EP1284360B1 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine Download PDF

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Publication number
EP1284360B1
EP1284360B1 EP02016075A EP02016075A EP1284360B1 EP 1284360 B1 EP1284360 B1 EP 1284360B1 EP 02016075 A EP02016075 A EP 02016075A EP 02016075 A EP02016075 A EP 02016075A EP 1284360 B1 EP1284360 B1 EP 1284360B1
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EP
European Patent Office
Prior art keywords
valve
pressure
fuel injection
fuel
space
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
EP02016075A
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German (de)
French (fr)
Other versions
EP1284360A2 (en
EP1284360A3 (en
Inventor
Peter Boehland
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1284360A2 publication Critical patent/EP1284360A2/en
Publication of EP1284360A3 publication Critical patent/EP1284360A3/en
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Publication of EP1284360B1 publication Critical patent/EP1284360B1/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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves

Definitions

  • the invention is based on a Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injector is through the DE 28 08 731 C2 or US 5,771,865-A known.
  • This fuel injection device has a fuel injection valve, the one in a Bore of a valve body slidably guided Injection valve member, through which at least one Injection opening is controlled.
  • the injection valve member is by the in a pressure room of the Fuel injection valve prevailing pressure against the Force of a arranged in a spring chamber closing spring in an opening direction for releasing the at least one Injection opening movable.
  • In the spring room is a maintained predetermined pressure, wherein the spring chamber For example, be connected to a low pressure area can.
  • the pressure chamber of the fuel injection valve is the Fuel injection from a high pressure fuel source fed under high pressure.
  • an electric controlled valve becomes at least indirectly a connection the pressure chamber or the high pressure source with a Relief space controlled.
  • Fuel injection becomes the connection through the valve opened with the discharge space, so that the pressure in the Pressure chamber drops and the fuel injector closes.
  • the pressure in the pressure chamber falls off very sharply, so that under certain circumstances, the vapor pressure of the fuel is exceeded, so that cavitation occurs. this leads to to a lot of wear and noise, what should be avoided.
  • the fuel injection device according to the invention with the Features according to claim 1 has the advantage that through the check valve, a pressure equalization between the Pressure chamber and the spring chamber is possible when the pressure in the pressure chamber is less than in the spring chamber. This will avoided that the pressure in the pressure chamber is below the vapor pressure of the fuel drops, so that no cavitation occurs.
  • the wear and noise emission of the Fuel injection device according to the invention is characterized reduced.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation
  • Figure 2 a in Figure 1 with II designated section of the Fuel injection device in an enlarged view according to a first embodiment
  • Figure 3 the Section II of the fuel injection device according to a second embodiment
  • Figure 4 the Fuel injection device according to a third Embodiment.
  • FIG 1 is a fuel injection device for a Internal combustion engine, for example, a motor vehicle shown.
  • the internal combustion engine is a self-igniting Internal combustion engine and has one or more cylinders on.
  • the fuel injector points to each Cylinder on a fuel injection valve 12.
  • At the in Figure 1 illustrated embodiment of Fuel injector has this for everyone Cylinder of the internal combustion engine one High-pressure fuel pump 10 on.
  • the High-pressure fuel pump 10 and the Fuel injection valve 12 are a so-called Combined pump-nozzle unit.
  • the High-pressure fuel pump 10 and the However, fuel injector 12 may also be disconnected be arranged from each other and via a line be connected to each other.
  • the high-pressure fuel pump 10th has a pump body 14, in which in a Cylinder bore 16 a pump piston 18 is tightly guided, by a cam of a camshaft of Internal combustion engine against the force of a return spring 19 is driven in a lifting movement.
  • the pump piston 18 limited in the cylinder bore 16 a Pump work chamber 22, in which the delivery stroke of Pump piston 18 fuel is compressed under high pressure.
  • the pump working chamber 22 is at the suction stroke of the pump piston 18 fuel from a fuel tank 24th fed, for example by means of a feed pump.
  • Of the Pump work chamber 22 has a connection with a Relief space on, as the example of the Can serve fuel tank 24, and that of a electrically controlled valve 23 is controlled.
  • the electrically controlled valve 23 is connected to a Control device 25 connected.
  • the fuel injection valve 12 has a valve body 26 on, which is explained in more detail below is formed in several parts, and with the pump body 14th connected is.
  • a valve body 26 In the valve body 26 is in a bore 30th an injection valve member 28 guided longitudinally displaceable.
  • the Bore 30 extends at least approximately parallel to Cylinder 16 of the pump body 14, but may also be inclined to go to this.
  • the valve body 26 has at its the Combustion chamber of the cylinder of the internal combustion engine facing End region at least one, preferably several Injection openings 32.
  • the injection valve member 28 has at its the combustion chamber end facing a For example, about conical sealing surface 34, which with one in the valve body 26 in the combustion chamber facing End region trained, for example, also about conical valve seat 36 cooperates, from or after the discharge the injection openings 32.
  • valve body 26 is between the injection valve member 28th and the bore 30 to the valve seat 36 toward an annular space 38th present, in its the valve seat 36 facing away End region by a radial extension of the bore 30 in a pressure chamber 40 surrounding the injection valve member 28 passes.
  • the injection valve member 28 has the height of the Pressure chamber 40 by a cross-sectional reduction to the Valve seat 36 facing pressure shoulder 42 on.
  • a prestressed closing spring 44 At the Combustion chamber facing away from the injection valve member 28th engages a prestressed closing spring 44, through which the Injection valve member 28 is pressed to the valve seat 36 back.
  • the closing spring 44 is arranged in a spring chamber 46, which connects to the bore 30.
  • the pressure chamber 40 is via a passage 48 extending through the valve body 26 connected to the pump working chamber 22.
  • the closing spring 44 is supported on the one hand at least indirectly, for example via a spring plate, on Injector valve member 28 and on the other hand at least indirectly, for example, also via a spring plate 51, on a bypass piston 50 from.
  • the bypass piston 50 is guided in a bore 80 of a housing part 81 and has at its the closing spring 44 facing end a Shank portion 52 which, through a connecting hole 53 in a partition wall 54 of the housing part 81 between the Spring chamber 46 and one of these in the housing part 81st subsequent memory space 55 passes.
  • the connecting hole 53 has a smaller diameter than the spring chamber 46 and the Storage space 55.
  • the bypass piston 50 has in the storage space 55 an area 56 with a larger diameter than that Connecting hole 53, so that a lifting movement of the Ausweichkolbens 50 in the spring chamber 46 in thereby is limited, that the area 56 of the bypass piston 50 at the partition 54 comes to rest as a stop.
  • the spring chamber 46 is as Hole formed in a housing part 82, which is a part of the valve body 26 forms.
  • the channel 48 passes through the Housing part 82 offset to the spring chamber 46 approximately parallel this.
  • a bore 58 to the pump working space 22nd in the housing part 81 from.
  • the bore 58 has a smaller diameter than the bore 80th
  • the Evasive piston 50 points to the bore 58 to the area 56th then a sealing surface 60, for example is formed approximately conical.
  • the sealing surface 60 acts with the mouth of the bore 58 in the storage space 55 am Housing part 81 as a seat together, which is also about may be formed cone-shaped.
  • the bypass piston 50 has a projecting into the bore 58 shaft 62, whose Diameter smaller than that of the area 56.
  • the shaft 62 has the sealing surface 60 then first a much smaller diameter than the bore 58 and towards its free end then a shaft area 64 with a diameter that is only slightly smaller than that Diameter of the bore 58.
  • the shaft portion 64 can on its periphery have one or more flats 65, through the openings between the shaft portion 64 and the Bore 58 are formed by the fuel in the Memory space 55 can get.
  • a Intermediate disc 83 is arranged, in which a bore 84th is formed, through which the bore 58 in the housing part 81st is connected to the pump working chamber 22.
  • the bore 84 represents a throttle point over which the bore 58 with the pump working chamber 22 is connected.
  • the alternate piston 50 limited in the bore 58 to the washer 83 out an antechamber 85, via the throttle point 84 with the Pump workspace 22 is connected.
  • a further housing part 86 as part of the Valve body 26 is arranged, which has a bore 87, through the one end portion of the injection valve member 28 passes and projects into the spring chamber 46.
  • the Injection valve member 28 is supported by its end in the Spring chamber 46 via a spring plate 88 on the closing spring 44 off.
  • the end portion of the injection valve member 28 has a smaller diameter than that in the bore 30th guided area.
  • the bore 30, the pressure chamber 40 as well the annular space 38, at the lower end of the valve seat 34th and the injection openings 32 are arranged are in one a part of the valve body 26 forming the valve housing 89th educated.
  • Between the housing part 86 and the Valve housing 89 is an intermediate disc 90 with less Thickness arranged.
  • the washer 90 has a bore 91, through which the end portion of the injection valve member 28 passes.
  • the channel 48 extends from the pressure chamber 40 through the Valve housing 89, the washer 90, the housing part 86th and the housing part 82.
  • the housing part 82 has on its the intermediate disc 83 side facing a groove 92, in the channel 48 opens and connected to the vestibule 85 is.
  • the channel 48 is thus on the groove 92, the vestibule 85th and the bore 84 is connected to the pump working space 22.
  • the channel 48 under Bypassing the anteroom 85 directly-via a hole in the Washer 83 is connected to the pump working chamber 22 is.
  • the washer 83 may-while on its the Pump body 14 facing side have a groove, the towards the pump working chamber 22 is open and in the channel 48 opens.
  • the groove may, for example, approximately radially to the Cylinder bore 16 extend and extends from the Cylinder bore 16 outward to the area of Washer 83, in which the channel 48 through this runs.
  • the connection of the pressure chamber 40 of the Fuel injection valve 12 with the pump working space 22nd through the channel 48 takes place in this case directly below Bypassing of the anteroom 85, of the escape piston 50 in the Bore 58 is limited to the intermediate disc 83 out.
  • the fuel injection valve 12 and the High-pressure fuel pump 10 are by means of a clamping sleeve 94th connected with each other.
  • the clamping sleeve 94 engages over Valve housing 89 and is in a threaded hole 95 in Pump body 14 screwed.
  • the washer 83, the Housing parts 81,82,86 and the washer 90 are between the valve housing 89 and the pump body 14th clamped.
  • the spring chamber 46 is connected to a low-pressure region, for example, with the fuel tank 24 or with an area where a slightly elevated pressure, for example, 2 to 5 bar is maintained.
  • Pressure chamber 40 of the fuel injection valve 12 introduces another channel 100 to the intermediate disc 90 down from, to the Channel 48 is offset in the circumferential direction and this for example, approximately diametrically opposite.
  • the channel 100 continues through the washer 90 and the housing part 86 and opens into the spring chamber 46 in the housing part 82nd Im Channel 100, a check valve 102 is arranged, the Pressure chamber 40 opens.
  • the check valve 102 has a by a closing spring 104 in the closing direction acted upon valve member 106.
  • the check valve 102 is between arranged the valve housing 89 and the washer 90.
  • the channel 100 is in the valve housing 89 to the washer 90th enlarged in diameter and in this is the Closing spring 104 and the valve member 106 is arranged.
  • the Channel 100 has a smaller one in the intermediate disk 90 Cross-section as the valve member 106, wherein the mouth of the channel 100 on the valve housing 89 side facing the intermediate disc 90 forms a valve seat 108, with the the valve member 106 cooperates and against the Valve member 106 is pressed by the closing spring 104.
  • FIG. 3 shows a second exemplary embodiment, in which the check valve 102 in the washer 90th is arranged to receive the check valve 102nd has a slightly greater thickness than the first Embodiment.
  • the channel 100 may be in the valve housing 89th run with a constant cross section and goes into the Washer 90 over.
  • the channel 100 has in the housing part 86 a smaller cross section than the valve member 106, wherein the Mouth of the channel 100 at the intermediate disc 90th facing side of the housing part 86 a valve seat 108th forms, with which the valve member 106 cooperates and against the valve member 106 is pressed by the closing spring 104 becomes.
  • the Fuel injector 12 is only for a short time Time period will be open and it will only be a small amount Fuel as a pilot injection into the combustion chamber injected.
  • the injected fuel quantity is in essentially from the opening pressure of the bypass piston 50 determined, that is the pressure in the pump working chamber 22 and in the Anteroom 85, in which the bypass piston 50 his Dodge stroke begins.
  • the opening stroke of the Injection valve member 28 during the pilot injection can be hydraulically limited by a damping device.
  • the pressure in the pump working chamber 22 continues to rise below in accordance with the profile of the pump piston 18th driving cam, so that on the Injection valve member 28 acting pressure force in Opening direction 29 increases again and due to the increased bias of the closing spring 44 increased Closing force exceeds, so that the Fuel injector 12 opens again.
  • the duration and the injected during this main injection Fuel quantity are determined by the time at which the control valve 23 by the control device 25 again is opened. After opening the control valve 23 is the Pump workspace 22 again with the Fuel tank 24 connected so that this is relieved and the fuel injection valve 12 closes.
  • the bypass piston 50 with the shaft portion 52 is replaced by the Force of the closing spring 44 back to its original position moved back.
  • the fuel injection device according to A third embodiment shown in which the Formation of the fuel injection valve 12 with the Check valve 102 is the same as the first or second Embodiment, but instead of High-pressure fuel pump 10, a high-pressure accumulator 110 as High-pressure source is used, from the fuel under high pressure supplied to the pressure chamber 40 of the fuel injection valve 12 becomes.
  • a high-pressure accumulator 110 is by a High pressure pump 112 fuel delivered.
  • an electrically controlled Valve 123 arranged by a control device 125th is controlled.
  • the high-pressure accumulator 110 serves as Pressure source for multiple fuel injection valves 12 or for all fuel injection valves 12 of the Internal combustion engine.
  • the function of the Fuel injection valve 12 with the check valve 102nd is the same as explained above.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention is based on a Fuel injection device for an internal combustion engine according to the preamble of claim 1.

Eine solche Kraftstoffeinspritzeinrichtung ist durch die DE 28 08 731 C2 oder die US 5,771,865-A bekannt. Diese Kraftstoffeinspritzeinrichtung weist ein Kraftstoffeinspritzventil auf, das ein in einer Bohrung eines Ventilkörpers verschiebbar geführtes Einspritzventilglied aufweist, durch das wenigstens eine Einspritzöffnung gesteuert wird. Das Einspritzventilglied ist durch den in einem Druckraum des Kraftstoffeinspritzventils herrschenden Druck gegen die Kraft einer in einem Federraum angeordneten Schließfeder in einer Öffnungsrichtung zur Freigabe der wenigstens einen Einspritzöffnung bewegbar. Im Federraum wird ein vorgegebener Druck aufrechterhalten, wobei der Federraum beispielsweise mit einem Niederdruckbereich verbunden sein kann. Dem Druckraum des Kraftstoffeinspritzventils wird zur Kraftstoffeinspritzung von einer Hochdruckquelle Kraftstoff unter hohem Druck zugeführt. Durch ein elektrische gesteuertes Ventil wird zumindest mittelbar eine Verbindung des Druckraums oder der Hochdruckquelle mit einem Entlastungsraum gesteuert. Zur Beendigung der Kraftstoffeinspritzung wird durch das Ventil die Verbindung mit dem Entlastungsraum geöffnet, so daß der Druck im Druckraum abfällt und das Kraftstoffeinspritzventil schließt. Der Druck im Druckraum fällt dabei sehr stark ab, so daß unter Umständen der Dampfdruck des Kraftstoffs unterschritten wird, so daß Kavitation auftritt. Dies führt zu einem starken Verschleiß und zu starkem Geräusch, was vermieden werden sollte.Such a fuel injector is through the DE 28 08 731 C2 or US 5,771,865-A known. This fuel injection device has a fuel injection valve, the one in a Bore of a valve body slidably guided Injection valve member, through which at least one Injection opening is controlled. The injection valve member is by the in a pressure room of the Fuel injection valve prevailing pressure against the Force of a arranged in a spring chamber closing spring in an opening direction for releasing the at least one Injection opening movable. In the spring room is a maintained predetermined pressure, wherein the spring chamber For example, be connected to a low pressure area can. The pressure chamber of the fuel injection valve is the Fuel injection from a high pressure fuel source fed under high pressure. By an electric controlled valve becomes at least indirectly a connection the pressure chamber or the high pressure source with a Relief space controlled. To end the Fuel injection becomes the connection through the valve opened with the discharge space, so that the pressure in the Pressure chamber drops and the fuel injector closes. The pressure in the pressure chamber falls off very sharply, so that under certain circumstances, the vapor pressure of the fuel is exceeded, so that cavitation occurs. this leads to to a lot of wear and noise, what should be avoided.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß durch das Rückschlagventil ein Druckausgleich zwischen dem Druckraum und dem Federraum ermöglicht ist, wenn der Druck im Druckraum geringer ist als im Federraum. Hierdurch wird vermieden, daß der Druck im Druckraum unter den Dampfdruck des Kraftstoffs absinkt, so daß keine Kavitation auftritt. Der Verschleiß und die Geräuscheimission der erfindungsgemäßen Kraftstoffeinspritzeinrichtung ist dadurch verringert.The fuel injection device according to the invention with the Features according to claim 1 has the advantage that through the check valve, a pressure equalization between the Pressure chamber and the spring chamber is possible when the pressure in the pressure chamber is less than in the spring chamber. This will avoided that the pressure in the pressure chamber is below the vapor pressure of the fuel drops, so that no cavitation occurs. The wear and noise emission of the Fuel injection device according to the invention is characterized reduced.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben.In the dependent claims are advantageous Embodiments and developments of the invention Fuel injector specified.

Zeichnungdrawing

Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine in schematischer Darstellung, Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Kraftstoffeinspritzeinrichtung in vergrößerter Darstellung gemäß einem ersten Ausführungsbeispiel, Figur 3 den Ausschnitt II der Kraftstoffeinspritzeinrichtung gemäß einem zweiten Ausführungsbeispiel und Figur 4 die Kraftstoffeinspritzeinrichtung gemäß einem dritten Ausführungsbeispiel.Several embodiments of the invention are in the Drawing shown and in the following description explained in more detail. FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation, Figure 2 a in Figure 1 with II designated section of the Fuel injection device in an enlarged view according to a first embodiment, Figure 3 the Section II of the fuel injection device according to a second embodiment and Figure 4 the Fuel injection device according to a third Embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine beispielsweise eines Kraftfahrzeugs dargestellt. Die Brennkraftmaschine ist eine selbstzündende Brennkraftmaschine und weist einen oder mehrere Zylinder auf. Die Kraftstoffeinspritzeinrichtung weist für jeden Zylinder ein Kraftstoffeinspritzventil 12 auf. Bei der in Figur 1 dargestellten Ausführung der Kraftstoffeinspritzeinrichtung weist diese für jeden Zylinder der Brennkraftmaschine eine Kraftstoffhochdruckpumpe 10 auf. Die Kraftstoffhochdruckpumpe 10 und das Kraftstoffeinspritzventil 12 sind zu einer sogenannten Pumpe-Düse-Einheit zusammengefaßt. Die Kraftstoffhochdruckpumpe 10 und das Kraftstoffeinspritzventil 12-können jedoch auch getrennt voneinander angeordnet sein und über eine Leitung miteinander verbunden sein. Die Kraftstoffhochdruckpumpe 10 weist einen Pumpenkörper 14 auf, in dem in einer Zylinderbohrung 16 ein Pumpenkolben 18 dicht geführt ist, der durch einen Nocken einer Nockenwelle der Brennkraftmaschine entgegen der Kraft einer Rückstellfeder 19 in einer Hubbewegung angetrieben wird. Der Pumpenkolben 18 begrenzt in der Zylinderbohrung 16 einen Pumpenarbeitsraum 22, in dem beim Förderhub des Pumpenkolbens 18 Kraftstoff unter Hochdruck verdichtet wird. Dem Pumpenarbeitsraum 22 wird beim Saughub des Pumpenkolbens 18 Kraftstoff aus einem Kraftstoffvorratsbehälter 24 zugeführt, beispielsweise mittels einer Förderpumpe. Der Pumpenarbeitsraum 22 weist eine Verbindung mit einem Entlastungsraum auf, als der beispielsweise der Kraftstoffvorratsbehälter 24 dienen kann, und die von einem elektrisch gesteuerten Ventil 23 gesteuert wird. Das elektrisch gesteuerte Ventil 23 ist mit einer Steuereinrichtung 25 verbunden.In Figure 1 is a fuel injection device for a Internal combustion engine, for example, a motor vehicle shown. The internal combustion engine is a self-igniting Internal combustion engine and has one or more cylinders on. The fuel injector points to each Cylinder on a fuel injection valve 12. At the in Figure 1 illustrated embodiment of Fuel injector has this for everyone Cylinder of the internal combustion engine one High-pressure fuel pump 10 on. The High-pressure fuel pump 10 and the Fuel injection valve 12 are a so-called Combined pump-nozzle unit. The High-pressure fuel pump 10 and the However, fuel injector 12 may also be disconnected be arranged from each other and via a line be connected to each other. The high-pressure fuel pump 10th has a pump body 14, in which in a Cylinder bore 16 a pump piston 18 is tightly guided, by a cam of a camshaft of Internal combustion engine against the force of a return spring 19 is driven in a lifting movement. The pump piston 18 limited in the cylinder bore 16 a Pump work chamber 22, in which the delivery stroke of Pump piston 18 fuel is compressed under high pressure. The pump working chamber 22 is at the suction stroke of the pump piston 18 fuel from a fuel tank 24th fed, for example by means of a feed pump. Of the Pump work chamber 22 has a connection with a Relief space on, as the example of the Can serve fuel tank 24, and that of a electrically controlled valve 23 is controlled. The electrically controlled valve 23 is connected to a Control device 25 connected.

Das Kraftstoffeinspritzventil 12 weist einen Ventilkörper 26 auf, der wie nachfolgend noch näher erläutert wird mehrteilig ausgebildet ist, und der mit dem Pumpenkörper 14 verbunden ist. Im Ventilkörper 26 ist in einer Bohrung 30 ein Einspritzventilglied 28 längsverschiebbar geführt. Die Bohrung 30 verläuft zumindest annähernd parallel zum Zylinder 16 des Pumpenkörpers 14, kann jedoch auch geneigt zu diesem verlaufen. Der Ventilkörper 26 weist an seinem dem Brennraum des Zylinders der Brennkraftmaschine zugewandten Endbereich wenigstens eine, vorzugsweise mehrere Einspritzöffnungen 32 auf. Das Einspritzventilglied 28 weist an seinem dem Brennraum zugewandten Endbereich eine beispielsweise etwa kegelförmige Dichtfläche 34 auf, die mit einem im Ventilkörper 26 in dessen dem Brennraum zugewandtem Endbereich ausgebildeten, beispielsweise ebenfalls etwa kegelförmigen Ventilsitz 36 zusammenwirkt, von dem oder nach dem die Einspritzöffnungen 32 abführen.The fuel injection valve 12 has a valve body 26 on, which is explained in more detail below is formed in several parts, and with the pump body 14th connected is. In the valve body 26 is in a bore 30th an injection valve member 28 guided longitudinally displaceable. The Bore 30 extends at least approximately parallel to Cylinder 16 of the pump body 14, but may also be inclined to go to this. The valve body 26 has at its the Combustion chamber of the cylinder of the internal combustion engine facing End region at least one, preferably several Injection openings 32. The injection valve member 28 has at its the combustion chamber end facing a For example, about conical sealing surface 34, which with one in the valve body 26 in the combustion chamber facing End region trained, for example, also about conical valve seat 36 cooperates, from or after the discharge the injection openings 32.

Im Ventilkörper 26 ist zwischen dem Einspritzventilglied 28 und der Bohrung 30 zum Ventilsitz 36 hin ein Ringraum 38 vorhanden, der in seinem dem Ventilsitz 36 abgewandten Endbereich durch eine radiale Erweiterung der Bohrung 30 in einen das Einspritzventilglied 28 umgebenden Druckraum 40 übergeht. Das Einspritzventilglied 28 weist auf Höhe des Druckraums 40 durch eine Querschnittsverringerung eine zum Ventilsitz 36 weisende Druckschulter 42 auf. Am dem Brennraum abgewandten Ende des Einspritzventilglieds 28 greift eine vorgespannte Schließfeder 44 an, durch die das Einspritzventilglied 28 zum Ventilsitz 36 hin gedrückt wird. In the valve body 26 is between the injection valve member 28th and the bore 30 to the valve seat 36 toward an annular space 38th present, in its the valve seat 36 facing away End region by a radial extension of the bore 30 in a pressure chamber 40 surrounding the injection valve member 28 passes. The injection valve member 28 has the height of the Pressure chamber 40 by a cross-sectional reduction to the Valve seat 36 facing pressure shoulder 42 on. At the Combustion chamber facing away from the injection valve member 28th engages a prestressed closing spring 44, through which the Injection valve member 28 is pressed to the valve seat 36 back.

Die Schließfeder 44 ist in einem Federraum 46 angeordnet, der sich an die Bohrung 30 anschließt. Der Druckraum 40 ist über einen durch den Ventilkörper 26 verlaufenden Kanal 48 mit dem Pumpenarbeitsraum 22 verbunden.The closing spring 44 is arranged in a spring chamber 46, which connects to the bore 30. The pressure chamber 40 is via a passage 48 extending through the valve body 26 connected to the pump working chamber 22.

Die Schließfeder 44 stützt sich einerseits zumindest mittelbar, beispielsweise über einen Federteller, am Einspritzventilglied 28 und andererseits zumindest mittelbar, beispielsweise ebenfalls über einen Federteller 51, an einem Ausweichkolben 50 ab. Der Ausweichkolben 50 ist in einer Bohrung 80 eines Gehäuseteils 81 geführt und weist an seinem der Schließfeder 44 zugewandten Endbereich einen Schaftteil 52 auf, der durch eine Verbindungsbohrung 53 in einer Trennwand 54 des Gehäuseteils 81 zwischen dem Federraum 46 und einem an diesen im Gehäuseteil 81 anschließenden Speicherraum 55 hindurchtritt. An dem in den Federraum 46 ragenden Ende des Schaftteils 52 stützt sich der Federteller 51 ab. Die Verbindungsbohrung 53 weist einen kleineren Durchmesser auf als der Federraum 46 und der Speicherraum 55. Der Ausweichkolben 50 weist im Speicherraum 55 einen Bereich 56 mit größerem Durchmesser auf als die Verbindungsbohrung 53, so daß eine Hubbewegung des Ausweichkolbens 50 in den Federraum 46 hinein dadurch begrenzt ist, daß der Bereich 56 des Ausweichkolbens 50 an der Trennwand 54 als Anschlag zur Anlage kommt. Der Ausweichkolben 50 ist mit seinem Bereich 56 in der Bohrung 80 mit gegenüber der Verbindungsbohrung 53 entsprechend größerem Durchmesser dicht geführt. Der Federraum 46 ist als Bohrung in einem Gehäuseteil 82 ausgebildet, das einen Teil des Ventilkörpers 26 bildet. Der Kanal 48 verläuft durch das Gehäuseteil 82 versetzt zum Federraum 46 etwa parallel zu diesem.The closing spring 44 is supported on the one hand at least indirectly, for example via a spring plate, on Injector valve member 28 and on the other hand at least indirectly, for example, also via a spring plate 51, on a bypass piston 50 from. The bypass piston 50 is guided in a bore 80 of a housing part 81 and has at its the closing spring 44 facing end a Shank portion 52 which, through a connecting hole 53 in a partition wall 54 of the housing part 81 between the Spring chamber 46 and one of these in the housing part 81st subsequent memory space 55 passes. At the in the Spring chamber 46 projecting end of the shaft portion 52 is supported the spring plate 51 from. The connecting hole 53 has a smaller diameter than the spring chamber 46 and the Storage space 55. The bypass piston 50 has in the storage space 55 an area 56 with a larger diameter than that Connecting hole 53, so that a lifting movement of the Ausweichkolbens 50 in the spring chamber 46 in thereby is limited, that the area 56 of the bypass piston 50 at the partition 54 comes to rest as a stop. Of the Ausweichkolben 50 is with its portion 56 in the bore 80 with respect to the connecting hole 53 accordingly larger diameter tightly guided. The spring chamber 46 is as Hole formed in a housing part 82, which is a part of the valve body 26 forms. The channel 48 passes through the Housing part 82 offset to the spring chamber 46 approximately parallel this.

Vom Speicherraum 55 führt von dessen dem Federraum 46 abgewandtem Ende eine Bohrung 58 zum Pumpenarbeitsraum 22 hin im Gehäuseteil 81 ab. Die Bohrung 58 weist einen kleineren Durchmesser auf als die Bohrung 80. Der Ausweichkolben 50 weist zur Bohrung 58 hin an den Bereich 56 anschließend eine Dichtfläche 60 auf, die beispielsweise etwa kegelförmig ausgebildet ist. Die Dichtfläche 60 wirkt mit der Mündung der Bohrung 58 in den Speicherraum 55 am Gehäuseteil 81 als Sitz zusammen, die ebenfalls etwa kegelförmig ausgebildet sein kann. Der Ausweichkolben 50 weist einen in die Bohrung 58 ragenden Schaft 62 auf, dessen Durchmesser kleiner als der des Bereichs 56 ist. Der Schaft 62 weist an die Dichtfläche 60 anschließend zunächst einen wesentlich kleineren Durchmesser auf als die Bohrung 58 und zu seinem freien Ende hin anschließend einen Schaftbereich 64 mit einem Durchmesser, der nur wenig kleiner ist als der Durchmesser der Bohrung 58. Der Schaftbereich 64 kann an seinem Umfang eine oder mehrere Abflachungen 65 aufweisen, durch die Öffnungen zwischen dem Schaftbereich 64 und der Bohrung 58 gebildet werden, durch die Kraftstoff in den Speicherraum 55 gelangen kann.From the storage space 55 leads from the spring chamber 46th distal end a bore 58 to the pump working space 22nd in the housing part 81 from. The bore 58 has a smaller diameter than the bore 80th The Evasive piston 50 points to the bore 58 to the area 56th then a sealing surface 60, for example is formed approximately conical. The sealing surface 60 acts with the mouth of the bore 58 in the storage space 55 am Housing part 81 as a seat together, which is also about may be formed cone-shaped. The bypass piston 50 has a projecting into the bore 58 shaft 62, whose Diameter smaller than that of the area 56. The shaft 62 has the sealing surface 60 then first a much smaller diameter than the bore 58 and towards its free end then a shaft area 64 with a diameter that is only slightly smaller than that Diameter of the bore 58. The shaft portion 64 can on its periphery have one or more flats 65, through the openings between the shaft portion 64 and the Bore 58 are formed by the fuel in the Memory space 55 can get.

Zwischen dem Gehäuseteil 81-und-dem Pumpenkörper 14 ist eine Zwischenscheibe 83 angeordnet, in der eine Bohrung 84 ausgebildet ist, durch die die Bohrung 58 im Gehäuseteil 81 mit dem Pumpenarbeitsraum 22 verbunden ist. Die Bohrung 84 stellt eine Drosselstelle dar, über die die Bohrung 58 mit dem Pumpenarbeitsraum 22 verbunden ist. Der Ausweichkolben 50 begrenzt in der Bohrung 58 zur Zwischenscheibe 83 hin einen Vorraum 85, der über die Drosselstelle 84 mit dem Pumpenarbeitsraum 22 verbunden ist.Between the housing part 81 and the pump body 14 is a Intermediate disc 83 is arranged, in which a bore 84th is formed, through which the bore 58 in the housing part 81st is connected to the pump working chamber 22. The bore 84 represents a throttle point over which the bore 58 with the pump working chamber 22 is connected. The alternate piston 50 limited in the bore 58 to the washer 83 out an antechamber 85, via the throttle point 84 with the Pump workspace 22 is connected.

Wenn sich der Ausweichkolben 50 in einer Ausgangsstellung befindet, in der dieser mit seiner Dichtfläche 60 am Dichtsitz an der Mündung der Bohrung 58 anliegt, so ist der Speicherraum 55 vom Vorraum 85 und damit vom Pumpenarbeitsraum 22 getrennt. In der Ausgangsstellung des Ausweichkolbens 50 wirkt der im Pumpenarbeitsraum 22 herrschende Druck auf die Stirnfläche des Schaftbereichs 64 und durch die Öffnungen zwischen dem Schaftbereich 64 und der Bohrung 58 auf die Dichtfläche 60 des Speicherkolbens 50 entsprechend dem Durchmesser der Bohrung 58. Der Ausweichkolben 50 wird durch die Kraft der Schließfeder 44 gegen den im Pumpenarbeitsraum 22 und damit im Vorraum 85 herrschenden Druck in seiner Ausgangsstellung gehalten, wenn die durch den Druck im Pumpenarbeitsraum 22 auf den Speicherkolben 50 ausgeübte Kraft geringer ist als die Kraft der Schließfeder 44.When the bypass piston 50 in an initial position in which this with its sealing surface 60 am Sealing seat abuts the mouth of the bore 58, so is the Storage space 55 from the antechamber 85 and thus from Pump work space 22 separated. In the starting position of the Ausweichkolbens 50 acts in the pump working space 22nd prevailing pressure on the end face of the shaft portion 64 and through the openings between the shaft portion 64 and the bore 58 on the sealing surface 60 of the accumulator piston 50th corresponding to the diameter of the bore 58th Der Ausweichkolben 50 is by the force of the closing spring 44th against the pump working space 22 and thus in the anteroom 85th prevailing pressure held in its initial position when by the pressure in the pump chamber 22 on the Accumulator piston 50 applied force is less than the force the closing spring 44.

Wenn der Druck im Pumpenarbeitsraum 22 und damit im Vorraum 85 so stark ansteigt, daß die auf den Ausweichkolben 50 erzeugte Kraft größer ist als die Kraft der Schließfeder 44, so bewegt sich der Ausweichkolben 50 und mit diesem der Schaftteil 52 in einer Ausweichbewegung in den Speicherraum 55, wobei sich der Schaftteil 52 in den Federraum 46 bewegt. Bei der Ausweichbewegung des Ausweichkolbens 50 wird Kraftstoff aus dem Speicherraum 55 in den Federraum 46 verdrängt, der durch einen-Ringspalt zwischen dem Schaftteil 52 des Ausweichkolbens 50 und der Verbindungsbohrung 53 hindurchtreten muß. Hierdurch wird eine Dämpfung der Ausweichbewegung des Schaftteils 52 und damit des Ausweichkolbens 50 erreicht.When the pressure in the pump chamber 22 and thus in the vestibule 85 increases so much that the on the escape piston 50th generated force is greater than the force of the closing spring 44, so moves the bypass piston 50 and with this the Shank part 52 in an evasive movement in the storage space 55, wherein the shaft portion 52 moves into the spring chamber 46. In the evasive movement of the bypass piston 50 is Fuel from the storage chamber 55 in the spring chamber 46th displaced by an annular gap between the shaft part 52 of the bypass piston 50 and the connecting hole 53rd must pass through. As a result, a damping of Evasive movement of the shaft portion 52 and thus the Evasive piston 50 reached.

Zum Kraftstoffeinspritzventil 12 hin anschließend ist an das Gehäuseteil 82 ein weiteres Gehäuseteil 86 als Teil des Ventilkörpers 26 angeordnet, das eine Bohrung 87 aufweist, durch die ein Endbereich des Einspritzventilglieds 28 hindurchtritt und in den Federraum 46 ragt. Das Einspritzventilglied 28 stützt sich mit seinem Endbereich im Federraum 46 über einen Federteller 88 an der Schließfeder 44 ab. Der Endbereich des Einspritzventilglieds 28 weist einen kleineren Durchmesser auf als dessen in der Bohrung 30 geführter Bereich. Die Bohrung 30, der Druckraum 40 sowie der Ringraum 38, an dessen unterem Ende der Ventilsitz 34 und die Einspritzöffnungen 32 angeordnet sind, sind in einem einen Teil des Ventilkörpers 26 bildenden Ventilgehäuse 89 ausgebildet. Zwischen dem Gehäuseteil 86 und dem Ventilgehäuse 89 ist eine Zwischenscheibe 90 mit geringer Dicke angeordnet. Die Zwischenscheibe 90 weist eine Bohrung 91 auf, durch die der Endbereich des Einspritzventilglieds 28 hindurchtritt.To the fuel injection valve 12 is then connected to the Housing part 82 a further housing part 86 as part of the Valve body 26 is arranged, which has a bore 87, through the one end portion of the injection valve member 28 passes and projects into the spring chamber 46. The Injection valve member 28 is supported by its end in the Spring chamber 46 via a spring plate 88 on the closing spring 44 off. The end portion of the injection valve member 28 has a smaller diameter than that in the bore 30th guided area. The bore 30, the pressure chamber 40 as well the annular space 38, at the lower end of the valve seat 34th and the injection openings 32 are arranged are in one a part of the valve body 26 forming the valve housing 89th educated. Between the housing part 86 and the Valve housing 89 is an intermediate disc 90 with less Thickness arranged. The washer 90 has a bore 91, through which the end portion of the injection valve member 28 passes.

Der Kanal 48 verläuft vom Druckraum 40 aus durch das Ventilgehäuse 89, die Zwischenscheibe 90, das Gehäuseteil 86 und das Gehäuseteil 82. Das Gehäuseteil 82 weist auf seiner der Zwischenscheibe 83 zugewandten Seite eine Nut 92 auf, in die der Kanal 48 mündet und die mit dem Vorraum 85 verbunden ist. Der Kanal 48 ist somit über die Nut 92, den Vorraum 85 und die Bohrung 84 mit dem Pumpenarbeitsraum 22 verbunden. Alternativ kann auch vorgesehen sein, daß der Kanal 48 unter Umgehung des Vorraums 85 direkt-über eine Bohrung in der Zwischenscheibe 83 mit dem Pumpenarbeitsraum 22 verbunden ist. Die Zwischenscheibe 83 kann-dabei auf ihrer dem Pumpenkörper 14 zugewandten Seite eine Nut aufweisen, die zum Pumpenarbeitsraum 22 hin offen ist und in die der Kanal 48 mündet. Die Nut kann beispielsweise etwa radial zu der Zylinderbohrung 16 verlaufen und erstreckt sich von der Zylinderbohrung 16 nach außen bis in den Bereich der Zwischenscheibe 83, in dem der Kanal 48 durch diese verläuft. Die Verbindung des Druckraums 40 des Kraftstoffeinspritzventils 12 mit dem Pumpenarbeitsraum 22 durch den Kanal 48 erfolgt in diesem Fall direkt unter Umgehung des Vorraums 85, der vom Ausweichkolben 50 in der Bohrung 58 zur Zwischenscheibe 83 hin begrenzt wird.The channel 48 extends from the pressure chamber 40 through the Valve housing 89, the washer 90, the housing part 86th and the housing part 82. The housing part 82 has on its the intermediate disc 83 side facing a groove 92, in the channel 48 opens and connected to the vestibule 85 is. The channel 48 is thus on the groove 92, the vestibule 85th and the bore 84 is connected to the pump working space 22. Alternatively, it can also be provided that the channel 48 under Bypassing the anteroom 85 directly-via a hole in the Washer 83 is connected to the pump working chamber 22 is. The washer 83 may-while on its the Pump body 14 facing side have a groove, the towards the pump working chamber 22 is open and in the channel 48 opens. The groove may, for example, approximately radially to the Cylinder bore 16 extend and extends from the Cylinder bore 16 outward to the area of Washer 83, in which the channel 48 through this runs. The connection of the pressure chamber 40 of the Fuel injection valve 12 with the pump working space 22nd through the channel 48 takes place in this case directly below Bypassing of the anteroom 85, of the escape piston 50 in the Bore 58 is limited to the intermediate disc 83 out.

Das Kraftstoffeinspritzventil 12 und die Kraftstoffhochdruckpumpe 10 sind mittels einer Spannhülse 94 miteinander verbunden. Die Spannhülse 94 übergreift das Ventilgehäuse 89 und ist in eine Gewindebohrung 95 im Pumpenkörper 14 eingeschraubt. Die Zwischenscheibe 83, die Gehäuseteile 81,82,86 sowie die Zwischenscheibe 90 sind zwischen dem Ventilgehäuse 89 und dem Pumpenkörper 14 eingespannt.The fuel injection valve 12 and the High-pressure fuel pump 10 are by means of a clamping sleeve 94th connected with each other. The clamping sleeve 94 engages over Valve housing 89 and is in a threaded hole 95 in Pump body 14 screwed. The washer 83, the Housing parts 81,82,86 and the washer 90 are between the valve housing 89 and the pump body 14th clamped.

Der Federraum 46 ist mit einem Niederdruckbereich verbunden, beispielsweise mit dem Kraftstoffvorratsbehälter 24 oder mit einem Bereich, in dem ein etwas erhöhter Druck, beispielsweise 2 bis 5 bar aufrechterhalten wird. Vom Druckraum 40 des Kraftstoffeinspritzventils 12 führt ein weiterer Kanal 100 zur Zwischenscheibe 90 hin ab, der zum Kanal 48 in Umfangsrichtung versetzt ist und diesem beispielsweise etwa diametral gegenüberliegt. Der Kanal 100 setzt sich durch die Zwischenscheibe 90 und das Gehäuseteil 86 fort und mündet in den Federraum 46 im Gehäuseteil 82. Im Kanal 100 ist ein Rückschlagventil 102 angeordnet, das zum Druckraum 40 hin öffnet. Das Rückschlagventil 102 weist ein durch eine Schließfeder 104 in Schließrichtung beaufschlagtes Ventilglied 106 auf.The spring chamber 46 is connected to a low-pressure region, for example, with the fuel tank 24 or with an area where a slightly elevated pressure, for example, 2 to 5 bar is maintained. from Pressure chamber 40 of the fuel injection valve 12 introduces another channel 100 to the intermediate disc 90 down from, to the Channel 48 is offset in the circumferential direction and this for example, approximately diametrically opposite. The channel 100 continues through the washer 90 and the housing part 86 and opens into the spring chamber 46 in the housing part 82nd Im Channel 100, a check valve 102 is arranged, the Pressure chamber 40 opens. The check valve 102 has a by a closing spring 104 in the closing direction acted upon valve member 106.

Bei einem in Figur 2 dargestellten ersten Ausführungsbeispiel ist das Rückschlagventil 102 zwischen dem Ventilgehäuse 89 und der Zwischenscheibe 90 angeordnet. Der Kanal 100 ist im Ventilgehäuse 89 zur Zwischenscheibe 90 hin im Durchmesser vergrößert und in diesem ist die Schließfeder 104 und das Ventilglied 106 angeordnet. Der Kanal 100 weist in der Zwischenscheibe 90 einen kleineren Querschnitt auf als das Ventilglied 106, wobei die Mündung des Kanals 100 an der dem Ventilgehäuse 89 zugewandten Seite der Zwischenscheibe 90 einen Ventilsitz 108 bildet, mit dem das Ventilglied 106 zusammenwirkt und gegen den das Ventilglied 106 durch die Schließfeder 104 gepresst wird. In a first shown in Figure 2 Embodiment, the check valve 102 is between arranged the valve housing 89 and the washer 90. The channel 100 is in the valve housing 89 to the washer 90th enlarged in diameter and in this is the Closing spring 104 and the valve member 106 is arranged. Of the Channel 100 has a smaller one in the intermediate disk 90 Cross-section as the valve member 106, wherein the mouth of the channel 100 on the valve housing 89 side facing the intermediate disc 90 forms a valve seat 108, with the the valve member 106 cooperates and against the Valve member 106 is pressed by the closing spring 104.

In Figur 3 ist ein zweites Ausführungsbeispiel dargestellt, bei dem das Rückschlagventil 102 in der Zwischenscheibe 90 angeordnet ist, die zur Aufnahme des Rückschlagventils 102 eine etwas größere Dicke aufweist als beim ersten Ausführungsbeispiel. Der Kanal 100 kann im Ventilgehäuse 89 mit konstantem Querschnitt verlaufen und geht in die Zwischenscheibe 90 über. Zu der dem Gehäuseteil 86 zugewandten Seite der Zwischenscheibe 90 hin weist der Kanal 100 einen größeren Querschnitt auf und in diesem Bereich des Kanals 100 ist die Schließfeder 104 und das Ventilglied 106 angeordnet. Der Kanal 100 weist im Gehäuseteil 86 einen kleineren Querschnitt auf als das Ventilglied 106, wobei die Mündung des Kanals 100 an der der Zwischenscheibe 90 zugewandten Seite des Gehäuseteils 86 einen Ventilsitz 108 bildet, mit dem das Ventilglied 106 zusammenwirkt und gegen den das Ventilglied 106 durch die Schließfeder 104 gepresst wird.FIG. 3 shows a second exemplary embodiment, in which the check valve 102 in the washer 90th is arranged to receive the check valve 102nd has a slightly greater thickness than the first Embodiment. The channel 100 may be in the valve housing 89th run with a constant cross section and goes into the Washer 90 over. To the the housing part 86th facing side of the washer 90 toward the channel 100 a larger cross section on and in this area of the Channel 100 is the closing spring 104 and the valve member 106th arranged. The channel 100 has in the housing part 86 a smaller cross section than the valve member 106, wherein the Mouth of the channel 100 at the intermediate disc 90th facing side of the housing part 86 a valve seat 108th forms, with which the valve member 106 cooperates and against the valve member 106 is pressed by the closing spring 104 becomes.

Nachfolgend wird die Funktion der Kraftstoffeinspritzeinrichtung erläutert. Der Pumpenarbeitsraum 22 wird während des Saughubs des Pumpenkolbens 18 mit Kraftstoff gefüllt. Beim Förderhub des Pumpenkolbens 18 ist das Steuerventil 23 zunächst geöffnet, so daß sich im Pumpenarbeitsraum 22 kein Hochdruck aufbauen kann. Wenn die Kraftstoffeinspritzung beginnen soll, so wird das Steuerventil 23 durch die Steuereinrichtung 25 geschlossen, so daß der Pumpenarbeitsraum 22 vom Kraftstoffvorratsbehälter 24 getrennt ist und sich in diesem Hochdruck aufbaut. Wenn der Druck im Pumpenarbeitsraum 22 und im Druckraum 40 so hoch ist, daß die über die Druckschulter 42 auf das Einspritzventilglied 28 wirkende Kraft in Öffnungsrichtung 29 größer ist als die Kraft der Schließfeder 44, so bewegt sich das Einspritzventilglied 28 in Öffnungsrichtung 29 und gibt die wenigstens eine Einspritzöffnung 32 frei, durch die Kraftstoff in den Brennraum des Zylinders eingespritzt wird. Der Ausweichkolben 50 befindet sich hierbei in seiner Ausgangsstellung. Der Druck im Pumpenarbeitsraum 22 steigt nachfolgend entsprechend dem Profil des den Pumpenkolben 18 antreibenden Nockens weiter an.Below is the function of Fuel injection device explained. Of the Pump work space 22 is during the suction stroke of the Pump piston 18 filled with fuel. During the delivery stroke of the Pump piston 18, the control valve 23 is initially opened, so that build up in the pump working chamber 22 no high pressure can. If the fuel injection should start, so will the control valve 23 by the controller 25th closed, so that the pump chamber 22 from Fuel tank 24 is separated and located in this Builds up high pressure. When the pressure in the pump working space 22 and in the pressure chamber 40 is so high that over the Pressure shoulder 42 acting on the injection valve member 28 Force in the opening direction 29 is greater than the force of Closing spring 44, so the injection valve member 28 moves in the opening direction 29 and gives the at least one Injection port 32 free, through the fuel in the Combustion chamber of the cylinder is injected. Of the Ausweichkolben 50 is here in his Starting position. The pressure in the pump working chamber 22 increases below according to the profile of the pump piston 18th driving cam on.

Wenn die durch den im Pumpenarbeitsraum 22 und damit im Vorraum 85 herrschenden Druck auf den Ausweichkolben 50 ausgeübte Kraft größer wird als die durch die Schließfeder 44 auf den Ausweichkolben 50 ausgeübte Kraft, so führt der Ausweichkolben 50 seine Ausweichhubbewegung aus und bewegt sich in den Speicherraum 55. Hierbei wird ein Druckabfall im Pumpenarbeitsraum 22 verursacht und außerdem die Vorspannung der Schließfeder 44 erhöht, die sich über den Schaftteil 52 am Speicherkolben 50 abstützt. Durch den Druckabfall im Pumpenarbeitsraum 22 und im Druckraum 40 ergibt sich eine geringere Kraft in Öffnungsrichtung 29 auf das Einspritzventilglied 28 und infolge der Erhöhung der Vorspannung der Schließfeder 44 ergibt sich eine erhöhte Kraft in Schließrichtung auf das Einspritzventilglied 28, so daß dieses wieder in Schließrichtung bewegt wird, mit seiner Dichtfläche 34 am Ventilsitz 36 zur Anlage kommt und die Einspritzöffnungen 32 verschließt, so daß die Kraftstoffeinspritzung unterbrochen wird. Das Kraftstoffeinspritzventil 12 ist dabei nur für eine kurze Zeitdauer geöffnet und es wird nur eine geringe Menge Kraftstoff als Voreinspritzung in den Brennraum eingespritzt. Die eingespritzte Kraftstoffmenge ist im wesentlichen vom Öffnungsdruck des Ausweichkolbens 50 bestimmt, das ist der Druck im Pumpenarbeitsraum 22 und im Vorraum 85, bei dem der Ausweichkolben 50 seine Ausweichhubbewegung beginnt. Der Öffnungshub des Einspritzventilglieds 28 während der Voreinspritzung kann durch eine Dämpfungseinrichtung hydraulisch begrenzt sein. If by the in the pump chamber 22 and thus in the Anteroom 85 prevailing pressure on the bypass piston 50th applied force is greater than that by the closing spring 44 force exerted on the bypass piston 50, so performs the Ausweichkolben 50 his Ausweichhubbewegung and moves in the storage space 55. In this case, a pressure drop in Pump workspace 22 causes and also the bias the closing spring 44 increases, extending over the shaft portion 52nd supported on the accumulator piston 50. Due to the pressure drop in the Pump working chamber 22 and in the pressure chamber 40 results in a lower force in the opening direction 29 on the Injector member 28 and as a result of the increase in Preload the closing spring 44 results in an increased Force in the closing direction on the injection valve member 28, so that this is moved again in the closing direction, with his Sealing surface 34 on the valve seat 36 comes to rest and the Injection openings 32 closes, so that the Fuel injection is interrupted. The Fuel injector 12 is only for a short time Time period will be open and it will only be a small amount Fuel as a pilot injection into the combustion chamber injected. The injected fuel quantity is in essentially from the opening pressure of the bypass piston 50 determined, that is the pressure in the pump working chamber 22 and in the Anteroom 85, in which the bypass piston 50 his Dodge stroke begins. The opening stroke of the Injection valve member 28 during the pilot injection can be hydraulically limited by a damping device.

Der Druck im Pumpenarbeitsraum 22 steigt nachfolgend weiter an entsprechend dem Profil des den Pumpenkolben 18 antreibenden Nockens, so daß die auf das Einspritzventilglied 28 wirkende Druckkraft in Öffnungsrichtung 29 wieder zunimmt und die infolge der erhöhten Vorspannung der Schließfeder 44 erhöhte Schließkraft übersteigt, so daß das Kraftstoffeinspritzventil 12 wieder öffnet. Dabei wird eine größere Kraftstoffmenge über eine längere Zeitdauer eingespritzt als während der Voreinspritzung. Die Zeitdauer und die während dieser Haupteinspritzung eingespritzte Kraftstoffmenge werden durch den Zeitpunkt bestimmt, zu dem das Steuerventil 23 durch die Steuereinrichtung 25 wieder geöffnet wird. Nach dem Öffnen des Steuerventils 23 ist der Pumpenarbeitsraum 22 wieder mit dem Kraftstoffvorratsbehälter 24 verbunden, so daß dieser entlastet ist und das Kraftstoffeinspritzventil 12 schließt. Der Ausweichkolben 50 mit dem Schaftteil 52 wird durch die Kraft der Schließfeder 44 wieder in seine Ausgangsstellung zurückbewegt.The pressure in the pump working chamber 22 continues to rise below in accordance with the profile of the pump piston 18th driving cam, so that on the Injection valve member 28 acting pressure force in Opening direction 29 increases again and due to the increased bias of the closing spring 44 increased Closing force exceeds, so that the Fuel injector 12 opens again. There will be a larger amount of fuel over a longer period of time injected as during the pilot injection. The duration and the injected during this main injection Fuel quantity are determined by the time at which the control valve 23 by the control device 25 again is opened. After opening the control valve 23 is the Pump workspace 22 again with the Fuel tank 24 connected so that this is relieved and the fuel injection valve 12 closes. The bypass piston 50 with the shaft portion 52 is replaced by the Force of the closing spring 44 back to its original position moved back.

Wenn der Druck im Druckraum 40 höher ist als im Federraum 46, so ist der Federraum 46 durch das geschlossene Rückschlagventil 102 vom Druckraum 40 getrennt. Wenn zur Beendigung der Kraftstoffeinspritzung das Steuerventil 23 die Verbindung des Pumpenarbeitsraums 22 und damit mittelbar auch des Druckraums 40 des Kraftstoffeinspritzventils 12 mit dem Entlastungsraum öffnet, so sinkt der Druck im Druckraum 40 stark ab. Wenn der Druck im Druckraum 40 geringer wird als der Druck im Federraum 46, so öffnet das Rückschlagventil 102, so daß der Druck im Druckraum 40 nicht unter den im Federraum 46 herrschenden Druck absinken kann und Kraftstoff aus dem Federraum 46 in den Druckraum 40 strömt. Hierdurch wird Kavitation im Druckraum 40 vermieden. When the pressure in the pressure chamber 40 is higher than in the spring chamber 46, the spring chamber 46 through the closed Check valve 102 separated from the pressure chamber 40. If to Termination of the fuel injection, the control valve 23rd the connection of the pump working chamber 22 and thus indirectly also the pressure chamber 40 of the fuel injection valve 12 with opens the discharge chamber, so the pressure in the pressure chamber decreases 40 strong. When the pressure in the pressure chamber 40 becomes lower as the pressure in the spring chamber 46, it opens Check valve 102, so that the pressure in the pressure chamber 40 is not can drop below the pressure prevailing in the spring chamber 46 pressure and fuel from the spring chamber 46 in the pressure chamber 40th flows. As a result, cavitation in the pressure chamber 40 is avoided.

In Figur 4 ist die Kraftstoffeinspritzeinrichtung gemäß einem dritten Ausführungsbeispiel dargestellt, bei dem die Ausbildung des Kraftstoffeinspritzventils 12 mit dem Rückschlagventil 102 gleich ist wie beim ersten oder zweiten Ausführungsbeispiel, jedoch anstelle der Kraftstoffhochdruckpumpe 10 ein Hochdruckspeicher 110 als Hochdruckquelle dient, aus der Kraftstoff unter Hochdruck dem Druckraum 40 des Kraftstoffeinspritzventils 12 zugeführt wird. In den Hochdruckspeicher 110 wird durch eine Hochdruckpumpe 112 Kraftstoff gefördert. Zwischen dem Hochdruckspeicher 110 und dem Druckraum 40 des Kraftstoffeinspritzventils 12 ist ein elektrisch gesteuertes Ventil 123 angeordnet, das von einer Steuereinrichtung 125 angesteuert wird. Der Hochdruckspeicher 110 dient als Druckquelle für mehrere Kraftstoffeinspritzventile 12 oder für sämtliche Kraftstoffeinspritzventile 12 der Brennkraftmaschine. Die Funktion des Kraftstoffeinspritzventils 12 mit dem Rückschlagventil 102 ist gleich wie vorstehend erläutert.In Figure 4, the fuel injection device according to A third embodiment shown in which the Formation of the fuel injection valve 12 with the Check valve 102 is the same as the first or second Embodiment, but instead of High-pressure fuel pump 10, a high-pressure accumulator 110 as High-pressure source is used, from the fuel under high pressure supplied to the pressure chamber 40 of the fuel injection valve 12 becomes. In the high-pressure accumulator 110 is by a High pressure pump 112 fuel delivered. Between the High-pressure accumulator 110 and the pressure chamber 40 of the Fuel injection valve 12 is an electrically controlled Valve 123 arranged by a control device 125th is controlled. The high-pressure accumulator 110 serves as Pressure source for multiple fuel injection valves 12 or for all fuel injection valves 12 of the Internal combustion engine. The function of the Fuel injection valve 12 with the check valve 102nd is the same as explained above.

Claims (7)

  1. Fuel injection device for an internal combustion engine, with a fuel injection valve (12) which has an injection-valve member (28) which is guided displaceably in a valve body (26) and by means of which at least one injection orifice (32) is controlled and which can be moved in the opening direction (29), counter to the force of a closing spring (44) arranged in a spring space (46), by means of the pressure prevailing in a pressure space (40) of the fuel injection valve (12), fuel under high pressure being supplied from a high-pressure source (10; 110) to the pressure space (40) of the fuel injection valve (12) for fuel injection, and with an electrically controlled valve (23; 123), by means of which a connection of the pressure space (40) to a relief space (24) is controlled at least indirectly and by means of which the pressure space (40) is connected to the relief space (24) for the termination of fuel injection, characterized in that the pressure space (40) of the fuel injection valve (12) has a connection (100) to the spring space (46), the said connection having arranged in it a non-return valve (102) opening towards the pressure space (40).
  2. Fuel injection device according to Claim 1, characterized in that the spring space (46) is connected to a low-pressure region in which a relatively low pressure is maintained.
  3. Fuel injection device according to Claim 1 or 2, characterized in that the non-return valve (102) has a valve member (104) acted upon in its closing direction by a closing spring (104).
  4. Fuel injection device according to one of Claims 1 to 3, characterized in that it has, as a high-pressure source for each fuel injection valve (12), a separate high-pressure fuel pump (10), by means of which fuel is supplied to the pressure space (40) of the fuel injection valve (12).
  5. Fuel injection device according to one of Claims 1 to 3, characterized in that it has as a high-pressure source, for a plurality of fuel injection valves (12), a high-pressure accumulator (110), into which fuel is conveyed by means of a high-pressure pump (112) and out of which fuel is supplied to the pressure space (40) of the fuel injection valve (12).
  6. Fuel injection device according to one of the preceding claims, characterized in that the valve body (26) of the fuel injection valve (12) is of multi-part design and has a valve housing (89) and an intermediate disc (90) added to the latter towards the spring space (46), and in that the non-return valve (102) has a valve member (106) which is arranged in the valve housing (89) and which cooperates with a valve seat (108) formed on the intermediate disc (90).
  7. Fuel injection device according to one of Claims 1 to 5, characterized in that the valve body (26) of the fuel injection valve (12) is of multi-part design and has a valve housing (89) and, added to the latter, an intermediate disc (90) and a housing part (82), and in that the non-return valve (102) is arranged in the intermediate disc (90) or in the housing part (89).
EP02016075A 2001-08-10 2002-07-19 Fuel injection device for an internal combustion engine Expired - Lifetime EP1284360B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10139545 2001-08-10
DE10139545A DE10139545A1 (en) 2001-08-10 2001-08-10 Fuel injection device for an internal combustion engine

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EP1284360A2 EP1284360A2 (en) 2003-02-19
EP1284360A3 EP1284360A3 (en) 2004-03-17
EP1284360B1 true EP1284360B1 (en) 2005-05-18

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EP02016075A Expired - Lifetime EP1284360B1 (en) 2001-08-10 2002-07-19 Fuel injection device for an internal combustion engine

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US (1) US6817547B2 (en)
EP (1) EP1284360B1 (en)
JP (1) JP2003106242A (en)
DE (2) DE10139545A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006026877A1 (en) * 2006-06-09 2007-12-13 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
EP2077390B1 (en) * 2008-01-07 2012-09-05 Continental Automotive GmbH Coupling arrangement and connection assembly

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3823827A1 (en) * 1988-07-14 1990-01-18 Bosch Gmbh Robert FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES, IN PARTICULAR PUMPEDUESE
DE4004610A1 (en) * 1989-04-21 1990-10-25 Bosch Gmbh Robert FUEL INJECTION SYSTEM, IN PARTICULAR PUMP JET, FOR COMBUSTION MACHINES
US5213083A (en) * 1991-10-11 1993-05-25 Caterpillar Inc. Actuating fluid pump having priming reservoir
US6257499B1 (en) * 1994-06-06 2001-07-10 Oded E. Sturman High speed fuel injector
US5611317A (en) * 1995-08-09 1997-03-18 Cummins Engine Company, Inc. Open nozzle fuel injector having drive train wear compensation
JPH09209867A (en) * 1996-02-07 1997-08-12 Mitsubishi Motors Corp Fuel injector
DE19752834A1 (en) * 1997-11-28 1999-06-02 Bosch Gmbh Robert Fuel injection device for internal combustion engines

Also Published As

Publication number Publication date
EP1284360A2 (en) 2003-02-19
US6817547B2 (en) 2004-11-16
EP1284360A3 (en) 2004-03-17
DE50203132D1 (en) 2005-06-23
DE10139545A1 (en) 2003-02-20
JP2003106242A (en) 2003-04-09
US20030042334A1 (en) 2003-03-06

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