EP1284360A2 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine Download PDF

Info

Publication number
EP1284360A2
EP1284360A2 EP02016075A EP02016075A EP1284360A2 EP 1284360 A2 EP1284360 A2 EP 1284360A2 EP 02016075 A EP02016075 A EP 02016075A EP 02016075 A EP02016075 A EP 02016075A EP 1284360 A2 EP1284360 A2 EP 1284360A2
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
pressure
fuel
chamber
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.)
Granted
Application number
EP02016075A
Other languages
German (de)
French (fr)
Other versions
EP1284360A3 (en
EP1284360B1 (en
Inventor
Peter Boehland
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1284360A2 publication Critical patent/EP1284360A2/en
Publication of EP1284360A3 publication Critical patent/EP1284360A3/en
Application granted granted Critical
Publication of EP1284360B1 publication Critical patent/EP1284360B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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 one Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is by DE 28 08 731 C2 known.
  • This fuel injector has a fuel injector that is one in one Bore of a valve body slidably guided Injection valve member through which at least one Injection opening is controlled.
  • the injector member is by the in a pressure room of the Pressure prevailing against the fuel injector Force of a closing spring arranged in a spring chamber in an opening direction for releasing the at least one Injection opening movable.
  • In the spring chamber is a maintain predetermined pressure, with the spring space For example, be connected to a low pressure area can.
  • the pressure chamber of the fuel injector becomes Fuel injection from a high pressure fuel source fed under high pressure. Through an electrical controlled valve becomes a connection at least indirectly the pressure chamber or the high pressure source with one Relief chamber controlled.
  • the fuel injection device according to the invention with the Features according to claim 1 has the advantage that a pressure equalization between the Pressure chamber and the spring chamber is enabled when the pressure in the pressure chamber is less than in the spring chamber. This will avoided that the pressure in the pressure chamber below the vapor pressure of the fuel drops so that no cavitation occurs. The wear and the noise emission of the Fuel injection device according to the invention is thereby reduced.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation
  • Figure 2 with in Figure 1 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 one second embodiment
  • Figure 4 the A fuel injector according to a third Embodiment.
  • FIG 1 is a fuel injection device for a Internal combustion engine, for example of 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 everyone Cylinder a fuel injection valve 12.
  • execution of Fuel injector has this for everyone Internal combustion engine cylinders High pressure fuel pump 10 on.
  • the High pressure fuel pump 10 and that Fuel injection valve 12 are a so-called Pump-nozzle unit summarized.
  • the High pressure fuel pump 10 and that However, fuel injector 12 can also be separated be arranged from each other and via a line be connected.
  • the high pressure fuel pump 10 has a pump body 14, in which in a Cylinder bore 16 a pump piston 18 is tightly guided, which by a cam of a camshaft Internal combustion engine against the force of a return spring 19 is driven in one stroke.
  • the pump piston 18 limits one in the cylinder bore 16 Pump working space 22 in which the delivery stroke of Pump piston 18 fuel is compressed under high pressure.
  • the pump working space 22 is during the suction stroke of the pump piston 18 fuel from a fuel tank 24 supplied, for example by means of a feed pump.
  • the Pump work space 22 has a connection to one Relief space on than that for example the Fuel tank 24 can serve, and that of one electrically controlled valve 23 is controlled.
  • the electrically controlled valve 23 is with 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 that with the pump body 14 connected is.
  • a valve body 26 In the valve body 26 is in a bore 30 an injection valve member 28 guided longitudinally.
  • the Bore 30 runs at least approximately parallel to Cylinder 16 of the pump body 14, however, can also be inclined run to this.
  • the valve body 26 has on its Combustion chamber of the cylinder facing the internal combustion engine End area at least one, preferably several Injection openings 32 on.
  • the injection valve member 28 has at its end area facing the combustion chamber for example, approximately conical sealing surface 34, which with one in the valve body 26 in its facing the combustion chamber End area trained, for example also about cone-shaped valve seat 36 cooperates, from or to which discharge the injection openings 32.
  • valve body 26 is between the injection valve member 28 and the bore 30 toward the valve seat 36 toward an annular space 38 available, the one facing away from the valve seat 36 End area through a radial expansion of the bore 30 in a pressure chamber 40 surrounding the injection valve member 28 transforms.
  • the injection valve member 28 has the level of Pressure chamber 40 through a reduction in cross-section Valve seat 36 having pressure shoulder 42. At the End of the injection valve member 28 facing away from the combustion chamber attacks a preloaded closing spring 44 through which the Injection valve member 28 is pressed toward the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46, which connects to the bore 30.
  • the pressure chamber 40 is via a channel 48 running through the valve body 26 connected to the pump workspace 22.
  • the closing spring 44 is at least supported on the one hand indirectly, for example via a spring plate, on Injection valve member 28 and at least on the other hand indirectly, for example also via a spring plate 51, on an evasive piston 50.
  • the escape piston 50 is guided and points in a bore 80 of a housing part 81 at its end region facing the closing spring 44 Shaft part 52, which through a connecting bore 53 in a partition 54 of the housing part 81 between the Spring chamber 46 and one of these in the housing part 81 subsequent storage space 55 passes through.
  • the connection bore 53 has one smaller diameter than the spring chamber 46 and the Storage space 55.
  • the escape piston 50 points in the storage space 55 an area 56 with a larger diameter than that Connecting bore 53 so that a lifting movement of the Dodge piston 50 into the spring chamber 46 thereby it is limited that the area 56 of the evasive piston 50 is on the partition 54 comes to rest as a stop.
  • the Diverter piston 50 is in the bore with its area 56 80 with respect to the connection bore 53 accordingly larger diameter tightly guided.
  • the spring chamber 46 is as Bore formed in a housing part 82, which is part of the valve body 26 forms.
  • the channel 48 runs through the Housing part 82 is offset approximately parallel to spring chamber 46 this.
  • the spring chamber 46 leads from the storage chamber 55 end facing away from a bore 58 to the pump workspace 22nd down in the housing part 81.
  • the bore 58 has one smaller diameter than the bore 80.
  • the Dodge piston 50 points toward bore 58 at area 56 then a sealing surface 60, for example is approximately conical.
  • the sealing surface 60 acts with the mouth of the bore 58 in the storage space 55 on Housing part 81 together as a seat, which is also about can be conical.
  • the escape piston 50 has a shaft 62 projecting into the bore 58, the Diameter is smaller than that of the area 56.
  • the shaft 62 initially points to the sealing surface 60 much smaller diameter than the bore 58 and then a shaft area towards its free end 64 with a diameter that is only slightly smaller than that Diameter of the bore 58.
  • the shaft area 64 can have one or more flats 65 around its circumference, through the openings between the shaft portion 64 and the Bore 58 are formed through the fuel in the Storage space 55 can reach.
  • the fuel injector 12 is then connected to the Housing part 82 a further housing part 86 as part of the Arranged valve body 26 which has a bore 87, through which an end region of the injection valve member 28 passes through and protrudes into the spring chamber 46.
  • the Injection valve member 28 is supported with its end region in the Spring chamber 46 via a spring plate 88 on the closing spring 44 from.
  • the end region of the injection valve member 28 has a smaller diameter than that in the bore 30 guided area.
  • Between the housing part 86 and the Valve housing 89 is an intermediate plate 90 with a smaller one Thickness arranged.
  • the intermediate plate 90 has a bore 91 through which the end portion of the injector member 28 passes through.
  • the channel 48 runs from the pressure chamber 40 through the Valve housing 89, the intermediate disk 90, the housing part 86 and the housing part 82.
  • the housing part 82 has on it a groove 92 on the side facing the intermediate disk 83, in which the channel 48 opens and which is connected to the anteroom 85 is.
  • the channel 48 is thus via the groove 92, the antechamber 85 and bore 84 communicates with pump workspace 22.
  • the channel 48 under Bypassing the anteroom 85 directly - via a hole in the Intermediate plate 83 connected to the pump work space 22 is.
  • the washer 83 can - on its Pump body 14 facing side have a groove that is open to the pump work space 22 and into which the channel 48 opens.
  • the groove can, for example, be approximately radial to the Cylinder bore 16 extend and extends from the Cylinder bore 16 to the outside in 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 work chamber 22 through the channel 48 in this case takes place directly below Bypassing the anteroom 85, which is in the Bore 58 to the washer 83 is limited.
  • the fuel injector 12 and the High-pressure fuel pump 10 are by means of an adapter sleeve 94 connected with each other.
  • the clamping sleeve 94 overlaps this Valve housing 89 and is in a threaded bore 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 14 clamped.
  • the spring chamber 46 is connected to a low pressure area, for example with the fuel tank 24 or with an area in which a slightly increased pressure, for example, 2 to 5 bar is maintained.
  • Pressure chamber 40 of fuel injector 12 introduces further channel 100 down to the intermediate plate 90, the to Channel 48 is offset in the circumferential direction and this for example diametrically opposite.
  • Channel 100 settles through the washer 90 and the housing part 86 continues and opens into the spring chamber 46 in the housing part 82
  • Channel 100 is a check valve 102 is arranged to Pressure chamber 40 opens.
  • the check valve 102 has a by a closing spring 104 in the closing direction acted valve member 106-on.
  • Exemplary embodiment is the check valve 102 between the valve housing 89 and the washer 90.
  • the channel 100 is in the valve housing 89 to the washer 90 enlarged in diameter and in this is the Closing spring 104 and the valve member 106 arranged.
  • the Channel 100 has a smaller one in the intermediate disk 90 Cross section on as the valve member 106, with the mouth of the channel 100 on the side facing the valve housing 89 the intermediate plate 90 forms a valve seat 108 with which the valve member 106 cooperates and against which 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 102 is slightly thicker than the first Embodiment.
  • the channel 100 can be in the valve housing 89 run with a constant cross-section and goes into the Washer 90 over.
  • 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 106 arranged.
  • the channel 100 has one in the housing part 86 smaller cross section than the valve member 106, the Mouth of the channel 100 at the intermediate disk 90 facing side of the housing part 86 a valve seat 108 forms with which the valve member 106 cooperates and against which the valve member 106 is pressed by the closing spring 104 becomes.
  • the function of Fuel injector explained.
  • the pump working space 22 is activated during the suction stroke of the Pump piston 18 filled with fuel.
  • the control valve 23 is initially open, so that no high pressure build up in the pump work space 22 can. If fuel injection is to begin, then the control valve 23 by the control device 25 closed, so that the pump working space 22 from Fuel tank 24 is separated and in this High pressure builds up.
  • the pressure in the pump work room 22 and in the pressure chamber 40 is so high that the over Pressure shoulder 42 acting on the injection valve member 28 Force in the opening direction 29 is greater than the force of the Closing spring 44, the injection valve member 28 moves in 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.
  • the Dodge piston 50 is in his Starting position.
  • the pressure in the pump work space 22 increases subsequently according to the profile of the pump piston 18 driving cam.
  • the Fuel injection valve 12 is only for a short time Open period and only a small amount Fuel as a pre-injection into the combustion chamber injected.
  • the amount of fuel injected is in essentially from the opening pressure of the evasive piston 50 determined, that is the pressure in the pump work chamber 22 and in Anteroom 85, in which the evasive piston 50 is its Evasion stroke movement begins.
  • the opening stroke of the Injection valve member 28 during the pre-injection can be hydraulically limited by a damping device.
  • the pressure in the pump work chamber 22 subsequently increases on according to 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 that as a result of increased bias of the closing spring 44 increased Closing force exceeds, so that Fuel injection valve 12 opens again. Doing so larger amount of fuel over a longer period of time injected than during pre-injection. The length of time and the one injected during this main injection Amount of fuel is 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 evasive piston 50 with the shaft part 52 is through the Force of the closing spring 44 back to its starting position moved back.
  • the spring chamber 46 If 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 pressure chamber 40. If to Stop fuel injection control valve 23 the connection of the pump work space 22 and thus indirectly also of the pressure chamber 40 of the fuel injection valve 12 opens the relief chamber, the pressure in the pressure chamber drops 40 sharply. When the pressure in the pressure chamber 40 becomes lower than 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 under the pressure prevailing in the spring chamber 46 and fuel from the spring chamber 46 into the pressure chamber 40 flows. In this way, cavitation in the pressure chamber 40 is avoided.
  • the fuel injection device according to FIG a third embodiment shown in which the Formation of the fuel injector 12 with the Check valve 102 is the same as the first or second Embodiment, but instead of High-pressure fuel pump 10 as a high-pressure accumulator 110 High pressure source serves from the fuel under high pressure supplied to the pressure chamber 40 of the fuel injection valve 12 becomes.
  • High pressure accumulator 110 is by a High pressure pump 112 fueled.
  • Between the High-pressure accumulator 110 and the pressure chamber 40 of the Fuel injector 12 is an electrically controlled one Valve 123 arranged by a control device 125 is controlled.
  • the high pressure accumulator 110 serves as Pressure source for multiple fuel injectors 12 or for all fuel injection valves 12 the Internal combustion engine.
  • the function of the Fuel injector 12 with check valve 102 is the same as explained above.

Landscapes

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

Abstract

The pressure chamber (40) of the fuel injection valve (12) has a connection (100) with the spring chamber (46), in which a non return valve (102) is located. It opens towards the pressure chamber.

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 one 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 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 injection device is by DE 28 08 731 C2 known. This fuel injector has a fuel injector that is one in one Bore of a valve body slidably guided Injection valve member through which at least one Injection opening is controlled. The injector member is by the in a pressure room of the Pressure prevailing against the fuel injector Force of a closing spring arranged in a spring chamber in an opening direction for releasing the at least one Injection opening movable. In the spring chamber is a maintain predetermined pressure, with the spring space For example, be connected to a low pressure area can. The pressure chamber of the fuel injector becomes Fuel injection from a high pressure fuel source fed under high pressure. Through an electrical controlled valve becomes a connection at least indirectly the pressure chamber or the high pressure source with one Relief chamber controlled. To end the Fuel injection is through the valve connection opened with the relief chamber so that the pressure in the Pressure chamber drops and the fuel injector closes. The pressure in the pressure chamber drops very sharply, so that the vapor pressure of the fuel is undershot, so that cavitation occurs. this leads to too much 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 a pressure equalization between the Pressure chamber and the spring chamber is enabled when the pressure in the pressure chamber is less than in the spring chamber. This will avoided that the pressure in the pressure chamber below the vapor pressure of the fuel drops so that no cavitation occurs. The wear and the noise emission of the Fuel injection device according to the invention is thereby reduced.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben.In the dependent claims are advantageous Refinements 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 description below explained in more detail. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation, Figure 2 with in Figure 1 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 one second embodiment and Figure 4 the A fuel injector 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 of 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 everyone Cylinder a fuel injection valve 12. At the in Figure 1 shown execution of Fuel injector has this for everyone Internal combustion engine cylinders High pressure fuel pump 10 on. The High pressure fuel pump 10 and that Fuel injection valve 12 are a so-called Pump-nozzle unit summarized. The High pressure fuel pump 10 and that However, fuel injector 12 can also be separated be arranged from each other and via a line be connected. The high pressure fuel pump 10 has a pump body 14, in which in a Cylinder bore 16 a pump piston 18 is tightly guided, which by a cam of a camshaft Internal combustion engine against the force of a return spring 19 is driven in one stroke. The pump piston 18 limits one in the cylinder bore 16 Pump working space 22 in which the delivery stroke of Pump piston 18 fuel is compressed under high pressure. The pump working space 22 is during the suction stroke of the pump piston 18 fuel from a fuel tank 24 supplied, for example by means of a feed pump. The Pump work space 22 has a connection to one Relief space on than that for example the Fuel tank 24 can serve, and that of one electrically controlled valve 23 is controlled. The electrically controlled valve 23 is with 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 that with the pump body 14 connected is. In the valve body 26 is in a bore 30 an injection valve member 28 guided longitudinally. The Bore 30 runs at least approximately parallel to Cylinder 16 of the pump body 14, however, can also be inclined run to this. The valve body 26 has on its Combustion chamber of the cylinder facing the internal combustion engine End area at least one, preferably several Injection openings 32 on. The injection valve member 28 has at its end area facing the combustion chamber for example, approximately conical sealing surface 34, which with one in the valve body 26 in its facing the combustion chamber End area trained, for example also about cone-shaped valve seat 36 cooperates, from or to which 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 28 and the bore 30 toward the valve seat 36 toward an annular space 38 available, the one facing away from the valve seat 36 End area through a radial expansion of the bore 30 in a pressure chamber 40 surrounding the injection valve member 28 transforms. The injection valve member 28 has the level of Pressure chamber 40 through a reduction in cross-section Valve seat 36 having pressure shoulder 42. At the End of the injection valve member 28 facing away from the combustion chamber attacks a preloaded closing spring 44 through which the Injection valve member 28 is pressed toward the valve seat 36.

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 channel 48 running through the valve body 26 connected to the pump workspace 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 at least supported on the one hand indirectly, for example via a spring plate, on Injection valve member 28 and at least on the other hand indirectly, for example also via a spring plate 51, on an evasive piston 50. The escape piston 50 is guided and points in a bore 80 of a housing part 81 at its end region facing the closing spring 44 Shaft part 52, which through a connecting bore 53 in a partition 54 of the housing part 81 between the Spring chamber 46 and one of these in the housing part 81 subsequent storage space 55 passes through. On that in the Spring chamber 46 protruding end of the shaft part 52 is supported the spring plate 51 from. The connection bore 53 has one smaller diameter than the spring chamber 46 and the Storage space 55. The escape piston 50 points in the storage space 55 an area 56 with a larger diameter than that Connecting bore 53 so that a lifting movement of the Dodge piston 50 into the spring chamber 46 thereby it is limited that the area 56 of the evasive piston 50 is on the partition 54 comes to rest as a stop. The Diverter piston 50 is in the bore with its area 56 80 with respect to the connection bore 53 accordingly larger diameter tightly guided. The spring chamber 46 is as Bore formed in a housing part 82, which is part of the valve body 26 forms. The channel 48 runs through the Housing part 82 is offset approximately parallel to spring chamber 46 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.The spring chamber 46 leads from the storage chamber 55 end facing away from a bore 58 to the pump workspace 22nd down in the housing part 81. The bore 58 has one smaller diameter than the bore 80. The Dodge piston 50 points toward bore 58 at area 56 then a sealing surface 60, for example is approximately conical. The sealing surface 60 acts with the mouth of the bore 58 in the storage space 55 on Housing part 81 together as a seat, which is also about can be conical. The escape piston 50 has a shaft 62 projecting into the bore 58, the Diameter is smaller than that of the area 56. The shaft 62 initially points to the sealing surface 60 much smaller diameter than the bore 58 and then a shaft area towards its free end 64 with a diameter that is only slightly smaller than that Diameter of the bore 58. The shaft area 64 can have one or more flats 65 around its circumference, through the openings between the shaft portion 64 and the Bore 58 are formed through the fuel in the Storage space 55 can reach.

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.There is a between the housing part 81 and the pump body 14 Intermediate disc 83 is arranged in which a bore 84 through which the bore 58 in the housing part 81 is connected to the pump work space 22. The bore 84 represents a throttle point through which the bore 58 with the pump work space 22 is connected. The alternative piston 50 limited in the bore 58 to the washer 83 an anteroom 85, which via the throttle 84 with the Pump work space 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 escape piston 50 is in a home position is in which this with its sealing surface 60 on Sealing seat at the mouth of the bore 58 is so Storage space 55 from the anteroom 85 and thus from Pump work space 22 separately. In the starting position of the Dodge piston 50 acts in the pump work chamber 22 prevailing pressure on the end face of the shaft region 64 and through the openings between the shaft portion 64 and the bore 58 on the sealing surface 60 of the accumulator piston 50 corresponding to the diameter of the bore 58. The Evasion piston 50 is driven by the force of the closing spring 44 against that in the pump work room 22 and thus in the anteroom 85 prevailing pressure held in its initial position when caused by the pressure in the pump working space 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.If the pressure in the pump work room 22 and thus in the antechamber 85 rises so much that the 50 on the evasive piston generated force is greater than the force of the closing spring 44, so the evasive piston 50 and with it moves Shaft part 52 in an evasive movement into the storage space 55, wherein the shaft part 52 moves into the spring chamber 46. When the evasive piston 50 moves Fuel from the storage space 55 into the spring space 46 displaced by an annular gap between the shaft part 52 of the escape piston 50 and the connecting bore 53 must pass through. This will dampen the Evasion of the shaft part 52 and thus the Dodge 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.The fuel injector 12 is then connected to the Housing part 82 a further housing part 86 as part of the Arranged valve body 26 which has a bore 87, through which an end region of the injection valve member 28 passes through and protrudes into the spring chamber 46. The Injection valve member 28 is supported with its end region in the Spring chamber 46 via a spring plate 88 on the closing spring 44 from. The end region of the injection valve member 28 has a smaller diameter than that in the bore 30 guided area. The bore 30, the pressure chamber 40 and the annular space 38, at the lower end of which the valve seat 34 and the injection ports 32 are arranged in one valve housing 89 forming part of valve body 26 educated. Between the housing part 86 and the Valve housing 89 is an intermediate plate 90 with a smaller one Thickness arranged. The intermediate plate 90 has a bore 91 through which the end portion of the injector member 28 passes through.

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 runs from the pressure chamber 40 through the Valve housing 89, the intermediate disk 90, the housing part 86 and the housing part 82. The housing part 82 has on it a groove 92 on the side facing the intermediate disk 83, in which the channel 48 opens and which is connected to the anteroom 85 is. The channel 48 is thus via the groove 92, the antechamber 85 and bore 84 communicates with pump workspace 22. Alternatively, it can also be provided that the channel 48 under Bypassing the anteroom 85 directly - via a hole in the Intermediate plate 83 connected to the pump work space 22 is. The washer 83 can - on its Pump body 14 facing side have a groove that is open to the pump work space 22 and into which the channel 48 opens. The groove can, for example, be approximately radial to the Cylinder bore 16 extend and extends from the Cylinder bore 16 to the outside in 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 work chamber 22 through the channel 48 in this case takes place directly below Bypassing the anteroom 85, which is in the Bore 58 to the washer 83 is limited.

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 injector 12 and the High-pressure fuel pump 10 are by means of an adapter sleeve 94 connected with each other. The clamping sleeve 94 overlaps this Valve housing 89 and is in a threaded bore 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 14 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 area, for example with the fuel tank 24 or with an area in which a slightly increased pressure, for example, 2 to 5 bar is maintained. from Pressure chamber 40 of fuel injector 12 introduces further channel 100 down to the intermediate plate 90, the to Channel 48 is offset in the circumferential direction and this for example diametrically opposite. Channel 100 settles through the washer 90 and the housing part 86 continues and opens into the spring chamber 46 in the housing part 82 Channel 100 is a check valve 102 is arranged to Pressure chamber 40 opens. The check valve 102 has a by a closing spring 104 in the closing direction acted valve member 106-on.

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 Exemplary embodiment is the check valve 102 between the valve housing 89 and the washer 90. The channel 100 is in the valve housing 89 to the washer 90 enlarged in diameter and in this is the Closing spring 104 and the valve member 106 arranged. The Channel 100 has a smaller one in the intermediate disk 90 Cross section on as the valve member 106, with the mouth of the channel 100 on the side facing the valve housing 89 the intermediate plate 90 forms a valve seat 108 with which the valve member 106 cooperates and against which 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 102 is slightly thicker than the first Embodiment. The channel 100 can be in the valve housing 89 run with a constant cross-section and goes into the Washer 90 over. To the housing part 86 facing the side of the intermediate plate 90, 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 106 arranged. The channel 100 has one in the housing part 86 smaller cross section than the valve member 106, the Mouth of the channel 100 at the intermediate disk 90 facing side of the housing part 86 a valve seat 108 forms with which the valve member 106 cooperates and against which 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.The function of Fuel injector explained. The pump working space 22 is activated 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 open, so that no high pressure build up in the pump work space 22 can. If fuel injection is to begin, then the control valve 23 by the control device 25 closed, so that the pump working space 22 from Fuel tank 24 is separated and in this High pressure builds up. When the pressure in the pump work room 22 and in the pressure chamber 40 is so high that the over Pressure shoulder 42 acting on the injection valve member 28 Force in the opening direction 29 is greater than the force of the Closing spring 44, the injection valve member 28 moves in 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. The Dodge piston 50 is in his Starting position. The pressure in the pump work space 22 increases subsequently according to the profile of the pump piston 18 driving cam.

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 the by in the pump work room 22 and thus in Antechamber 85 prevailing pressure on the evasive piston 50 force exerted is greater than that by the closing spring 44 force exerted on the evasive piston 50, so leads Dodge piston 50 its evasive stroke movement and moves itself in the storage space 55. Here, a pressure drop in Pump work space 22 causes and also the bias the closing spring 44 increases, which extends over the shaft part 52 is supported on the accumulator piston 50. Due to the pressure drop in Pump work chamber 22 and in the pressure chamber 40 results in one lower force in the opening direction 29 on the Injector valve member 28 and due to the increase in Preload of 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 comes to rest on the valve seat 36 and the Injection openings 32 closes, so that the Fuel injection is interrupted. The Fuel injection valve 12 is only for a short time Open period and only a small amount Fuel as a pre-injection into the combustion chamber injected. The amount of fuel injected is in essentially from the opening pressure of the evasive piston 50 determined, that is the pressure in the pump work chamber 22 and in Anteroom 85, in which the evasive piston 50 is its Evasion stroke movement begins. The opening stroke of the Injection valve member 28 during the pre-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 work chamber 22 subsequently increases on according to 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 that as a result of increased bias of the closing spring 44 increased Closing force exceeds, so that Fuel injection valve 12 opens again. Doing so larger amount of fuel over a longer period of time injected than during pre-injection. The length of time and the one injected during this main injection Amount of fuel is 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 evasive piston 50 with the shaft part 52 is through the Force of the closing spring 44 back to its starting 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. If 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 pressure chamber 40. If to Stop fuel injection control valve 23 the connection of the pump work space 22 and thus indirectly also of the pressure chamber 40 of the fuel injection valve 12 opens the relief chamber, the pressure in the pressure chamber drops 40 sharply. When the pressure in the pressure chamber 40 becomes lower than 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 under the pressure prevailing in the spring chamber 46 and fuel from the spring chamber 46 into the pressure chamber 40 flows. In this way, 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.The fuel injection device according to FIG a third embodiment shown in which the Formation of the fuel injector 12 with the Check valve 102 is the same as the first or second Embodiment, but instead of High-pressure fuel pump 10 as a high-pressure accumulator 110 High pressure source serves 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 fueled. Between the High-pressure accumulator 110 and the pressure chamber 40 of the Fuel injector 12 is an electrically controlled one Valve 123 arranged by a control device 125 is controlled. The high pressure accumulator 110 serves as Pressure source for multiple fuel injectors 12 or for all fuel injection valves 12 the Internal combustion engine. The function of the Fuel injector 12 with check valve 102 is the same as explained above.

Claims (7)

Kraftstsoffeinspritzeinrichtung für eine Brennkraftmaschine mit einem Kraftstoffeinspritzventil (12), das ein in einem Ventilkörper (26) verschiebbar geführtes Einspritzventilglied (28) aufweist, durch das wenigstens eine Einspritzöffnung (32) gesteuert wird und das durch den in einem Druckraum (40) des Kraftstoffeinspritzventils (12) herrschenden Druck gegen die Kraft einer in einem Federraum (46) angeordneten Schließfeder (44) in Öffnungsrichtung (29) bewegbar ist, wobei dem Druckraum (40) des Kraftstoffeinspritzventils (12) zur Kraftstoffeinspritzung Kraftstoff unter hohem Druck von einer Hochdruckquelle (10;110) zugeführt wird, und mit einem elektrisch gesteuerten Ventil (23;123), durch das zumindest mittelbar eine Verbindung des Druckraums (40) mit einem Entlastungsraum (24) gesteuert wird und durch das zur Beendigung der Kraftstoffeinspritzung der Druckraum (40) mit dem Entlastungsraum (24) verbunden wird, dadurch gekennzeichnet, daß der Druckraum (40) des Kraftstoffeinspritzventils (12) eine Verbindung (100) mit dem Federraum (46) aufweist, in der ein zum Druckraum (40) hin öffnendes Rückschlagventil (102) angeordnet ist.Fuel injection device for an internal combustion engine with a fuel injection valve (12), which has an injection valve member (28) displaceably guided in a valve body (26), through which at least one injection opening (32) is controlled and through which in a pressure chamber (40) of the fuel injection valve ( 12) prevailing pressure against the force of a closing spring (44) arranged in a spring chamber (46) can be moved in the opening direction (29), the pressure chamber (40) of the fuel injection valve (12) for fuel injection under high pressure fuel from a high pressure source (10; 110) is supplied, and with an electrically controlled valve (23; 123), through which at least indirectly a connection of the pressure chamber (40) to a relief chamber (24) is controlled and through which to end the fuel injection, the pressure chamber (40) with the Relief chamber (24) is connected, characterized in that the pressure chamber (40) of the fuel feed scratch valve (12) has a connection (100) with the spring chamber (46), in which a check valve (102) opening towards the pressure chamber (40) is arranged. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Federraum (46) mit einem Niederdruckbereich verbunden ist, in dem ein relativ geringer Druck aufrechterhalten wird. Fuel injection device according to Claim 1, characterized in that the spring chamber (46) is connected to a low-pressure region in which a relatively low pressure is maintained. Kraftstoffeinspritzeinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Rückschlagventil (102) ein in seiner Schließrichtung durch eine Schließfeder (104) beaufschlagtes Ventilglied (104) aufweist.Fuel injection device according to Claim 1 or 2, characterized in that the check valve (102) has a valve member (104) acted upon in its closing direction by a closing spring (104). Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß diese als Hochdruckquelle für jedes Kraftstoffeinspritzventil (12) eine separate Kraftstoffhochdruckpumpe (10) aufweist, durch die Kraftstoff dem Druckraum (40) des Kraftstoffeinspritzventils (12) zugeführt wird.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) through which fuel is supplied to the pressure chamber (40) of the fuel injection valve (12). Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß diese als Hochdruckquelle einen Hochdruckspeicher (110) für mehrere Kraftstoffeinspritzventile (12) aufweist, in den Kraftstoff mittels einer Hochdruckpumpe (112) gefördert wird und aus dem Kraftstoff dem Druckraum (40) des Kraftstoffeinspritzventils (12) zugeführt wird.Fuel injection device according to one of Claims 1 to 3, characterized in that it has a high pressure source (110) for a plurality of fuel injection valves (12) as the high pressure source, into which fuel is conveyed by means of a high pressure pump (112) and from the fuel the pressure chamber (40) of the Fuel injection valve (12) is supplied. Kraftstoffeinspritzeinrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Ventilkörper (26) des Kraftstofeinspritzventils (12) mehrteilig ausgebildet ist und ein Ventilgehäuse (89) und eine an dieses zum Federraum (46) hin angefügte Zwischenscheibe (90) aufweist, daß das Rückschlagventil (102) ein im Ventilgehäuse (89) angeordnetes Ventilglied (106) aufweist, das mit einem an der Zwischenscheibe (90) ausgebildeten Ventilsitz (108) zusammenwirkt.Fuel injection device according to one of the preceding claims, characterized in that the valve body (26) of the fuel injection valve (12) is constructed in several parts and has a valve housing (89) and an intermediate disk (90) attached to the spring chamber (46) in such a way that the check valve (102) has a valve member (106) arranged in the valve housing (89), which cooperates with a valve seat (108) formed on the intermediate disk (90). Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Ventilkörper (26) des Kraftstoffeinspritzventils (12) mehrteilig ausgebildet ist und ein Ventilgehäuse (89) sowie an dieses angefügt eine Zwischenscheibe (90) und ein Gehäuseteil (82) aufweist, und daß das Rückschlagventil (102) in der Zwischenscheibe (90) oder im Gehäuseteil (82) angeordnet ist.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 constructed in several parts and has a valve housing (89) and an intermediate disk (90) and a housing part (82) attached thereto, and that the check valve (102) in the intermediate plate (90) or in the housing part (82) is arranged.
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

Publications (3)

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

Family

ID=7695168

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02016075A Expired - Lifetime EP1284360B1 (en) 2001-08-10 2002-07-19 Fuel injection device for an internal combustion engine

Country Status (4)

Country Link
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

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5213083A (en) * 1991-10-11 1993-05-25 Caterpillar Inc. Actuating fluid pump having priming reservoir
US5771865A (en) * 1996-02-07 1998-06-30 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Fuel injection system of an engine and a control method therefor

Family Cites Families (5)

* 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
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
DE19752834A1 (en) * 1997-11-28 1999-06-02 Bosch Gmbh Robert Fuel injection device for internal combustion engines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5213083A (en) * 1991-10-11 1993-05-25 Caterpillar Inc. Actuating fluid pump having priming reservoir
US5771865A (en) * 1996-02-07 1998-06-30 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Fuel injection system of an engine and a control method therefor

Also Published As

Publication number Publication date
EP1284360A3 (en) 2004-03-17
DE50203132D1 (en) 2005-06-23
JP2003106242A (en) 2003-04-09
DE10139545A1 (en) 2003-02-20
EP1284360B1 (en) 2005-05-18
US20030042334A1 (en) 2003-03-06
US6817547B2 (en) 2004-11-16

Similar Documents

Publication Publication Date Title
EP1636484B1 (en) Injector for internal combustion engines
EP1458970B1 (en) Fuel-injection device for an internal combustion engine
EP1490592A1 (en) Fuel injection device for an internal combustion engine
EP1363015A1 (en) Fuel injection system for an internal combustion engine
EP1402174B1 (en) Fuel injection device for an internal combustion engine
EP1260700B1 (en) Fuel injection system for internal combustion engine
DE10205185A1 (en) Fuel injection device for an internal combustion engine
WO2001031191A2 (en) Fuel injection valve for internal combustion engines
EP1384000B1 (en) Fuel injection device for an internal combustion engine
EP1310668A2 (en) Fuel injection system for a combustion engine
EP1284360B1 (en) Fuel injection device for an internal combustion engine
EP1383999B1 (en) Fuel injection device for an internal combustion engine
EP1260702A2 (en) A fuel injection system for an internal combustion engine
EP1377745B1 (en) Method for operating a pump-nozzle unit and a corresponding pump-nozzle unit
EP1552138B1 (en) Fuel injection device for an internal combustion engine
EP1606511B1 (en) Fuel injection device for a combustion engine
WO2003027490A1 (en) Fuel injection device for an internal combustion engine
EP1601870A1 (en) Fuel injection valve for an internal combustion engine
DE10233101A1 (en) Fuel injection device for an internal combustion engine
DE10162384A1 (en) Fuel injection device for an internal combustion engine
DE10323562A1 (en) Fuel injection device for an internal combustion engine
DE10337848A1 (en) Fuel injection valve for internal combustion engine has piston controlling connection between fuel-filled chamber, low pressure region so connection is at least approximately closed at start of valve element opening and is then opened up
DE10227011A1 (en) Fuel injection device for an internal combustion engine
EP1430216A1 (en) Fuel injection device for an internal combustion engine
WO2004046539A1 (en) Fuel injection valve of a fuel injection device for an engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

RIC1 Information provided on ipc code assigned before grant

Ipc: 7F 02M 59/36 B

Ipc: 7F 02M 59/46 A

Ipc: 7F 02M 63/00 B

Ipc: 7F 02M 57/02 B

Ipc: 7F 02M 55/00 B

Ipc: 7F 02M 61/16 B

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

17P Request for examination filed

Effective date: 20040917

AKX Designation fees paid

Designated state(s): DE ES FR GB IT

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050518

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50203132

Country of ref document: DE

Date of ref document: 20050623

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20050829

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20050914

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

ET Fr: translation filed
26N No opposition filed

Effective date: 20060221

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080718

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20080723

Year of fee payment: 7

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090719

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090719

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20100924

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130201

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50203132

Country of ref document: DE

Effective date: 20130201