EP1306548B1 - Fuel injection apparatus in which the displacement control is improved - Google Patents

Fuel injection apparatus in which the displacement control is improved Download PDF

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Publication number
EP1306548B1
EP1306548B1 EP02015909A EP02015909A EP1306548B1 EP 1306548 B1 EP1306548 B1 EP 1306548B1 EP 02015909 A EP02015909 A EP 02015909A EP 02015909 A EP02015909 A EP 02015909A EP 1306548 B1 EP1306548 B1 EP 1306548B1
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EP
European Patent Office
Prior art keywords
pump
directional control
control valve
fuel
fuel injection
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
EP02015909A
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German (de)
French (fr)
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EP1306548A3 (en
EP1306548A2 (en
Inventor
Peter Schueler
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1306548A2 publication Critical patent/EP1306548A2/en
Publication of EP1306548A3 publication Critical patent/EP1306548A3/en
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Publication of EP1306548B1 publication Critical patent/EP1306548B1/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
    • F02M63/02—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening

Definitions

  • the invention relates to a fuel injection system for an internal combustion engine with a control unit, with a high-pressure fuel pump, with at least one pump element and with a prefeed pump, wherein the prefeed pump delivers fuel from a tank to the suction side of the pump or elements and wherein the funded by the prefeed pump amount of fuel through a directional control valve to the one or more pump elements or in addition to a low pressure region of the high-pressure fuel pump is passed.
  • This known from DE 196 53 339 A1 high-pressure fuel pump has a directional control valve which distributes depending on the pressure on the suction side of the high-pressure fuel pump funded by the prefeed pump fuel to the low pressure region of the high-pressure fuel pump or the suction side of the pump elements. With this directional valve consequential damage to the high-pressure fuel pump should be avoided if, for example. By a clogged fuel filter, the flow rate of the feed pump is not sufficient. Through a throttle bore in the directional control valve, the low-pressure region of the high-pressure fuel pump is permanently connected to the suction side of the High-pressure fuel pump connected. Therefore, the flow rate of the electrical feed pump must be sized relatively large. A zero-feed throttle is not provided in this high-pressure fuel pump. The pressure control is rather on the high pressure side of the high-pressure fuel pump by a pressure relief valve, resulting in a poor overall efficiency of the fuel injection system.
  • the invention has for its object to provide a Kraftstoffeinspritzanalge whose performance is improved in most operating conditions, whose structure has been simplified and which is easily adaptable to different internal combustion engines and Vor meetingpumpen.
  • This object is achieved according to the invention for a fuel injection system of an internal combustion engine with a control unit, with a high-pressure fuel pump, with at least one pump element and with a prefeed pump, wherein the prefeed pump fuel from a tank to the suction side or the pump elements promotes, solved that funded by the prefeed pump Amount of fuel is passed through a continuously variable directional control valve to the one or more pump elements or in addition to a low pressure region of the high-pressure fuel pump, and that the directional control valve is controlled by the control unit in dependence on the operating condition of the internal combustion engine and the fuel injection system.
  • the flow control of the high-pressure fuel pump can be made more efficient, since the fuel quantity sucked in by the high-pressure fuel pump is regulated and not the high-pressure fuel on the pressure side of the high-pressure fuel pump throttled for pressure control.
  • a venting of the high-pressure fuel pump can be made by a suitable control of the continuously adjustable directional control valve, if this should be necessary.
  • the cooling as well as the lubrication of the high-pressure fuel pump by a suitable control of the continuously adjustable directional control valve according to the operating conditions of the high-pressure fuel pump and / or the internal combustion engine, so that is always taken care of sufficient lubrication and cooling of the high-pressure fuel pump.
  • the directional control valve is designed as a single-stage three-way valve with an input and a first output and a second output that the input of the directional control valve is in communication with the delivery side of the prefeed that the first output of Directional valve is in communication with the suction side of the pump or elements, and that the second output of the directional control valve is in communication with the low pressure region of the high-pressure fuel pump.
  • the advantages according to the invention can be realized in a simple manner.
  • the entire delivery of the feed pump can be directed to the pump elements, it can be the low pressure range of the high-pressure fuel pump enllibraryet and cooling and lubrication of the fuel high-pressure pump can meet demand be measured.
  • the feed pump must promote only against the necessary minimum pressure, so that the energy consumption of the pre-supply pump minimized and their life is maximized.
  • the directional control valve has a slider guided in a valve housing, wherein in a further embodiment of the invention it can be provided that the valve housing has a recess, that the input of the directional control valve opens into the recess, and that the slider in dependence Position in the valve housing, the first output and the second output of the directional control valve more or less releases.
  • the directional control valve releases the first output and shuts off the second output when no input signal is applied to the directional control valve, and / or that with increasing input signal, the slider releases the second output to an increasing extent and the first output increasingly blocked, so that in a simple manner the desired distribution of the funded by the feed pump fuel flow can be done on the pump elements and / or the low pressure area.
  • a cooperating with the slide valve seat is formed in the valve housing, which is closed at fully controlled directional control valve by the slide and thus separates the first output from the input, so that no fuel reaches the pump elements.
  • This valve position is especially in the push mode of the internal combustion engine advantage. Because of the low pressures that act on the directional control valve according to the invention, this valve seat can reliably and without leakage seal the first output, so that the pump elements suck no fuel and Thus, a zero delivery throttle in the high pressure region of the high-pressure fuel pump can be dispensed with. As a result, the energy consumption of the prefeed pump is further reduced and also further improves the starting behavior of the internal combustion engine.
  • a throttle is present between the first output and the second output.
  • Alternative embodiments of the invention provide that the throttle is designed as a bore in the slide or in the valve housing or by the clearance between the slide and the valve housing.
  • a pressure relief valve is provided between the first output and a suction side of the prefeed pump.
  • This pressure relief valve is especially advantageous when the prefeed pump is driven by the internal combustion engine or the high-pressure fuel pump and thus increases the delivery capacity with increasing speed of the internal combustion engine approximately linearly.
  • the pressure relief valve prevents the power requirement of the feed pump increases proportionally with the speed of the internal combustion engine.
  • the aforementioned object is also achieved by a method for generating and supplying high-pressure fuel in a fuel injection system, with a control unit, with at least one pump element, with a prefeed pump, wherein the prefeed pump fuel from a tank to the suction side or the pump elements promotes and wherein the funded by the prefeed pump fuel through a Directional valve is passed to the one or more pump elements or in addition to a low pressure region of the high-pressure fuel pump, achieved in that the delivery rate of the feed pump is distributed depending on the operating condition of the internal combustion engine or the fuel injection system on the suction side of the pump or elements and the low pressure region of the high-pressure fuel pump.
  • a prefeed pump 1 sucks fuel from a tank 5, not shown, via a feed line 3.
  • the fuel is filtered in a pre-filter 7 and a filter with water 9.
  • the prefeed pump 1 is designed as a gear pump and has a first pressure relief valve 11. Suction side becomes the feed pump 1 throttled by a first throttle 13. A pressure side 15 of the prefeed pump 1 supplies a high-pressure fuel pump 17 with fuel.
  • the high-pressure fuel pump 17 is designed as a radial piston pump with three pump elements 19 and drives the prefeed pump 1 at. On the suction side of the pump elements 19 a suction valve 21 is ever provided. On the pressure side of the pump elements 19, a non-return valve 23 is provided which prevents the fuel under high pressure, which was pumped by the pump elements 19 into a common rail 25, from flowing back into the pump elements 19.
  • the high pressure lines of the fuel injection system are shown in FIGS. 1 and 2 with thick lines, while the low pressure areas of the fuel injection system are shown with thin lines.
  • the common rail 25 supplies one or more injectors, not shown in FIG. 1, with fuel via a respective high-pressure line 27.
  • the high-pressure fuel pump 17 is supplied by the feed pump 1 on the one hand with fuel for the pump elements 19 and on the other hand with fuel for lubrication.
  • the distribution of the funded by the feed pump 1 fuel is carried out by means of a continuously adjustable directional control valve 33. Construction and function of the directional control valve 33 will be described below with reference to FIGS. 3 and 4 in detail described.
  • the directional control valve 33 has an input 35 which communicates with the pressure side 15 of the feed pump 1, a first output 37 and a second output 39.
  • a slide 41 of the directional control valve 33 distributes the amount of fuel delivered by the prefeed pump 1 to the first outlet 37 and the second output 39.
  • the amount of fuel which serves to lubricate the high-pressure fuel pump 17 is supplied via the second output 39 and a line 43 of the high-pressure fuel pump 17. Via a distribution line 45, the pump elements 19 are supplied with fuel from the first output 37 of the directional control valve 33.
  • a second throttle 49 may be provided, which is also referred to below as the zero-feed throttle.
  • the zero flow throttle 49 By the zero flow throttle 49, the fuel from the distribution line 45 can flow into the low pressure region of the fuel injection system. Due to the outflow of fuel through the zero flow throttle 49 of the above-mentioned pressure build-up in the Distribution line 45 during coasting due to the leakage of the directional control valve 33 in the first output 37 prevented.
  • FIG. 2 shows a second embodiment is shown schematically.
  • the Vör malpumpe is disposed in the tank 5 and is driven by electrical energy.
  • the same components have been provided with the same reference numerals as in FIG. 1 and the same applies with regard to FIG. 1.
  • no zero-feed throttle is provided.
  • FIG. 3 shows a first exemplary embodiment of a continuously adjustable directional control valve 33 according to the invention.
  • the slider 41 In a valve housing 51, the slider 41 is guided. In the valve housing 51, a recess 53 is provided in which the inlet 35 opens. The input 35 communicates with the pressure side 15 of the prefeed pump 1 (not shown in FIG. 3).
  • the slider 41 has a first control edge (55) and a second control edge (57), which cooperate with the recess 53.
  • the slider 41 is adjusted by a compression spring 59 and an electromagnet 61.
  • the first control edge 55 blocks the hydraulic connection between the recess 53, or inlet 35, and the second outlet 39 of the directional control valve. This means that the entire amount of fuel delivered by the prefeed pump, not shown, flows via the inlet 35 and the recess 53 to the first outlet 37 and thus to the pump elements 19 (not shown).
  • the slider 41 moves upward against the spring force of the compression spring 59 in FIG. Once the first control edge 55 releases the recess 53, a partial flow of the not shown prefeed pump funded fuel flow into the second output 39. Depending on the position of the slide 41 relative to the recess 53, the ratio of the amount of fuel flowing into the first output 37 and the second output 39 changes. As soon as the second control edge 57 has reached the upper end of the recess 53 in FIG. 3, the slider 41 blocks the connection between the input 35 and the first output 37.
  • an optimal distribution of the amount of fuel delivered by the prefeed pump to the pump elements or the low pressure region of the high-pressure fuel pump 17 can be made. If, for example, value is placed on the best possible starting behavior of the internal combustion engine, during commissioning of the internal combustion engine, the entire amount of fuel delivered by the prefeed pump can be directed to the pump elements 19 (not shown). This results in a very fast pressure build-up on the high pressure side of the high-pressure fuel pump.
  • the first output 37 can be blocked by the slide 41, so that the funded by the feed pump, not shown fuel quantity flows exclusively in the low pressure region of the high-pressure fuel pump and there High-pressure fuel pump cools, removes vapor bubbles and lubricates the high-pressure fuel pump.
  • the prefeed pump automatically opposes only the pressure at the first outlet 37 on the suction side of the pump elements 19 (not shown), then that the energy requirement of the pre-feed pump is only as great as absolutely necessary. Excess fuel is discharged via the second output 39. This also significantly increases the service life of the pre-feed pump. There is no additional overflow valve required to control the element inlet pressure.
  • a throttle 63 is provided in the form of a bore in the slider 41.
  • the throttle 63 can assume the function of a zero-feed throttle 49 (see above FIG. 1). Through the throttle bore, it is also possible to vent the low-pressure circuit when the solenoid 61 is de-energized. When the solenoid 61 is fully energized, i. the connection of input 35 and first output 37 is blocked, the throttle 63 acts as a zero feed throttle. In all other operating conditions, the throttle 63 ensures that always a minimum amount of cooling and lubricating via the second output 39 in the low pressure region of the high-pressure fuel pump 17, not shown, can flow.
  • the throttle 63 can also be realized by the clearance between the slide 41 and the valve housing 51. Alternatively, it is also conceivable to provide a bore (not shown) in housing 51, which connects first output 37 and second output 39 to one another.
  • FIG. 4 shows a second embodiment of a directional control valve 33 according to the invention.
  • the throttle 63 is in a bypass 65, which branches off from the input 35 and in the part of the valve housing 51 opens from which the second output 39 goes off, arranged.
  • this interconnection of the throttle 63 ensures that the necessary minimum cooling and lubricating amount of fuel can flow off via the second output 39, regardless of the position of the slide 41.
  • a sealing seat 67 is provided in the upper part of the valve housing 51 in FIG.
  • the second control edge 57 of the slider 41 rests on the sealing seat 67 and seals the inlet 35 from the first outlet 37 without leakage.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Kraftstoffeinspritzanlage für eine Brennkraftmaschine mit einem Steuergerät, mit einer Kraftstoffhochdruckpumpe, mit mindestens einem Pumpenelement und mit einer Vorförderpumpe, wobei die Vorförderpumpe Kraftstoff aus einem Tank zur Saugseite des oder der Pumpenelemente fördert und wobei die von der Vorförderpumpe geförderte Kraftstoffmenge durch ein Wegeventil zu dem oder den Pumpenelementen oder zusätzlich zu einem Niederdruckbereich der Kraftstoffhochdruckpumpe geleitet wird.The invention relates to a fuel injection system for an internal combustion engine with a control unit, with a high-pressure fuel pump, with at least one pump element and with a prefeed pump, wherein the prefeed pump delivers fuel from a tank to the suction side of the pump or elements and wherein the funded by the prefeed pump amount of fuel through a directional control valve to the one or more pump elements or in addition to a low pressure region of the high-pressure fuel pump is passed.

Diese aus der DE 196 53 339 A1 bekannte Kraftstoffhochdruckpumpe weist ein Wegeventil auf, welches in Abhängigkeit des Drucks auf der Saugseite der Kraftstoffhochdruckpumpe den von der Vorförderpumpe geförderten Kraftstoff auf den Niederdruckbereich der Kraftstoffhochdruckpumpe oder die Saugseite der Pumpenelemente verteilt. Mit diesem Wegeventil sollen Folgeschäden an der Kraftstoffhochdruckpumpe vermieden werden, wenn, bspw. durch einen verstopften Kraftstofffilter, die Fördermenge der Vorförderpumpe nicht ausreichend ist. Durch eine Drosselbohrung in dem Wegeventil ist der Niederdruckbereich der Kraftstoffhochdruckpumpe permanent mit der Saugseite der Kraftstoffhochdruckpumpe verbunden. Deshalb muss die Förderleistung der elektrischen Vorförderpumpe relativ groß bemessen werden. Eine Nullförderdrossel ist bei dieser Kraftstoffhochdruckpumpe nicht vorgesehen. Die Druckregelung erfolgt vielmehr auf der Hochdruckseite der Kraftstoffhochdruckpumpe durch ein Druckbegrenzungsventil, was zu einen schlechten Gesamtwirkungsgrad des Kraftstoffeinspritzsystems führt.This known from DE 196 53 339 A1 high-pressure fuel pump has a directional control valve which distributes depending on the pressure on the suction side of the high-pressure fuel pump funded by the prefeed pump fuel to the low pressure region of the high-pressure fuel pump or the suction side of the pump elements. With this directional valve consequential damage to the high-pressure fuel pump should be avoided if, for example. By a clogged fuel filter, the flow rate of the feed pump is not sufficient. Through a throttle bore in the directional control valve, the low-pressure region of the high-pressure fuel pump is permanently connected to the suction side of the High-pressure fuel pump connected. Therefore, the flow rate of the electrical feed pump must be sized relatively large. A zero-feed throttle is not provided in this high-pressure fuel pump. The pressure control is rather on the high pressure side of the high-pressure fuel pump by a pressure relief valve, resulting in a poor overall efficiency of the fuel injection system.

Der Erfindung liegt die Aufgabe zugrunde, eine Kraftstoffeinspritzanalge bereitzustellen, deren Betriebsverhalten in den meisten Betriebszuständen verbessert wird, deren Aufbau vereinfacht wurde und die auf einfachste Weise an unterschiedliche Brennkraftmaschinen und Vorförderpumpen adaptierbar ist.The invention has for its object to provide a Kraftstoffeinspritzanalge whose performance is improved in most operating conditions, whose structure has been simplified and which is easily adaptable to different internal combustion engines and Vorförderpumpen.

Diese Aufgabe wird erfindungsgemäß für eine Kraftstoffeinspritzanlage einer Brennkraftmaschine mit einem Steuergerät, mit einer Kraftstoffhochdruckpumpe, mit mindestens einem Pumpenelement und mit einer Vorförderpumpe, wobei die Vorförderpumpe Kraftstoff aus einem Tank zur Saugseite des oder der Pumpenelemente fördert, dadurch gelöst, dass die von der Vorförderpumpe geförderte Kraftstoffmenge durch ein stetig verstellbares Wegeventil zu dem oder den Pumpenelementen oder zusätzlich zu einem Niederdruckbereich der Kraftstoffhochdruckpumpe geleitet wird, und dass das Wegeventil von dem Steuergerät in Abhängkeit des Betriebszustands der Brennkraftmaschine und des Kraftstoffeinspritzsystems angesteuert wird.This object is achieved according to the invention for a fuel injection system of an internal combustion engine with a control unit, with a high-pressure fuel pump, with at least one pump element and with a prefeed pump, wherein the prefeed pump fuel from a tank to the suction side or the pump elements promotes, solved that funded by the prefeed pump Amount of fuel is passed through a continuously variable directional control valve to the one or more pump elements or in addition to a low pressure region of the high-pressure fuel pump, and that the directional control valve is controlled by the control unit in dependence on the operating condition of the internal combustion engine and the fuel injection system.

Durch den Einsatz eines stetig verstellbaren Wegeventils kann die Fördermengenregelung der Kraftstoffhochdruckpumpe effizienter erfolgen, da die von der Kraftstoffhochdruckpumpe angesaugte Kraftstoffmenge geregelt wird und nicht der unter hohem Druck stehende Kraftstoff auf der Druckseite der Kraftstoffhochdruckpumpe zur Druckregelung gedrosselt wird. Außerdem kann durch eine geeignete Ansteuerung des stetig verstellbaren Wegeventils beim Start der Brennkraftmaschine die gesamte Fördermenge der Vorförderpumpe zu den Pumpenelementen geführt werden, so dass der Druckaufbau auf der Druckseite der Kraftstoffhochdruckpumpe schnellstmöglich erfolgt und somit auch die Brennkraftmaschine schnellstmöglich startet. Außerdem kann durch eine geeignete Ansteuerung des stetig verstellbaren Wegeventils eine Entlüftung der Kraftstoffhochdruckpumpe vorgenommen werden, wenn dies erforderlich sein sollte. Außerdem kann die Kühlung ebenso wie die Schmierung der Kraftstoffhochdruckpumpe durch eine geeignete Ansteuerung des stetig verstellbaren Wegeventils entsprechend den Betriebszuständen der Kraftstoffhochdruckpumpe und/oder der Brennkraftmaschine erfolgen, so dass immer für eine ausreichende Schmierung und Kühlung der Kraftstoffhochdruckpumpe gesorgt ist.Through the use of a continuously adjustable directional control valve, the flow control of the high-pressure fuel pump can be made more efficient, since the fuel quantity sucked in by the high-pressure fuel pump is regulated and not the high-pressure fuel on the pressure side of the high-pressure fuel pump throttled for pressure control. In addition, can be performed by a suitable control of the continuously variable directional control valve at the start of the internal combustion engine, the entire delivery of the feed pump to the pump elements, so that the pressure build-up on the pressure side of the high-pressure fuel pump takes place as quickly as possible and thus the engine starts as soon as possible. In addition, a venting of the high-pressure fuel pump can be made by a suitable control of the continuously adjustable directional control valve, if this should be necessary. In addition, the cooling as well as the lubrication of the high-pressure fuel pump by a suitable control of the continuously adjustable directional control valve according to the operating conditions of the high-pressure fuel pump and / or the internal combustion engine, so that is always taken care of sufficient lubrication and cooling of the high-pressure fuel pump.

Bei einer Variante der erfindungsgemäßen Kraftstoffhochdruckpumpe ist vorgesehen, dass das Wegeventil als einstufiges Drei-Wegeventil mit einem Eingang sowie einem ersten Ausgang und einem zweiten Ausgang ausgebildet ist, dass der Eingang des Wegeventils mit der Förderseite der Vorförderpumpe in Verbindung steht, dass der erste Ausgang des Wegeventils mit der Saugseite des oder der Pumpenelemente in Verbindung steht, und dass der zweite Ausgang des Wegeventils mit dem Niederdruckbereich der Kraftstoffhochdruckpumpe in Verbindung steht. Bei dieser Variante können auf einfache Weise die erfindungsgemäßen Vorteile realisiert werden. Insbesondere kann, je nach Ansteuerung des Wegeventils, die gesamte Fördermenge der Vorförderpumpe zu den Pumpenelementen geleitet werden, es kann der Niederdruckbereich der Kraftstoffhochdruckpumpe enlüftet werden und Kühlung sowie Schmierung der Kraftstoffstoffhochdruckpumpe können bedarfsgerecht bemessen werden. Außerdem muss die Vorförderpumpe nur gegen den notwendigen Mindestdruck anfördern, so dass die Energieaufnahme der Vorförderpumpe minimiert und deren Lebensdauer maximiert wird.In a variant of the high-pressure fuel pump according to the invention it is provided that the directional control valve is designed as a single-stage three-way valve with an input and a first output and a second output that the input of the directional control valve is in communication with the delivery side of the prefeed that the first output of Directional valve is in communication with the suction side of the pump or elements, and that the second output of the directional control valve is in communication with the low pressure region of the high-pressure fuel pump. In this variant, the advantages according to the invention can be realized in a simple manner. In particular, depending on the control of the directional control valve, the entire delivery of the feed pump can be directed to the pump elements, it can be the low pressure range of the high-pressure fuel pump enlüftet and cooling and lubrication of the fuel high-pressure pump can meet demand be measured. In addition, the feed pump must promote only against the necessary minimum pressure, so that the energy consumption of the pre-supply pump minimized and their life is maximized.

In weiterer Ergänzung der Erfindung weist das Wegeventil einen in einem Ventilgehäuse geführten Schieber auf, wobei in weiterer Ausgestaltung der Erfindung vorgesehen sein kann, dass das Ventilgehäuse eine Ausnehmung aufweist, dass der Eingang des Wegeventils in die Ausnehmung mündet, und dass der Schieber in Abhängigkeit seiner Stellung in dem Ventilgehäuse den ersten Ausgang und den zweiten Ausgang des Wegeventils mehr oder weniger freigibt.In a further feature of the invention, the directional control valve has a slider guided in a valve housing, wherein in a further embodiment of the invention it can be provided that the valve housing has a recess, that the input of the directional control valve opens into the recess, and that the slider in dependence Position in the valve housing, the first output and the second output of the directional control valve more or less releases.

Dabei kann in weiterer Ergänzung der Erfindung vorgesehen sein, dass das Wegeventil den ersten Ausgang freigibt und den zweiten Ausgang absperrt, wenn kein Eingangssignal am Wegeventil anliegt, und/oder dass mit zunehmenden Eingangssignal der Schieber den zweiten Ausgang in zunehmendem Maße freigibt und den ersten Ausgang in zunehmendem Maße absperrt, so dass auch auf einfache Weise die gewünschte Verteilung des von der Vorförderpumpe geförderten Kraftstoffstroms auf die Pumpenelemente und/oder den Niederdruckbereich erfolgen kann.It can be provided in a further supplement to the invention that the directional control valve releases the first output and shuts off the second output when no input signal is applied to the directional control valve, and / or that with increasing input signal, the slider releases the second output to an increasing extent and the first output increasingly blocked, so that in a simple manner the desired distribution of the funded by the feed pump fuel flow can be done on the pump elements and / or the low pressure area.

Bei einer anderen Ausgestaltung der Erfindung ist in dem Ventilgehäuse ein mit dem Schieber zusammenwirkender Ventilsitz ausgebildet, der bei voll angesteuertem Wegeventil von dem Schieber verschlossen wird und somit den ersten Ausgang vom Eingang trennt, so dass kein Kraftstoff mehr zu den Pumpenelementen gelangt. Diese Ventilstellung ist vor allem im Schiebebetrieb der Brennkraftmaschine von Vorteil. Wegen der geringen Drücke, die auf das erfindungsgemäße Wegeventil wirken, kann dieser Ventilsitz zuverlässig und ohne Leckage den ersten Ausgang abdichten, so dass die Pumpenelemente keinen Kraftstoff ansaugen und somit auf eine Nullförderdrossel im Hochdruckbereich der Kraftstoffhochdruckpumpe verzichtet werden kann. Dadurch wird die Energieaufnahme der Vorförderpumpe weiter reduziert und außerdem das Startverhalten der Brennkraftmaschine weiter verbessert.In another embodiment of the invention, a cooperating with the slide valve seat is formed in the valve housing, which is closed at fully controlled directional control valve by the slide and thus separates the first output from the input, so that no fuel reaches the pump elements. This valve position is especially in the push mode of the internal combustion engine advantage. Because of the low pressures that act on the directional control valve according to the invention, this valve seat can reliably and without leakage seal the first output, so that the pump elements suck no fuel and Thus, a zero delivery throttle in the high pressure region of the high-pressure fuel pump can be dispensed with. As a result, the energy consumption of the prefeed pump is further reduced and also further improves the starting behavior of the internal combustion engine.

Um eine Mindestversorgung der des Niederdruckbereichs der Kraftstoffhochdruckpumpe mit Kraftstoff zur Schmierung und zur Kühlung zu gewährleisten, kann vorgesehen sein, dass zwischen erstem Ausgang und zweitem Ausgang eine Drossel vorhanden ist. Alternative Ausführungsformen der Erfindung sehen vor, dass die Drossel als Bohrung in dem Schieber oder im Ventilgehäuse oder durch das Spiel zwischen Schieber und Ventilgehäuse ausgeführt wird.In order to ensure a minimum supply of the low-pressure region of the high-pressure fuel pump with fuel for lubrication and cooling, it can be provided that a throttle is present between the first output and the second output. Alternative embodiments of the invention provide that the throttle is designed as a bore in the slide or in the valve housing or by the clearance between the slide and the valve housing.

Um die Leistungsaufnahme der Vorförderpumpe weiter zu begrenzen ist in weiterer Ergänzung der Erfindung vorgesehen, dass zwischen erstem Ausgang und einer Saugseite der Vorförderpumpe ein Druckbegrenzungsventil vorgesehen ist. Dieses Druckbegrenzungsventil ist vor allem dann vorteilhaft, wenn die Vorförderpumpe von der Brennkraftmaschine oder der Kraftstoffhochdruckpumpe angetrieben wird und somit die Förderleistung mit zunehmender Drehzahl der Brennkraftmaschine annähernd linear ansteigt. Das Druckbegrenzungsventil verhindert, dass auch der Leistungsbedarf der Vorförderpumpe mit der Drehzahl der Brennkraftmaschine proportional ansteigt.In order to further limit the power consumption of the feed pump is provided in a further supplement to the invention that between the first output and a suction side of the prefeed pump, a pressure relief valve is provided. This pressure relief valve is especially advantageous when the prefeed pump is driven by the internal combustion engine or the high-pressure fuel pump and thus increases the delivery capacity with increasing speed of the internal combustion engine approximately linearly. The pressure relief valve prevents the power requirement of the feed pump increases proportionally with the speed of the internal combustion engine.

Die eingangs genannte Aufgabe wird erfindungsgemäß auch gelöst durch ein Verfahren zum Erzeugen und Zuführen von unter Hochdruck stehendem Kraftstoff in einer Kraftstoffeinspritzanlage, mit einem Steuergerät, mit mindestens einem Pumpenelement, mit einer Vorförderpumpe, wobei die Vorförderpumpe Kraftstoff aus einem Tank zur Saugseite des oder der Pumpenelemente fördert und wobei die von der Vorförderpumpe geförderte Kraftstoffmenge durch ein Wegeventil zu dem oder den Pumpenelementen oder zusätzlich zu einem Niederdruckbereich der Kraftstoffhochdruckpumpe geleitet wird, dadurch gelöst, dass die Fördermenge der Vorförderpumpe in Abhängigkeit des Betriebszustands der Brennkraftmaschine oder des Kraftstoffeinspritzsystems auf die Saugseite des oder der Pumpenelemente und den Niederdruckbereich der Kraftstoffhochdruckpumpe verteilt wird. Mit dem erfindungsgemäßen Verfahren lassen sich die eingangs genannten Vorteile der Erfindung ebenfalls realisieren.The aforementioned object is also achieved by a method for generating and supplying high-pressure fuel in a fuel injection system, with a control unit, with at least one pump element, with a prefeed pump, wherein the prefeed pump fuel from a tank to the suction side or the pump elements promotes and wherein the funded by the prefeed pump fuel through a Directional valve is passed to the one or more pump elements or in addition to a low pressure region of the high-pressure fuel pump, achieved in that the delivery rate of the feed pump is distributed depending on the operating condition of the internal combustion engine or the fuel injection system on the suction side of the pump or elements and the low pressure region of the high-pressure fuel pump. With the method according to the invention, the advantages of the invention mentioned above can also be realized.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung und deren Beschreibung entnehmbar.Further advantages and advantageous embodiments of the invention are the following drawings and their description can be removed.

Zeichnungdrawing

Es zeigen:

Figur 1 und 2
Ausführungsbeispiele erfindungsgemäßer Kraftstoffeinspritzsysteme und
Figur 3 und 4
Ausführungsbeispiele von erfindungsgemäßen stetig verstellbaren Wegeventilen.
Show it:
FIGS. 1 and 2
Embodiments of inventive fuel injection systems and
FIGS. 3 and 4
Embodiments of the invention continuously adjustable directional control valves.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein Ausführungsbeispiel eines erfindungsgemäßen Common-Rail-Einspritzsystems schematisch dargestellt. Eine Vorförderpumpe 1 saugt über eine Zulaufleitung 3 nicht dargestellten Kraftstoff aus einem Tank 5 an. Dabei wird der Kraftstoff in einem Vorfilter 7 und einem Filter mit Wasserabscheider 9 gefiltert.1 shows an embodiment of a common rail injection system according to the invention is shown schematically. A prefeed pump 1 sucks fuel from a tank 5, not shown, via a feed line 3. The fuel is filtered in a pre-filter 7 and a filter with water 9.

Die Vorförderpumpe 1 ist als Zahnradpumpe ausgebildet und weist ein erstes Überdruckventil 11 auf. Saugseitig wird die Vorförderpumpe 1 durch eine erste Drossel 13 gedrosselt. Eine Druckseite 15 der Vorförderpumpe 1 versorgt eine Kraftstoffhochdruckpumpe 17 mit Kraftstoff. Die Kraftstoffhochdruckpumpe 17 ist als Radialkolbenpumpe mit drei Pumpenelementen 19 ausgeführt und treibt die Vorförderpumpe 1 an. Auf der Saugseite der Pumpenelemente 19 ist je ein Saugventil 21.vorgesehen. Auf der Druckseite der Pumpenelemente 19 ist je ein Rückschlagventil 23 vorgesehen, welches verhindert, dass der unter hohem Druck stehende Kraftstoff, welcher von den Pumpenelementen 19 in ein Common-Rail 25 gefördert wurde, in die Pumpenelemente 19 zurückfließen kann.The prefeed pump 1 is designed as a gear pump and has a first pressure relief valve 11. Suction side becomes the feed pump 1 throttled by a first throttle 13. A pressure side 15 of the prefeed pump 1 supplies a high-pressure fuel pump 17 with fuel. The high-pressure fuel pump 17 is designed as a radial piston pump with three pump elements 19 and drives the prefeed pump 1 at. On the suction side of the pump elements 19 a suction valve 21 is ever provided. On the pressure side of the pump elements 19, a non-return valve 23 is provided which prevents the fuel under high pressure, which was pumped by the pump elements 19 into a common rail 25, from flowing back into the pump elements 19.

Die unter Hochdruck stehenden Leitungen des Kraftstoffeinspritzsystems sind in den Fig. 1 und 2 mit dicken Linien gezeichnet, während die unter niedrigem Druck stehenden Bereiche des Kraftstoffeinspritzsystems mit dünnen Linien dargestellt sind.The high pressure lines of the fuel injection system are shown in FIGS. 1 and 2 with thick lines, while the low pressure areas of the fuel injection system are shown with thin lines.

Der Common-Rail 25 versorgt einen oder mehrere in Figur 1 nicht dargestellte Injektoren mit Kraftstoff über je eine Hochdruckleitung 27. Ein Druckregelventil 28, welches bei Bedarf den Common-Rail mit einer Rücklaufleitung 29 verbindet, regelt den Einspritzdruck der Injektoren (nicht dargestellt). Über die Rücklaufleitung 29 und eine Leckageleitung 31 werden die Leckage und die Steuermengen des oder der nicht dargestellten Injektoren in den Tank 5 zurückgeführt.The common rail 25 supplies one or more injectors, not shown in FIG. 1, with fuel via a respective high-pressure line 27. A pressure-regulating valve 28, which if necessary connects the common rail to a return line 29, regulates the injection pressure of the injectors (not shown). Via the return line 29 and a leakage line 31, the leakage and the control amounts of the injector or not shown, are returned to the tank 5.

Die Kraftstoffhochdruckpumpe 17 wird von der Vorförderpumpe 1 einerseits mit Kraftstoff für die Pumpenelemente 19 und andererseits mit Kraftstoff zur Schmierung versorgt. Die Aufteilung des von der Vorförderpumpe 1 geförderten Kraftstoffs erfolgt mit Hilfe eines stetig verstellbaren Wegeventils 33. Aufbau und Funktion des Wegeventils 33 werden nachfolgend anhand der Fig. 3 und 4 noch ausführlich beschrieben. Das Wegeventil 33 hat einen Eingang 35, der mit der Druckseite 15 der Vorförderpumpe 1 in Verbindung steht, einen ersten Ausgang 37 und einen zweiten Ausgang 39. Ein Schieber 41 des Wegeventils 33 verteilt die von der Vorförderpumpe 1 geförderte Kraftstoffmenge auf den ersten Ausgang 37 und den zweiten Ausgang 39.The high-pressure fuel pump 17 is supplied by the feed pump 1 on the one hand with fuel for the pump elements 19 and on the other hand with fuel for lubrication. The distribution of the funded by the feed pump 1 fuel is carried out by means of a continuously adjustable directional control valve 33. Construction and function of the directional control valve 33 will be described below with reference to FIGS. 3 and 4 in detail described. The directional control valve 33 has an input 35 which communicates with the pressure side 15 of the feed pump 1, a first output 37 and a second output 39. A slide 41 of the directional control valve 33 distributes the amount of fuel delivered by the prefeed pump 1 to the first outlet 37 and the second output 39.

Die Kraftstoffmenge, welche zur Schmierung der Kraftstoffhochdruckpumpe 17 dient, wird über den zweiten Ausgang 39 und eine Leitung 43 der Kraftstoffhochdruckpumpe 17 zugeführt. Über eine Verteilleitung 45 werden die Pumpenelemente 19 mit Kraftstoff aus dem ersten Ausgang 37 des Wegeventils 33 versorgt.The amount of fuel which serves to lubricate the high-pressure fuel pump 17 is supplied via the second output 39 and a line 43 of the high-pressure fuel pump 17. Via a distribution line 45, the pump elements 19 are supplied with fuel from the first output 37 of the directional control valve 33.

Im Schiebebetrieb, d.h. bspw. bei einer Bergabfahrt eines Kraftfahrzeugs, soll kein Kraftstoff in die Pumpenelemente 19 fließen und auch kein Kraftstoff von den nicht dargestellten Injektoren in die Brennräume der Brennkraftmaschine eingespritzt werden. Da unter ungünstigen Umständen in diesem Betriebszustand bei manchen Ausführungsformen des Wegeventils 33 Kraftstoff aus dem ersten Ausgang 37 des Wegeventils 33 zu den Pumpenelementen 19 gelangen kann, würde sich ohne geeignete Abhilfemaßnahmen auf der Saugseite der Pumpenelemente 19 ein Druck aufbauen, der so groß ist, dass die Pumpenelemente 19 während des Saughubs die Saugventile 21 öffnen und Kraftstoff ansaugen. Dies hätte zur Folge, dass der Druck im Common-Rail 25 unzulässig ansteigt.In push mode, i. For example, in a downhill driving of a motor vehicle, no fuel should flow into the pump elements 19 and no fuel from the injectors, not shown, are injected into the combustion chambers of the internal combustion engine. Since unfavorable circumstances in this operating state in some embodiments of the directional valve 33 fuel from the first output 37 of the directional control valve 33 can reach the pump elements 19, would build up without suitable remedial measures on the suction side of the pump elements 19, a pressure that is so great that the pump elements 19 open the suction valves 21 during the intake stroke and suck in fuel. This would mean that the pressure in the common rail 25 increases inadmissible.

Um dies zu verhindern, kann eine zweite Drossel 49 vorgesehen werden, die nachfolgend auch als Nullförder-Drossel bezeichnet wird. Durch die Nullförder-Drossel 49 kann der Kraftstoff aus der Verteilleitung 45 in den Niederdruckbereich der Kraftstoffeinspritzanlage abfließen. Durch den Abfluss von Kraftstoff durch die Nullförder-Drossel 49 wird der oben erwähnte Druckaufbau in der Verteilleitung 45 beim Schiebebetrieb auf Grund der Leckage des Wegeventils 33 in den ersten Ausgang 37 verhindert.To prevent this, a second throttle 49 may be provided, which is also referred to below as the zero-feed throttle. By the zero flow throttle 49, the fuel from the distribution line 45 can flow into the low pressure region of the fuel injection system. Due to the outflow of fuel through the zero flow throttle 49 of the above-mentioned pressure build-up in the Distribution line 45 during coasting due to the leakage of the directional control valve 33 in the first output 37 prevented.

In Figur 2 ist ein zweites Ausführungsbeispiel schematisch dargestellt. Bei diesem Ausführungsbeispiel ist die Vörförderpumpe im Tank 5 angeordnet und wird mit elektrischer Energie angetrieben. Gleiche Bauteile wurden mit den gleichen Bezugszeichen wie in Fig. 1 versehen und es gilt das bezüglich Fig. 1 Gesagte entsprechend. Bei dem Ausführungsbeispiel gemäß Fig. 2 ist keine Nullförderdrossel vorgesehen.2 shows a second embodiment is shown schematically. In this embodiment, the Vörförderpumpe is disposed in the tank 5 and is driven by electrical energy. The same components have been provided with the same reference numerals as in FIG. 1 and the same applies with regard to FIG. 1. In the embodiment according to FIG. 2, no zero-feed throttle is provided.

In Figur 3 ist ein erstes Ausführungsbeispiel eines erfindungsgemäßen stetig verstellbaren Wegeventils 33 dargestellt. In einem Ventilgehäuse 51 ist der Schieber 41 geführt. Im Ventilgehäuse 51 ist eine Ausnehmung 53 vorgesehen in welche der Eingang 35 mündet. Der Eingang 35 steht mit der Druckseite 15 der Vorförderpumpe 1 (in Figur 3 nicht dargestellt) in Verbindung. Der Schieber 41 hat eine erste Steuerkante (55) und eine zweite Steuerkante (57), welche mit der Ausnehmung 53 zusammenwirken. Der Schieber 41 wird über eine Druckfeder 59 und einen Elektromagneten 61 verstellt. In der in Figur 3 dargestellten Position des Schiebers 41 sperrt die erste Steuerkante 55 die hydraulische Verbindung zwischen Ausnehmung 53, bzw. Eingang 35, und zweitem Ausgang 39 des Wegeventils. Dies bedeutet, dass die gesamte von der nicht dargestellten Vorförderpumpe geförderte Kraftstoffmenge über den Eingang 35 und die Ausnehmung 53 zum ersten Ausgang 37 und damit zu den Pumpenelementen 19 (nicht dargestellt) strömt.FIG. 3 shows a first exemplary embodiment of a continuously adjustable directional control valve 33 according to the invention. In a valve housing 51, the slider 41 is guided. In the valve housing 51, a recess 53 is provided in which the inlet 35 opens. The input 35 communicates with the pressure side 15 of the prefeed pump 1 (not shown in FIG. 3). The slider 41 has a first control edge (55) and a second control edge (57), which cooperate with the recess 53. The slider 41 is adjusted by a compression spring 59 and an electromagnet 61. In the position of the slide 41 shown in FIG. 3, the first control edge 55 blocks the hydraulic connection between the recess 53, or inlet 35, and the second outlet 39 of the directional control valve. This means that the entire amount of fuel delivered by the prefeed pump, not shown, flows via the inlet 35 and the recess 53 to the first outlet 37 and thus to the pump elements 19 (not shown).

Wenn der Elektromagnet 61 bestromt wird, bewegt sich der Schieber 41 entgegen der Federkraft der Druckfeder 59 in Figur 3 nach oben. Sobald die erste Steuerkante 55 die Ausnehmung 53 freigibt, kann ein Teilstrom der von der nicht dargestellten Vorförderpumpe geförderten Kraftstoff in den zweiten Ausgang 39 strömen. Je nach Stellung des Schiebers 41 relativ zur Ausnehmung 53 ändert sich das Verhältnis der in den ersten Ausgang 37 und den zweiten Ausgang 39 strömenden Kraftstoffmenge. Sobald die zweite Steuerkante 57 das in Figur 3 obere Ende der Ausnehmung 53 erreicht hat, sperrt der Schieber 41 die Verbindung zwischen Eingang 35 und ersten Ausgang 37.When the electromagnet 61 is energized, the slider 41 moves upward against the spring force of the compression spring 59 in FIG. Once the first control edge 55 releases the recess 53, a partial flow of the not shown prefeed pump funded fuel flow into the second output 39. Depending on the position of the slide 41 relative to the recess 53, the ratio of the amount of fuel flowing into the first output 37 and the second output 39 changes. As soon as the second control edge 57 has reached the upper end of the recess 53 in FIG. 3, the slider 41 blocks the connection between the input 35 and the first output 37.

Somit kann je nach Stellung des Schiebers 41 in Abhängigkeit des Betriebszustands der Brennkraftmaschine oder des Kraftstoffeinspritzsystems eine optimale Aufteilung der von der Vorförderpumpe geförderten Kraftstoffmenge auf die Pumpenelemente oder den Niederdruckbereich der Kraftstoffhochdruckpumpe 17 vorgenommen werden. Wenn bspw. Wert auf ein möglichst gutes Startverhalten der Brennkraftmaschine gelegt wird, kann bei der Inbetriebnahme der Brennkraftmaschine die gesamte von der Vorförderpumpe geförderte Kraftstoffmenge zu den Pumpenelementen 19 (nicht dargestellt) geleitet werden. Dadurch ergibt sich ein sehr schneller Druckaufbau auf der Hochdruckseite der Kraftstoffhochdruckpumpe.Thus, depending on the position of the slide 41, depending on the operating state of the internal combustion engine or the fuel injection system, an optimal distribution of the amount of fuel delivered by the prefeed pump to the pump elements or the low pressure region of the high-pressure fuel pump 17 can be made. If, for example, value is placed on the best possible starting behavior of the internal combustion engine, during commissioning of the internal combustion engine, the entire amount of fuel delivered by the prefeed pump can be directed to the pump elements 19 (not shown). This results in a very fast pressure build-up on the high pressure side of the high-pressure fuel pump.

Wenn, bspw. vor einem Heißstart der Brennkraftmaschine, die Kraftstoffhochdruckpumpe gespült und gekühlt werden soll, kann der erste Ausgang 37 durch den Schieber 41 versperrt werden, so dass die von der nicht dargestellten Vorförderpumpe geförderte Kraftstoffmenge ausschließlich in den Niederdruckbereich der Kraftstoffhochdruckpumpe strömt und dort die Kraftstoffhochdruckpumpe kühlt, Dampfblasen abtransportiert und die Kraftstoffhochdruckpumpe schmiert.If, for example, before a hot start of the internal combustion engine, the high-pressure fuel pump is to be flushed, the first output 37 can be blocked by the slide 41, so that the funded by the feed pump, not shown fuel quantity flows exclusively in the low pressure region of the high-pressure fuel pump and there High-pressure fuel pump cools, removes vapor bubbles and lubricates the high-pressure fuel pump.

Besonders vorteilhaft an dem erfindungsgemäßen Wegeventil ist, dass die Vorförderpumpe automatisch nur den am ersten Ausgang 37 anstehenden Druck.auf der Saugseite der Pumpenelemente 19 (nicht dargestellt) entgegensteht, so dass der Energiebedarf der Vorförderpumpe nur so groß ist, wie unbedingt notwendig. Überschüssiger Kraftstoff wird über den zweiten Ausgang 39 abgefördert. Dadurch erhöht sich auch die Lebensdauer der Vorförderpumpe entscheidend. Es ist kein zusätzliches Überströmventil zur Steuerung des Elementzulaufdruckes erforderlich.It is particularly advantageous on the directional control valve according to the invention that the prefeed pump automatically opposes only the pressure at the first outlet 37 on the suction side of the pump elements 19 (not shown), then that the energy requirement of the pre-feed pump is only as great as absolutely necessary. Excess fuel is discharged via the second output 39. This also significantly increases the service life of the pre-feed pump. There is no additional overflow valve required to control the element inlet pressure.

In dem Schieber 41 ist eine Drossel 63 in Form einer Bohrung im Schieber 41 vorgesehen. Die Drossel 63 kann die Funktion einer Nullförderdrossel 49 (siehe oben Figur 1) übernehmen. Durch die Drosselbohrung ist es auch möglich den Niederdruckkreislauf zu entlüften, wenn der Elektromagnet 61 stromlos geschaltet ist. Wenn der Elektromagnet 61 voll bestromt ist, d.h. die Verbindung von Eingang 35 und erstem Ausgang 37 ist gesperrt, wirkt die Drossel 63 als Nullförderdrossel. In allen anderen Betriebszuständen stellt die Drossel 63 sicher, dass stets eine Mindestkühl- und Schmiermenge über den zweiten Ausgang 39 in den Niederdruckbereich der nicht dargestellten Kraftstoffhochdruckpumpe 17 strömen kann. Alternativ kann die Drossel 63 auch durch das Spiel zwischen Schieber 41 und dem Ventilgehäuse 51 realisiert werden. Alternativ ist es auch denkbar im Gehäuse 51 eine Bohrung (nicht dargestellt) vorzusehen, welche ersten Ausgang 37 und zweiten Ausgang 39 miteinander verbindet.In the slider 41, a throttle 63 is provided in the form of a bore in the slider 41. The throttle 63 can assume the function of a zero-feed throttle 49 (see above FIG. 1). Through the throttle bore, it is also possible to vent the low-pressure circuit when the solenoid 61 is de-energized. When the solenoid 61 is fully energized, i. the connection of input 35 and first output 37 is blocked, the throttle 63 acts as a zero feed throttle. In all other operating conditions, the throttle 63 ensures that always a minimum amount of cooling and lubricating via the second output 39 in the low pressure region of the high-pressure fuel pump 17, not shown, can flow. Alternatively, the throttle 63 can also be realized by the clearance between the slide 41 and the valve housing 51. Alternatively, it is also conceivable to provide a bore (not shown) in housing 51, which connects first output 37 and second output 39 to one another.

In Figur 4 ist ein zweites Ausführungsbeispiel eines erfindungsgemäßen Wegeventils 33 dargestellt. Bei diesem Ausführungsbeispiel ist die Drossel 63 in einem Bypass 65, der vom Eingang 35 abzweigt und in den Teil des Ventilgehäuses 51 mündet von dem der zweite Ausgang 39 abgeht, angeordnet. Bei dieser Verschaltung der Drossel 63 ist sichergestellt, dass über den zweiten Ausgang 39 die notwendige Mindestkühl- und Schmiermenge an Kraftstoff abfließen kann, unabhängig von der Stellung des Schiebers 41. In dem in Figur 4 oberen Bereich des Ventilgehäuses 51 ist ein Dichtsitz 67 vorgesehen. Bei vollbestromtem Elektromagnet 61 liegt die zweite Steuerkante 57 des Schiebers 41 auf dem Dichtsitz 67 auf und dichtet ohne Leckage den Eingang 35 vom ersten Ausgang 37 ab. Die Anforderung an die Dichtfunktion des Dichtsitzes 67 wird durch das in dieser Stellung des Schiebers 41 vorteilhafter Weise auf niedrigem Niveau befindliche Druckgefälle erleichtert, da über den dann voll geöffneten zweiten Ausgang 39 eine Verbindung zum Niederdruckbereich der Kraftstoffhochdruckpumpe besteht. Aus diesem Grund ist bei diesem Ausführungsbeispiel keine Nullförderdrossel notwendig.FIG. 4 shows a second embodiment of a directional control valve 33 according to the invention. In this embodiment, the throttle 63 is in a bypass 65, which branches off from the input 35 and in the part of the valve housing 51 opens from which the second output 39 goes off, arranged. In this interconnection of the throttle 63 ensures that the necessary minimum cooling and lubricating amount of fuel can flow off via the second output 39, regardless of the position of the slide 41. In the upper part of the valve housing 51 in FIG a sealing seat 67 is provided. When fully energized solenoid 61, the second control edge 57 of the slider 41 rests on the sealing seat 67 and seals the inlet 35 from the first outlet 37 without leakage. The requirement for the sealing function of the sealing seat 67 is facilitated by the pressure gradient advantageously located at a low level in this position of the slide 41, since there is a connection to the low-pressure region of the high-pressure fuel pump via the then fully opened second outlet 39. For this reason, no zero-feed throttle is necessary in this embodiment.

Claims (17)

  1. Fuel injection system for an internal combustion engine having a control unit, having a high pressure fuel pump, having at least one pump element (19) and having a prefeed pump (1), the prefeed pump (1) feeding fuel from a tank (5) to the suction side of the pump element(s) (19), and the quantity of fuel fed by the prefeed pump (1) being conducted by means of a directional control valve (33) to the pump element(s) (19) or additionally to a low pressure region of the high pressure fuel pump (17), characterized in that the directional control valve (33) is embodied as a continuously adjustable directional control valve (33), and in that the directional control valve (33) is actuated by the control unit as a function of the operating state of the internal combustion engine and/or of the fuel injection system.
  2. Fuel injection system according to Claim 1, characterized in that the directional control valve (33) is embodied as a single-stage 3-way directional control valve having an inlet (35) and a first outlet (37) and a second outlet (39), in that the inlet (35) of the directional control valve (33) is connected to the pressure side (15) of the prefeed pump (1), in that the first outlet (37) of the directional control valve (33) is connected to the suction side of the pump element(s) (19), and in that the second outlet (39) of the directional control valve (33) is connected to the low pressure region of the high pressure fuel pump (17).
  3. Fuel injection system according to Claim 1 or 2, characterized in that the directional control valve (33) has a slide valve (41) which is guided in a valve housing (51).
  4. Fuel injection system according to Claim 3, characterized in that the valve housing (51) has a recess (53), in that the inlet (35) of the directional control valve (33) opens out into the recess (53), and in that the slide valve (41) unblocks the first outlet (37) and the second outlet (39) of the directional control valve (33) to a greater or lesser extent as a function of its position in the valve housing (51).
  5. Fuel injection system according to one of Claims 2 to 4, characterized in that the directional control valve (33) unblocks the first outlet (37) and blocks the second outlet (39) when no input signal is applied to the directional control valve (33).
  6. Fuel injection system according to one of Claims 2 to 5, characterized in that, as the input signal increases, the slide valve (41) unblocks the second outlet (39) to a greater extent and blocks the first outlet (37) to a greater extent.
  7. Fuel injection system according to one of Claims 3 to 6, characterized in that a sealing seat (67) which interacts with the slide valve (41) is formed in the valve housing (51), and in that when the directional control valve (33) is fully actuated, the slide valve (41) bears against the sealing seat (67) and separates the first outlet (37) from the inlet (35).
  8. Fuel injection system according to one of Claims 3 to 7, characterized in that a throttle (63) is provided between the first outlet (37) and the second outlet (39).
  9. Fuel injection system according to Claim 8, characterized in that the throttle (63) is embodied as a bore in the slide valve (41).
  10. Fuel injection system according to Claim 8, characterized in that the throttle (63) is embodied as a bore in the valve housing (51).
  11. Fuel injection system according to Claim 8, characterized in that the throttle (63) is set by the play between the slide valve (41) and the valve housing (51).
  12. Fuel injection system according to one of Claims 2 to 11, characterized in that a pressure limiting valve (11) is provided between the inlet (35) and a suction side of the prefeed pump (1).
  13. Fuel injection system according to one of Claims 2 to 12, characterized in that a throttle (63) is provided between the pressure side (15) of the prefeed pump (1) and a second outlet (39) of the directional control valve (33).
  14. Fuel injection system according to one of the preceding claims, characterized in that the prefeed pump (1) is driven by an electric drive, the internal combustion engine or the high pressure fuel pump (17).
  15. Method for generating and feeding highly pressurized fuel in a fuel injection system according to one of the preceding claims, having a control unit, having at least one pump element (19) and having a prefeed pump (1), the prefeed pump (1) feeding fuel from a tank (5) to the suction side of the pump element(s) (19), and the quantity of fuel fed by the prefeed pump (1) being conducted by means of a directional control valve (33) to the pump element(s) (19) or additionally to a low pressure region of the high pressure fuel pump (17), characterized in that the directional control valve (33) is embodied as a continuously adjustable directional control valve (33), and in that the directional control valve (33) is actuated by the control unit, and in that the feed quantity of the prefeed pump (1) is distributed between the suction side of the pump element(s) (19) and the low pressure region of the high pressure fuel pump as a function of the operating state of the internal combustion engine and/or of the fuel injection system.
  16. Computer program which can be executed on a processing unit, in particular on a control unit for controlling an internal combustion engine, characterized in that the computer program is programmed to carry out a method according to Claim 15 when the computer program is executed on the processing unit.
  17. Computer program according to Claim 16, characterized in that the computer program is stored on a memory element, in particular on a memory element assigned to the processing unit, the memory element being embodied as a random access memory (RAM), a read only memory (ROM), a flash memory, an optical storage medium or a magnetic storage medium.
EP02015909A 2001-10-27 2002-07-17 Fuel injection apparatus in which the displacement control is improved Expired - Lifetime EP1306548B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10153185 2001-10-27
DE10153185A DE10153185A1 (en) 2001-10-27 2001-10-27 Fuel injection system with improved delivery control

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EP1306548A2 EP1306548A2 (en) 2003-05-02
EP1306548A3 EP1306548A3 (en) 2005-11-09
EP1306548B1 true EP1306548B1 (en) 2007-03-14

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EP (1) EP1306548B1 (en)
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JP2003184681A (en) 2003-07-03
US6823845B2 (en) 2004-11-30
DE50209708D1 (en) 2007-04-26
EP1306548A3 (en) 2005-11-09
DE10153185A1 (en) 2003-05-15
JP4138444B2 (en) 2008-08-27
US20030089339A1 (en) 2003-05-15
EP1306548A2 (en) 2003-05-02

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