EP0898650B1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines Download PDF

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Publication number
EP0898650B1
EP0898650B1 EP97943768A EP97943768A EP0898650B1 EP 0898650 B1 EP0898650 B1 EP 0898650B1 EP 97943768 A EP97943768 A EP 97943768A EP 97943768 A EP97943768 A EP 97943768A EP 0898650 B1 EP0898650 B1 EP 0898650B1
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EP
European Patent Office
Prior art keywords
control valve
pressure
injection
valve member
fuel
Prior art date
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Expired - Lifetime
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EP97943768A
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German (de)
French (fr)
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EP0898650A1 (en
Inventor
Franz Guggenbichler
Jaroslaw Hlousek
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0898650A1 publication Critical patent/EP0898650A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 27 59 255 A.
  • This fuel injection device has an injection line supplied with high-pressure fuel, which is connected to a respective injection valve whose opening and closing movements are controlled by an electrically controlled, arranged on the injection valve control valve, which is designed as a 3/2-way valve.
  • the 3/2-way valve has a control valve member with a spherical closing body, on which two sealing surfaces are formed.
  • the control valve member connects a high-pressure passage opening into an injection port of the injection valve to the injection passage or to a relief passage.
  • the control valve member is actuated by a prevailing in a working space pressure against a restoring force, wherein the working space is designed as a fillable with high pressure hydraulic hydraulic working space on the control valve member of the 3/2-way valve.
  • the control valve member has a piston-shaped portion which is acted upon by the pressure prevailing in the working space against a force acting on the spherical closing body hydraulic opening force in the closing direction of a flow cross-section between the injection line and the high-pressure passage and the working space can be opened in a discharge chamber.
  • the hydraulic opening force on the control valve member is generated by acting on the closing body fuel high pressure of the injection line.
  • a further 3/2 control valve is provided, through which the working space is connected to the injection line or to the discharge space.
  • a fuel injection device in which a high-pressure pump can be filled with fuel common high-pressure accumulation chamber is provided, which is connected via injection lines with injection valves.
  • the opening and closing movements of the injection valves are each controlled by an electrically controlled, arranged on the injection valve control valve.
  • the control valve is designed as a 2/2-way valve and has a piston-shaped control valve member with a sealing surface which connects a opening to an injection port of the injection valve high-pressure channel with the injection line or separates from the injection line.
  • the high-pressure channel is constantly connected via a throttle point with a discharge line, so that even when connected to the injection line high-pressure channel fuel flows into the discharge line and thus large leakage quantities are present.
  • the control valve member can be actuated by a prevailing in a working space pressure against a restoring force, wherein the working space is designed as a fillable with high pressure hydraulic hydraulic working space on the control valve member of the 2/2-way valve.
  • the control valve member is acted upon by the prevailing pressure in the working chamber against an opening force acting on this in the closing direction of a flow cross-section between the injection line and the high-pressure channel and the working space can be opened in a discharge chamber.
  • the opening force on the control valve member is generated by a spring.
  • the pressure in the working space is controlled by a constant inflow and a controlled outflow.
  • the working space is bounded by an upper end face of the control valve member.
  • the working space is constantly connected via a throttle cross-section with the injection line and from the working space leads from a closable discharge channel whose cross-section is greater than the throttle cross section to the injection line.
  • the discharge channel is openable and controllable by means of an electric control valve.
  • At the control valve member an annular groove is provided in the region of the overlap with the injection line, are formed by the opposing annular end faces on the control valve member, where the high fuel pressure acts. Due to the opposing annular end faces of the high fuel pressure does not generate a resultant force on the control valve member when this is in its closed position in which the high pressure passage is separated from the injection line. An opening movement of the control valve member is only possible by the opening force generating spring.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that it has a simple structure with the piston-shaped control valve member and the hydraulically generated opening force, for which no spring is required.
  • the illustrated in Figure 1 first embodiment of the fuel injection device for internal combustion engines has a high-pressure fuel pump 1, which is connected on the suction side via a fuel delivery line 3 with a fuel-filled low-pressure chamber 5 and the pressure side via the delivery line 3 with a high-pressure accumulator 7. From this high-pressure accumulation chamber 7 lead injection lines 9 to the individual, projecting into the combustion chamber of the engine to be supplied injection valves 11, wherein the Control of the injection process in each case an electrically actuated, designed as a 3/2-way valve control valve 13 is provided on each injection valve 11.
  • the injection valve 11 is clamped by means of a clamping nut 15 axially against a valve holding body 17 on which a lateral high pressure port 19 is provided, in which a pipe socket 21 of the corresponding injection line 9 is inserted.
  • the valve holding body 17 has an axial through hole 23 into which a piston-shaped control valve member 25 of the control valve 13 is inserted on the side facing away from the injection valve 11.
  • This formed as a double-seat valve control valve 13 connects a discharge from the injection line 9 in the pipe socket 21 connecting channel 27 with a valve holding body 17 axially penetrating the high-pressure channel 29 at the injection valve 11 facing the end face of the valve holding body 17 in a known manner to a not shown pressure line in Injection valve 11 opens, on the other hand opens up to a Jerusalem speakbaren by a valve needle 31 of the injection valve 11 injection cross section of the injection valve 11.
  • the high pressure passage 29 via the control valve 13 is alternately connected to the injection line 9 or a discharge line 33, which is formed from the injection valve side part of the through hole 23 and a laxative from this return line and which opens into the low pressure chamber 5.
  • the adjusting movement of the control valve member 25 of the control valve 13 is controlled by a solenoid valve 35 which is inserted on the side facing away from the injector 11 in the valve holding body 17 and which is controlled by an electrical control unit 37, which processes a variety of operating parameters of the engine to be supplied ,
  • the control valve member 25 of the control valve 13, shown enlarged in FIG. 2, is designed as a stepped piston whose cross-section points downwards in the direction of the injection valve. 11 tapered over two conical annular surfaces.
  • a first upper annular end face 39 is provided in the region of the junction of the connecting channel 27 to the injection line 9.
  • a second annular end surface forms a first conical valve sealing surface 41, which cooperates with a first conical valve seat 43, said first sealing seat formed between the valve sealing surface 41 and the valve seat 43 closes the injection line 9 with respect to the high-pressure channel 29.
  • the control valve member 25 has a sleeve 45 to which a second, the first valve sealing surface 41 facing valve sealing surface 47 is provided, which cooperates with a second valve seat 49 on the wall of the through hole 23.
  • the valve seat surfaces 43 and 49 are formed so that they limit the adjustment movement of the control valve member 25 in both stroke directions.
  • the second sealing cross-section formed between the second valve sealing surface 47 and the second valve seat surface 49 closes the connection between the high-pressure channel 29 and the relief line 33 formed in part through the through-bore 23 into the low-pressure space 5.
  • a hydraulic working chamber 51 is provided, which is limited by the upper, the injection valve 11 facing away from face 53 of the control valve member 25 in the bore 23.
  • the hydraulic working space 51 is delimited by an intermediate disk 55 to the solenoid valve 35.
  • a discharge channel 57 discharging from the working chamber 51 is provided, which leads into a return channel opening into the low-pressure chamber 5 59 opens and which can be closed by a valve member of the solenoid valve 35.
  • This valve member of the solenoid valve 35 is formed as a valve ball 61, which is guided in a valve seat adjacent to the discharge channel 57 and the discharge port 57 is held closed by the force of a solenoid valve spring 63 at de-energized solenoid valve 35.
  • the valve ball 61 is articulated to an armature 65 of the solenoid valve 35, which is displaced against the restoring force of the spring 63 in energized solenoid valve 35 in the direction away from the working space 51, so that the valve ball 61 is lifted from the pending in the working space 51 pressure from its seat and the discharge channel 57 is opened to the return line 59.
  • a filling bore 67 is provided in the control valve member 25, which has a throttle point 69 whose cross section is smaller than the cross section of the discharge channel 57.
  • this filling bore 67 opening into the end face 53 leads below the first annular end face 39 of the control valve member 25, so that the hydraulic working chamber 51 is connected at all times to the injection line 9 via the filling bore 67.
  • a portion of the high-pressure fuel passes through the remaining between the control valve member 25 and the wall of the bore 23 annular gap 71 throttled into the hydraulic working chamber 51, so that even with a possible closure of the filling bore 67 is an emergency operation of the control valve 13th is guaranteed.
  • the fuel injection device for internal combustion engines shown in Figures 1 and 2 in a first embodiment operates in the following manner.
  • the system starts up, it first starts with the high-pressure fuel pump 1, a high-pressure fuel in common high-pressure accumulator 7 (common rail) constructed, which continues through the various injection lines 9 to the respective valve holding body 17 of the injectors 11.
  • the solenoid valve 35 is de-energized prior to the start of the injection phase, so that the valve ball 61 of the solenoid valve 35 keeps the discharge channel 57 closed.
  • the hydraulic working chamber 51 is filled via the filling bore 67 with high pressure fuel and presses the control valve member 25 due to the area ratio between the end face 53 and the first annular end face 39 with the first valve sealing surface 41 against the first valve seat 43.
  • the illustrated in Figure 3 second embodiment of the fuel injection device according to the invention differs from the first embodiment in the manner of forming the control valve member 25 of the control valve 13.
  • the control valve member 25 is now integrally formed and guided in a cylinder sleeve 73 inserted into the through hole 23 of the valve holding body 17 ,
  • a lower, the solenoid valve 35 facing away from cross-sectional part of the control valve member 25 forms a guide member 75 of the control valve member 25, which slides with little clearance in the inner diameter of the cylinder sleeve 73.
  • the filling of the hydraulic working chamber 51 in the second embodiment takes place only via the annular gap 71 between the control valve member 25 and the inner wall of the cylinder liner 73.
  • the annular gap 71 is designed as a throttle point such that the entire flow area is smaller than the cross section of the discharge channel 57 of the hydraulic working chamber 51.
  • the fuel discharge from a, the second sealing seat between the valve sealing surface 47 and the valve seat 49 downstream relief space 77 in the discharge line 23, 33 takes place via a remote from the upper end face 53 lower end face 79 in the control valve member 25 outgoing blind hole 81, from which a trained as a throttle bore transverse bore 83 dissipates, which opens into the discharge chamber 77.
  • the illustrated in Figure 5 fourth embodiment of the fuel injection device is analogous to that in the figure 3 illustrated second embodiment and additionally has a stroke-controlled throttle between the first and second sealing seat.
  • This stroke-controlled throttle is formed by an annular collar 89 on the control valve member 25, whose transition regions to the adjacent shaft portion of the control valve member 25 are conical.
  • This annular collar 89 acts together with an annular web 91 on the wall of the through hole 23 such that it is in the first valve seat 43 abutting first valve sealing surface 41 with this in coverage.
  • the fifth embodiment of the fuel injection device shown in Figure 6 in a simplified overall illustration also differs from the previous embodiments by the design of the control valve member 25.
  • the throttle cross-section between the injection line 9 and the working chamber 51 defining annular gap 71 by an annular groove 93 in a upper throttle gap 95 and a lower throttle gap 97 divided.
  • the second sealing seat controlling the overflow cross section between the high-pressure channel 29 and the discharge line 33 is designed as a slide valve seat in the fifth exemplary embodiment.
  • the control valve member 25 at its lower the Injection valve 11 facing the end of a slide head 99, whose outer diameter corresponds to the diameter of the through hole 23 in the guide portion 75 except for a very small clearance.
  • the upper, the solenoid valve 35 facing the boundary edge of the slide head 99 forms a valve control edge 101, which cooperates with the guide portion 75 of the through hole 23 and their immersion in the overlap with the guide portion 75 of the through hole 23 controlling the connection between the high pressure passage 29 and relief line 33 controls
  • the valve control edge 101 of the slide head 99 is preceded by a further annular collar 103 on the control valve member 25, which forms a Abflußdrosselstelle for flowing out of the high-pressure passage 29 in the discharge line 33 high-pressure fuel.
  • the stroke limit of the control valve member 25 in the direction of the solenoid valve 35 is effected in the fifth embodiment by the contact of the upper end face 53 of the control valve member 25 on a hydraulic working space 51 delimiting end wall 105th
  • the sixth exemplary embodiment of the fuel injection device shown in FIG. 7 is constructed analogously to the second exemplary embodiment shown in FIG. 3 and has, in addition to this, a further throttle point in the relief line 33.
  • This throttle point is formed by a throttle insert 107 inserted into the relief line 33, whose flow area is designed so that at the injection end, the closing of the injector supported and possible Nacheinspritzen is prevented.
  • the fuel from the through hole 23 via the discharge line 33 is first led to the solenoid valve 35 and from there via the return passage 59th derived to the low pressure chamber 5.
  • This flow through the solenoid valve 35 has the advantage that the solenoid valve chamber can be cooled and vented during operation of the fuel injector.
  • FIG. 8 shows a seventh exemplary embodiment, the structure of which essentially corresponds to the third exemplary embodiment shown in FIG.
  • an additional throttle point 111 is provided between the high-pressure inlet channel 27 and the valve seat 43, via which the flow of the injection fuel in the ⁇ réelleshubphase, in particular at its beginning is controlled and by the Schinnehubterrorism the control valve member 25 can be attenuated .
  • This throttling point 111 is formed in the seventh embodiment as a narrow gap between the inner wall of the cylinder liner 73 and the control valve member 25, wherein the control valve member 25 a paragraph 113 is provided, through which the narrow gap is opened after a certain opening stroke of the control valve member 25 in a larger flow area.

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

Abstract

The present invention relates to a fuel injection device for internal combustion engines, comprising a high pressure pump (1) fitted with a common high pressure collector (Common Rail) to be filled with fuel. Said collector is connected through injection pipes (9) to injection valves (11) emerging into the combustion chamber of the engine. The opening and closing motion of said valves is controlled by an electrically driven pilot valve (13) designed as a 3/2-way valve which connects a high pressure channel (29) opening out into an injection opening of the injection valve (11) to an injection pipe (9) or a discharge pipe )33). On the rod (25) of the pilot valve (13) there is a hydraulic working chamber (51), which is filled with HP fuel and can be handled so as to adjust the position of the pilot valve (13) rod (25) in the discharge channel (57).

Description

Die Erfindung betrifft eine Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen nach der Gattung des Anspruchs 1.The invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1.

Eine solche Kraftstoffeinspritzeinrichtung ist durch die DE 27 59 255 A bekannt. Diese Kraftstoffeinspritzeinrichtung weist eine mit Kraftstoffhochdruck versorgte Einspritzleitung auf, die mit jeweils einem Einspritzventil verbunden ist, dessen Öffnungs- und Schließbewegungen von einem elektrisch angesteuerten, am Einspritzventil angeordneten Steuerventil gesteuert wird, das als 3/2-Wegeventil ausgebildet ist. Das 3/2-Wegeventil weist ein Steuerventilglied mit einem kugelförmigen Schließkörper auf, an dem zwei Dichtflächen ausgebildet sind. Das Steuerventilglied verbindet einen an eine Einspritzöffnung des Einspritzventils mündenden Hochdruckkanal mit der Einspritzleitung oder mit einer Entlastungsleitung. Das Steuerventilglied ist durch einen in einem Arbeitsraum herrschenden Druck entgegen einer Rückstellkraft betätigbar, wobei der Arbeitsraum als ein mit Kraftstoffhochdruck befüllbarer hydraulischer Arbeitsraum am Steuerventilglied des 3/2-Wegeventils ausgebildet ist. Das Steuerventilglied weist einen kolbenförmigen Abschnitt auf, der von dem im Arbeitsraum herrschenden Druck entgegen einer an diesem über den kugelförmigen Schließkörper wirkenden hydraulischen Öffnungskraft in Schließrichtung eines Durchströmquerschnitts zwischen Einspritzleitung und Hochdruckkanal beaufschlagt und der Arbeitsraum ist in einen Entlastungsraum aufsteuerbar. Die hydraulische Öffnungskraft auf das Steuerventilglied wird durch den auf dessen Schließkörper wirkenden Kraftstoffhochdruck der Einspritzleitung erzeugt. Für die Steuerung des im Arbeitsraum herrschenden Drucks ist ein weiteres 3/2-Stellventil vorgesehen, durch das der Arbeitsraum mit der Einspritzleitung oder mit dem Entlastungsraum verbunden wird. Insgesamt weist diese bekannte Kraftstoffeinspritzeinrichtung wegen des Steuerventilglieds und wegen des 3/2-Stellventils einen aufwendigen Aufbau auf.Such a fuel injection device is known from DE 27 59 255 A. This fuel injection device has an injection line supplied with high-pressure fuel, which is connected to a respective injection valve whose opening and closing movements are controlled by an electrically controlled, arranged on the injection valve control valve, which is designed as a 3/2-way valve. The 3/2-way valve has a control valve member with a spherical closing body, on which two sealing surfaces are formed. The control valve member connects a high-pressure passage opening into an injection port of the injection valve to the injection passage or to a relief passage. The control valve member is actuated by a prevailing in a working space pressure against a restoring force, wherein the working space is designed as a fillable with high pressure hydraulic hydraulic working space on the control valve member of the 3/2-way valve. The control valve member has a piston-shaped portion which is acted upon by the pressure prevailing in the working space against a force acting on the spherical closing body hydraulic opening force in the closing direction of a flow cross-section between the injection line and the high-pressure passage and the working space can be opened in a discharge chamber. The hydraulic opening force on the control valve member is generated by acting on the closing body fuel high pressure of the injection line. For the control of the pressure prevailing in the working chamber, a further 3/2 control valve is provided, through which the working space is connected to the injection line or to the discharge space. Overall, this known fuel injection device due to the control valve member and because of the 3/2-way valve on a complex structure.

Durch die DE 196 12 738 ist eine Kraftstoffeinspritzeinrichtung bekannt, bei der ein von einer Hochdruckpumpe mit Kraftstoff befüllbarer gemeinsamer Hochdrucksammelraum vorgesehen ist, der über Einspritzleitungen mit Einspritzventilen verbunden ist. Die Öffnungs- und Schließbewegungen der Einspritzventile werden jeweils von einem elektrisch angesteuerten, am Einspritzventil angeordneten Steuerventil gesteuert. Das Steuerventil ist als 2/2-Wegeventil ausgebildet und weist ein kolbenförmiges Steuerventilglied mit einer Dichtfläche auf, das einen an eine Einspritzöffnung des Einspritzventils mündenden Hochdruckkanal mit der Einspritzleitung verbindet oder von der Einspritzleitung trennt. Der Hochdruckkanal ist ständig über eine Drosselstelle mit einer Entlastungsleitung verbunden, so dass auch bei mit der Einspritzleitung verbundenem Hochdruckkanal Kraftstoff in die Entlastungsleitung abströmt und somit große Leckagemengen vorhanden sind. Das Steuerventilglied ist durch einen in einem Arbeitsraum herrschenden Druck gegen eine Rückstellkraft betätigbar, wobei der Arbeitsraum als ein mit Kraftstoffhochdruck befüllbarer hydraulischer Arbeitsraum am Steuerventilglied des 2/2-Wegeventils ausgebildet ist. Das Steuerventilglied ist von dem im Arbeitsraum herrschenden Druck entgegen einer an diesem wirkenden Öffnungskraft in Schließrichtung eines Durchströmquerschnitts zwischen Einspritzleitung und Hochdruckkanal beaufschlagt und der Arbeitsraum ist in einen Entlastungsraum aufsteuerbar. Die Öffnungskraft auf das Steuerventilglied wird durch eine Feder erzeugt. Der Druck im Arbeitsraum wird durch einen konstanten Zufluß und einen gesteuerten Abfluss gesteuert. Der Arbeitsraum wird von einer oberen Stirnfläche des Steuerventilglieds begrenzt. Der Arbeitsraum ist über einen Drosselquerschnitt ständig mit der Einspritzleitung verbunden und vom Arbeitsraum führt ein verschließbarer Entlastungskanal ab, dessen Querschnitt größer ist als der Drosselquerschnitt zur Einspritzleitung. Der Entlastungskanal ist mittels eines elektrischen Stellventils auf- und zusteuerbar. Am Steuerventilglied ist im Bereich der Überdeckung mit der Einspritzleitung eine Ringnut vorgesehen, durch die einander gegenüberliegende Ringstirnflächen am Steuerventilglied gebildet sind, an denen der Kraftstoffhochdruck wirkt. Aufgrund der einander gegenüberliegenden Ringstirnflächen erzeugt der Kraftstoffhochdruck keine resultierende Kraft auf das Steuerventilglied wenn sich dieses in seiner Schließstellung befindet, in der der Hochdruckkanal von der Einspritzleitung getrennt ist. Eine Öffnungsbewegung des Steuerventilglieds ist nur durch die die Öffnungskraft erzeugende Feder möglich.From DE 196 12 738 a fuel injection device is known in which a high-pressure pump can be filled with fuel common high-pressure accumulation chamber is provided, which is connected via injection lines with injection valves. The opening and closing movements of the injection valves are each controlled by an electrically controlled, arranged on the injection valve control valve. The control valve is designed as a 2/2-way valve and has a piston-shaped control valve member with a sealing surface which connects a opening to an injection port of the injection valve high-pressure channel with the injection line or separates from the injection line. The high-pressure channel is constantly connected via a throttle point with a discharge line, so that even when connected to the injection line high-pressure channel fuel flows into the discharge line and thus large leakage quantities are present. The control valve member can be actuated by a prevailing in a working space pressure against a restoring force, wherein the working space is designed as a fillable with high pressure hydraulic hydraulic working space on the control valve member of the 2/2-way valve. The control valve member is acted upon by the prevailing pressure in the working chamber against an opening force acting on this in the closing direction of a flow cross-section between the injection line and the high-pressure channel and the working space can be opened in a discharge chamber. The opening force on the control valve member is generated by a spring. The pressure in the working space is controlled by a constant inflow and a controlled outflow. The working space is bounded by an upper end face of the control valve member. The working space is constantly connected via a throttle cross-section with the injection line and from the working space leads from a closable discharge channel whose cross-section is greater than the throttle cross section to the injection line. The discharge channel is openable and controllable by means of an electric control valve. At the control valve member an annular groove is provided in the region of the overlap with the injection line, are formed by the opposing annular end faces on the control valve member, where the high fuel pressure acts. Due to the opposing annular end faces of the high fuel pressure does not generate a resultant force on the control valve member when this is in its closed position in which the high pressure passage is separated from the injection line. An opening movement of the control valve member is only possible by the opening force generating spring.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat den Vorteil, dass diese mit dem kolbenförmigen Steuerventilglied und der hydraulisch erzeugten Öffnungskraft, für die keine Feder erforderlich ist, einen einfachen Aufbau aufweist.The fuel injection device according to the invention with the features of claim 1 has the advantage that it has a simple structure with the piston-shaped control valve member and the hydraulically generated opening force, for which no spring is required.

Vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung sind in den abhängigen Ansprüchen angegeben.Advantageous embodiments and further developments of the fuel injection device according to the invention are specified in the dependent claims.

Zeichnungdrawing

Sechs Ausführungsbeispiele der erfindungsgemäßen Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen

die Figur 1
ein erstes Ausführungsbeispiel in einer Gesamtdarstellung, bei dem die Drosselstrecke zwischen Einspritzleitung und hydraulischem Arbeitsraum am Steuerventil durch eine Drosselbohrung in dessen Steuerventilglied ausgebildet ist,
die Figur 2
eine vergrößerte Schnittdarstellung durch das Steuerventil der Figur 1,
die Figur 3
ein zweites Ausführungsbeispiel analog zur Darstellung der Figur 2 mit einer Steuerventilgliedführung im unteren Bereich, die über eine Drosselbohrung mit dem Entlastungsraum verbunden ist und bei dem der Drosselquerschnitt zwischen der Einspritzleitung und dem hydraulischen Arbeitsraum über einen Ringspalt zwischen dem Ventilglied des Steuerventils und der diesen führenden Bohrungswand gebildet ist,
die Figur 4
ein drittes Ausführungsbeispiel analog zur Darstellung der Figur 3, bei dem Abflachungen am Führungsdurchmesser des Steuerventilgliedes vorgesehen sind,
die Figur 5
ein viertes Ausführungsbeispiel analog zur Darstellung der Figur 3 mit einer hubgesteuerten Drossel zwischen den beiden Ventilsitzen am Steuerventil,
die Figur 6
ein fünftes Ausführungsbeispiel in einer Gesamtdarstellung, bei dem das Steuerventilglied einteilig ausgebildet ist und der zweite Ventilsitz zwischen dem Hochdruckkanal und der Entlastungsleitung als Schieberventil ausgebildet ist,
die Figur 7
ein sechstes Ausführungsbeispiel in einem Schnitt durch die Einspritzeinrichtung, bei dem eine Drossel in der Entlastungsleitung vorgesehen ist und
die Figur 8
ein siebentes Ausführungsbeispiel, bei zwischen dem Hochdruckzulauf und dem Ventilsitz eine zusätzliche Drosselstelle vorgesehen ist.
Six embodiments of the fuel injection device according to the invention for internal combustion engines are shown in the drawing and are explained in more detail in the following description. Show it
the figure 1
a first embodiment in an overall view, in which the throttle section between injection line and hydraulic working space is formed on the control valve through a throttle bore in the control valve member,
the figure 2
an enlarged sectional view through the control valve of Figure 1,
the figure 3
a second embodiment analogous to the representation of Figure 2 with a control valve member guide in the lower region, which is connected via a throttle bore to the discharge chamber and wherein the throttle cross-section between the injection line and the hydraulic working space via an annular gap between the valve member of the control valve and this leading bore wall is formed,
FIG. 4
a third embodiment analogous to the representation of Figure 3, in the flattening are provided on the guide diameter of the control valve member,
the figure 5
A fourth embodiment analogous to the representation of Figure 3 with a stroke-controlled throttle between the two valve seats on the control valve,
the figure 6
a fifth embodiment in an overall view, in which the control valve member is integrally formed and the second valve seat is formed between the high pressure passage and the discharge line as a slide valve,
the figure 7
a sixth embodiment in a section through the injector, in which a throttle is provided in the discharge line and
the figure 8
a seventh embodiment, is provided at between the high-pressure inlet and the valve seat, an additional throttle point.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Das in der Figur 1 dargestellte erste Ausführungsbeispiel der Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen weist eine Kraftstoffhochdruckpumpe 1 auf, die saugseitig über eine Kraftstoffförderleitung 3 mit einem kraftstoffgefüllten Niederdruckraum 5 und druckseitig über die Förderleitung 3 mit einem Hochdrucksammelraum 7 verbunden ist. Von diesem Hochdrucksammelraum 7 führen Einspritzleitungen 9 zu den einzelnen, in den Brennraum der zu versorgenden Brennkraftmaschine ragenden Einspritzventilen 11 ab, wobei zur Steuerung des Einspritzvorganges jeweils ein elektrisch betätigbares, als 3/2-Wegeventil ausgebildetes Steuerventil 13 an jedem Einspritzventil 11 vorgesehen ist.The illustrated in Figure 1 first embodiment of the fuel injection device for internal combustion engines has a high-pressure fuel pump 1, which is connected on the suction side via a fuel delivery line 3 with a fuel-filled low-pressure chamber 5 and the pressure side via the delivery line 3 with a high-pressure accumulator 7. From this high-pressure accumulation chamber 7 lead injection lines 9 to the individual, projecting into the combustion chamber of the engine to be supplied injection valves 11, wherein the Control of the injection process in each case an electrically actuated, designed as a 3/2-way valve control valve 13 is provided on each injection valve 11.

Dabei ist das Einspritzventil 11 mittels einer Spannmutter 15 axial gegen einen Ventilhaltekörper 17 verspannt, an dem ein seitlicher Hochdruckanschluß 19 vorgesehen ist, in den ein Rohrstutzen 21 der entsprechenden Einspritzleitung 9 eingesetzt ist. Der Ventilhaltekörper 17 weist eine axiale Durchgangsbohrung 23 auf, in die auf der dem Einspritzventil 11 abgewandten Seite ein kolbenförmiges Steuerventilglied 25 des Steuerventils 13 eingesetzt ist. Dieses als Doppelsitzventil ausgebildete Steuerventil 13 verbindet dabei einen von der Einspritzleitung 9 im Rohrstutzen 21 abführenden Verbindungskanal 27 mit einem den Ventilhaltekörper 17 axial durchdringenden Hochdruckkanal 29, der an der dem Einspritzventil 11 zugewandten Stirnfläche des Ventilhaltekörpers 17 in bekannter Weise an eine nicht näher dargestellte Druckleitung im Einspritzventil 11 mündet, die andererseits bis an einen von einer Ventilnadel 31 des Einspritzventils 11 aufsteuerbaren Einspritzquerschnitt des Einspritzventils 11 mündet. Dabei ist der Hochdruckkanal 29 über das Steuerventil 13 wechselnd mit der Einspritzleitung 9 oder einer Entlastungsleitung 33 verbindbar, die aus dem einspritzventilseitigen Teil der Durchgangsbohrung 23 und einer von dieser abführenden Rücklaufleitung gebildet ist und die in den Niederdruckraum 5 mündet. Die Verstellbewegung des Steuerventilgliedes 25 des Steuerventils 13 wird dabei von einem Magnetventil 35 gesteuert, das auf der dem Einspritzventil 11 abgewandten Seite in den Ventilhaltekörper 17 eingesetzt ist und das von einem elektrischen Steuergerät 37 angesteuert wird, das eine Vielzahl von Betriebsparametern der zu versorgenden Brennkraftmaschine verarbeitet.In this case, the injection valve 11 is clamped by means of a clamping nut 15 axially against a valve holding body 17 on which a lateral high pressure port 19 is provided, in which a pipe socket 21 of the corresponding injection line 9 is inserted. The valve holding body 17 has an axial through hole 23 into which a piston-shaped control valve member 25 of the control valve 13 is inserted on the side facing away from the injection valve 11. This formed as a double-seat valve control valve 13 connects a discharge from the injection line 9 in the pipe socket 21 connecting channel 27 with a valve holding body 17 axially penetrating the high-pressure channel 29 at the injection valve 11 facing the end face of the valve holding body 17 in a known manner to a not shown pressure line in Injection valve 11 opens, on the other hand opens up to a aufsteuerbaren by a valve needle 31 of the injection valve 11 injection cross section of the injection valve 11. In this case, the high pressure passage 29 via the control valve 13 is alternately connected to the injection line 9 or a discharge line 33, which is formed from the injection valve side part of the through hole 23 and a laxative from this return line and which opens into the low pressure chamber 5. The adjusting movement of the control valve member 25 of the control valve 13 is controlled by a solenoid valve 35 which is inserted on the side facing away from the injector 11 in the valve holding body 17 and which is controlled by an electrical control unit 37, which processes a variety of operating parameters of the engine to be supplied ,

Das in der Figur 2 vergrößert dargestellte Steuerventilglied 25 des Steuerventils 13 ist als Stufenkolben ausgebildet, dessen Querschnitt sich nach unten in Richtung Einspritzventil. 11 über zwei konisch ausgebildete Ringflächen verjüngt. Dabei ist eine erste obere Ringstirnfläche 39 im Bereich der Einmündung des Verbindungskanals 27 zur Einspritzleitung 9 vorgesehen. Eine zweite Ringstirnfläche bildet eine erste konische Ventildichtfläche 41, die mit einem ersten konischen Ventilsitz 43 zusammenwirkt, wobei dieser zwischen der Ventildichtfläche 41 und dem Ventilsitz 43 gebildete erste Dichtsitz die Einspritzleitung 9 gegenüber dem Hochdruckkanal 29 verschließt. An seinem unteren, dem Einspritzventil 11 zugewandten Ende weist das Steuerventilglied 25 eine Hülse 45 auf, an der eine zweite, der ersten Ventildichtfläche 41 zugewandte Ventildichtfläche 47 vorgesehen ist, die mit einem zweiten Ventilsitz 49 an der Wand der Durchgangsbohrung 23 zusammenwirkt. Dabei sind die Ventilsitzflächen 43 und 49 so ausgebildet, daß sie die Verstellbewegung des Steuerventilgliedes 25 in beiden Hubrichtungen begrenzen. Der zwischen der zweiten Ventildichtfläche 47 und der zweiten Ventilsitzfläche 49 gebildete zweite Dichtquerschnitt verschließt dabei die Verbindung zwischen dem Hochdruckkanal 29 und der zum Teil durch die Durchgangsbohrung 23 gebildeten Entlastungsleitung 33 in den Niederdruckraum 5.The control valve member 25 of the control valve 13, shown enlarged in FIG. 2, is designed as a stepped piston whose cross-section points downwards in the direction of the injection valve. 11 tapered over two conical annular surfaces. In this case, a first upper annular end face 39 is provided in the region of the junction of the connecting channel 27 to the injection line 9. A second annular end surface forms a first conical valve sealing surface 41, which cooperates with a first conical valve seat 43, said first sealing seat formed between the valve sealing surface 41 and the valve seat 43 closes the injection line 9 with respect to the high-pressure channel 29. At its lower, the injection valve 11 facing the end, the control valve member 25 has a sleeve 45 to which a second, the first valve sealing surface 41 facing valve sealing surface 47 is provided, which cooperates with a second valve seat 49 on the wall of the through hole 23. In this case, the valve seat surfaces 43 and 49 are formed so that they limit the adjustment movement of the control valve member 25 in both stroke directions. The second sealing cross-section formed between the second valve sealing surface 47 and the second valve seat surface 49 closes the connection between the high-pressure channel 29 and the relief line 33 formed in part through the through-bore 23 into the low-pressure space 5.

Zur Betätigung des Steuerventilgliedes 25 ist ein hydraulischer Arbeitsraum 51 vorgesehen, der durch die obere, dem Einspritzventil 11 abgewandte Stirnfläche 53 des Steuerventilgliedes 25 in der Bohrung 23 begrenzt ist. Auf der dem Steuerventilglied 25 abgewandten Seite ist der hydraulische Arbeitsraum 51 durch eine Zwischenscheibe 55 zum Magnetventil 35 begrenzt. In dieser Zwischenscheibe 55 ist ein vom Arbeitsraum 51 abführender Entlastungskanal 57 vorgesehen, der in einen in den Niederdruckraum 5 mündenden Rücklaufkanal 59 einmündet und der durch ein Ventilglied des Magnetventils 35 verschließbar ist. Dieses Ventilglied des Magnetventils 35 ist dabei als Ventilkugel 61 ausgebildet, die in einem an den Entlastungskanal 57 angrenzenden Ventilsitz geführt ist und die bei stromlos geschaltetem Magnetventil 35 den Entlastungkanal 57 durch die Kraft einer Magnetventilfeder 63 geschlossen hält. Die Ventilkugel 61 ist an einem Anker 65 des Magnetventils 35 angelenkt, der bei bestromtem Magnetventil 35 entgegen der Rückstellkraft der Feder 63 in der vom Arbeitsraum 51 abgewandten Richtung verschoben wird, so daß die Ventilkugel 61 von dem im Arbeitsraum 51 anstehenden Druck von ihrem Sitz abgehoben und der Entlastungskanal 57 zur Rücklaufleitung 59 aufgesteuert wird.For actuation of the control valve member 25, a hydraulic working chamber 51 is provided, which is limited by the upper, the injection valve 11 facing away from face 53 of the control valve member 25 in the bore 23. On the side facing away from the control valve member 25, the hydraulic working space 51 is delimited by an intermediate disk 55 to the solenoid valve 35. In this intermediate disk 55, a discharge channel 57 discharging from the working chamber 51 is provided, which leads into a return channel opening into the low-pressure chamber 5 59 opens and which can be closed by a valve member of the solenoid valve 35. This valve member of the solenoid valve 35 is formed as a valve ball 61, which is guided in a valve seat adjacent to the discharge channel 57 and the discharge port 57 is held closed by the force of a solenoid valve spring 63 at de-energized solenoid valve 35. The valve ball 61 is articulated to an armature 65 of the solenoid valve 35, which is displaced against the restoring force of the spring 63 in energized solenoid valve 35 in the direction away from the working space 51, so that the valve ball 61 is lifted from the pending in the working space 51 pressure from its seat and the discharge channel 57 is opened to the return line 59.

Zur Befüllung des hydraulischen Arbeitsraumes 51 mit unter hohem Druck stehenden Kraftstoff ist im Steuerventilglied 25 eine Füllbohrung 67 vorgesehen, die eine Drosselstelle 69 aufweist, deren Querschnitt kleiner als der Querschnitt des Entlastungskanals 57 ausgebildet ist. Dabei führt diese in die Stirnfläche 53 mündende Füllbohrung 67 unterhalb der ersten Ringstirnfläche 39 des Steuerventilgliedes 25 ab, so daß der hydraulische Arbeitsraum 51 über die Füllbohrung 67 jederzeit mit der Einspritzleitung 9 verbunden ist. Zusätzlich zu dieser Befüllung des hydraulischen Arbeitsraumes 51 gelangt ein Teil der Kraftstoffhochdruckmenge über den zwischen dem Steuerventilglied 25 und der Wand der Bohrung 23 verbleibenden Ringspalt 71 gedrosselt in den hydraulischen Arbeitsraum 51, so daß auch bei einem möglichen Verschluß der Füllbohrung 67 eine Notlauffunktion des Steuerventils 13 gewährleistet ist.For filling the hydraulic working chamber 51 with fuel under high pressure, a filling bore 67 is provided in the control valve member 25, which has a throttle point 69 whose cross section is smaller than the cross section of the discharge channel 57. In the process, this filling bore 67 opening into the end face 53 leads below the first annular end face 39 of the control valve member 25, so that the hydraulic working chamber 51 is connected at all times to the injection line 9 via the filling bore 67. In addition to this filling of the hydraulic working chamber 51, a portion of the high-pressure fuel passes through the remaining between the control valve member 25 and the wall of the bore 23 annular gap 71 throttled into the hydraulic working chamber 51, so that even with a possible closure of the filling bore 67 is an emergency operation of the control valve 13th is guaranteed.

Die in den Figuren 1 und 2 in einem ersten Ausführungsbeispiel gezeigte Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen arbeitet in folgender Weise. Beim Anlaufen des Systems wird zunächst über die Kraftstoffhochdruckpumpe 1 ein Kraftstoffhochdruck im gemeinsamen Hochdrucksammelraum 7 (Common Rail) aufgebaut, der sich über die verschiedenen Einspritzleitungen 9 bis an die jeweiligen Ventilhaltekörper 17 der Einspritzventile 11 fortsetzt. Das Magnetventil 35 ist vor Beginn der Einspritzphase stromlos geschaltet, so daß die Ventilkugel 61 des Magnetventils 35 den Entlastungskanal 57 verschlossen hält. Dabei wird der hydraulische Arbeitsraum 51 über die Füllbohrung 67 mit Kraftstoffhochdruck befüllt und preßt das Steuerventilglied 25 aufgrund des Flächenverhältnisses zwischen der Stirnfläche 53 und der ersten Ringstirnfläche 39 mit der ersten Ventildichtfläche 41 gegen den ersten Ventilsitz 43. Somit ist die Verbindung zwischen der Einspritzleitung 9 und dem an den Einspritzquerschnitt am Einspritzventil 11 mündenden Hochdruckkanal 29 verschlossen. Gleichzeitig ist der zweite Dichtquerschnitt zwischen der zweiten Ventildichtfläche 47 und dem zweiten Ventilsitz 49 geöffnet, so daß sich der Druck im Hochdruckkanal 29 bis auf einen bestimmten Restdruck in die Entlastungsleitung 33 entspannen kann. Soll eine Einspritzung am Einspritzventil 11 erfolgen, wird zunächst das Magnetventil 35 über das elektrische Steuergerät 37 bestromt, so daß der Anker 65 angezogen wird und die Ventilkugel 61 den Entlastungskanal 57 freigibt. Da der Querschnitt des Entlastungskanals 57 größer ist als der der Drosselstelle 69 in der Füllbohrung 67 entspannt sich der Druck im Arbeitsraum 51 sehr rasch über den Magnetventilraum in den Rücklaufkanal 59, so daß der an der Ringstirnfläche 39 anstehende Kraftstoffhochdruck nunmehr ausreicht, das Steuerventilglied 25 zu verschieben. Dabei wird das Steuerventilglied 25 bei dieser Öffnungshubbewegung derart verschoben, daß der erste Dichtquerschnitt zwischen der ersten Ventildichtfläche 41 und dem ersten Ventilsitz 43 nunmehr aufgesteuert wird und der zweite Dichtsitz zwischen der zweiten Ventildichtfläche 47 und dem zweiten Ventilsitz 49 durch Anlage des Steuerventilgliedes 25 am zweiten Ventilsitz 49 verschlossen wird. Dabei strömt nunmehr der in der Einspritzleitung 9 befindliche, unter hohem Druck stehende Kraftstoff am Steuerventilglied 25 entlang in den Hochdruckkanal 29 zum Einspritzventil 11 und hebt dort in bekannter Weise die Ventilnadel 31 entgegen der Rückstellkraft einer Ventilfeder von deren Nadelsitz, so daß der Kraftstoff am Einspritzventil 11 über die Einspritzöffnungen in den Brennraum der zu versorgenden Brennkraftmaschine eingespritzt wird.The fuel injection device for internal combustion engines shown in Figures 1 and 2 in a first embodiment operates in the following manner. When the system starts up, it first starts with the high-pressure fuel pump 1, a high-pressure fuel in common high-pressure accumulator 7 (common rail) constructed, which continues through the various injection lines 9 to the respective valve holding body 17 of the injectors 11. The solenoid valve 35 is de-energized prior to the start of the injection phase, so that the valve ball 61 of the solenoid valve 35 keeps the discharge channel 57 closed. In this case, the hydraulic working chamber 51 is filled via the filling bore 67 with high pressure fuel and presses the control valve member 25 due to the area ratio between the end face 53 and the first annular end face 39 with the first valve sealing surface 41 against the first valve seat 43. Thus, the connection between the injection line 9 and the closed to the injection cross section at the injection valve 11 high-pressure passage 29 closed. At the same time, the second sealing cross section between the second valve sealing surface 47 and the second valve seat 49 is opened, so that the pressure in the high pressure passage 29 can relax to a certain residual pressure in the relief line 33. If an injection takes place at the injection valve 11, first the solenoid valve 35 is energized via the electrical control unit 37, so that the armature 65 is attracted and the valve ball 61 releases the discharge channel 57. Since the cross section of the discharge channel 57 is greater than that of the throttle point 69 in the filling bore 67, the pressure in the working chamber 51 relaxes very quickly via the solenoid valve space in the return passage 59, so that the pending on the annular face 39 high fuel pressure is now sufficient, the control valve member 25 move. The control valve member 25 is displaced in this opening stroke movement such that the first sealing cross section between the first valve sealing surface 41 and the first valve seat 43 is now controlled and the second sealing seat between the second valve sealing surface 47 and the second valve seat 49 by conditioning the control valve member 25 on the second valve seat 49 is closed. In this case, now located in the injection line 9, under high pressure fuel flows on the control valve member 25 along the high pressure passage 29 to the injection valve 11 and lifts there in a known manner, the valve needle 31 against the restoring force of a valve spring of the needle seat, so that the fuel at the injection valve 11 is injected via the injection openings in the combustion chamber of the internal combustion engine to be supplied.

Die Hochdruckeinspritzung am Einspritzventil 11 wird durch erneutes stromlos schalten des Magnetventils 35 beendet, in dessen Folge die Magnetventilfeder 63 die Ventilkugel 61 an ihren Sitz am Entlastungskanal 57 zurückverschiebt, so daß - sich über die Füllbohrung 67 erneut ein Schließdruck im hydraulischen Arbeitsraum 51 aufbauen kann, der das Steuerventilglied 25 des als 3/2-Wegeventils ausgebildeten Steuerventils 13 erneut mit der ersten Ventildichtfläche 41 in Anlage an den ersten Ventilsitz 43 verschiebt. Somit ist die Verbindung der Einspritzleitung 9 zum Hochdruckkanal 29 wieder verschlossen. Gleichzeitig wird der zweite Dichtsitz zwischen der zweiten Ventildichtfläche 47 und dem zweiten Ventilsitz 49 erneut aufgesteuert, so daß sich der im Hochdruckkanal 29 befindliche Kraftstoffhochdruck sehr rasch in die Entlastungsleitung 33 entspannt, was ein rasches Nadelschließen am Kraftstoffeinspritzventil 11 zur Folge hat.The high-pressure injection at the injection valve 11 is switched off by again de-energize the solenoid valve 35, as a result, the valve spring 61, the valve ball 61 zurückverschiebt back to their seat on the discharge channel 57 so that - over the filling bore 67 again a closing pressure in the hydraulic working chamber 51 can build up the control valve member 25 of the control valve 13 designed as a 3/2-way valve moves again with the first valve sealing surface 41 in abutment against the first valve seat 43. Thus, the connection of the injection line 9 to the high-pressure channel 29 is closed again. At the same time, the second sealing seat between the second valve sealing surface 47 and the second valve seat 49 is opened again, so that the high pressure channel 29 located in the high pressure channel 29 relaxes quickly in the discharge line 33, which has a rapid needle closing on the fuel injection valve 11 result.

Das in der Figur 3 dargestellte zweite Ausführungsbeispiel der erfindungsgemäßen Kraftstoffeinspritzeinrichtung unterscheidet sich zum ersten Ausführungsbeispiel in der Art der Ausbildung des Steuerventilgliedes 25 des Steuerventils 13. Das Steuerventilglied 25 ist dabei nunmehr einteilig ausgebildet und in einer in der Durchgangsbohrung 23 des Ventilhaltekörpers 17 eingesetzten Zylinderbüchse 73 geführt. Dabei bildet ein unterer, dem Magnetventil 35 abgewandter Querschnittsteil des Steuerventilgliedes 25 einen Führungsteil 75 des Steuerventilgliedes 25, der mit geringem Spiel im Innendurchmesser der zylinderbüchse 73 gleitet. Zudem erfolgt die Befüllung des hydraulischen Arbeitsraumes 51 im zweiten Ausführungsbeispiel nur noch über den Ringspalt 71 zwischen dem Steuerventilglied 25 und der Innenwand der Zylinderbüchse 73. Der Ringspalt 71 ist dabei als Drosselstelle derart ausgebildet, daß der gesamte Durchflußquerschnitt kleiner ausgebildet ist als der Querschnitt des Entlastungskanals 57 des hydraulischen Arbeitsraumes 51. Die Kraftstoffabfuhr aus einem, dem zweiten Dichtsitz zwischen der Ventildichtfläche 47 und dem Ventilsitz 49 nachgeschalteten Entlastungsraum 77 in die Entlastungsleitung 23, 33 erfolgt dabei über eine von der der oberen Stirnfläche 53 abgewandten unteren Stirnfläche 79 im Steuerventilglied 25 ausgehenden Sackbohrung 81, von der eine als Drosselbohrung ausgebildete Querbohrung 83 abführt, die in den Entlastungsraum 77 mündet.The illustrated in Figure 3 second embodiment of the fuel injection device according to the invention differs from the first embodiment in the manner of forming the control valve member 25 of the control valve 13. The control valve member 25 is now integrally formed and guided in a cylinder sleeve 73 inserted into the through hole 23 of the valve holding body 17 , In this case, a lower, the solenoid valve 35 facing away from cross-sectional part of the control valve member 25 forms a guide member 75 of the control valve member 25, which slides with little clearance in the inner diameter of the cylinder sleeve 73. In addition, the filling of the hydraulic working chamber 51 in the second embodiment takes place only via the annular gap 71 between the control valve member 25 and the inner wall of the cylinder liner 73. The annular gap 71 is designed as a throttle point such that the entire flow area is smaller than the cross section of the discharge channel 57 of the hydraulic working chamber 51. The fuel discharge from a, the second sealing seat between the valve sealing surface 47 and the valve seat 49 downstream relief space 77 in the discharge line 23, 33 takes place via a remote from the upper end face 53 lower end face 79 in the control valve member 25 outgoing blind hole 81, from which a trained as a throttle bore transverse bore 83 dissipates, which opens into the discharge chamber 77.

Bei dem in der Figur 4 dargestellten dritten Ausführungsbeispiel erfolgt der Kraftstoffübertritt vom Hochdruckkanal 29 in die Entlastungsleitung 23, 33 über einen Flächenanschliff 85 an der Umfangsfläche des Steuerventilgliedes 25 im Führungsbereich 75. Dabei ist die axiale Länge dieses rechtwinklig ausgebildeten Flächenanschliffs 85 so ausgeführt, daß der dem Magnetventil 35 zugewandte obere Teil des Flächenanschliffes ständig mit dem Hochdruckkanal 29 verbunden ist, während das untere eine Steuerkante 87 bildende Ende des Flächenanschliffes 85 erst bei Anlage der ersten Ventildichtfläche 41 am ersten Ventilsitz 43 aus der Überdekkung mit der Zylinderbüchse 73 austaucht, was zusätzlich zur Systemsicherheit der Kraftstoffeinspritzeinrichtung beiträgt.In the third embodiment shown in Figure 4, the fuel passage from the high pressure passage 29 in the discharge line 23, 33 via a Flächenanschliff 85 on the peripheral surface of the control valve member 25 in the guide portion 75. The axial length of this rectangular trained Flächenanschliffs 85 is designed so that the upper part of the Flächenanschliffes facing the solenoid valve 35 is constantly connected to the high pressure passage 29, while the lower a control edge 87 forming end of the Flächenanschliffes 85 only when planting the first valve sealing surface 41 on the first valve seat 43 from the Überdekkung with the cylinder liner 73 emerges, which in addition to System safety of the fuel injector contributes.

Das in der Figur 5 dargestellte vierte Ausführungsbeispiel der Kraftstoffeinspritzeinrichtung ist analog zum in der Figur 3 dargestellten zweiten Ausführungsbeispiel aufgebaut und weist zusätzlich eine hubgesteuerte Drossel zwischen dem ersten und zweiten Dichtsitz auf. Diese hubgesteuerte Drossel ist durch einen Ringbund 89 am Steuerventilglied 25 ausgebildet, dessen Übergangsbereiche zum angrenzenden Schaftteil des Steuerventilgliedes 25 konisch ausgebildet sind. Dieser Ringbund 89 wirkt dabei mit einem Ringsteg 91 an der Wand der Durchgangsbohrung 23 derart zusammen, daß er bei am ersten Ventilsitz 43 anliegender ersten Ventildichtfläche 41 mit diesem in Überdeckung steht. Während der Verstellhubbewegung des Steuerventilgliedes 25 in Richtung Magnetventil 35 taucht der Ringbund 89 stetig aus der Überdeckung mit dem Ringsteg 91 aus und gibt dabei während des Aufsteuerns der Verbindung zwischen der Einspritzleitung 9 bzw. dem Verbindungskanal 27 mit dem Hochdruckkanal 29 stetig einen größeren Überströmquerschnitt frei. Somit kann die zum Einspritzventil strömende Kraftstoffhochdruckmenge zu Beginn des Einspritzvorganges gedrosselt werden, wodurch sich der Einspritzverlauf am Einspritzventil 11 formen läßt.The illustrated in Figure 5 fourth embodiment of the fuel injection device is analogous to that in the figure 3 illustrated second embodiment and additionally has a stroke-controlled throttle between the first and second sealing seat. This stroke-controlled throttle is formed by an annular collar 89 on the control valve member 25, whose transition regions to the adjacent shaft portion of the control valve member 25 are conical. This annular collar 89 acts together with an annular web 91 on the wall of the through hole 23 such that it is in the first valve seat 43 abutting first valve sealing surface 41 with this in coverage. During the Verstellhubbewegung of the control valve member 25 in the direction of the solenoid valve 35 of the annular collar 89 emerges steadily from the overlap with the annular web 91, while during the opening of the connection between the injection line 9 and the connecting channel 27 with the high-pressure channel 29 steadily a larger overflow free. Thus, the fuel high pressure amount flowing to the injection valve can be throttled at the beginning of the injection process, whereby the injection curve can be formed on the injection valve 11.

Das in der Figur 6 in einer vereinfachten Gesamtdarstellung gezeigte fünfte Ausführungsbeispiel der Kraftstoffeinspritzeinrichtung unterscheidet sich zu den vorangegangenen Ausführungsbeispielen ebenfalls durch die Ausgestaltung des Steuerventilgliedes 25. Dabei ist der den Drosselquerschnitt zwischen der Einspritzleitung 9 und dem Arbeitsraum 51 bestimmende Ringspalt 71 durch eine Ringnut 93 in einen oberen Drosselspalt 95 und einen unteren Drosselspalt 97 unterteilt. Über die axiale Erstreckung der Ringnut 93 läßt sich nunmehr der Durchfluß am Ringspalt 71 zwischen Einspritzleitung 9 und Arbeitsraum 51 genau einstellen. Der den Überströmquerschnitt zwischen dem Hochdruckkanal 29 und der Entlastungleitung 33 steuernde zweite Dichtsitz ist beim fünften Ausführungsbeispiel als Schieberventilsitz ausgebildet. Dazu weist das Steuerventilglied 25 an seinem unteren dem Einspritzventil 11 zugewandten Ende einen Schieberkopf 99 auf, dessen Außendurchmesser bis auf ein sehr geringes Spiel dem Durchmesser der Durchgangsbohrung 23 im Führungsbereich 75 entspricht. Dabei bildet die obere, dem Magnetventil 35 zugewandte Begrenzungskante des Schieberkopfes 99 eine Ventilsteuerkante 101, die mit dem Führungsabschnitt 75 der Durchgangsbohrung 23 zusammenwirkt und deren Eintauchen in die Überdeckung mit dem Führungsabschnitt 75 der Durchgangsbohrung 23 das Zusteuern der Verbindung zwischen Hochdruckkanal 29 und Entlastungsleitung 33 steuert. Zudem ist der Ventilsteuerkante 101 des Schieberkopfes 99 ein weiterer Ringbund 103 am Steuerventilglied 25 vorgeschaltet, der eine Abflußdrosselstelle für den aus dem Hochdruckkanal 29 in die Entlastungsleitung 33 abströmenden Hochdruckkraftstoff bildet. Die Hubbegrenzung des Steuerventilgliedes 25 in Richtung Magnetventil 35 erfolgt beim fünften Ausführungsbeispiel durch die Anlage der oberen Stirnfläche 53 des Steuerventilgliedes 25 an einer den hydraulischen Arbeitsraum 51 begrenzenden Stirnwand 105.The fifth embodiment of the fuel injection device shown in Figure 6 in a simplified overall illustration also differs from the previous embodiments by the design of the control valve member 25. Here, the throttle cross-section between the injection line 9 and the working chamber 51 defining annular gap 71 by an annular groove 93 in a upper throttle gap 95 and a lower throttle gap 97 divided. Over the axial extent of the annular groove 93, the flow at the annular gap 71 between injection line 9 and working chamber 51 can now be adjusted precisely. The second sealing seat controlling the overflow cross section between the high-pressure channel 29 and the discharge line 33 is designed as a slide valve seat in the fifth exemplary embodiment. For this purpose, the control valve member 25 at its lower the Injection valve 11 facing the end of a slide head 99, whose outer diameter corresponds to the diameter of the through hole 23 in the guide portion 75 except for a very small clearance. In this case, the upper, the solenoid valve 35 facing the boundary edge of the slide head 99 forms a valve control edge 101, which cooperates with the guide portion 75 of the through hole 23 and their immersion in the overlap with the guide portion 75 of the through hole 23 controlling the connection between the high pressure passage 29 and relief line 33 controls , In addition, the valve control edge 101 of the slide head 99 is preceded by a further annular collar 103 on the control valve member 25, which forms a Abflußdrosselstelle for flowing out of the high-pressure passage 29 in the discharge line 33 high-pressure fuel. The stroke limit of the control valve member 25 in the direction of the solenoid valve 35 is effected in the fifth embodiment by the contact of the upper end face 53 of the control valve member 25 on a hydraulic working space 51 delimiting end wall 105th

Das in der Figur 7 dargestellte sechste Ausführungsbeispiel der Kraftstoffeinspritzeinrichtung ist analog zum in der Figur 3 gezeigten zweiten Ausführungsbeispiel aufgebaut und weist zusätzlich zu diesem eine weitere Drosselstelle in der Entlastungsleitung 33 auf. Diese Drosselstelle ist dabei durch einen in die Entlastungsleitung 33 eingesetzten Drosseleinsatz 107 gebildet, dessen Durchflußquerschnitt so ausgelegt ist, daß am Einspritzende das Schließen des Einspritzventils unterstützt und eventuelles Nacheinspritzen verhindert wird. Zudem kann somit der am Einspitzende im Hochdruckkanal 29 verbleibende Restdruck des Kraftstoffes derart eingestellt werden, daß Kavitationsschäden vermieden werden können. Dabei wird der Kraftstoff aus der Durchgangsbohrung 23 über die Entlastungsleitung 33 zunächst zum Magnetventil 35 geführt und von dort über den Rücklaufkanal 59 zum Niederdruckraum 5 abgeleitet. Dieses Durchströmen des Magnetventils 35 hat dabei den Vorteil, daß der Magnetventilraum während des Betriebs der Kraftstoffeinspritzeinrichtung gekühlt und entlüftet werden kann.The sixth exemplary embodiment of the fuel injection device shown in FIG. 7 is constructed analogously to the second exemplary embodiment shown in FIG. 3 and has, in addition to this, a further throttle point in the relief line 33. This throttle point is formed by a throttle insert 107 inserted into the relief line 33, whose flow area is designed so that at the injection end, the closing of the injector supported and possible Nacheinspritzen is prevented. In addition, thus remaining at the Einspitzende in the high pressure passage 29 remaining pressure of the fuel can be adjusted so that cavitation damage can be avoided. The fuel from the through hole 23 via the discharge line 33 is first led to the solenoid valve 35 and from there via the return passage 59th derived to the low pressure chamber 5. This flow through the solenoid valve 35 has the advantage that the solenoid valve chamber can be cooled and vented during operation of the fuel injector.

In der Figur 8 ist ein siebentes Ausführungsbeispiel dargestellt, dessen Aufbau im wesentlichen dem in der Figur 4 dargestellten dritten Ausführungsbeispiel entspricht.
Dabei ist beim siebenten Ausführungsbeispiel gemäß der Figur 8 eine zusätzliche Drosselstelle 111 zwischen dem Hochdruckzulaufkanal 27 und dem Ventilsitz 43 vorgesehen, über die der Durchfluß des Einspritzkraftstoffes in der Öffnungshubphase, insbesondere an dessen Beginn steuerbar ist und durch die die Schließhubbewegung des Steuerventilgliedes 25 gedämpft werden kann. Diese Drosselstelle 111 ist dabei im siebenten Ausführungsbeispiel als Engspalt zwischen der Innenwand der Zylinderbüchse 73 und dem Steuerventilglied 25 ausgebildet, wobei am Steuerventilglied 25 ein Absatz 113 vorgesehen ist, durch den der Engspalt nach einem bestimmten Öffnungshub des Steuerventilgliedes 25 in einen größeren Durchflußquerschnitt aufgesteuert wird.FIG. 8 shows a seventh exemplary embodiment, the structure of which essentially corresponds to the third exemplary embodiment shown in FIG.
In the seventh embodiment according to FIG 8, an additional throttle point 111 is provided between the high-pressure inlet channel 27 and the valve seat 43, via which the flow of the injection fuel in the Öffnungshubphase, in particular at its beginning is controlled and by the Schließhubbewegung the control valve member 25 can be attenuated , This throttling point 111 is formed in the seventh embodiment as a narrow gap between the inner wall of the cylinder liner 73 and the control valve member 25, wherein the control valve member 25 a paragraph 113 is provided, through which the narrow gap is opened after a certain opening stroke of the control valve member 25 in a larger flow area.

Claims (11)

  1. Fuel injection device for internal combustion engines having a common high-pressure collection space (7) which can be filled with fuel from a high-pressure pump (1) and is connected via injection lines (9) to injection valves (11), the opening and closing movements of which are in each case controlled by an electrically actuated control valve (13) arranged at the injection valve (11), the control valve (13) being designed as a 3/2 directional control valve, having a control valve member (25), which includes two sealing surfaces (41, 47) and connects a high-pressure passage (29), which opens out at an injection opening of the injection valve (11), to the injection line (9), or a pressure relief line (33), it being possible for the control valve member (25) to be actuated, counter to a restoring force, by a pressure which is present in a working space (51), the working space (51) being designed as a hydraulic working space (51), which can be filled with high-pressure fuel, at the control valve member (25) of the 3/2 directional control valve (13), which acts on the control valve member (25), counter to a hydraulic opening force acting thereon, in the closing direction of a cross section of through-flow between injection line (9) and high-pressure passage (29) and can be opened into a pressure relief space (59), characterized in that the pressure in the working space (51) can be controlled by a constant incoming flow and a controlled outgoing flow, in that the hydraulic working space (51) is delimited by an upper end face (53) of the piston-like control valve member (25), in that the working space (51) is continuously connected, via a throttling cross section (69, 71), to the injection line (9), in that a closable pressure relief passage (57), the cross section of which is larger than the throttling cross section (69, 71) to the injection line (9), leads away from the working space (51), in that the pressure relief passage (57) can be opened and closed by means of an electrical actuating valve (35), and in that at the control valve member (25) in the region of the overlap with the injection line (9) there is provided an annular end face (39), on which the high-pressure fuel acts in the opposite direction to the pressure on the control valve member (25) which is present in the working space (51), in order to generate the hydraulic opening force on the control valve member (25) and, when the pressure relief passage (57) is opened, to move the control valve member (25) into the position in which the cross section of through-flow between the injection line (9) and the high-pressure passage (29) is open.
  2. Fuel injection device according to Claim 1, characterized in that the electrical actuating valve (35) is designed as a solenoid valve, the actuating member of which is formed by a valve ball (61) which interacts with a valve seat adjoining the pressure relief passage (57).
  3. Fuel injection device according to Claim 1, characterized in that the throttling cross section to the injection line (9) is formed by a throttling bore (69) in the control valve member (25).
  4. Fuel injection device according to Claim 1, characterized in that the 3/2 directional control valve (13) is designed as a double seat valve, having a first sealing seat (41, 43), which controls the through-flow between the injection line (9) and the high-pressure passage (29), and a second sealing seat (47, 49), which controls the through-flow between the high-pressure passage (29) and the pressure relief line (33), the two valve seat faces (43, 49) being arranged facing one another and in each case delimiting the adjustment movement of the control valve member (25) in a lifting direction.
  5. Fuel injection device according to Claim 1, characterized in that the throttling cross section between the working space (51) and the injection line (9) is formed as an annular gap (71) between the circumferential surface of the piston-like control valve member (25) and the wall of a cylinder bore (23) which guides the latter.
  6. Fuel injection device according to Claim 1, characterized in that the piston-like control valve member (25) is of single-piece design.
  7. Fuel injection device according to Claim 4, characterized in that an aperture opening between the second sealing seat (47, 49) and the pressure relief line (33) is provided at the control valve member (25).
  8. Fuel injection device according to Claim 7, characterized in that the aperture opening is designed as a blind bore (81) which opens out into the pressure relief line (23, 33) and into which a transverse bore (83) opens out.
  9. Fuel injection device according to Claim 7, characterized in that the aperture opening is designed as a ground surface (85) on the control valve member (25), which is only opened after closure of the transition cross section between the injection line (9) and the high-pressure passage (29).
  10. Fuel injection device according to Claim 4, characterized in that a lift-controlled throttle (89, 91), which throttles the quantity of high-pressure fuel flowing from the injection line (9) to the high-pressure passage (29) in a first phase of the injection operation, is provided between the first and second sealing seats (43, 49).
  11. Fuel injection device according to Claim 1, characterized in that a throttling location (107) is inserted into the pressure relief line (33) which can be opened by the control valve (13).
EP97943768A 1997-01-21 1997-09-13 Fuel injection device for internal combustion engines Expired - Lifetime EP0898650B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19701879 1997-01-21
DE19701879A DE19701879A1 (en) 1997-01-21 1997-01-21 Fuel injection device for internal combustion engines
PCT/DE1997/002053 WO1998031933A1 (en) 1997-01-21 1997-09-13 Fuel injection device for internal combustion engines

Publications (2)

Publication Number Publication Date
EP0898650A1 EP0898650A1 (en) 1999-03-03
EP0898650B1 true EP0898650B1 (en) 2006-11-22

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US (1) US6431148B1 (en)
EP (1) EP0898650B1 (en)
JP (1) JP3980069B2 (en)
DE (2) DE19701879A1 (en)
WO (1) WO1998031933A1 (en)

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AT1626U1 (en) * 1995-04-05 1997-08-25 Avl Verbrennungskraft Messtech STORAGE INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINES
AT408134B (en) * 1995-06-06 2001-09-25 Avl Verbrennungskraft Messtech STORAGE INJECTION SYSTEM FOR DIESEL INTERNAL COMBUSTION ENGINES
GB9616521D0 (en) 1996-08-06 1996-09-25 Lucas Ind Plc Injector
FI101739B1 (en) 1996-08-16 1998-08-14 Waertsila Nsd Oy Ab An injection valve
DE19706467C1 (en) 1997-02-19 1998-03-26 Daimler Benz Ag Fuel injector for multi-cylinder IC engines
DE19744723A1 (en) 1997-10-10 1999-04-15 Bosch Gmbh Robert Fuel injector
IT1296143B1 (en) 1997-11-18 1999-06-09 Elasis Sistema Ricerca Fiat CONTROL DEVICE FOR A FUEL INJECTOR FOR INTERNAL COMBUSTION ENGINES.

Also Published As

Publication number Publication date
JP2000507327A (en) 2000-06-13
DE19701879A1 (en) 1998-07-23
WO1998031933A1 (en) 1998-07-23
DE59712768D1 (en) 2007-01-04
EP0898650A1 (en) 1999-03-03
US6431148B1 (en) 2002-08-13
JP3980069B2 (en) 2007-09-19

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