im Kolben (36, 37) integrierte Bohrung ausgeführt ist.8. Fuel injection device according to claim 7, characterized in that the throttle (47) is designed as an integrated bore in the piston (36, 37).
9. Kraftstoffeinspritzeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Rückraum (38) über ein Steuerventil (31) mit einer Niederdruckleitung (32) verbindbar ist.9. Fuel injection device according to one of the preceding claims, characterized in that the rear space (38) can be connected to a low-pressure line (32) via a control valve (31).
10. Druckübersetzungseinrichtung mit einem beweglichen Kolben, der einen an eine Kraftstoffhochdruckquelle anschließbaren Raum von einem mit einem Kraftstoffin ektor verbindbaren Hochdruckraum trennt, wobei durch Befüllen eines Rückraumes der Druckübersetzungseinrichtung mit Kraftstoff beziehungsweise durch Entleeren des Rückraums von Kraftstoff der Kraftstoffdruck im Hochdruckraum variiert werden kann, dadurch gekennzeichnet, dass ein Ventil (50; 70) mit einem verschiebbar angeordneten Ventilkörper (51; 78) vorgesehen ist, so dass der Hochdruckraum10. Pressure booster device with a movable piston that separates a room that can be connected to a high-pressure fuel source from a high-pressure room that can be connected to a fuel injector, whereby the fuel pressure in the high-pressure room can be varied by filling a rear area of the pressure booster device with fuel or by emptying the rear area of fuel characterized in that a valve (50; 70) with a displaceably arranged valve body (51; 78) is provided, so that the high-pressure chamber
(40) über das Ventil (50; 70) mit dem Raum (35) verbindbar (56, 53, 52; 76, 86, 88, 72) und der Rückraum (38) über das Ventil mit dem Raum (35) verbindbar (55, 53, 52; 74, 88, 72) ist. (40) can be connected to the room (35) via the valve (50; 70) (56, 53, 52; 76, 86, 88, 72) and the rear area (38) can be connected to the room (35) via the valve ( 55, 53, 52; 74, 88, 72).
EP02742691A 2001-05-17 2002-04-26 Fuel injection device with pressure translation device and pressure translation device Expired - Lifetime EP1392962B1 (en)

Applications Claiming Priority (3)

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DE10123914 2001-05-17
DE10123914A DE10123914B4 (en) 2001-05-17 2001-05-17 Fuel injection device with pressure booster device and pressure booster device
PCT/DE2002/001535 WO2002092992A1 (en) 2001-05-17 2002-04-26 Fuel injection device with pressure translation device and pressure translation device

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DE10123914B4 (en) 2005-10-20
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EP1392962B1 (en) 2006-09-13
JP2004519610A (en) 2004-07-02

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