EP1042608B1 - Kraftstoffversorgungsanlage einer brennkraftmaschine - Google Patents

Kraftstoffversorgungsanlage einer brennkraftmaschine Download PDF

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Publication number
EP1042608B1
EP1042608B1 EP99931008A EP99931008A EP1042608B1 EP 1042608 B1 EP1042608 B1 EP 1042608B1 EP 99931008 A EP99931008 A EP 99931008A EP 99931008 A EP99931008 A EP 99931008A EP 1042608 B1 EP1042608 B1 EP 1042608B1
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EP
European Patent Office
Prior art keywords
fuel
pump
valve
supply system
electromagnet
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
EP99931008A
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German (de)
English (en)
French (fr)
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EP1042608A1 (de
Inventor
Helmut Rembold
Werner-Karl Marquardt
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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
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic 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
    • 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
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/367—Pump inlet valves of the check valve type being open when actuated
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • 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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/108—Valves characterised by the material
    • F04B53/1082—Valves characterised by the material magnetic
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/15—By-passing over the pump

Definitions

  • the invention is based on a fuel supply system for supplying fuel to an internal combustion engine according to the preamble of claim 1, as e.g. out DE-A-19 630 938 is known.
  • a first fuel pump from a fuel tank promotes fuel via a fuel connection to a second fuel pump.
  • the second fuel pump in turn conveys the fuel into a pressure line to which at least one fuel valve is connected.
  • the number of fuel valves is equal to the number of cylinders of the internal combustion engine.
  • the fuel supply system may be constructed so that the fuel valve injects the fuel directly into a combustion chamber of the internal combustion engine. During operation of this fuel supply system, a high pressure in the pressure line leading to the fuel valve is required.
  • the second fuel pump is usually directly from the Internal combustion engine mechanically driven.
  • the second fuel pump usually has one in a pump room hinund forthcoming pump body, the frequency of Pump body rigidly to the speed of the internal combustion engine is coupled.
  • Flow rate of the second fuel pump can be controlled can, can between the first fuel pump and the second fuel pump a flow rate controlling Control valve can be provided during a pressure stroke the pump body a part of the fuel from the Pump room in the fuel connection between the first Flow back the fuel pump and the second fuel pump leaves.
  • Another disadvantage is that because of the previously required size of the control valve a relatively long Time passes until the flow area of the control valve is completely closed, so that in this transitional period a portion of the fuel from the pump room of the second Fuel pump in the fuel connection under relative high pressure flows back, which is an undesirable Energy loss and an undesirable heating of the fuel means.
  • control valve is relatively small overall can be dimensioned and still arises during the Flowing the fuel from the fuel connection in the pump chamber through the relatively large flow area a relatively small flow resistance. This in turn has the advantage that when the fuel flows into the Pump room the risk of the formation of a gas bubble in the Fuel despite using a relatively small control valve is greatly reduced.
  • the invention running control valve can be particularly fast and closed or opened at the exact time.
  • control valve is designed so that when decreasing Energizing or switching off the energization of the electromagnet the counteracting the magnetic force of the electromagnet Spring displaces the valve member into a closed position, in which the flow area is closed, so one gets the advantage that even with a functional failure the electromagnet of the control valve, the second fuel pump the fuel from the fuel connection in the too can promote the fuel valves leading pressure line.
  • control valve is designed as a so-called seat valve, then can with relatively little displacement of the valve member advantageously a relatively large flow area controlled or opened and closed.
  • the fuel supply system according to the invention for Metering of fuel for an internal combustion engine can at used different types of internal combustion engines become.
  • fuel is preferably a gasoline fuel, especially gasoline, used.
  • the internal combustion engine is for example, a gasoline engine with external or internal Mixture formation and spark ignition, the engine with a reciprocating piston (reciprocating engine) or with a rotatably mounted piston (Wankel piston engine) be provided can.
  • the ignition of the fuel-air mixture happens usually with a spark plug.
  • the internal combustion engine is for example a hybrid engine. With this engine with Charge stratification becomes the fuel-air mixture in the combustion chamber Enriched in the area of the spark plug so far that a safe ignition is guaranteed, combustion in the Medium but takes place in a strongly lean mixture.
  • the gas change in the combustion chamber of the internal combustion engine can for example, after the four-stroke process or after Two-stroke procedure done.
  • Gas exchange valves intake valves and exhaust valves
  • the internal combustion engine can be designed in such a way that at least one fuel valve directly into the fuel the combustion chamber of the internal combustion engine injected.
  • the control the performance of the internal combustion engine takes place depending on the operating mode by controlling the combustion chamber supplied Amount of fuel. But there is also an operating mode at which for the combustion of the fuel the combustion chamber supplied air is controlled by a throttle valve. Also on the position of the throttle, the of the Internal combustion engine to be delivered power controlled.
  • the internal combustion engine has, for example, a cylinder with a piston, or it can with multiple cylinders and be provided with a corresponding number of pistons.
  • a fuel valve per cylinder is provided.
  • the fuel valves 16 are often referred to in the art as injectors or injectors.
  • the first fuel pump 6 has a pressure side 6h and a suction side 6n.
  • the second fuel pump 12 has a High pressure side 12h and a low pressure side 12n.
  • the fuel connection 10 leads from the pressure side 6h of the first Fuel pump 6 to the low pressure side 12n of the second Fuel pump 12.
  • From the fuel connection 10 branches a fuel line 22 from. Via the fuel line 22 can fuel from the fuel 10 directly in the fuel tank 2 are returned.
  • a pressure regulating valve or Pressure control valve 26 is provided in the fuel line 22 .
  • the pressure control valve 26 works as a pressure relief valve or as a Differential pressure valve; It ensures that in the fuel connection 10 a largely constant feed pressure Regardless of how much fuel from the second fuel pump 12 from the fuel connection 10th is removed.
  • the pressure control valve 26 regulates the pressure for example, to 3 bar, which corresponds to 300 kPa.
  • the first fuel pump 6 is driven by the electric motor 8.
  • the first fuel pump 6, the electric motor 8 and the pressure control valve 26 are in the range of Fuel tank 2. These parts are preferably arranged outside the fuel tank 2 or located inside the fuel tank 2, what symbolically represented by a dot-dash line is.
  • a mechanical transmission means 12m Via a mechanical transmission means 12m is the second Fuel pump 12 mechanically with a not shown Output shaft of the internal combustion engine coupled. Because the second fuel pump 12 mechanically rigidly to the output shaft the internal combustion engine is coupled, the works second fuel pump 12 purely proportional to the speed of the Output shaft of the internal combustion engine. The speed of the Output shaft is, depending on the current operating condition the internal combustion engine, very different. at the output shaft is for example a Camshaft of the internal combustion engine.
  • the second fuel pump 12 has a pump room 28.
  • the second fuel pump 12 In the fuel connection 10, on the low pressure side 12n the second fuel pump 12 is located on the input side in front of the pump chamber 28, a control valve 30.
  • the control valve 30 essentially serves to control the second Fuel pump 12 to be pumped amount of fuel, why the control valve 30 as a quantity control valve can be designated. This will be even closer explained.
  • the second fuel pump 12 is located within a with dash-dotted lines symbolically indicated housing 12g. Also, the check valve 32 may be within of the housing 12g are located.
  • the control valve 30 has a Valve body 30g. The valve housing 30g is attached to the housing Flanged 12g or integrated into the housing 12g. The Control valve 30 can also be installed directly in the housing 12g be.
  • the from the second fuel pump 12 to the fuel valves 16 leading pressure line 14 can simplify be divided into a line section 42, a Storage space 44 and in distribution lines 46.
  • the fuel valves 16 are each a distribution line 46 to the Memory space 44 connected.
  • a pressure sensor 48 is connected to the Memory space 44 connected and senses the respective Pressure of the fuel in the pressure line 14. Accordingly This pressure is the pressure sensor 48, an electrical signal to the control device 20.
  • the fuel supply system further includes a sensor 54 or more sensors 54 and an accelerator pedal sensor 56.
  • the sensors 54, 56 sense the operating condition, below the internal combustion engine is working.
  • the operating condition for the internal combustion engine may consist of several single operating conditions put together.
  • the single operating conditions are for example: temperature and / or pressure of the fuel in the fuel connection 10, temperature and / or pressure of the fuel in the pressure line 14, air temperature, Cooling water temperature, oil temperature, engine speed the internal combustion engine or speed of the output shaft the internal combustion engine, composition of the exhaust gas the internal combustion engine, injection time of the fuel valves 16, etc.
  • the accelerator pedal sensor 56 is located in the region of Accelerator pedal and detects, as another single operating condition, the position of the accelerator pedal and thus the desired by the driver Speed.
  • the electric motor 8, the fuel valves 16, the pressure sensor 48 and the sensors 54, 56 are via electrical Lines 58 connected to the controller 20.
  • the electrical line 58 between the fuel valves 16 and the controller 20 is configured so that the Control device 20 of each of the fuel valves 16 can control separately.
  • the electrical lines 58 shown in phantom are the electrical lines 58 shown in phantom.
  • the first fuel pump 6 is For example, a robust, easy to produce Positive displacement pump, which is essentially a specific Constant amount of fuel promotes.
  • feed pressure The pressure of the fuel in the fuel connection 10th
  • the second fuel pump 12 delivers the fuel from the Fuel connection 10, through the control valve 30 in the Pump chamber 28 and from the pump chamber 28 through the output-side check valve 32 in the pressure line 14th
  • the pressure in the pressure line 14 may during the normal Operating state, for example, be around 100 bar, which 10 MPa corresponds. That's why it's important to make sure that the second fuel pump 12 exactly the instantaneous required amount of fuel in the pressure line 14 pumps, so that no fuel from the pressure line 14 in the low pressure area of the fuel supply system must be returned, which is very undesirable, unnecessary would mean dissipation.
  • the control valve 30 shown symbolically in FIG is in a first valve position 30.1, in a second Valve position 30.2 and in a third valve position 30.3 switchable.
  • the symbolic valve positions 30.1, 30.2, 30.3 are just for the sake of clarity shown because of different sizes.
  • the control valve 30 has an actuator 60.
  • the actuator 60 essentially comprises an electromagnet 62 and one of the magnetic force of the electromagnet 62 counteracting Spring 64.
  • the control valve 30 has a valve member 66 ( Figure 2).
  • the valve member 66 is separated from that by the control valve 30 flowing therethrough of the fuel against the force of a contact spring 68 actuated.
  • the valve member 66 At flow of Fuel from the fuel connection 10 in the pump room 28 of the second fuel pump 12, so if the pressure in the fuel connection 10 is greater than the pressure in the Pump chamber 28, the valve member 66 (Fig.
  • the control valve 30 In the first valve position 30.1 the connection or a flow area 74 between the fuel connection 10 and the pump room 28 locked. In the second Valve position 30.2, the control valve 30 has the flow area 74 just slightly open, and the fuel can with some throttling from the pump room 28 back in the fuel connection 10 flow. In the third valve position 30.3, the control valve 30 has the flow area 74 wide open, and the fuel can be largely unthrottled from the fuel connection 10 in the pump room 28 flow in.
  • the second fuel pump 12 is constructed so that the Pump chamber 28 alternately enlarged and reduced, while the internal combustion engine via the transmission means 12m, the second fuel pump 12 drives.
  • the pump room 28 increases or decreases, for example, by a pump body 72 (FIG. 2) mounted in the housing 12g from the internal combustion engine via the mechanical Transfer means 12m to axially reciprocating Movement is driven.
  • a suction stroke the second fuel pump 12, d. H. when the pump body 72 down (relative to Fig. 2) moves, increases the pump chamber 28.
  • a pressure stroke i. H. if the Pump body 72 pressed upward (relative to FIG. 2) is, then the pump chamber 28 is reduced.
  • the electromagnet 62 is not energized and the from the fuel connection 10 in the pump chamber 28th inflowing fuel displaces the valve member 66 (Fig. 2), so that the control valve 30 in the third Valve position 30.3 is located, whereby the flow area 74 of the control valve 30 is wide open and the Fuel largely unthrottled from the fuel connection 10 can flow into the pump chamber 28.
  • the electromagnet 62 initially energized, and the control valve 30 is in its second valve position 30.2.
  • control valve 30 pushes the second fuel pump 12 the fuel from the pump chamber 28 through the Control valve 30 back into the fuel connection 10th
  • the controller 20 calculates the controller 20 the time at which the flow area 74 of the Control valve 30 is to be closed.
  • the electromagnet 62 is energized, and the control valve 30 is in its first valve position 30.1 switched.
  • FIG. 2 shows by way of example a section of the first exemplary embodiment. The parts not shown in Figure 2 correspond to those shown in the remaining figures.
  • FIG. 2 essentially shows a longitudinal section through the control valve 30, which is in the unactuated switch position 30.2.
  • the actuator 60 includes in addition to the electromagnet 62 and the spring 64 is a control body 76.
  • the actuator 76 is composed of an armature 76a and one with the anchor 76a fixedly connected plunger 76b.
  • Electromagnet 62 pushes the spring 64, the actuating body 76th down (relative to FIG. 2) until the armature 76a abuts a lower, provided on the valve housing 30g stop disc 78u comes to the plant.
  • With sufficiently strong Energization of the electromagnet 62 is the actuator 76th up (FIG. 2) against the force of the spring 64, until the armature 76a at an upper, on the valve housing 30g provided stop disc 78o is applied.
  • FIG. 2 shows the control valve 30 in FIG the second valve position 30.2.
  • the distance between the valve seat 80 and the valve member 66 is relatively low, so that for switching to the first valve position 30.1 (Fig. 1) of the actuating body 76th only very slightly upwards (relative to FIG. 2) moves must be until the valve member 66 to close the flow area 74 comes to rest on the valve seat 80. As a result, the flow area 74 can be very fast getting closed.
  • the pump body 72 moves below (with reference to FIG. 2). This reduces the pressure of the Fuel in the pump chamber 28 below the feed pressure of Fuel in the fuel connection 10. This pressure difference acts on the valve member 66 down (Fig. 2) against the force of the application spring 68.
  • the force of Apply spring 68 is quite small, so that already a small pressure difference between the fuel connection 10 and the pump chamber 28, the valve member 66 hydraulically after below (Fig. 2) presses. This ensures that the Pressure in the pump chamber 28 does not sink too far, so that no unwanted gas bubbles in the pump chamber 28 may arise. If the valve member 66 is pressed down hydraulically (FIG. 2), then raises the valve member 66 of the actuator body 76th of the actuator 60 from.
  • valve member 66 By taking off is achieved that of the pressure difference between the pump chamber 28th and the fuel connection 10 hydraulically acted upon Valve member 66 in total only a small mass to be moved has, which gives the advantage that already a small Pressure difference, the valve member 66 dynamically very fast adjusted in the direction you want. With others Words, even a small pressure difference displaces that Valve member 66 against the force of the application spring 68 down (Fig. 2) and upwards (Fig. 2), to the valve member 66 at the plunger 76b of the actuating body 76 or on the valve seat 80th comes to the plant. The valve member 66 can from the valve seat 80th or from the actuator 76 so far lift until the valve member 66 at a provided on the valve housing 30g valve member stop 82 comes to the plant.
  • control valve 30 is energized by energizing the Electromagnet 62 in the first valve position 30.1 (FIG. 1) adjusted, in which the flow area 74 is closed is.
  • the control valve 30 is energized by energizing the Electromagnet 62 in the first valve position 30.1 (FIG. 1) adjusted, in which the flow area 74 is closed is.
  • the Figures 3 and 4 explained embodiment during energizing of the electromagnet 62 of the flow area 74th open.
  • the directions the magnetic force of the electromagnet 62 and the spring force the spring 64 of the actuator 60 reversed.
  • FIG. 3 shows the exemplary embodiment when the electromagnet 62 is not energized, so that the control valve 30 is in the first valve position 30.1, in which the flow area 74 is closed.
  • FIG. 4 shows the second exemplary embodiment when the electromagnet 62 is fully energized, whereby the control valve 30 is in the second valve position 30.2.
  • the electromagnet 62 is energized. It will, however proposed, at least towards the end of the suction stroke, at the latest just before the beginning of the compression stroke, the electromagnet 62 to energize, so that the actuator body 76 down in the in 4 valve position 30.2 shown is adjusted. This ensures that at the beginning of the print stroke of Flow section 74 is opened, so that the not in the pressure line 14 needed fuel in the fuel connection 10 can flow back.
  • valve member 66 Because at the beginning of the Druckhubs the valve member 66 rests against the actuating body 76 and between the valve seat 80 and the valve member 66 only one small distance, the valve member 66 must for Close the flow area 74 only a short way cover so that closing the flow area 74 can happen very quickly. During the print stroke can the flow area 74 will be much smaller than during the suction stroke.
  • the controller determines 20 the time at which during the print stroke the Energization of the electromagnet 62 is turned off, thereby the adjusting body 76 upwards (with reference to FIGS. 3 and 4) is moved, and the valve member 66 closes by conditioning on the valve seat 80, the flow area 74.
  • the control valve 30 By Switching off the energization of the electromagnet 62 of the actuator 60, the control valve 30 during a pressure stroke from the second valve position 30.2 shown in FIG in the illustrated in Figure 3 first valve position 30.1 be switched very quickly. After switching to the first valve position 30.1 pushes the pump body 72 the Fuel from the pump chamber 28 through the output side Check valve 32 in the pressure line 14.
  • the time of switching of the control valve 30 the respectively required amount of fuel with high dosing accuracy be pumped into the pressure line 14.
  • the fuel supply system has a following Emergency function described: If in the in the figures 3 and 4 illustrated embodiment of the electromagnet 62nd should fail as a result of a defect or his Power supply is interrupted, then it is Valve member 66 during the entire pressure stroke in the in Figure 3 shown position in which the flow area 74 is closed, so that the whole of the Pump chamber 28 during the pressure stroke displaced amount of fuel through the outlet-side check valve 32 in the pressure line 14 is pumped. During the suction stroke can the valve member 66 even in the event of failure of the electromagnet 62, lift off from valve seat 80 as previously described. at Failure of the solenoid 62 of the actuator 60, the pump the second fuel pump 12 anyway, but without the possibility of accurate metering of the pressure line 14 pumped fuel quantity.
  • a significant influence on the required force for Holding the valve member 66 in the second valve position 30.2 is the pressure of the fuel in the pump chamber 28 at Pushing back the fuel from the pump chamber 28 in the Fuel connection 10. This is in the pump room 28 essentially to a back pressure.
  • the dynamic pressure is mainly determined by the flow velocity, with the fuel from the pump chamber 28 is displaced.
  • the Flow rate depends on the speed of the upwards moving pump body 72 from.
  • the speed the pump body 72 is determined by the pump speed, with which the fuel pump 12 is driven by the camshaft becomes. It is therefore proposed, the electromagnet 62 preferably in response to the valve member To energize 66 attacking dynamic pressure, then only spend even a little additional power to switch to have to. Because the dynamic pressure of the speed of the upwardly moving pump body 72 depends, in turn the pump speed corresponds, it is proposed that Electromagnet 62 in dependence on the pump speed energize.
  • the voltage of the electrical power unit 18 ( Figure 1) is usually limited, it takes from the beginning the switching on of the electromagnet 62 a certain time, until the solenoid 62 with its full maximum magnetic force can act on the actuator 76.
  • the in the Figures 3 and 4 illustrated embodiment is in Turning off the magnetic force of the electromagnet 62 of the flow area 74 closed, in particular the Closing the flow area 74 particularly fast, within a short time, should happen.
  • the controller 20 in such a way that the Turning off the magnetic force happens faster than that Switching on the magnetic force, results in the in the Figures 3 and 4 illustrated embodiment advantageously a particularly short closing time when closing the flow area 74, because here to close the fürflußqueritess 74, the magnetic force of the electromagnet 62 must be turned off. Therefore, in the second Embodiment of the second fuel pump 12th Promoted fuel quantity controlled very precisely become.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
EP99931008A 1998-07-29 1999-05-04 Kraftstoffversorgungsanlage einer brennkraftmaschine Expired - Lifetime EP1042608B1 (de)

Applications Claiming Priority (3)

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DE19834121A DE19834121A1 (de) 1998-07-29 1998-07-29 Kraftstoffversorgungsanlage einer Brennkraftmaschine
DE19834121 1998-07-29
PCT/DE1999/001329 WO2000006895A1 (de) 1998-07-29 1999-05-04 Kraftstoffversorgungsanlage einer brennkraftmaschine

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KR100634031B1 (ko) 2006-10-17
DE19834121A1 (de) 2000-02-03
JP4489951B2 (ja) 2010-06-23
DE59907935D1 (de) 2004-01-15
WO2000006895A1 (de) 2000-02-10
JP2002521616A (ja) 2002-07-16
EP1042608A1 (de) 2000-10-11
US6345608B1 (en) 2002-02-12
KR20010030766A (ko) 2001-04-16

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