EP1509694B1 - High-pressure accumulator for fuel injection systems with integrated pressure control valve - Google Patents

High-pressure accumulator for fuel injection systems with integrated pressure control valve Download PDF

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Publication number
EP1509694B1
EP1509694B1 EP03709622A EP03709622A EP1509694B1 EP 1509694 B1 EP1509694 B1 EP 1509694B1 EP 03709622 A EP03709622 A EP 03709622A EP 03709622 A EP03709622 A EP 03709622A EP 1509694 B1 EP1509694 B1 EP 1509694B1
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EP
European Patent Office
Prior art keywords
pressure
low
regulating valve
fuel injection
injection system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03709622A
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German (de)
French (fr)
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EP1509694A1 (en
Inventor
Kurt Frank
Werner Wagner
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/005—Pressure relief valves
    • F02M63/0052—Pressure relief valves with means for adjusting the opening pressure, e.g. electrically controlled
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • accumulator injection systems are used today for injecting the fuel in addition to pump-nozzle systems and pump-line-nozzle systems.
  • These accumulator injection systems include a high pressure accumulator which is supplied with high pressure fuel via a high pressure pump.
  • the high-pressure pump is the interface between the high-pressure part and the low-pressure part of the injection system.
  • the high-pressure pump can be assigned a pressure regulating valve, which serves on the one hand to open at high pressure in the high-pressure reservoir, so that fuel flows from this via a manifold back to the fuel tank and on the other hand to seal the high-pressure side against the low-pressure side at too low pressure in the high-pressure storage space.
  • Fig. 9 is a pressure regulating valve known.
  • the pressure control valve is used on a high-pressure pump, see page 267, Figure 7 of the same publication.
  • the pressure regulating valve comprises a ball valve, which contains a ball-shaped closing body.
  • an armature is received, which is acted upon on the one hand by a compression spring and the other hand, an electromagnet is arranged opposite.
  • the armature of the pressure control valve is lapped around the lubrication and cooling of fuel.
  • the pressure control valve If the pressure control valve is not activated, the high-pressure reservoir or the outlet of the high-pressure pump is subjected to high pressure via the high-pressure inlet to the pressure control valve. Since the electroless electromagnet exerts no force outweighs the High pressure force against the force of the compression spring, so that the pressure regulating valve is opened and this remains more or less open depending on the amount of fuel delivered.
  • the pressure control valve is activated, i. E. when the electromagnet is energized, the pressure in the high-pressure circuit is increased.
  • a magnetic force is generated in addition to the force exerted by the compression spring.
  • the pressure control valve is closed until there is an equilibrium of forces between the high-pressure force on the one hand and the spring force and the magnetic force on the other hand.
  • the magnetic force of the electromagnet is proportional to the driving current I of the magnetic coils within the pressure regulating valve.
  • the drive current I can be clocked by pulse width modulation.
  • the pressure control valve for example, flanged laterally to the high-pressure pump.
  • both the high-pressure accumulator (common rail) and the pressure control valve are each formed as separate components.
  • these separately formed components of the storage injection system have high production costs due to the precise production engineering of their high-pressure side sealing points.
  • sealing elements are to be provided on the high-pressure side sealing points, which are able to cope with the mechanical stresses occurring at high-pressure-side sealing points. Due to the pressure level prevailing on the high pressure side, leaks inevitably occur at the high pressure side sealing points in the course of operation of the accumulator injection system.
  • control seat represents the point at which a closing element designed, for example, as a spherical closing body is pressed into a seat by an anchor part of the pressure regulating valve.
  • This seat determines the air gap between the armature plate and an end face of the magnet core which adjusts itself in a pressure control valve, which is controlled via a solenoid valve.
  • the more accurate the air gap between these components of the pressure control valve can be formed the more accurate Pressure difference .DELTA.p corresponding to a tolerance set to the pressure regulating valve can be achieved.
  • Deformed by the seat, in which the ball-shaped closing element is pressed by an excessive heating due to uneven temperature distribution it turns after prolonged operation and associated temperature increase in the high-pressure reservoir a due to the changing air gap of the magnetic components within the pressure control valve changing air gap.
  • the pressure tolerance ⁇ p proportional to the magnet current I is negatively influenced, so that the control accuracy of a component of a storage injection system sealed from separate components on the high pressure side decreases.
  • a device for discharging fluid from a system under high pressure, in particular for discharging fuel from a rail of a common rail engine is known from DE-A 199 52 774.
  • the system described has at least one outlet opening, which can be closed by a valve device.
  • the sealing point between the high-pressure components of a storage injection system namely the high-pressure accumulator and the pressure control valve can be moved from the high-pressure critical side to the less critical low pressure side.
  • the installation of the pressure control valve in the high-pressure reservoir with low-pressure side seal makes a high-pressure side seal, which is exposed to high mechanical loads and there are adjusting leaks entailed unnecessary.
  • the seat for the closing element for example formed as a valve ball on the pressure control valve, can be laid in an end face of the high-pressure reservoir. This allows a good heat dissipation, since the seat is solid, a good heat transfer in the material of the high-pressure accumulator space, made possible. Since a homogeneous temperature distribution at the high-pressure storage space can be achieved with the solution according to the invention, there is no decrease in the hardness of the material due to strong heating, which considerably increases the strength of the high-pressure storage space configured according to the invention.
  • the seat for the to be controlled via the pressure control valve closing element can be incorporated into the end face of the high pressure storage space.
  • manufacturing technology easily produced blind hole bore can be produced.
  • the Umbangs simulation the blind hole is advantageous-wise in abutment with an end face on the pressure control valve, so that a further heat dissipation possibility pictorial material connection is created.
  • FIG. 1 shows the components of a fuel injection system with high-pressure storage space.
  • the fuel injection system 1 shown in FIG. 1 comprises a fuel tank 2 in which fuel corresponding to a fuel level 3 is located. Below the fuel level 3 within the fuel tank 2, a pre-filter 4 is arranged, which is connected upstream of a pre-feed unit 5.
  • the pre-feed unit 5 conveys the fuel sucked in via the prefilter 4 from the fuel tank 2 via a fuel filter 6 into a low-pressure line section 7, which opens into a high-pressure delivery unit 8.
  • the high-pressure delivery unit 8 which may be, for example, a high-pressure pump, is controlled via a control line 9 by a central control unit 14, which is only shown schematically here.
  • the high-pressure delivery unit 8 comprises a pressure regulating valve 12 flanged to it with an electrical connection 14, which is likewise actuated via the control unit 13 via the central control device 14. From the high-pressure delivery unit 8 branches off a high-pressure inlet, via which a tubular configured high-pressure accumulator chamber 15 (common rail) is acted upon by high-pressure fuel. Furthermore, a fuel return line 11 branches off from the high-pressure delivery unit 8, which discharges into a return 17, which in turn leads excess, outflowing fuel back into the fuel tank 2.
  • the pressure sensor 16 is in turn connected via a pressure signal line 25 with a central signal line 24 in connection, which in turn extends from the control unit 14 again.
  • the high-pressure feed lines 18 open at the respective inlet port 20 of the injector of the fuel injectors 19.
  • the fuel injectors 19 in turn include actuators, which may be designed as piezo actuators, mechanical-hydraulic translators or as solenoid valves and initiate the injection operations in a corresponding order.
  • the actuators of the individual fuel injectors 19 are also connected via Aktoran Kunststoffungs effet 22 with the central signal line 24, which emanates from the schematically represented central control unit 14, in connection.
  • the individual fuel injectors 19 return lines 21, which also open into the already mentioned return 17 to the fuel tank 1, so that, for example, taxed-off control volumes can flow into the fuel tank 2.
  • control unit 14 From the control unit 14 branches in addition to the already mentioned control line 13 for controlling an electromagnet contained in the pressure control valve 12 and a control line 9 for the high-pressure delivery unit 8 and a pressure sensor line 25 to the pressure sensor 16 of the high-pressure accumulator chamber 15, a drive line 26 from which accommodated in the fuel tank 2 Pre-feed unit 5 can be controlled.
  • the central control unit 14 of the fuel injection system also receives signals from a crankshaft sensor 27, which serves to detect the rotational position of the internal combustion engine, signals from a camshaft sensor 28, via which the corresponding phase position of the internal combustion engine can be determined and input signals of an accelerator pedal sensor 29.
  • the central control unit 14 signals characterizing the boost pressure 30 via the central signal line 24 via a corresponding sensor accommodated in the intake tract of the internal combustion engine.
  • FIG. 2 shows the high-pressure reservoir of the fuel injection system in longitudinal section.
  • the high-pressure accumulator chamber 15 substantially encloses a cavity 33.
  • the high-pressure accumulator chamber 15 shown in FIG. 2 is designed as a separate component and comprises on its first end face 37 an insert element 39 designed as a closure, to which the return line 17 shown in FIG. 1 can be connected to the fuel tank ,
  • the high-pressure storage space 15 on its second end face 38 comprises a high-pressure port 40, to which the high-pressure inlet 10 shown in FIG. 1 can be connected.
  • the pressure sensor 16 shown in FIG. 1 is accommodated on its outer peripheral surface and is connected to the control unit 14 via the pressure sensor line 25 shown in FIG. 1 (see illustration according to FIG. 1).
  • connection stubs 34 are formed on the peripheral surface of the high-pressure accumulator space, to which the high-pressure supply lines 18 can be connected to the fuel injectors 19 (cf. illustration according to FIG. 1).
  • the connecting pieces 34 each enclose transverse bores 35, which are in communication with the cavity 33 of the high-pressure reservoir 15 and via which the high-pressure fuel from the high-pressure reservoir 15 to the individual fuel injectors 19 forward.
  • mounting tabs 36 are also forged or welded, via which the high-pressure accumulator chamber 15 in the cylinder head area of a self-igniting internal combustion engine can be connected to this.
  • the high-pressure accumulator chamber 15 shown in FIG. 2 comprises five connecting stubs 34, so that five high-pressure supply lines 18 to the fuel injectors 19 of a self-igniting internal combustion engine can be supplied with fuel under high pressure.
  • the high-pressure accumulator 15 shown as a separate component in Figure 2 can of course be designed both to supply a four-cylinder autoignition internal combustion engine as well as to supply a six- or eight-cylinder internal combustion engine with fuel.
  • Figure 3 shows a high-pressure side in the high-pressure reservoir sealed electrically controlled pressure control valve according to the prior art.
  • the pressure regulating valve shown in section in FIG. 3 contains an electrical connection 41, which can be clipped onto annular grooves of a housing body or molded onto it.
  • an electromagnet 46 is arranged within the housing body.
  • the electromagnet 46 opposite an armature plate 42 is arranged, which is acted upon by a compression spring 44.
  • the anchor plate 42 and the compression spring 44 are enclosed by an approximately bell-shaped use 43.
  • the anchor plate 42 is in communication with an anchor member 45 which has a taper in the form of a truncated cone at the end opposite the anchor plate 42.
  • the tapered end of the anchor member 45 acts on a here formed as a valve ball closing element 47, which is received in a valve seat 49.
  • a high-pressure side seal 48 is provided with reference numeral 48, with which the pressure control valve shown in section can be arranged on both a high pressure pumping unit for a high pressure pump or at a high pressure reservoir.
  • the designated by reference numeral 48 high-pressure side seal requires high processing quality, minimum tolerances and is exposed to extremely high mechanical stresses during operation and therefore represents a weak point of a fuel injection system for self-igniting internal combustion engines with increasing life.
  • FIG. 4 shows a pressure regulating valve which can be sealed at the low pressure side of a high pressure storage space.
  • both the high-pressure storage space 15 and the pressure regulating valve 57 emerge in a longitudinal section.
  • the high-pressure accumulator space 15 is formed in a wall thickness adapted to the prevailing pressure level in this chamber. According to the number of fuel injectors 19 to be supplied with fuel of a self-igniting internal combustion engine 15 connecting pieces 34 are formed on the outer peripheral surface of the high pressure accumulator chamber, which are each traversed by a transverse bore 35. Via the transverse bores 35, the high-pressure fuel from the cavity 33 of the high pressure accumulator chamber 15 flows via the connecting pieces 34 into the respective high pressure supply lines 18 to the injectors 19, which inject the fuel into the combustion chambers of the internal combustion engine to be supplied.
  • a bore 52 for example, designed as a blind hole, is formed at one end of the high-pressure storage chamber 15.
  • the blind hole 52 at one end of the high-pressure accumulator 15 forms a low-pressure region in this mounted pressure control valve 57.
  • the low-pressure region is assigned a low-pressure connection 51, via which low-pressure region 52, 51 emerging from the cavity 33 of the high-pressure accumulator 15 exiting fuel in the low pressure region of the fuel injection system, for example, in a return line 17 to the fuel tank (see illustration of Figure 1) can flow back.
  • the pressure control valve 57 shown in Figure 4 is seatless and includes an end face 53 which is formed in a smaller diameter compared to the outer diameter of the pressure control valve 57.
  • annular groove 55 may extend, in which a Sealing element 56 can be inserted.
  • the recessed into the annular groove 55 sealing element 56 forms within the low-pressure region 51, 52, a low-pressure side seal 54, which is exposed to much lower compressive stresses compared to a high-pressure side seal (see illustration of Figure 3, position 48).
  • a recess could also be arranged in the region of the frontal contact surface of the pressure control valve body with the blind hole 52 enclosing the high-pressure reservoir 15 annular surface.
  • the low-pressure-side sealing surface could thus be displaced into the contact area between the annular portion which delimits the blind hole 52 and the enlarged diameter body of the pressure regulating valve 57.
  • Both exemplified low-pressure side seals 54 have in common that they lower mechanical stresses, compared to a high-pressure side sealing point 48 between the pressure control valve 57 and the high-pressure accumulator space 15 are formed.
  • the arrangement of a pressure regulating valve 57 shown in FIG. 4 allows a high pressure reservoir 15 at a first end 37 and a second end 38 to dispense with a line connection between the high pressure reservoir and the pressure control valve.
  • the pressure regulating valve 57 comprises an armature part 45, which, with its end facing away from the compression spring 44, acts on the closing element 47 which is configured spherically here.
  • the ball-shaped closing element 47 in FIG. 4 cooperates with a valve seat 59 or 61.
  • the seat 59 can be incorporated directly into an end wall 58 of the high-pressure reservoir 15.
  • the cavity 33 of the high pressure accumulator chamber 15 is limited by the end face 58, which is penetrated by a bore containing a throttle immediately upstream of the closing element 47.
  • the opening of the cavity 33 which can be opened or closed by the ball-shaped closing element 47 lies with respect to its end facing the cavity 33 at a distance 62 with respect to the line of symmetry of the transverse bore 35 of a first high-pressure port 34.
  • the distance 62 between the transverse bore 35 of the first high-pressure port 34 and the end face of the high-pressure accumulator chamber 15 is sized so that reduce mechanical stresses within the high-pressure accumulator space 15 between the transverse bore 35 and the end face of the high-pressure accumulator chamber 15.
  • the valve seat 59 for the closing element 47 formed in the end face 58 of the high-pressure storage chamber 15 has the particular advantage that the valve seat 59 is formed in a solidly formed region.
  • a uniform temperature distribution i. a uniform heat transfer into the material surrounding the valve seat 49 possible, so that no decrease in material hardness or unacceptably high material stresses can occur, which can affect the calibration of the pressure control valve 57, which is preferably actuated by an electromagnet 46 at normal temperature.
  • an insert part 60 in the case of two-part or multi-part high-pressure storage chambers 15 for limiting the cavity 33, an insert part 60 can be pressed or welded into it.
  • a valve seat 61 can be incorporated into the insert part 60.
  • the end face of the insert part 60 facing the high-pressure storage space 33 is preferably also arranged at a distance 62 relative to the line of symmetry of the transverse bore 35 of the first high-pressure port 34
  • the low-pressure-side region 52, 51, in which the seal 54 lies, is essentially delimited by the blind bore 52 on one of the end faces of the high-pressure reservoir 15 and the bottom of the blind bore 52, in which the valve seat 59 for the closing element 47 in the case of one-piece high-pressure reservoirs 15 and 15, respectively the valve seat 61 is located in multi-part high-pressure accumulator spaces 15 with a pressed-in or welded-in insert part 60.
  • a high-pressure side seal can be omitted, whereby a simple achievable tightness between the high-pressure accumulator chamber 15 and the pressure control valve 57 can be achieved.
  • the inventively proposed low-pressure side seal 54 can be produced at a seatless at an end face 37 and 38 to the high-pressure accumulator 15 integrated pressure control valve 57 substantially cheaper because a much lower pressure level is to be sealed.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a fuel injection system for internal combustion engines, comprising a high-pressure accumulator compartment (15). Said high-pressure accumulator compartment (15) is impinged upon with highly pressurized fuel by a high-pressure feed unit (8) and supplies the fuel injectors (19, 23) with fuel. The fuel injection system comprises a pressure control valve (57) that is disposed between a high pressure side (33) and a low pressure side (50, 51, 52) and that actuates a valve element (47). The pressure control valve (57) is actuated by means of an electric actuator (46). The pressure control valve (57), with a front (53), delimits the low pressure zone (50, 51, 52) on the high-pressure accumulator compartment (15) and is sealed off by means of a low pressure seal (54).

Description

Technisches GebietTechnical area

An selbstzündenden Verbrennungskraftmaschinen werden heute neben Pumpe-Düsen-Systemen und Pumpe-Leitung-Düse-Systemen Speichereinspritzsysteme zum Einspritzen des Kraftstoffes eingesetzt. Diese Speichereinspritzsysteme umfassenen einen Hochdruckspeicherraum, der über eine Hochdruckpumpe mit unter hohem Druck stehenden Kraftstoff versorgt wird. Die Hochdruckpumpe stellt die Schnittstelle zwischen dem Hochdruckteil und dem Niederdruckteil des Einspritzsystemes dar. Der Hochdruckpumpe kann dabei ein Druckregelventil zugeordnet sein, welches einerseits dazu dient, bei zu hohem Druck im Hochdruckspeicherraum zu öffnen, so dass Kraftstoff aus diesem über eine Sammelleitung zurück zum Kraftstoffbehälter strömt und andererseits dazu, bei zu niedrigem Druck im Hochdruckspeicherraum die Hochdruckseite gegen die Niederdruckseite abzudichten.On self-igniting internal combustion engines storage injection systems are used today for injecting the fuel in addition to pump-nozzle systems and pump-line-nozzle systems. These accumulator injection systems include a high pressure accumulator which is supplied with high pressure fuel via a high pressure pump. The high-pressure pump is the interface between the high-pressure part and the low-pressure part of the injection system. The high-pressure pump can be assigned a pressure regulating valve, which serves on the one hand to open at high pressure in the high-pressure reservoir, so that fuel flows from this via a manifold back to the fuel tank and on the other hand to seal the high-pressure side against the low-pressure side at too low pressure in the high-pressure storage space.

Stand der TechnikState of the art

Aus der Veröffentlichung "Dieselmotor-Management", 2. aktualisierte und erweiterte Auflage, Vieweg 1989, Braunschweig; Wiesbaden, ISBN 3-528-03873-X, Seite 270, Abb. 9 ist ein Druckregelventil bekannt. Das Druckregelventil wird an einer Hochdruckpumpe eingesetzt, vergleiche Seite 267, Bild 7 derselben Veröffentlichung. Das Druckregelventil umfasst ein Kugelventil, welches einen kugelförmig ausgebildeten Schliesskörper enthält. Innerhalb des Druckregelventiles ist ein Anker aufgenommen, der einerseits von einer Druckfeder beaufschlagt ist und dem andererseits ein Elektromagnet gegenüberliegend angeordnet ist. Der Anker des Druckregelventiles ist zur Schmierung und zur Kühlung von Kraftstoff umspült.From the publication "Diesel Engine Management", 2nd updated and expanded edition, Vieweg 1989, Braunschweig; Wiesbaden, ISBN 3-528-03873-X, page 270, Fig. 9 is a pressure regulating valve known. The pressure control valve is used on a high-pressure pump, see page 267, Figure 7 of the same publication. The pressure regulating valve comprises a ball valve, which contains a ball-shaped closing body. Within the pressure control valve, an armature is received, which is acted upon on the one hand by a compression spring and the other hand, an electromagnet is arranged opposite. The armature of the pressure control valve is lapped around the lubrication and cooling of fuel.

Ist das Druckregelventil nicht angesteuert, so steht dem Hochdruckspeicherraum oder am Ausgang der Hochdruckpumpe anliegende hohe Druck über den Hochdruckzulauf am Druckregelventil an. Da der stromlose Elektromagnet keine Kraft ausübt, überwiegt die Hochdruckkraft gegenüber der Kraft der Druckfeder, so dass das Druckregelventil geöffnet und dieses je nach geförderter Kraftstoffmenge mehr oder weniger geöffnet bleibt.If the pressure control valve is not activated, the high-pressure reservoir or the outlet of the high-pressure pump is subjected to high pressure via the high-pressure inlet to the pressure control valve. Since the electroless electromagnet exerts no force outweighs the High pressure force against the force of the compression spring, so that the pressure regulating valve is opened and this remains more or less open depending on the amount of fuel delivered.

Wird das Druckregelventil hingegen angesteuert, d.h. wird der Elektromagnet bestromt, wird der Druck im Hochdruckkreis erhöht. Dazu wird zusätzlich zur durch die Druckfeder ausgeübten Kraft eine magnetische Kraft erzeugt. Das Druckregelventil wird geschlossen, bis zwischen der Hochdruckkraft einerseits und der Federkraft sowie der Magnetkraft andererseits ein Kräftegleichgewicht vorliegt. Die magnetische Kraft des Elektromagneten ist proportional zum Ansteuerstrom I der Magnetspulen innerhalb des Druckregelventiles. Der Ansteuerstrom I lässt sich durch Pulsweitenmodulation takten.If the pressure control valve is activated, i. E. when the electromagnet is energized, the pressure in the high-pressure circuit is increased. For this purpose, a magnetic force is generated in addition to the force exerted by the compression spring. The pressure control valve is closed until there is an equilibrium of forces between the high-pressure force on the one hand and the spring force and the magnetic force on the other hand. The magnetic force of the electromagnet is proportional to the driving current I of the magnetic coils within the pressure regulating valve. The drive current I can be clocked by pulse width modulation.

Gemäß der oben genannten Veröffentlichung, Seite 270, Bild 7 wird das Druckregelventil beispielsweise seitlich an die Hochdruckpumpe angeflanscht. Daneben ist es auch möglich, das Druckregelventil und den Hochdruckspeicherraum (Common-Rail) hochdruckseitig abzudichten. In diesem Falle sind sowohl der Hochdruckspeicherraum (Common-Rail) und das Druckregelventil jeweils als separate Komponenten ausgebildet. Diese separat ausgebildeten Komponenten des Speichereinspritzsystemes weisen jedoch aufgrund der genauen fertigungstechnischen Bearbeitung ihrer hochdruckseitigen Dichtstellen hohe Herstellkosten auf. Ferner sind an den hochdruckseitigen Dichtstellen Dichtelemente vorzusehen, die den an hochdruckseitigen Dichtstellen auftretenden mechanischen Beanspruchungen gewachsen sind. Aufgrund des hochdruckseitig herrschenden Druckniveaus entstehen an den hochdruckseitig ausgebildeten Dichtstellen im Laufe des Betriebes des Speichereinspritzsystemes zwangsläufig Undichtigkeiten.According to the above publication, page 270, Figure 7, the pressure control valve, for example, flanged laterally to the high-pressure pump. In addition, it is also possible to seal the pressure control valve and the high pressure accumulator (common rail) high pressure side. In this case, both the high-pressure accumulator (common rail) and the pressure control valve are each formed as separate components. However, these separately formed components of the storage injection system have high production costs due to the precise production engineering of their high-pressure side sealing points. Furthermore, sealing elements are to be provided on the high-pressure side sealing points, which are able to cope with the mechanical stresses occurring at high-pressure-side sealing points. Due to the pressure level prevailing on the high pressure side, leaks inevitably occur at the high pressure side sealing points in the course of operation of the accumulator injection system.

Ferner können Bauraumprobleme dadurch entstehen, dass zwischen dem Hochdruckspeicherraum und dem Druckregelventil eine aufgrund der Grösse und der Einbauorientierung dieser Komponenten des Speichereinspritzsystemes im Bauraum Leitungen zwischen diesen erforderlich werden. Werden separate Komponenten gefügt, so ist deren Montage innerhalb des Motorraumes im Zylinderkopfbereich einer selbstzündenden Verbrennungskraftmaschine in bezug auf die Montage schwierig und zeitaufwendig. Ferner können bei den hochdruckseitig zueinander abgedichteten Komponenten Hochdruckspeicherraum und Druckregelventil Temperaturprobleme hinsichtlich des Regelsitzes auftreten. Der Regelsitz stellt die Stelle dar, an der ein beispielsweise als kugelförmiger Schliesskörper ausgebildetes Schliesselement durch einen Ankerteil des Druckregelventiles in einen Sitz gedrückt wird. Die genaue Position dieses Sitzes bestimmt wiederum den sich in einem Druckregelventil, welches über ein Magnetventil angesteuert ist, einstellenden Luftspalt zwischen der Ankerplatte und einer Stirnseite des Magnetkerns. Je genauer der Luftspalt zwischen diesen Komponenten des Druckregelventiles ausgebildet werden kann, eine umso genauere Druckdifferenz Δp entsprechend einer an das Druckregelventil gestellten Toleranz lässt sich erzielen. Verformt sich die Sitzfläche, in welche das kugelförmig ausgebildete Schließelement hineingedrückt wird, durch eine unzulässig starke Erwärmung aufgrund ungleichmäßiger Temperaturverteilung, so stellt sich nach längerem Betrieb und damit verbundener Temperaturerhöhung im Hochdruckspeicherraum eine aufgrund des sich verändernden Luftspaltes der Magnetkomponenten innerhalb des Druckregelventiles verändernder Luftspalt ein. Dadurch wird die zum Magnetstrom I proportionale Drucktoleranz Δp negativ beeinflusst, so dass die Regelgenauigkeit eines aus separaten, hochdruckseitig zueinander abgedichteten Komponenten eines Speichereinspritzsystemes abnimmt.Furthermore, installation space problems may arise because between the high-pressure storage space and the pressure regulating valve, a line between them is required due to the size and installation orientation of these components of the storage injection system in the construction space. If separate components are added, their installation within the engine compartment in the cylinder head region of a self-igniting internal combustion engine is difficult and time-consuming with respect to the assembly. Furthermore, temperature problems with respect to the control seat can occur in the high-pressure side space sealed to each other components high-pressure reservoir and pressure control valve. The control seat represents the point at which a closing element designed, for example, as a spherical closing body is pressed into a seat by an anchor part of the pressure regulating valve. The exact position of this seat, in turn, determines the air gap between the armature plate and an end face of the magnet core which adjusts itself in a pressure control valve, which is controlled via a solenoid valve. The more accurate the air gap between these components of the pressure control valve can be formed, the more accurate Pressure difference .DELTA.p corresponding to a tolerance set to the pressure regulating valve can be achieved. Deformed by the seat, in which the ball-shaped closing element is pressed by an excessive heating due to uneven temperature distribution, it turns after prolonged operation and associated temperature increase in the high-pressure reservoir a due to the changing air gap of the magnetic components within the pressure control valve changing air gap. As a result, the pressure tolerance Δp proportional to the magnet current I is negatively influenced, so that the control accuracy of a component of a storage injection system sealed from separate components on the high pressure side decreases.

Eine Vorrichtung zum Ablassen von Fluid aus einem unter hohem Druck stehenden System, insbesondere zum Ablassen von Kraftstoff aus einiem Rail eines Common-Rail-Motors ist aus DE-A 199 52 774 bekannt. Das beschriebene System weist wenigstens eine Auslassöffnung auf, welche von einer Ventileinrichtung verschließbar ist.A device for discharging fluid from a system under high pressure, in particular for discharging fuel from a rail of a common rail engine is known from DE-A 199 52 774. The system described has at least one outlet opening, which can be closed by a valve device.

Darstellung der ErfindungPresentation of the invention

Mit der erfindungsgemäß vorgeschlagenen Lösung kann die Dichtstelle zwischen den hochdruckführenden Baukomponenten eines Speichereinspritzsystemes, nämlich dem Hochdruckspeicherraum und dem Druckregelventil, von der dichtungskritischen Hochdruckseite auf die weniger kritische Niederdruckseite verlegt werden.With the proposed solution according to the invention, the sealing point between the high-pressure components of a storage injection system, namely the high-pressure accumulator and the pressure control valve can be moved from the high-pressure critical side to the less critical low pressure side.

Der Einbau des Druckregelventiles in den Hochdruckspeicherraum mit niederdruckseitiger Abdichtung macht eine hochdruckseitige Abdichtung, die hohen mechanischen Belastungen ausgesetzt ist und sich dort einstellenden Undichtigkeiten nach sich zieht, entbehrlich. Der Sitz für das Schliesselement, am Druckregelventil beispielsweise ausgebildet als eine Ventilkugel, kann in eine Stirnseite des Hochdruckspeicherraumes verlegt werden. Dies gestattet eine gute Wärmeabfuhr, da der Sitz massiv, eine gute Wärmeübertragung im Material des Hochdruckspeicherraumes ermöglichend, ausgebildet ist. Da mit der erfindungsgemäßen Lösung eine homogene Temperaturverteilung am Hochdruckspeicherraum erzielbar ist, entfällt eine aufgrund einer starken Erwärmung auftretende Abnahme der Materialhärte, was die Festigkeit des erfindungsgemäß konfigurierten Hochdruckspeicherraumes erheblich erhöht. Ein weiterer Vorteil liegt darin, dass eine Sitzspülung vermieden werden kann. Mittels einer Sitzspülung wurde bei bisherigen Ausführungsvarianten eines Hochdruckspeicherraumes durch Kühlung des Sitzbereiches innerhalb des Niederdruckkreislaufes eine Kühlung des selben erreicht, um dessen unzulässige Erwärmung zu verhindern. Dies machte jedoch zusätzliche Anschlüsse innerhalb des Niederdruckkreislaufes erforderlich, die mit der erfindungsgemäßen Lösung nunmehr entfallen können.The installation of the pressure control valve in the high-pressure reservoir with low-pressure side seal makes a high-pressure side seal, which is exposed to high mechanical loads and there are adjusting leaks entailed unnecessary. The seat for the closing element, for example formed as a valve ball on the pressure control valve, can be laid in an end face of the high-pressure reservoir. This allows a good heat dissipation, since the seat is solid, a good heat transfer in the material of the high-pressure accumulator space, made possible. Since a homogeneous temperature distribution at the high-pressure storage space can be achieved with the solution according to the invention, there is no decrease in the hardness of the material due to strong heating, which considerably increases the strength of the high-pressure storage space configured according to the invention. Another advantage is that a seat purge can be avoided. By means of a seat flush was in previous embodiments of a high-pressure storage space by cooling the seating area within the low-pressure circuit a cooling of the same achieved in order to prevent its excessive heating. However, this made additional connections within the low pressure circuit required, which can now be eliminated with the inventive solution.

In einer Ausführungsvariante der erfindungsgemäßen Lösung kann der Sitz für das über das Druckregelventil anzusteuernde Schliesselement in die Stirnseite des Hochdruckspeicherraumes eingearbeitet werden. In diesem Falle kann zur Schaffung eines Niederdruckraumes zwischen dem Hochdruckspeicherraum und dem Druckregelventil eine an der Stiernseite des Hochdruckspeicherraumes fertigungstechnisch einfach herzustellende Sack-lochbohrung hergestellt werden. Die Umbangsfläche des Sacklochbohrung liegt vorteilhaft-erweise in Anlage zu einer stirnfläche am Druckregelventil, so dass eine weitere eine Wärmeabfuhrmöglichkeit bildente Materialverbindung geschaffen wird.In one embodiment of the solution according to the invention, the seat for the to be controlled via the pressure control valve closing element can be incorporated into the end face of the high pressure storage space. In this case, to create a low-pressure space between the high-pressure reservoir and the pressure control valve at the Bull side of the high-pressure storage space manufacturing technology easily produced blind hole bore can be produced. The Umbangsfläche the blind hole is advantageous-wise in abutment with an end face on the pressure control valve, so that a further heat dissipation possibility pictorial material connection is created.

Eine andere Ausfügrungsvariante besteht darin, den Sitz für das Schliesselement des Druckregelventiles in einem Einsatzteil auszubilden, falls der Hohlraum des Hochdruck-speicherraumes durchgängig beschaffen sein soll. Das dem Ventilsitz enthaltente Einsatzteil kann in den Hohlraum des Hochdruckspeicherraumes eingepresst oder in diesen eingeschweisst werden. Auch gemäß dieser Ausführungsvariante wird durch die der Stirnseite des Druckregelventil gegenüberliegende Stirnseite des Einsatzteiles ein Niederdruckraum gebildet, in dem die niederdruckseitige Abdichtung ausgebildet werden kann. Sowohl das Einsatzteil mit Ventilsitz als auch die Stirnseite des Hochdruckspeicherraumes in der erst genannten Ausführungsvariante können eine eine Drosselstelle enthaltende Durchgangsbohrung umfassen, die durch das vom Druckregelventil beaufschlagte Schliesselement verschlossen ist.Another variant Ausfügrungsvariante is to form the seat for the closing element of the pressure control valve in an insert part, if the cavity of the high-pressure storage space should be designed consistently. The insert part containing the valve seat can be pressed into the cavity of the high-pressure reservoir or welded into it. Also according to this embodiment, a low-pressure space is formed by the end face of the pressure control valve opposite end face of the insert part, in which the low-pressure side seal can be formed. Both the insert part with the valve seat and the end face of the high-pressure reservoir in the first-mentioned embodiment variant may comprise a through bore containing a throttle point, which is closed by the closing element acted upon by the pressure control valve.

Nach der Aufnahme des Druckregelventiles an einer der Stirnseite des Hochdrucksammelraumes wird am Druckregelventil die Druckregelfunktion entsprechend einer geforderten Drucktoleranz Δp = f (I), mit I = Ansteuerstrom (Druckregelventil) und der Luftspalt zwischen einer als Magnetventil beispielsweise ausgebildeten Betätigungskomponente des Druckregelventiles eingestellt.After receiving the pressure control valve on one of the front side of the high-pressure accumulation chamber, the pressure control function is set according to a required pressure tolerance Δp = f (I), with I = drive current (pressure control valve) and the air gap between a trained as a solenoid valve actuating component of the pressure control valve.

Zeichnungdrawing

Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben.With reference to the drawing, the invention will be described below in more detail.

Es zeigt:

Figur 1
die Komponenten eines Speichereinspritzsystemes mit Hochdruckspeicherraum,
Figur 2
den Hochdruckspeicherraum im Längsschnitt,
Figur 3
ein hochdruckseitig im Hochdruckspeicherraum abgedichtetes elektrisch angesteuertes Druckregelventil gemäß dem Stand der Technik und
Figur 4
ein Druckregelventil, welches an der Niederdruckseite des Hochdruckspeicherraumes abgedichtet wird.
It shows:
FIG. 1
the components of a storage injection system with high-pressure storage space,
FIG. 2
the high-pressure storage space in longitudinal section,
FIG. 3
a high-pressure side in the high pressure accumulator sealed electrically controlled pressure control valve according to the prior art and
FIG. 4
a pressure regulating valve, which is sealed at the low pressure side of the high-pressure reservoir.

Ausführungsvariantenvariants

Der Darstellung gemäß Figur 1 sind die Komponenten eines Kraftstoffeinspritzsystemes mit Hochdruckspeicherraum zu entnehmen.The illustration according to FIG. 1 shows the components of a fuel injection system with high-pressure storage space.

Das in Figur 1 dargestellte Kraftstoffeinspritzsystem 1 umfasst einen Kraftstoffbehälter 2, in dem sich Kraftstoff entsprechend eines Kraftstoffniveaus 3 befindet. Unterhalb des Kraftstoffspiegels 3 innerhalb des Kraftstoffbehälters 2 ist ein Vorfilter 4 angeordnet, der einem Vorförderaggregat 5 vorgeschaltet ist. Das Vorförderaggregat 5 fördert den über den Vorfilter 4 angesaugten Kraftstoff aus dem Kraftstoffbehälter 2 über einen Kraftstofffilter 6 in einen Niederdruckleitungsabschnitt 7, der in ein Hochdruckförderaggregat 8 mündet. Das Hochdruckförderaggregat 8, bei dem es sich beispielsweise um eine Hochdruckpumpe handeln kann, wird über eine Ansteuerleitung 9 von einem hier nur schematisch dargestellten zentralen Steuergerät 14 angesteuert. Das Hochdruckförderaggregat 8 umfasst neben dem Anschluss des Niederdruckleitungsanschlusses 7 ein an dieses angeflanschtes Druckregelventil 12 mit einem elektrischen Anschluss 14, welcher über eine Ansteuerung 13 ebenfalls über das zentrale Steuergerät 14 angesteuert wird. Vom Hochdruckförderaggregat 8 zweigt ein Hochdruckzulauf ab, über den ein rohrförmig konfigurierter Hochdruckspeicherraum 15 (Common-Rail) mit unter hohem Druck stehenden Kraftstoff beaufschlagt wird. Ferner zweigt vom Hochdruckförderaggregat 8 eine Kraftstoffrücklaufleitung 11 ab, welche in einen Rücklauf 17 mündet, der seinerseits überschüssigen, abströmenden Kraftstoff wieder in den Kraftstoffbehälter 2 zurückleitet.The fuel injection system 1 shown in FIG. 1 comprises a fuel tank 2 in which fuel corresponding to a fuel level 3 is located. Below the fuel level 3 within the fuel tank 2, a pre-filter 4 is arranged, which is connected upstream of a pre-feed unit 5. The pre-feed unit 5 conveys the fuel sucked in via the prefilter 4 from the fuel tank 2 via a fuel filter 6 into a low-pressure line section 7, which opens into a high-pressure delivery unit 8. The high-pressure delivery unit 8, which may be, for example, a high-pressure pump, is controlled via a control line 9 by a central control unit 14, which is only shown schematically here. In addition to the connection of the low-pressure line connection 7, the high-pressure delivery unit 8 comprises a pressure regulating valve 12 flanged to it with an electrical connection 14, which is likewise actuated via the control unit 13 via the central control device 14. From the high-pressure delivery unit 8 branches off a high-pressure inlet, via which a tubular configured high-pressure accumulator chamber 15 (common rail) is acted upon by high-pressure fuel. Furthermore, a fuel return line 11 branches off from the high-pressure delivery unit 8, which discharges into a return 17, which in turn leads excess, outflowing fuel back into the fuel tank 2.

Der über den Hochdruckzulauf 10 vom Hochdruckförderaggregat 8 geförderte, unter sehr hohem Druck stehende Kraftstoff tritt in den Hochdruckspeicherraum 15 (Common-Rail) ein, an dessen Außenumfang ein Drucksensor 16 aufgenommen sein kann. Der Drucksensor 16 steht seinerseits über eine Drucksignalleitung 25 mit einer zentralen Signalleitung 24 in Verbindung, die sich ihrerseits wieder ausgehend vom Steuergerät 14 erstreckt. Vom Hochdruckspeicherraum 15, der z.B. als ein rohrförmig konfiguriertes Bauteil ausgebildet werden kann, zweigen Hochdruckleitungen 18 in einer der Anzahl der Kraftstoffinjektoren 19 entsprechenden Anzahl ab. Die Hochdruckzuleitungen 18 münden am jeweiligen Zulaufanschluss 20 der Injektorkörper der Kraftstoffinjektoren 19. Die Kraftstoffinjektoren 19 umfassen ihrerseits Aktoren, die z.B. als Piezoaktoren, mechanisch-hydraulische Übersetzer oder auch als Magnetventile beschaffen sein können und die die Einspritzvorgänge in entsprechender Reihenfolge initiieren. Die Aktoren der einzelnen Kraftstoffinjektoren 19 stehen über Aktoransteuerungsleitungen 22 ebenfalls mit der zentralen Signalleitung 24, die vom schematisch wiedergegebenen zentralen Steuergerät 14 ausgeht, in Verbindung. Daneben weisen die einzelnen Kraftstoffinjektoren 19 Rücklaufleitungen 21 auf, die ebenfalls in den bereits erwähnten Rücklauf 17 zum Kraftstoffbehälter 1 münden, so dass z.B. abzusteuernde Steuervolumina in den Kraftstoffbehälter 2 abströmen können.The funded via the high-pressure inlet 10 from the high-pressure delivery unit 8, under very high pressure fuel enters the high-pressure accumulator chamber 15 (common rail), on the outer circumference of a pressure sensor 16 may be added. The pressure sensor 16 is in turn connected via a pressure signal line 25 with a central signal line 24 in connection, which in turn extends from the control unit 14 again. From the high-pressure storage space 15, which can be formed, for example, as a tubular configured component, branch off high-pressure lines 18 in a number corresponding to the number of fuel injectors 19. The high-pressure feed lines 18 open at the respective inlet port 20 of the injector of the fuel injectors 19. The fuel injectors 19 in turn include actuators, which may be designed as piezo actuators, mechanical-hydraulic translators or as solenoid valves and initiate the injection operations in a corresponding order. The actuators of the individual fuel injectors 19 are also connected via Aktoransteuerungsleitungen 22 with the central signal line 24, which emanates from the schematically represented central control unit 14, in connection. In addition, the individual fuel injectors 19 return lines 21, which also open into the already mentioned return 17 to the fuel tank 1, so that, for example, taxed-off control volumes can flow into the fuel tank 2.

Vom Steuergerät 14 zweigen neben der bereits erwähnten Ansteuerleitung 13 zur Ansteuerung eines im Druckregelventil 12 enthaltenen Elektromagneten und einer Ansteuerleitung 9 für das Hochdruckförderaggregat 8 sowie einer Drucksensorleitung 25 zum Drucksensor 16 des Hochdruckspeicherraumes 15, auch eine Ansteuerleitung 26 ab, mit welcher das im Kraftstoffbehälter 2 untergebrachte Vorförderaggregat 5 ansteuerbar ist. Das zentrale Steuergerät 14 des Kraftstoffeinspritzsystemes empfängt darüber hinaus Signale von einem Kurbelwellensensor 27, der zur Erfassung der Drehlage der Verbrennungskraftmaschine dient, ferner Signale eines Nockenwellensensors 28, über den die entsprechende Phasenlage der Verbrennungskraftmaschine bestimmbar ist sowie Eingangssignale eines Fahrpedalsensors 29. Ferner erhält das zentrale Steuergerät 14 über die zentrale Signalleitung 24 den Ladedruck 30 charakterisierende Signale über einen entsprechenden im Ansaugtrakt der Verbrennungskraftmaschine untergebrachten Sensor. Darüber hinaus wird die Motortemperatur 31, beispielsweise erfasst an den Wänden der Brennräume der Verbrennungskraftmaschine sowie die Temperatur 32 des Kühlfluides der Verbrennungskraftmaschine über die zentrale Signalleitung 24 an das in Figur 1 wiedergegebene zentrale Steuergerät 14 übermittelt.From the control unit 14 branches in addition to the already mentioned control line 13 for controlling an electromagnet contained in the pressure control valve 12 and a control line 9 for the high-pressure delivery unit 8 and a pressure sensor line 25 to the pressure sensor 16 of the high-pressure accumulator chamber 15, a drive line 26 from which accommodated in the fuel tank 2 Pre-feed unit 5 can be controlled. The central control unit 14 of the fuel injection system also receives signals from a crankshaft sensor 27, which serves to detect the rotational position of the internal combustion engine, signals from a camshaft sensor 28, via which the corresponding phase position of the internal combustion engine can be determined and input signals of an accelerator pedal sensor 29. Further receives the central control unit 14 signals characterizing the boost pressure 30 via the central signal line 24 via a corresponding sensor accommodated in the intake tract of the internal combustion engine. In addition, the engine temperature 31, for example, recorded on the walls of the combustion chambers of the internal combustion engine and the temperature 32 of the cooling fluid of the internal combustion engine via the central signal line 24 to the reproduced in Figure 1 central control unit 14 transmitted.

Der Darstellung gemäß Figur 2 ist der Hochdruckspeicherraum des Kraftstoffeinspritzsystemes im Längsschnitt zu entnehmen.The illustration according to FIG. 2 shows the high-pressure reservoir of the fuel injection system in longitudinal section.

Der Hochdruckspeicherraum 15 umschliesst im wesentlichen einen Hohlraum 33. Der in Figur 2 dargestellte Hochdruckspeicherraum 15 ist als separates Bauteil ausgebildet und umfasst an seiner ersten Stirnseite 37 ein als Verschluss ausgebildetes Einsatzelement 39, an welchem der in Figur 1 dargestellte Rücklauf 17 zum Kraftstoffbehälter angeschlossen werden kann. An seiner zweiten Stirnseite 38 umfasst der Hochdruckspeicherraum 15 gemäß der Darstellung in Figur 2 einen Hochdruckanschluss 40, an welchem der in Figur 1 dargestellte Hochdruckzulauf 10 anschliessbar ist. An seiner Aussenumfangsfläche ist der in Figur 1 dargestellte Drucksensor 16 aufgenommen, der über die in Figur 1 dargestellte Drucksensorleitung 25 mit dem Steuergerät 14 (vergleiche Darstellung gemäß Figur 1) verbunden ist.The high-pressure accumulator chamber 15 substantially encloses a cavity 33. The high-pressure accumulator chamber 15 shown in FIG. 2 is designed as a separate component and comprises on its first end face 37 an insert element 39 designed as a closure, to which the return line 17 shown in FIG. 1 can be connected to the fuel tank , As shown in FIG. 2, the high-pressure storage space 15 on its second end face 38 comprises a high-pressure port 40, to which the high-pressure inlet 10 shown in FIG. 1 can be connected. The pressure sensor 16 shown in FIG. 1 is accommodated on its outer peripheral surface and is connected to the control unit 14 via the pressure sensor line 25 shown in FIG. 1 (see illustration according to FIG. 1).

Entsprechend der Anzahl der mit Kraftstoff über den Hochdruckspeicherraum 15 zu versorgenden Kraftstoffinjektoren 19 sind an der Umfangsfläche des Hochdruckspeicherraumes 15 Anschlussstutzen 34 ausgebildet, an welchen die Hochdruckzuleitungen 18 zu den Kraftstoffinjektoren 19 (vergleiche Darstellung gemäß Figur 1) anschliessbar sind. Die Anschlussstutzen 34 umschliessen jeweils Querbohrungen 35, die mit dem Hohlraum 33 des Hochdruckspeicherraumes 15 in Verbindung stehen und über diesen den unter hohem Druck stehenden Kraftstoff aus dem Hochdruckspeicherraum 15 den einzelnen Kraftstoffinjektoren 19 zuleiten. An der Aussenumfangsfläche des Hochdruckspeicherraumes 15 gemäß der Darstellung in Figur 2 sind darüber hinaus Befestigungslaschen 36 angeschmiedet oder angeschweisst, über welche der Hochdruckspeicherraum 15 im Zylinderkopfbereich einer selbst zündenden Verbrennungskraftmaschine mit diesem verbunden werden kann.Corresponding to the number of fuel injectors 19 to be supplied with fuel via the high-pressure accumulator space 15, connection stubs 34 are formed on the peripheral surface of the high-pressure accumulator space, to which the high-pressure supply lines 18 can be connected to the fuel injectors 19 (cf. illustration according to FIG. 1). The connecting pieces 34 each enclose transverse bores 35, which are in communication with the cavity 33 of the high-pressure reservoir 15 and via which the high-pressure fuel from the high-pressure reservoir 15 to the individual fuel injectors 19 forward. On the outer peripheral surface of the high pressure accumulator chamber 15 as shown in Figure 2 mounting tabs 36 are also forged or welded, via which the high-pressure accumulator chamber 15 in the cylinder head area of a self-igniting internal combustion engine can be connected to this.

Der in Figur 2 dargestellte Hochdruckspeicherraum 15 umfasst fünf Anschlussstutzen 34, so dass fünf Hochdruckzuleitungen 18 zu den Kraftstoffinjektoren 19 einer selbstzündenden Verbrennungskraftmaschine mit unter hohem Druck stehenden Kraftstoff versorgt werden können. Der in Figur 2 als separates Bauteil dargestellte Hochdruckspeicherraum 15 kann selbstverständlich sowohl zur Versorgung einer vierzylindrigen selbstzündenden Verbrennungskraftmaschine als auch zur Versorgung einer sechs- oder achtzylindrigen Verbrennungskraftmaschine mit Kraftstoff ausgelegt werden.The high-pressure accumulator chamber 15 shown in FIG. 2 comprises five connecting stubs 34, so that five high-pressure supply lines 18 to the fuel injectors 19 of a self-igniting internal combustion engine can be supplied with fuel under high pressure. The high-pressure accumulator 15 shown as a separate component in Figure 2 can of course be designed both to supply a four-cylinder autoignition internal combustion engine as well as to supply a six- or eight-cylinder internal combustion engine with fuel.

Figur 3 zeigt ein hochdruckseitig im Hochdruckspeicherraum abgedichtetes elektrisch angesteuertes Druckregelventil gemäß dem Stand der Technik.Figure 3 shows a high-pressure side in the high-pressure reservoir sealed electrically controlled pressure control valve according to the prior art.

Das in Figur 3 im Schnitt dargestellte Druckregelventil enthält einen elektrischen Anschluss 41, der an Ringnuten eines Gehäusekörpers aufgeklippst werden kann oder an diesem angespritzt ist. Innerhalb des Gehäusekörpers ist ein Elektromagnet 46 angeordnet. Dem Elektromagneten 46 gegenüberliegend ist eine Ankerplatte 42 angeordnet, die durch eine Druckfeder 44 beaufschlagt ist. Die Ankerplatte 42 sowie die Druckfeder 44 sind von einem etwa glockenförmig beschaffenen Einsatz 43 umschlossen. Die Ankerplatte 42 steht mit einem Ankerteil 45 in Verbindung, welche eine Verjüngung in Form eines Kegelstumpfes an den der Ankerplatte 42 gegenüberliegenden Ende aufweist. Das verjüngte Ende des Ankerteiles 45 wirkt auf ein hier als Ventilkugel ausgebildetes Schliesselement 47 ein, welches in einem Ventilsitz 49 aufgenommen ist. Der verjüngte, kegelförmig auslaufende Bereich des Ankerteiles 45, welcher auf das in Kugelform ausgebildete Schliesselement 47 einwirkt, ist von einem niederdruckseitigem Raum 50 umschlossen, welcher Öffnungen 51 enthält, über welche bei Betätigung des Schliesselementes 47 hochdruckseitig austretender Kraftstoff in den Niederdruckbereich etwa zum Kraftstoffbehälter des Kraftstoffeinspritzsystemes zurückgefördert wird. An dem in Figur 3 im Schnitt dargestellten Druckregelventil ist eine mit Bezugszeichen 48 gekennzeichnete hochdruckseitige Abdichtung 48 ausgebildet, mit welcher das im Schnitt dargestellte Druckregelventil gemäß Figur 3 sowohl an einem Hochdruckförderaggregat für eine Hochdruckpumpe oder auch an einem Hochdruckspeicherraum angeordnet werden kann. Die mit Bezugszeichen 48 gekennzeichnete hochdruckseitige Abdichtung erfordert eine hohe Bearbeitungsgüte, geringste Toleranzen und ist im Betrieb extrem hohen mechanischen Beanspruchungen ausgesetzt und stellt daher mit zunehmender Lebensdauer eine Schwachstelle eines Kraftstoffeinspritzsystems für selbstzündende Verbrennungskraftmaschinen dar.The pressure regulating valve shown in section in FIG. 3 contains an electrical connection 41, which can be clipped onto annular grooves of a housing body or molded onto it. Within the housing body, an electromagnet 46 is arranged. The electromagnet 46 opposite an armature plate 42 is arranged, which is acted upon by a compression spring 44. The anchor plate 42 and the compression spring 44 are enclosed by an approximately bell-shaped use 43. The anchor plate 42 is in communication with an anchor member 45 which has a taper in the form of a truncated cone at the end opposite the anchor plate 42. The tapered end of the anchor member 45 acts on a here formed as a valve ball closing element 47, which is received in a valve seat 49. The tapered, conically tapered portion of the anchor member 45 which acts on the ball-shaped closing element 47 is enclosed by a niederdruckseitigem space 50 which contains openings 51, on which high pressure side exiting fuel in the low pressure region about the fuel tank of the fuel injection system is promoted back. At the pressure control valve shown in section in section 3, a high-pressure side seal 48 is provided with reference numeral 48, with which the pressure control valve shown in section can be arranged on both a high pressure pumping unit for a high pressure pump or at a high pressure reservoir. The designated by reference numeral 48 high-pressure side seal requires high processing quality, minimum tolerances and is exposed to extremely high mechanical stresses during operation and therefore represents a weak point of a fuel injection system for self-igniting internal combustion engines with increasing life.

Figur 4 zeigt ein Druckregelventil, welches an der Niederdruckseite eines Hochdruckspeicherraumes abgedichtet werden kann.FIG. 4 shows a pressure regulating valve which can be sealed at the low pressure side of a high pressure storage space.

Aus der Darstellung gemäß Figur 4 gehen im Längsschnitt sowohl der Hochdruckspeicherraum 15 als auch das Druckregelventil 57 hervor.From the illustration according to FIG. 4, both the high-pressure storage space 15 and the pressure regulating valve 57 emerge in a longitudinal section.

Der Hochdruckspeicherraum 15 ist in einer das in diesem herrschenden Druckniveau angepassten Wandstärke ausgebildet. Entsprechend der Anzahl der mit Kraftstoff zu versorgenden Kraftstoffinjektoren 19 einer selbst zündenden Verbrennungskraftmaschine sind an der Aussenumfangsfläche des Hochdruckspeicherraumes 15 Anschlussstutzen 34 ausgebildet, die je von einer Querbohrung 35 durchsetzt sind. Über die Querbohrungen 35 strömt der unter hohem Druck stehende Kraftstoff aus dem Hohlraum 33 des Hochdruckspeicherraumes 15 über die Anschlussstutzen 34 in die jeweiligen Hochdruckzuleitungen 18 zu den Injektoren 19, die den Kraftstoff in die Brennräume der zu versorgenden Verbrennungskraftmaschine einspritzen.The high-pressure accumulator space 15 is formed in a wall thickness adapted to the prevailing pressure level in this chamber. According to the number of fuel injectors 19 to be supplied with fuel of a self-igniting internal combustion engine 15 connecting pieces 34 are formed on the outer peripheral surface of the high pressure accumulator chamber, which are each traversed by a transverse bore 35. Via the transverse bores 35, the high-pressure fuel from the cavity 33 of the high pressure accumulator chamber 15 flows via the connecting pieces 34 into the respective high pressure supply lines 18 to the injectors 19, which inject the fuel into the combustion chambers of the internal combustion engine to be supplied.

Zur Aufnahme des Druckregelventiles 57 ist an einem Ende des Hochdruckspeicherraumes 15 eine beispielsweise als Sackloch beschaffene Bohrung 52 ausgebildet. Die Sacklochbohrung 52 an einem Ende des Hochdruckspeicherraumes 15 bildet bei in dieser montierten Druckregelventil 57 einen Niederdruckbereich. Dem Niederdruckbereich ist ein Niederdruckanschluss 51 zugeordnet, über welcher in den Niederdruckbereich 52, 51 eintretender, aus dem Hohlraum 33 des Hochdruckspeicherraumes 15 austretender, Kraftstoff im Niederdruckbereich des Kraftstoffeinspritzsystemes so z.B. in einen Rücklauf 17 zum Kraftstoffbehälter (vergleiche Darstellung gemäß Figur 1) zurückströmen kann. Das in Figur 4 dargestellte Druckregelventil 57 ist sitzlos ausgebildet und umfasst eine Stirnseite 53, die in einen im Vergleich zum Aussendurchmesser des Druckregelventiles 57 geringeren Durchmesser ausgebildet ist. Innerhalb des Bereiches des Druckregelventiles 57, der in geringerem Durchmesser ausgebildet ist, kann eine Ringnut 55 verlaufen, in welcher ein Dichtelement 56 eingelassen sein kann. Das in die Ringnut 55 eingelassene Dichtelement 56 bildet innerhalb des Niederdruckbereiches 51, 52 eine niederdruckseitige Abdichtung 54, die im Vergleich zu einer hochdruckseitigen Abdichtung (vergleiche Darstellung gemäß Figur 3, Position 48) wesentlich niedrigeren Druckbeanspruchungen ausgesetzt ist. Anstelle der in Figur 4 dargestellten Position der Ringnut 55, welche das Dichtelement 56 aufnimmt, könnte eine Ausnehmung auch im Bereich der stirnseitigen Kontaktfläche des Druckregelventilkörpers mit dem das Sackloch 52 am Hochdruckspeicherraum 15 umschliessenden ringförmigen Fläche angeordnet werden. Die niederdruckseitige Dichtfläche könnte somit in den Stosskontaktbereich zwischen dem ringförmigen Abschnitt, der das Sackloch 52 begrenzt und dem vergrößerten Durchmesser ausgebildeten Körpers des Druckregelventiles 57 verlegt werden. Beiden beispielhaft aufgezeigten niederdruckseitigen Abdichtungen 54 ist gemeinsam, das sie geringeren mechanischen Beanspruchungen, verglichen zu einer hochdruckseitigen Abdichtungsstelle 48 zwischen Druckregelventil 57 und dem Hochdruckspeicherraum 15 ausgebildet sind. Ferner ermöglicht die in Figur 4 dargestellte Anordnung eines Druckregelventiles 57 unmittelbar an einen Hochdruckspeicherraum 15 an einer ersten Stirnseite 37 wie auch an einer zweiten Stirnseite 38 den Verzicht auf eine Leitungsverbindung zwischen Hochdruckspeicherraum und Druckregelventil.For receiving the pressure regulating valve 57, a bore 52, for example, designed as a blind hole, is formed at one end of the high-pressure storage chamber 15. The blind hole 52 at one end of the high-pressure accumulator 15 forms a low-pressure region in this mounted pressure control valve 57. The low-pressure region is assigned a low-pressure connection 51, via which low-pressure region 52, 51 emerging from the cavity 33 of the high-pressure accumulator 15 exiting fuel in the low pressure region of the fuel injection system, for example, in a return line 17 to the fuel tank (see illustration of Figure 1) can flow back. The pressure control valve 57 shown in Figure 4 is seatless and includes an end face 53 which is formed in a smaller diameter compared to the outer diameter of the pressure control valve 57. Within the region of the pressure control valve 57, which is formed in a smaller diameter, an annular groove 55 may extend, in which a Sealing element 56 can be inserted. The recessed into the annular groove 55 sealing element 56 forms within the low-pressure region 51, 52, a low-pressure side seal 54, which is exposed to much lower compressive stresses compared to a high-pressure side seal (see illustration of Figure 3, position 48). Instead of the position shown in Figure 4 of the annular groove 55 which receives the sealing element 56, a recess could also be arranged in the region of the frontal contact surface of the pressure control valve body with the blind hole 52 enclosing the high-pressure reservoir 15 annular surface. The low-pressure-side sealing surface could thus be displaced into the contact area between the annular portion which delimits the blind hole 52 and the enlarged diameter body of the pressure regulating valve 57. Both exemplified low-pressure side seals 54 have in common that they lower mechanical stresses, compared to a high-pressure side sealing point 48 between the pressure control valve 57 and the high-pressure accumulator space 15 are formed. Furthermore, the arrangement of a pressure regulating valve 57 shown in FIG. 4 allows a high pressure reservoir 15 at a first end 37 and a second end 38 to dispense with a line connection between the high pressure reservoir and the pressure control valve.

Das Druckregelventil 57 umfasst analog zum in Figur 3 im Schnitt dargestellten Druckregelventil ein Ankerteil 45, welches mit seinem der Druckfeder 44 abgewandten Ende das hier kugelförmig konfigurierte Schliesselement 47 beaufschlagt. Das in Figur 4 kugelförmig ausgebildete Schliesselement 47 arbeitet mit einem Ventilsitz 59 bzw. 61 zusammen.Analogous to the pressure regulating valve shown in section in FIG. 3, the pressure regulating valve 57 comprises an armature part 45, which, with its end facing away from the compression spring 44, acts on the closing element 47 which is configured spherically here. The ball-shaped closing element 47 in FIG. 4 cooperates with a valve seat 59 or 61.

In einer ersten Ausführungsvariante der erfindungsgemäß vorgeschlagenen Lösung kann der Sitz 59 unmittelbar in einer Stirnwand 58 des Hochdruckspeicherraum 15 eingearbeitet werden. In dieser Ausführungsvariante, d.h. bei einem einteilig konfigurierten Hochdruckspeicherraum 15 wird der Hohlraum 33 des Hochdruckspeicherraumes 15 durch die Stirnseite 58 begrenzt, welche von einer eine Drosselstelle unmittelbar vor dem Schliesselement 47 enthaltenden Bohrung durchsetzt ist. Über den mittels des Ankerteils 45 des Druckregelventiles 57 in den Ventilsitz 59 gedrückten Schliesskörper 47 kann eine Druckentlastung des Hohlraumes 33 des Hochdruckspeicherraumes 15 erfolgen. Die durch das kugelförmig ausgebildete Schliesselement 47 freigebbare bzw. verschliessbare Öffnung des Hohlraumes 33 liegt bezüglich ihrer dem Hohlraum 33 zuweisenden Stirnseite in einem Abstand 62 in bezug auf die Symmetrielinie der Querbohrung 35 eines ersten Hochdruckanschlusses 34. Der Abstand 62 zwischen der Querbohrung 35 des ersten Hochdruckanschlusses 34 und der Stirnseite des Hochdruckspeicherraumes 15 ist so bemessen, das sich mechanische Spannungen innerhalb des Hochdruckspeicherraumes 15 zwischen der Querbohrung 35 und der Stirnseite des Hochdruckspeicherraumes 15 abbauen.In a first embodiment of the proposed solution according to the invention, the seat 59 can be incorporated directly into an end wall 58 of the high-pressure reservoir 15. In this embodiment, ie in a one-piece configured high-pressure accumulator chamber 15, the cavity 33 of the high pressure accumulator chamber 15 is limited by the end face 58, which is penetrated by a bore containing a throttle immediately upstream of the closing element 47. By way of the closing body 47 pressed into the valve seat 59 by means of the armature part 45 of the pressure regulating valve 57, a pressure relief of the cavity 33 of the high-pressure storage chamber 15 can take place. The opening of the cavity 33 which can be opened or closed by the ball-shaped closing element 47 lies with respect to its end facing the cavity 33 at a distance 62 with respect to the line of symmetry of the transverse bore 35 of a first high-pressure port 34. The distance 62 between the transverse bore 35 of the first high-pressure port 34 and the end face of the high-pressure accumulator chamber 15 is sized so that reduce mechanical stresses within the high-pressure accumulator space 15 between the transverse bore 35 and the end face of the high-pressure accumulator chamber 15.

Der in der Stirnseite 58 des Hochdruckspeicherraumes 15 ausgebildete Ventilsitz 59 für das Schliesselement 47 hat insbesondere den Vorteil, dass der Ventilsitz 59 in einem massiv ausgebildeten Bereich ausgebildet ist. Bei sich aufgrund der hohen Drücke einstellender Erwärmung ist eine gleichmäßige Temperaturverteilung, d.h. eine gleichmäßige Wärmeübertragung in das den Ventilsitz 49 umgebende Material möglich, so dass keine Abnahme der Materialhärte bzw. unzulässig hohe Materialspannungen auftreten können, welcher die bei Normaltemperatur vorgenommene Kalibrierung des Druckregelventiles 57, welches vorzugsweise durch einen Elektromagneten 46 betätigt wird, beeinträchtigen können. Damit ist eine Verschiebung der Drucktoleranz Δp = f(I), mit I = Magnetstrom, ausgeschlossen. Mit der bei der in Figur 4 dargestellten Ausführungsvariante eines in den Hochdruckspeicherraum 15 integrierten Druckregelventiles 57 wird eine Kalibrierung, d.h. das Einstellen eines Luftspaltes am Elektromagneten des Druckregelventiles 57 zur Einstellung der Toleranzkennlinie Δp = f(I) am Hochdruckspeicherraum montierten Zustand des Druckregelventiles 57 vorgenommen.The valve seat 59 for the closing element 47 formed in the end face 58 of the high-pressure storage chamber 15 has the particular advantage that the valve seat 59 is formed in a solidly formed region. With heating due to the high pressures, a uniform temperature distribution, i. a uniform heat transfer into the material surrounding the valve seat 49 possible, so that no decrease in material hardness or unacceptably high material stresses can occur, which can affect the calibration of the pressure control valve 57, which is preferably actuated by an electromagnet 46 at normal temperature. This excludes a shift in the pressure tolerance Δp = f (I), with I = magnetic current. With the embodiment variant of a pressure regulating valve 57 integrated into the high-pressure storage chamber 15, as shown in FIG. the setting of an air gap on the electromagnet of the pressure control valve 57 for setting the tolerance curve .DELTA.p = f (I) mounted state of the pressure control valve 57 mounted on the high-pressure accumulator space.

In einer zweiten Ausführungsvariante der erfmdungsgemäß vorgeschlagenen Lösung kann bei zwei- oder mehrteilig ausgebildeten Hochdruckspeicherräumen 15 zur Begrenzung des Hohlraumes 33 ein Einsatzteil 60 in diesen eingepresst oder verschweisst werden. In dieser Ausführungsvariante der erfindungsgemäß vorgeschlagenen Lösung lässt sich ein Ventilsitz 61 in das Einsatzteil 60 einarbeiten. Die dem Hochdruckspeicherraum 33 zuweisende Stirnseite des Einsatzteiles 60 wird bevorzugt ebenfalls in einem Abstand 62 bezogen auf die Symmetrielinie der Querbohrung 35 des ersten Hochdruckanschlusses 34 angeordnetIn a second embodiment variant of the solution proposed according to the invention, in the case of two-part or multi-part high-pressure storage chambers 15 for limiting the cavity 33, an insert part 60 can be pressed or welded into it. In this embodiment of the solution proposed according to the invention, a valve seat 61 can be incorporated into the insert part 60. The end face of the insert part 60 facing the high-pressure storage space 33 is preferably also arranged at a distance 62 relative to the line of symmetry of the transverse bore 35 of the first high-pressure port 34

Bei in den Hohlraum 33 gepressten oder eingeschweissten Einsatzteil 60 besteht ebenfalls eine gute Wärmeabfuhr ermöglichende Verbindung zum Vollmaterial des Hochdruckspeicherraumes 15, so dass die am Ventilsitz 61, der genau bearbeitet wird, auftretende Erwärmung kein Verziehen des Sitzes 61 innerhalb des Einsatzteiles 60 und damit ein Verschieben der Kennlinie des Druckregelventiles 57 auftreten kann.When inserted into the cavity 33 or welded insert 60 is also a good heat dissipation enabling connection to the solid material of the high-pressure reservoir 15, so that the valve seat 61, which is accurately processed, occurring heating distortion of the seat 61 within the insert 60 and thus a move the characteristic of the pressure control valve 57 may occur.

Darüber hinaus besteht bei beiden beschriebenen Ausführungsvarianten der Anordnung eines sitzlosen Druckregelventiles 57 in einer als Sackloch 52 ausgebildeten Bohrung an einem Hochdruckspeicherraum 15 eine Wärmebrücke der Gestalt, dass das die Sacklochbohrung 52 umgebende Material des Hochdruckspeicherraumes 15 mit einer Stirnseite am Körper des Druckregelventiles 57 anliegt und auf diese Weise als Druckregelventil 57 bzw. dessen Aussenumfangsfläche zur Wärmeabfuhr dienen kann. Der Körper des Druckregelventiles 57, an dessen der Stirnseite 53 gegenüberliegenden Ende elektrischer Anschlüsse 63 bzw. 41 ausgebildet werden können, weist bevorzugt im Bereich der Stirnseite 53 einen Bereich mit verjüngtem Durchmesser auf in welchem eine Ringnut 55, die das Dichtelement 56 der niederdruckseitigen Abdichtung 54 aufnimmt, eingebracht werden kann. Der niederdruckseitige Bereich 52, 51, in welchem die Abdichtung 54 liegt, wird im wesentlichen durch die Sacklochbohrung 52 an einer der Stirnseiten des Hochdruckspeicherraumes 15 sowie den Boden der Sacklochbohrung 52 begrenzt, in welchem der Ventilsitz 59 für das Schliesselement 47 bei einteiligen Hochdruckspeicherräumen 15 bzw. der Ventilsitz 61 bei mehrteiligen Hochdruckspeicherräumen 15 mit eingepresstem oder eingeschweisstem Einsatzteil 60 liegt. Gemäß der in Figur 4 dargestellten Lösung kann eine hochdruckseitige Abdichtung entfallen, wodurch eine einfache erreichbare Dichtigkeit zwischen dem Hochdruckspeicherraum 15 und dem Druckregelventil 57 erreicht werden kann. Ferner lässt sich durch die in beiden Ausführungsvarianten gegebene Anordnung des Sitzes 59 bzw. 61 für das kugelförmig ausgebildete Schliesselement 47 eine gute Sitzkühlung erreichen, da eine Wärmeabfuhr über das den Sitz 59 bzw. 61 umgebende Vollmaterial erfolgen kann. Ferner ist bei der erfindungsgemäß vorgeschlagenen Lösung in beiden Ausführungsvarianten eine Sitzspülung entbehrlich.In addition, in both embodiments described the arrangement of a seatless pressure control valve 57 in a trained as a blind hole 52 bore at a high-pressure reservoir 15, a thermal bridge of the shape that surrounds the blind hole 52 surrounding material of the high-pressure reservoir 15 with an end face on the body of the pressure control valve 57 and on this way as a pressure control valve 57 and its outer peripheral surface can serve for heat dissipation. The body of the pressure control valve 57, on whose end face 53 opposite end of electrical terminals 63 and 41 can be formed, preferably in the region of the end face 53 a region with a tapered diameter in which an annular groove 55, which receives the sealing element 56 of the low-pressure side seal 54, are introduced can. The low-pressure-side region 52, 51, in which the seal 54 lies, is essentially delimited by the blind bore 52 on one of the end faces of the high-pressure reservoir 15 and the bottom of the blind bore 52, in which the valve seat 59 for the closing element 47 in the case of one-piece high-pressure reservoirs 15 and 15, respectively the valve seat 61 is located in multi-part high-pressure accumulator spaces 15 with a pressed-in or welded-in insert part 60. According to the solution shown in Figure 4, a high-pressure side seal can be omitted, whereby a simple achievable tightness between the high-pressure accumulator chamber 15 and the pressure control valve 57 can be achieved. Furthermore, can be achieved by the given in both embodiments arrangement of the seat 59 and 61 for the spherical closure member 47 a good seat cooling, as heat dissipation over the seat 59 and 61 surrounding solid material can be done. Furthermore, in the proposed solution according to the invention in both embodiments, a seat flushing is unnecessary.

Aufgrund der niederdruckseitigen Abdichtung vom Hochdruckspeicherraum 15 und Druckregelventil 57 treten weiterhin geringere Montagekräfte auf. Im Vergleich zu einer hochdruckseitigen Abdichtung, welche besondere Anforderungen an die Fertigungsgenauigkeit und die eingesetzten Werkstoffe insbesondere des Dichtelementes stellt, lässt sich die erfindungsgemäß vorgeschlagene niederdruckseitige Abdichtung 54 bei einem sitzlosen an einer Stirnseite 37 bzw. 38 an den Hochdruckspeicherraum 15 integrierten Druckregelventiles 57 wesentlich kostengünstiger herstellen, da ein wesentlich niedrigere Druckniveau abzudichten ist.Due to the low-pressure side seal from the high pressure accumulator chamber 15 and pressure control valve 57 continue to lower assembly forces. Compared to a high-pressure side seal, which places special demands on the manufacturing accuracy and the materials used in particular the sealing element, the inventively proposed low-pressure side seal 54 can be produced at a seatless at an end face 37 and 38 to the high-pressure accumulator 15 integrated pressure control valve 57 substantially cheaper because a much lower pressure level is to be sealed.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
KraftstoffeinspritzsystemFuel injection system
22
KraftstoffbehälterFuel tank
33
KraftstoffniveauFuel level
44
Vorfilterprefilter
55
VorförderaggregatVorförderaggregat
66
KraftstofffilterFuel filter
77
NiederdruckleitungsabschnittLow-pressure line section
88th
Hochdruck-FörderaggregatHigh-pressure pumping assembly
99
Ansteuerleitungdrive line
1010
HochdruckzulaufHigh-pressure inlet
1111
KraftstoffrücklaufFuel return
1212
DruckregelventilPressure control valve
1313
Ansteuerraum ElektromagnetControl room electromagnet
1414
Steuergerätcontrol unit
1515
HochdruckspeicherraumHigh-pressure accumulator
1616
Drucksensorpressure sensor
1717
Rücklauf zum KraftstoffbehälterReturn to the fuel tank
1818
Hochdruckzuleitung zum InjektorHigh pressure supply line to the injector
1919
Kraftstoffinjektorfuel injector
2020
Zulaufseitesupply side
2121
Rücklaufseite KraftstoffeinspritzsystemReturn side fuel injection system
2222
Aktoransteuerungactuator control
2323
Einspritzdüseinjection
2424
Zentrale SignalleitungCentral signal line
2525
DrucksensorleitungThe pressure sensor lead
2626
Ansteuerung VorförderpumpeControl of pre-feed pump
2727
Kurbelwellensensorcrankshaft sensor
2828
Nockenwellensensorcamshaft position sensor
2929
FahrpedalsensorAccelerator pedal sensor
3030
LadedrucksensorBoost pressure sensor
3131
Temperaturfühlertemperature sensor
3232
KühlfluidsensorCooling fluid sensor
3333
Hohlraumcavity
3434
Anschlussstutzen für HochdruckzuleitungConnecting piece for high pressure supply line
3535
Querbohrungcross hole
3636
Befestigungslaschenmounting tabs
3737
Erste Stirnseite HochdruckspeicherraumFirst face high pressure reservoir
3838
Zweite Stirnseite HochdruckspeicherraumSecond face High-pressure reservoir
3939
Verschlussshutter
4040
Anschlussstutzen HochdruckanschlussConnecting piece high pressure connection
4141
Elektrischer AnschlussElectrical connection
4242
Ankerplatteanchor plate
4343
Glockenförmiger EinsatzBell-shaped insert
4444
Druckfedercompression spring
4545
Ankerteilanchor part
4646
Elektromagnetelectromagnet
4747
Schliesselementclosing element
4848
Hochdruckseitige AbdichtungHigh pressure side seal
4949
Ventilsitzvalve seat
5050
NiederdruckraumLow-pressure chamber
5151
NiederdruckanschlussLow pressure port
5252
Sacklochblind
5353
Stirnseite DruckregelventilFront side pressure control valve
5454
NiederdruckabdichtungLow pressure seal
5555
Ringnutring groove
5656
Dichtelementsealing element
5757
Druckregelventil (sitzlos)Pressure control valve (seatless)
5858
Stimwand HochdruckspeicherraumStim wall high-pressure storage room
5959
Stirnwandseitiger Sitz für Schliesselement 47Front-side seat for closing element 47
6060
Einsatzteilinsert
6161
Ventilsitz für SchliesselementValve seat for closing element
6262
Abstand zum ersten Hochdruckanschluss 34Distance to the first high pressure port 34
6363
Elektrische Anschlüsse DruckregelventilElectrical connections Pressure control valve

Claims (11)

  1. Fuel injection system for internal combustion engines, with a high-pressure accumulator space (15) which is acted upon via a high-pressure conveying assembly (8) with fuel which is under high pressure, and supplies fuel injectors (19) with fuel, the fuel injection system containing a pressure-regulating valve (57) which is arranged between a high-pressure side (33) and a low-pressure side (50, 51, 52), the pressure-regulating valve (57) actuating a closing element (47) and the pressure-regulating valve (57) being actuable via an electrical actuator (46), the pressure-regulating valve (57) delimiting with one end face (53) a low-pressure space (51, 52) at the high-pressure accumulator space (15) and being sealed off via a sealing point (54) located on the low-pressure side, characterized in that the high-pressure accumulator space (15, 58) is produced in one piece, the low-pressure region (51, 52) being formed by the end face (53) of the pressure-regulating valve (57) and one end face (58) of the high-pressure accumulator space (15), and that end face (58) of the high-pressure accumulator space (15) which is located on the low-pressure side having a seat (59) for the closing element (47) of the pressure-regulating valve (57).
  2. Fuel injection system for internal combustion engines, with a high-pressure accumulator space (15) which is acted upon via a high-pressure conveying assembly (8) with fuel which is under high pressure, and supplies fuel injectors (19) with fuel, the fuel injection system containing a pressure-regulating valve (57) which is arranged between a high-pressure side (33) and a low-pressure side (50, 51, 52), the pressure-regulating valve (57) actuating a closing element (47), and the pressure-regulating valve (57) being actuable via an electrical actuator (46), the pressure-regulating valve (57) delimiting with one end face (53) a low-pressure space (51, 52) at the high-pressure accumulator space (15) and being sealed off via a sealing point (54) located on the low-pressure side, characterized in that the high-pressure accumulator space (15, 60) is of multi-part design and comprises an insert part (60) delimiting the cavity (33) of the high-pressure accumulator space (15), the low-pressure region (51, 52) being formed by the end face (53) of the pressure-regulating valve (57) and by that end face of the insert part (60) which is located on the low-pressure side, and that end face of the insert part (60) which is located on the low-pressure side having a seat (61) for the closing element (47) of the pressure-regulating valve (57).
  3. Fuel injection system according to Claim 1 or 2, characterized in that the pressure-regulating valve (57) is received in a seat (52) at the high-pressure accumulator space (15).
  4. Fuel injection system according to Claim 1 or 2, characterized in that the low-pressure region (51, 52) has a connection piece located on the low-pressure side.
  5. Fuel injection system according to Claim 2, characterized in that the insert part (60) is pressed into the cavity (33) of the high-pressure accumulator space (15).
  6. Fuel injection system according to Claim 2, characterized in that the insert part (60) is welded into the cavity (53) of the high-pressure accumulator space (15).
  7. Fuel injection system according to Claim 1 or 2, characterized in that the seal (54) located on the low-pressure side comprises an annular groove (55) with a peripheral sealing element (56) received in it.
  8. Fuel injection system according to Claim 1 or 2, characterized in that a ring of the high-pressure accumulator space (15), the said ring surrounding the end face (53) of the pressure-regulating valve (57), bears on the end face, as a heat transmission bridge, against the body of the pressure-regulating valve (57).
  9. Fuel injection system according to Claim 1 or 2, characterized in that the seat (59, 61) of the closing element (47) at the high-pressure accumulator space (15) lies in a material region having properties conducive to the discharge of heat.
  10. Fuel injection system according to Claim 9, characterized in that the seat (59, 61) of the closing element (47) lies in a solid material region.
  11. Fuel injection system according to Claim 1 or 2, characterized in that the insert part (60) delimiting the cavity (33) or the end face (58) of the high-pressure accumulator space (15) are arranged, on the high-pressure side, at a distance (62) with respect to a transverse bore (35) of a first high-pressure connection piece (34).
EP03709622A 2002-05-23 2003-02-18 High-pressure accumulator for fuel injection systems with integrated pressure control valve Expired - Lifetime EP1509694B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10222895A DE10222895A1 (en) 2002-05-23 2002-05-23 High pressure accumulator for fuel injection systems with integrated pressure control valve
DE10222895 2002-05-23
PCT/DE2003/000486 WO2003100247A1 (en) 2002-05-23 2003-02-18 High-pressure accumulator for fuel injection systems with integrated pressure control valve

Publications (2)

Publication Number Publication Date
EP1509694A1 EP1509694A1 (en) 2005-03-02
EP1509694B1 true EP1509694B1 (en) 2006-08-23

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EP03709622A Expired - Lifetime EP1509694B1 (en) 2002-05-23 2003-02-18 High-pressure accumulator for fuel injection systems with integrated pressure control valve

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US (1) US7185635B2 (en)
EP (1) EP1509694B1 (en)
JP (1) JP2005526930A (en)
DE (2) DE10222895A1 (en)
WO (1) WO2003100247A1 (en)

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JP2005526930A (en) 2005-09-08
EP1509694A1 (en) 2005-03-02
DE10222895A1 (en) 2003-12-11
DE50304760D1 (en) 2006-10-05
US7185635B2 (en) 2007-03-06
US20060102150A1 (en) 2006-05-18
WO2003100247A1 (en) 2003-12-04

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