EP1423599A1 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine

Info

Publication number
EP1423599A1
EP1423599A1 EP02758168A EP02758168A EP1423599A1 EP 1423599 A1 EP1423599 A1 EP 1423599A1 EP 02758168 A EP02758168 A EP 02758168A EP 02758168 A EP02758168 A EP 02758168A EP 1423599 A1 EP1423599 A1 EP 1423599A1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
pump
injection valve
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
EP02758168A
Other languages
German (de)
French (fr)
Other versions
EP1423599B1 (en
Inventor
Joachim Winter
Wendelin Potz
Gerhard Mack
Christoph Buehler
Friedrich Moser
Thomas Kuegler
Philippe Allio
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 EP1423599A1 publication Critical patent/EP1423599A1/en
Application granted granted Critical
Publication of EP1423599B1 publication Critical patent/EP1423599B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • 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
    • F02M59/30—Varying fuel delivery in quantity or timing with variable-length-stroke pistons
    • 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
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • 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
    • F02M59/46—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
    • 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
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators

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 known from EP 0 957 261 AI. This
  • Fuel injection device has a high-pressure fuel pump and a fuel injection valve connected to each cylinder of the internal combustion engine.
  • the high-pressure fuel pump has a pump piston which is driven by the internal combustion engine in a stroke movement and which delimits a pump work space which is connected to a pressure space of the fuel injection valve.
  • the fuel injection valve has an injection valve member, through which at least one injection opening is controlled and which can be moved in an opening direction against the closing force by the pressure prevailing in the pressure chamber. A connection of the is controlled by an electrically controlled control valve to control the fuel injection
  • the fuel injection device according to the invention with the features according to claim 1 has the advantage that additional injection cross section can be released or closed by the second injection valve member depending on the operating parameters of the internal combustion engine with the at least one second injection opening, so that the injection cross section to the
  • Operating conditions of the internal combustion engine can be optimally adjusted.
  • the design according to claim 2 enables easy control of the control pressure in the control room.
  • no additional component is required for this.
  • the embodiment according to claim 4 makes it possible that at the start of delivery of the pump piston initially only a small injection cross-section is released with the at least one injection opening and, with a larger stroke of the pump piston, a larger injection cross-section is additionally released with the at least one second injection opening.
  • the embodiment according to claim 5 enables a change in the stroke of the pump piston, from which the at least one second injection opening is opened.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation according to a first exemplary embodiment
  • FIG. 2 in an enlarged representation a section of a fuel injection valve denoted by II in FIG. 1 and FIG. 3 the fuel injection device according to a second exemplary embodiment.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the fuel injection device is designed as a so-called pump-nozzle system or as a pump-line-nozzle system and has a high-pressure fuel pump 10 and a fuel injection valve 12 connected to each cylinder of the internal combustion engine. When designed as a pump-line-nozzle system, the high-pressure fuel pump 10 is removed from the
  • Fuel injection valve 12 arranged and connected to it via a line.
  • the fuel injection device is designed as a pump-nozzle system, with the high-pressure fuel pump 10 and the like
  • Fuel injection valve 12 are connected directly to one another and form a structural unit.
  • the high-pressure fuel pump 10 has a pump piston 18 which is tightly guided in a cylinder bore 16 in a pump body 14 and is driven in a lifting movement by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19.
  • the pump piston 18 delimits a pump working chamber 22 in the cylinder 16, in which fuel is compressed under high pressure during the delivery stroke of the pump piston 18.
  • the pump working chamber 22 is supplied with fuel from a fuel reservoir 24 of the motor vehicle in a manner not shown in detail.
  • the fuel injection valve 12 has a valve body 26, which can be constructed in several parts, in which a first injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30.
  • the valve body 26 has at its end region facing the combustion chamber of the cylinder of the internal combustion engine at least one first, preferably a plurality of first injection openings 32, which are arranged distributed over the circumference of the valve body 26.
  • the first injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the first injection openings 32 lead away.
  • valve body 26 there is an annular space 38 between the injection valve member 28 and the bore 30 towards the valve seat 36, which, in its end region facing away from the valve seat 36, merges into a pressure space 40 surrounding the first injection valve member 28 by a radial expansion of the bore 30.
  • the first injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 by reducing the cross section.
  • a first prestressed closing spring 44 engages, by means of which the first injection valve member 28 is pressed toward the valve seat 36.
  • the first closing spring 44 is arranged in a first spring chamber 46 of the valve body 26, which adjoins the bore 30.
  • Fuel injection valve 12 is hollow and in this is coaxial in the injection valve member 28 trained bore a second injection valve member 128 slidably guided.
  • the second injection valve member 128 controls at least one second injection opening 132 in the valve body 26.
  • the at least one second injection opening 132 is offset in the direction of the longitudinal axis of the injection valve members 28, 128 to the at least one first injection opening 32 toward the combustion chamber.
  • the second injection valve member 128 has, for example, an approximately conical sealing surface 134 on its end region facing the combustion chamber, which cooperates with a valve seat 136 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the second injection openings 132 lead away.
  • the second injection valve member 128 can be formed in two parts and have a part which has the sealing surface 134 and faces the combustion chamber and a second part which adjoins the first part away from the combustion chamber. Near the end of the second injection valve member 128 on the combustion chamber side, a pressure surface 142 is formed thereon, on which the pressure prevailing in the pressure chamber 40 acts when the first injection valve member 28 is open.
  • a second spring chamber 146 is formed in the valve body 26, in which a second closing spring 144 acting on the second injection valve member 128 is arranged.
  • the end of the first injection valve member 28 projects into the first spring chamber 46 and is supported on the first closing spring 144.
  • the first closing spring 44 is supported with its end facing away from the first injection valve member 28 on a sleeve 47 which is arranged between the first spring chamber 46 and the second spring chamber 146 and is pressed, for example, into the valve body 26.
  • Injection valve member 128 protrudes through sleeve 47 into second spring space 146 and is supported by one Spring plate 147 on the second closing spring 144.
  • the second closing spring 144 is supported at the bottom of the second spring chamber 146 with its end facing away from the second valve member 128.
  • a control chamber 50 is delimited in the second spring chamber 146 by the spring plate 147.
  • a channel 52 leads from the pump work chamber 22 through the pump body 14 and the valve body 26 into the pressure chamber 40 of the fuel injection valve 12.
  • An electrically controlled valve 23 controls a connection of the pump work chamber 22 to a relief chamber, such as the fuel reservoir 24 or at least indirectly, for example Can serve area in which a slightly higher pressure than the fuel reservoir 24 is maintained. As long as no fuel injection is to take place, the connection of the pump work chamber 22 to the relief chamber is opened by the control valve 23, so that in the
  • control valve 23 separates the pump work chamber 22 from the relief chamber, so that high pressure can build up in the pump work chamber 22 during the delivery stroke of the pump piston 18.
  • the control valve 23 can be designed as a solenoid valve or as a piezo valve.
  • the pump piston 18 has a channel 60 running in it, which on the one hand opens into the pump working chamber 22 in a section running in the direction of the longitudinal axis of the pump piston 18 at the front end of the pump piston 18 and on the other hand in an approximately radial to the longitudinal axis of the pump piston 18 extending section at a distance from the front end on the outer surface of the pump piston 18 opens.
  • the radial section of channel 60 can, for example, be formed diametrically through the pump piston 18.
  • a circumferential annular groove 62 is formed in the pump body 14 in the cylinder bore 16 and is connected to the control chamber 50 via a channel 63 running through the pump body 14 and the valve body 26. A connection of the control chamber 50 to the pump working chamber 22 is thus controlled by the pump piston 18 depending on its stroke.
  • Pump working chamber 22 serves as a pressure source for controlling the pressure in the control chamber 50.
  • the mouth of the channel 60 on the outer surface of the pump piston 18 is in register with the annular groove 62, so that the control chamber 50 is connected to the pump work space 22.
  • the mouth of the channel 60 on the outer surface of the pump piston 18 is offset from the annular groove 62, so that the control chamber 50 is separated from the pump work chamber 22.
  • an intermediate shaft 70 is arranged, on which a transmission element 71 is arranged in the form of a two-armed rocker arm, which rolls with one end, for example, via a roller 72 on the cam 20, and which rolls its other end is hinged to the pump piston 18. It is provided that the position of the intermediate shaft 70 can be changed with the rocker arm 71, as a result of which the initial stroke position of the pump piston 18 can be changed.
  • 1 shows the intermediate shaft 70 with the rocker arm 71 and the left half of the pump piston 18 with solid lines in a first position in which the pump piston 18 has an initial stroke position in which the pump piston 18 is relatively far into the cylinder bore 16 in the pump body 14 dips.
  • the position of the intermediate shaft 70 can be adjusted, for example, by means of a hydraulic one
  • Adjustment device 74 take place, by which the mounting of the intermediate shaft 70 is shifted.
  • the adjusting device 74 can also be designed as an eccentric through which the bearing of the intermediate shaft 70 is displaced.
  • the control valve 23 is opened, so that fuel reaches the pump working chamber 22 from the fuel reservoir 24.
  • the start of the fuel injection is determined by the control valve 23 closing, so that the pump work chamber 22 is separated from the relief chamber and high pressure builds up in the pump work chamber 22.
  • the adjusting shaft 74 sets the intermediate shaft 70 into the required position. If the pump piston 18 has its initial stroke position shown in its right half in FIG. 1, the control chamber 50 is connected to the pump working chamber 22, so that there is a high control pressure in the latter.
  • the fuel injection valve 12 opens by the first Injection valve member 28 lifts with its sealing surface 34 from the valve seat 36 and the at least one first injection opening 32 opens.
  • the control pressure in the control chamber 50 acts on the second injection valve member 128 via the spring plate 147 and supports the closing spring 144, so that the pressure force acting on the second injection valve member 128 via the pressure surface 142 through the pressure surface 142 is not sufficient for the second injection valve member 128 to open.
  • Fuel injection valve 12 is thus opened with the first injection openings 32 only a part of the entire injection cross section, so that correspondingly only a small amount of fuel is injected.
  • the control chamber 50 is preferably connected to a relief chamber via at least one throttle point, so that the pressure in the control chamber 50 decreases.
  • only the force of the second closing spring 144 and possibly a small pressure force acts on the second injection valve member 128, so that the pressure force acting on the second injection valve member 128 through the pressure surface 142 through the pressure surface 142 is sufficient to also cover the second To open injection valve member 128 so that the at least one second injection opening 132 is also released.
  • the entire injection cross section is released at the fuel injection valve 12 and a larger amount of fuel is injected.
  • the end of the fuel injection is determined by the opening of the control valve 23, as a result of which the pump work chamber 22 is connected to the relief chamber and no high pressure can build up in it.
  • the pump piston 18 can have a further channel 65, which comes into overlap with the annular groove 62 when the pump piston 18 is at a maximum stroke into the pump working chamber 22 and establishes a connection to a relief chamber. With a maximum stroke of the pump piston 18, the control chamber 50 is thus connected to a relief chamber and pressure-relieved.
  • the injection cross sections formed by the first injection openings 32 and the second injection openings 132 are at least approximately the same size, so that when only the first injection valve member 28 is opened, half of the total
  • Injection cross section is released.
  • the first injection openings 32 form a larger or smaller injection cross section than the second injection openings 132.
  • the adjusting device 74 is controlled by an electrical control device 76, which also controls the control valve 23. If taking into account these operating parameters at the beginning of the fuel injection, only a small amount of fuel is to be injected, the adjusting device 74 is controlled by the control device 76 in such a way that the intermediate shaft 70 and thus the pump piston 18 are in the starting stroke position shown in FIG. 1 in the right half and at the beginning of fuel injection, only the first injection valve member 2 £ of the fuel injection valve 12 opens.
  • the adjusting device 74 is controlled by the control device 76 such that the intermediate shaft 70 and thus the pump piston 18 are shown in the left half in FIG. 1 Starting stroke position is and both injection valve members 28 and 128 of the fuel injection valve 12 open at the beginning of the fuel injection.
  • a high-pressure fuel pump 10 is provided for each cylinder, but only one camshaft 20 and one intermediate shaft 70 are provided for driving it. In order to change the position of the intermediate shaft 70 and the initial stroke position of the pump pistons 18 of all high-pressure fuel pumps 10, only one adjusting device 74 is required.
  • FIG. 3 shows the fuel injection device according to a second exemplary embodiment, in which the basic structure is the same as in the first exemplary embodiment.
  • the pump working chamber 22 is not used as the pressure source for controlling the pressure in the control chamber 50 in the second exemplary embodiment, but rather a fuel inlet, through which fuel flows into the pump working chamber 22 during the suction stroke of the pump piston 18 is fed.
  • a fuel channel 80 formed in the pump body 14 is connected to the fuel inlet and opens at the jacket of the cylinder bore 16 in which the pump piston 18 is guided. In a region offset in the circumferential direction for the opening of the fuel channel 80, the channel 63, which leads to the control chamber 50, opens at the jacket of the cylinder bore 16.
  • a channel 82 is formed in the pump piston 18, which extends, for example, radially to the longitudinal axis of the pump piston 18 and which opens into the jacket of the pump piston 18.
  • the connection of the fuel channel 80 with the channel 63 to the control chamber 50 is controlled by the pump piston 18 depending on its stroke position through its channel 82.
  • the intermediate shaft 70 is again shown with the pump piston 18 in different positions.
  • the channel 82 of the pump piston 18 is in register with the mouth of the fuel channel 80 and the mouth of the channel 63 leading to the control chamber 50, so that the control chamber 50 with the fuel channel 80 connected is.
  • the increased pressure in the fuel channel 80 thus acts in the control chamber 50, so that in the fuel injection valve 12 the second injection valve member 128 remains in its closed position and only the first injection valve member 28 opens.
  • the channel 82 of the pump piston 18 is not in overlap with the opening of the fuel channel 80 and the opening of the channel 63 leading to the control chamber 50, but is arranged offset to these, so that the control chamber 50 is separated from the fuel channel 80. No increased pressure thus acts in the control chamber 50, so that both injection valve members 28 and 128 open in the fuel injection valve 12.

Abstract

The fuel injection device is provided - for each cylinder of the internal combustion engine with a high-pressure fuel pump (10) with a working pumping chamber (22) and a fuel injection valve (12) connected thereto.The fuel injection valve (12) comprises a first injection valve member (28) which is used to control at least one first injection opening (32) and which on account of the pressure produced in the working pumping chamber (22) can be moved counter to a closing force in a direction of opening (29). A second injection valve member (128) is displaceably guided in the first hollow injection valve member (28) and used to control at least one second injection opening (132); whereby the pressure prevailing in the pressure chamber (40) enables it to be moved counter to a closing force in a direction of opening (29), whereby the second injection valve member (128) can be impinged upon by the pressure prevailing in a control chamber (50) filled with fuel, said pressure being able to be controlled according to operational parameters of the combustion engine in such a way that the second injection valve (128) can be blocked in a position closing the at least one second injection opening (132) as a result of the pressure prevailing in the control chamber (50) independently of an opening movement of the first injection valve member (28).

Description

Kraftstoffeinspritzeinrichtung für eine BrennkraftmaschineFuel injection device for an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einerThe invention is based on one
Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.Fuel injection device for an internal combustion engine according to the preamble of claim 1.
Eine solche Kraftstoffeinspritzeinrichtung ist durch die EP 0 957 261 AI bekannt. DieseSuch a fuel injection device is known from EP 0 957 261 AI. This
Kraftstoffeinspritzeinrichtung weist für jeden Zylinder der Brennkraftmaschine eine Kraftstoffhochdruckpumpe und ein mit dieser verbundenes Kraftstoffeinspritzventil auf. Die Kraftstoffhochdruckpumpe weist einen durch die Brennkraftmaschine in einer Hubbewegung angetriebenen Pumpenkolben auf, der einen Pumpenarbeitsraum begrenzt, der mit einem Druckraum des Kraftstoffeinspritzventils verbunden ist. Das Kraftstoffeinspritzventil weist ein Einspritzventilglied auf, durch das wenigstens eine Einspritzöffnung gesteuert wird und das durch den im Druckraum herrschenden Druck gegen eine Schließkraft in einer Öffnungsrichtung bewegbar ist. Durch ein elektrisch gesteuertes Steuerventil wird zur Steuerung der Kraftstoffeinspritzung eine Verbindung desFuel injection device has a high-pressure fuel pump and a fuel injection valve connected to each cylinder of the internal combustion engine. The high-pressure fuel pump has a pump piston which is driven by the internal combustion engine in a stroke movement and which delimits a pump work space which is connected to a pressure space of the fuel injection valve. The fuel injection valve has an injection valve member, through which at least one injection opening is controlled and which can be moved in an opening direction against the closing force by the pressure prevailing in the pressure chamber. A connection of the is controlled by an electrically controlled control valve to control the fuel injection
Pumpenarbeitsraums mit einem Entlastungsraum gesteuert. Wenn der Druck im Pumpenarbeitsraum und damit im Druckraum des Kraftstoffeinspritzventils den Öffnungsdruck erreicht, so bewegt sich das Einspritzventilglied in Öffnungsrichtung und gibt die wenigstens eine Einspritzöffnung frei. Der Einspritzquerschnitt, der durch das Einspritzventilglied dabei gesteuert wird ist immer gleich groß. Dies ermöglicht nicht unter allen Betriebsbedingungen der Brennkraftmaschine eine optimale Kraftstoffeinspritzung. Vorteile der ErfindungPump work room controlled with a relief room. When the pressure in the pump work chamber and thus in the pressure chamber of the fuel injection valve reaches the opening pressure, the injection valve member moves in the opening direction and releases the at least one injection opening. The injection cross section that is controlled by the injection valve member is always the same size. This does not enable optimal fuel injection under all operating conditions of the internal combustion engine. Advantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß durch das zweite Einspritzventilglied abhängig von Betriebsparametern der Brennkraftmaschine mit der wenigstens einen zweiten Einspritzöffnung zusätzlicher Einspritzquerschnitt freigegeben oder verschlossen werden kann, so daß der Einspritzquerschnitt an dieThe fuel injection device according to the invention with the features according to claim 1 has the advantage that additional injection cross section can be released or closed by the second injection valve member depending on the operating parameters of the internal combustion engine with the at least one second injection opening, so that the injection cross section to the
Betriebsbedingungen der Brennkraftmaschine optimal angepasst werden kann .Operating conditions of the internal combustion engine can be optimally adjusted.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben. Die Ausbildung gemäß Anspruch 2 ermöglicht eine einfache Steuerung des Steuerdrucks im Steuerraum. Bei der Ausbildung gemäß Anspruch 3 ist hierfür kein zusätzliches Bauteil erforderlich. Die Ausbildung gemäß Anspruch 4 ermöglicht es, daß bei Förderbeginn des Pumpenkolbens zunächst mit der wenigstens einen Einspritzöffnung nur ein geringer Einspritzquerschnitt und bei größerem Hub des Pumpenkolbens zusätzlich mit der wenigstens einen zweiten Einspritzöffnung ein größerer Einspritzquerschnitt freigegeben wird. Die Ausbildung gemäß Anspruch 5 ermöglicht eine Änderung des Hubwegs des Pumpenkolbens, ab dem die wenigstens eine zweite Einspritzöffnung aufgesteuert wird.Advantageous refinements and developments of the fuel injection device according to the invention are specified in the dependent claims. The design according to claim 2 enables easy control of the control pressure in the control room. In the embodiment according to claim 3, no additional component is required for this. The embodiment according to claim 4 makes it possible that at the start of delivery of the pump piston initially only a small injection cross-section is released with the at least one injection opening and, with a larger stroke of the pump piston, a larger injection cross-section is additionally released with the at least one second injection opening. The embodiment according to claim 5 enables a change in the stroke of the pump piston, from which the at least one second injection opening is opened.
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 gemäß einem ersten Ausführungsbeispiel, Figur 2 in vergrößerter Darstellung einen in Figur 1 mit II bezeichneten Ausschnitt eines Kraftstoffeinspritzventils und Figur 3 die Kraftstoffeinspritzeinrichtung gemäß einem zweiten Ausführungsbeispiel .Several embodiments of the invention are shown in the drawing and explained in more detail in the following description. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation according to a first exemplary embodiment, FIG. 2 in an enlarged representation a section of a fuel injection valve denoted by II in FIG. 1 and FIG. 3 the fuel injection device according to a second exemplary embodiment.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In den Figuren 1 bis 3 ist eineIn Figures 1 to 3 is one
Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine eines Kraftfahrzeugs dargestellt. Die Brennkraftmaschine ist vorzugsweise eine selbstzündende Brennkraftmaschine. Die Kraftstoffeinspritzeinrichtung ist als sogenanntes Pumpe- Düse-System oder als Pumpe-Leitung-Düse-System ausgebildet und weist für jeden Zylinder der Brennkraftmaschine jeweils eine Kraftstoffhochdruckpumpe 10 und ein mit dieser verbundenes Kraftstoffeinspritzventil 12 auf. Bei einer Ausbildung als Pumpe-Leitung-Düse-System ist die Kraftstoffhochdruckpumpe 10 entfernt vomFuel injection device for an internal combustion engine of a motor vehicle shown. The internal combustion engine is preferably a self-igniting internal combustion engine. The fuel injection device is designed as a so-called pump-nozzle system or as a pump-line-nozzle system and has a high-pressure fuel pump 10 and a fuel injection valve 12 connected to each cylinder of the internal combustion engine. When designed as a pump-line-nozzle system, the high-pressure fuel pump 10 is removed from the
Kraftstoffeinspritzventil 12 angeordnet und mit diesem über eine Leitung verbunden. Bei den dargestellten Ausführungsbeispielen ist die Kraftstoffeinspritzeinrichtung als Pumpe-Düse-System ausgebildet, wobei die Kraftstoffhochdruckpumpe 10 und dasFuel injection valve 12 arranged and connected to it via a line. In the exemplary embodiments shown, the fuel injection device is designed as a pump-nozzle system, with the high-pressure fuel pump 10 and the like
Kraftstoffeinspritzventil 12 direkt miteinander verbunden sind und eine Baueinheit bilden. Die Kraftstoffhochdruckpumpe 10 weist einen in einer Zylinderbohrung 16 in einem Pumpenkörper 14 dicht geführten Pumpenkolben 18 auf, der durch einen Nocken 20 einer Nockenwelle der Brennkraftmaschine entgegen der Kraft einer Rückstellfeder 19 in einer Hubbewegung angetrieben wird. Der Pumpenkolben 18 begrenzt im Zylinder 16 einen Pumpenarbeitsraum 22, in dem beim Förderhub des Pumpenkolbens 18 Kraftstoff unter Hochdruck verdichtet wird. Dem Pumpenarbeitsraum 22 wird beim Saughub des Pumpenolbens 18 in nicht näher dargestellter Weise Kraftstoff aus einem Kraftstoffvorratsbehälter 24 des Kraftfahrzeugs zugeführt.Fuel injection valve 12 are connected directly to one another and form a structural unit. The high-pressure fuel pump 10 has a pump piston 18 which is tightly guided in a cylinder bore 16 in a pump body 14 and is driven in a lifting movement by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19. The pump piston 18 delimits a pump working chamber 22 in the cylinder 16, in which fuel is compressed under high pressure during the delivery stroke of the pump piston 18. During the suction stroke of the pump piston 18, the pump working chamber 22 is supplied with fuel from a fuel reservoir 24 of the motor vehicle in a manner not shown in detail.
Das Kraftstoffeinspritzventil 12 weist einen Ventilkörper 26 auf, der mehrteilig ausgebildet sein kann, in dem ein erstes Einspritzventilglied 28 in einer Bohrung 30 längsverschiebbar geführt ist. Der Ventilkörper 26 weist an seinem dem Brennraum des Zylinders der Brennkraftmaschine zugewandten Endbereich wenigstens eine erste, vorzugsweise mehrere erste Einspritzöffnungen 32 auf, die über den Umfang des Ventilkörpers 26 verteilt angeordnet sind. Das erste 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 Ventilsitz 36 zusammenwirkt, von dem oder nach dem die ersten Einspritzöffnungen 32 abführen. 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 erste Einspritzventilglied 28 umgebenden Druckraum 40 übergeht. Das erste Einspritzventilglied 28 weist auf Höhe des Druckraums 40 durch eine Querschnittsverringerung eine Druckschulter 42 auf. Am dem Brennraum abgewandten Ende des ersten Einspritzventilglieds 28 greift eine erste vorgespannte Schließfeder 44 an, durch die das erste Einspritzventilglied 28 zum Ventilsitz 36 hin gedrückt wird. Die erste Schließfeder 44 ist in einem ersten Federraum 46 des Ventilkörpers 26 angeordnet, der sich an die Bohrung 30 anschließt .The fuel injection valve 12 has a valve body 26, which can be constructed in several parts, in which a first injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30. The valve body 26 has at its end region facing the combustion chamber of the cylinder of the internal combustion engine at least one first, preferably a plurality of first injection openings 32, which are arranged distributed over the circumference of the valve body 26. The first injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the first injection openings 32 lead away. In the valve body 26 there is an annular space 38 between the injection valve member 28 and the bore 30 towards the valve seat 36, which, in its end region facing away from the valve seat 36, merges into a pressure space 40 surrounding the first injection valve member 28 by a radial expansion of the bore 30. The first injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 by reducing the cross section. At the end of the first injection valve member 28 facing away from the combustion chamber, a first prestressed closing spring 44 engages, by means of which the first injection valve member 28 is pressed toward the valve seat 36. The first closing spring 44 is arranged in a first spring chamber 46 of the valve body 26, which adjoins the bore 30.
Das erste Einspritzventilglied 28 desThe first injection valve member 28 of the
Kraftstoffeinspritzventils 12 ist hohl ausgebildet und in diesem ist in einer koaxial im Einspritzventilglied 28 ausgebildeten Bohrung ein zweites Einspritzventilglied 128 verschiebbar geführt. Durch das zweite Einspritzventilglied 128 wird wenigstens eine zweite Einspritzöffnung 132 im Ventilkörper 26 gesteuert. Die wenigstens eine zweite Einspritzöfnung 132 ist in Richtung der Längsachse der Einspritzventilglieder 28,128 zu der wenigstens einen ersten Einspritzöffnung 32 zum Brennraum hin versetzt angeordnet. Das zweite Einspritzventilglied 128 weist an seinem dem Brennraum zugewandten Endbereich eine beispielsweise etwa kegelförmige Dichtfläche 134 auf, die mit einem im Ventilkörper 26 in dessen dem Brennraum zugewandtem Endbereich ausgebildeten Ventilsitz 136 zusammenwirkt, von dem oder nach dem die zweiten Einspritzöffnungen 132 abführen. Das zweite Einspritzventilglied 128 kann zweiteilig ausgebildet sein und einen die Dichtfläche 134 aufweisenden, dem Brennraum zugewandten Teil und einen vom Brennraum weg an den ersten Teil anschließenden zweiten Teil aufweisen. Nahe dem brennraumseitigen Ende des zweiten Einspritzventilglieds 128 ist an diesem eine Druckfläche 142 gebildet, auf die bei geöffnetem erstem Einspritzventilglied 28 der im Druckraum 40 herrschende Druck wirkt.Fuel injection valve 12 is hollow and in this is coaxial in the injection valve member 28 trained bore a second injection valve member 128 slidably guided. The second injection valve member 128 controls at least one second injection opening 132 in the valve body 26. The at least one second injection opening 132 is offset in the direction of the longitudinal axis of the injection valve members 28, 128 to the at least one first injection opening 32 toward the combustion chamber. The second injection valve member 128 has, for example, an approximately conical sealing surface 134 on its end region facing the combustion chamber, which cooperates with a valve seat 136 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the second injection openings 132 lead away. The second injection valve member 128 can be formed in two parts and have a part which has the sealing surface 134 and faces the combustion chamber and a second part which adjoins the first part away from the combustion chamber. Near the end of the second injection valve member 128 on the combustion chamber side, a pressure surface 142 is formed thereon, on which the pressure prevailing in the pressure chamber 40 acts when the first injection valve member 28 is open.
An den ersten Federraum 46 vom Brennraum weg anschließend ist im Ventilkörper 26 ein zweiter Federraum 146 ausgebildet, in dem eine zweite, auf das zweite Einspritzventilglied 128 wirkende Schließfeder 144 angeordnet ist. Das erste Einspritzventilglied 28 ragt mit seinem Ende in den ersten Federraum 46 hinein und stützt sich an der ersten Schließfeder 144 ab. Die erste Schließfeder 44 stützt sich mit ihrem dem ersten Einspritzventilglied 28 abgewandten Ende an einem zwischen dem ersten Federraum 46 und dem zweiten Federraum 146 angeordneten Hülse 47 ab, die beispielsweise in den Ventilkörper 26 eingepresst ist. Das zweiteFollowing the first spring chamber 46 away from the combustion chamber, a second spring chamber 146 is formed in the valve body 26, in which a second closing spring 144 acting on the second injection valve member 128 is arranged. The end of the first injection valve member 28 projects into the first spring chamber 46 and is supported on the first closing spring 144. The first closing spring 44 is supported with its end facing away from the first injection valve member 28 on a sleeve 47 which is arranged between the first spring chamber 46 and the second spring chamber 146 and is pressed, for example, into the valve body 26. The second
Einspritzventilglied 128 ragt durch die Hülse 47 hindurch in den zweiten Federraum 146 und stützt sich über einen Federteller 147 an der zweiten Schließfeder 144 ab. Die zweite Schließfeder 144 stützt sich mit ihrem dem zweiten Ventilglied 128 abgewandten Ende am Boden des zweiten Federraums 146 ab. Durch den Federteller 147 wird im zweiten Federraum 146 ein Steuerraum 50 begrenzt.Injection valve member 128 protrudes through sleeve 47 into second spring space 146 and is supported by one Spring plate 147 on the second closing spring 144. The second closing spring 144 is supported at the bottom of the second spring chamber 146 with its end facing away from the second valve member 128. A control chamber 50 is delimited in the second spring chamber 146 by the spring plate 147.
Vom Pumpenarbeitsraum 22 führt durch den Pumpenkörper 14 und den Ventilkörper 26 ein Kanal 52 in den Druckraum 40 des Kraftstoffeinspritzventils 12. Durch ein elektrisch gesteuertes Ventil 23 wird eine Verbindung des Pumpenarbeitsraums 22 mit einem Entlastungsraum gesteuert, als der beispielsweise zumindest mittelbar der Kraftstoffvorratsbehälter 24 oder ein Bereich dienen kann, in dem ein gegenüber dem Kraftstoffvorratsbehälter 24 etwas erhöhter Druck aufrechterhalten wird. Solange keine Kraftstoffeinspritzung erfolgen soll ist durch das Steuerventil 23 die Verbindung des Pumpenarbeitsraums 22 mit dem Entlastungsraum geöffnet, so daß sich imA channel 52 leads from the pump work chamber 22 through the pump body 14 and the valve body 26 into the pressure chamber 40 of the fuel injection valve 12. An electrically controlled valve 23 controls a connection of the pump work chamber 22 to a relief chamber, such as the fuel reservoir 24 or at least indirectly, for example Can serve area in which a slightly higher pressure than the fuel reservoir 24 is maintained. As long as no fuel injection is to take place, the connection of the pump work chamber 22 to the relief chamber is opened by the control valve 23, so that in the
Pumpenarbeitsraum 22 kein Hochdruck aufbauen kann. Wenn eine Kraftstoffeinspritzung erfolgen soll wird durch das Steuerventil 23 der Pumpenarbeitsraum 22 vom Entlastungsraum getrennt, so daß sich beim Förderhub des Pumpenkolbens 18 im Pumpenarbeitsraum 22 Hochdruck aufbauen kann. Das Steuerventil 23 kann als Magnetventil oder als Piezoventil ausgebildet sein.Pump work room 22 can not build up high pressure. If fuel injection is to take place, the control valve 23 separates the pump work chamber 22 from the relief chamber, so that high pressure can build up in the pump work chamber 22 during the delivery stroke of the pump piston 18. The control valve 23 can be designed as a solenoid valve or as a piezo valve.
Die Kraftstoffeinspritzeinrichtung ist in den Figuren 1 und 2 gemäß einem ersten Ausführungsbeispiel dargestellt. Beim ersten Ausführungsbeispiel weist der Pumpenkolben 18 einen in diesem verlaufenden Kanal 60 auf, der einerseits in einem in Richtung des Längsachse des Pumpenkolbens 18 verlaufenden Abschnitt am Stirnende des Pumpenkolbens 18 in den Pumpenarbeitsraum 22 mündet und der andererseits in einem etwa radial zur Längsachse des Pumpenkolbens 18 verlaufenden Abschnitt mit Abstand vom Stirnende an der Mantelfläche des Pumpenkolbens 18 mündet. Der radiale Abschnitt des Kanals 60 kann beispielsweise diametral durchgehend durch den Pumpenkolben 18 ausgebildet sein. Im Pumpenkörper 14 ist in der Zylinderbohrung 16 eine umlaufende Ringnut 62 ausgebildet, die über einen durch den Pumpenkörper 14 und den Ventilkörper 26 verlaufenden Kanal 63 mit dem Steuerraum 50 verbunden ist. Durch den Pumpenkolben 18 wird somit abhängig von dessen Hub eine Verbindung des Steuerraums 50 mit dem Pumpenarbeitsraum 22 gesteuert. DerThe fuel injection device is shown in Figures 1 and 2 according to a first embodiment. In the first exemplary embodiment, the pump piston 18 has a channel 60 running in it, which on the one hand opens into the pump working chamber 22 in a section running in the direction of the longitudinal axis of the pump piston 18 at the front end of the pump piston 18 and on the other hand in an approximately radial to the longitudinal axis of the pump piston 18 extending section at a distance from the front end on the outer surface of the pump piston 18 opens. The radial section of channel 60 can, for example, be formed diametrically through the pump piston 18. A circumferential annular groove 62 is formed in the pump body 14 in the cylinder bore 16 and is connected to the control chamber 50 via a channel 63 running through the pump body 14 and the valve body 26. A connection of the control chamber 50 to the pump working chamber 22 is thus controlled by the pump piston 18 depending on its stroke. The
Pumpenarbeitsraum 22 dient als Druckquelle für die Steuerung des Drucks im Steuerraum 50. Bei geringem Förderhub des Pumpenkolbens 18 in den Pumpenarbeitsraum 22 hinein befindet sich die Mündung des Kanals 60 an der Mantelfläche des Pumpenkolbens 18 in Überdeckung mit der Ringnut 62, so daß der Steuerraum 50 mit dem Pumpenarbeitsraum 22 verbunden ist. Bei zunehmendem Förderhub des Pumpenkolbens 18 in den Pumpenarbeitsraum 22 hinein ist die Mündung des Kanals 60 an der Mantelfläche des Pumpenkolbens 18 zu der Ringnut 62 versetzt, so daß der Steuerraum 50 vom Pumpenarbeitsraum 22 getrennt ist.Pump working chamber 22 serves as a pressure source for controlling the pressure in the control chamber 50. With a small delivery stroke of the pump piston 18 into the pump working chamber 22, the mouth of the channel 60 on the outer surface of the pump piston 18 is in register with the annular groove 62, so that the control chamber 50 is connected to the pump work space 22. As the delivery stroke of the pump piston 18 increases into the pump work chamber 22, the mouth of the channel 60 on the outer surface of the pump piston 18 is offset from the annular groove 62, so that the control chamber 50 is separated from the pump work chamber 22.
Zwischen der Nockenwelle der Brennkraftmaschine mit dem Nocken 20 und dem Pumpenkolben 18 ist eine Zwischenwelle 70 angeordnet, auf der ein Übertragungselement 71 in Form eines zweiarmigen Kipphebels angeordnet ist, der mit seinem einen Ende beispielsweise über eine Rolle 72 auf dem Nocken 20 abrollt und der mit seinem anderen Ende am Pumpenkolben 18 angelenkt ist. Es ist vorgesehen, daß die Lage der Zwischenwelle 70 mit dem Kipphebel 71 veränderbar ist, wodurch die Ausgangshubstellung des Pumpenkolbens 18 verändert werden kann. In Figur 1 ist die Zwischenwelle 70 mit dem Kipphebel 71 und der linken Hälfte des Pumpenkolbens 18 mit durchgezogenen Linien in einer ersten Lage dargestellt, in der der Pumpenkolben 18 eine Ausgangshubstellung aufweist, in der der Pumpenkolben 18 relativ weit in die Zylinderbohrung 16 im Pumpenkörper 14 eintaucht. In Figur 1 ist die Zwischenwelle 70 mit dem Kipphebel 71 und der rechten Hälfte des Pumpenkolbens 18 mit gestrichelten Linien in einer zweiten Lage dargestellt, in der der Pumpenkolben 18 in seiner Ausgangshubstellung gegenüber der ersten Lage weniger weit in die Zylinderbohrung 16 im Pumpenkörper 14 eintaucht.Between the camshaft of the internal combustion engine with the cam 20 and the pump piston 18, an intermediate shaft 70 is arranged, on which a transmission element 71 is arranged in the form of a two-armed rocker arm, which rolls with one end, for example, via a roller 72 on the cam 20, and which rolls its other end is hinged to the pump piston 18. It is provided that the position of the intermediate shaft 70 can be changed with the rocker arm 71, as a result of which the initial stroke position of the pump piston 18 can be changed. 1 shows the intermediate shaft 70 with the rocker arm 71 and the left half of the pump piston 18 with solid lines in a first position in which the pump piston 18 has an initial stroke position in which the pump piston 18 is relatively far into the cylinder bore 16 in the pump body 14 dips. In Figure 1, the intermediate shaft 70 with the Rocker arm 71 and the right half of the pump piston 18 are shown with dashed lines in a second position, in which the pump piston 18 in its initial stroke position dips less far into the cylinder bore 16 in the pump body 14 than the first position.
Eine Verstellung der Lage der Zwischenwelle 70 kann beispielsweise mittels einer hydraulischenThe position of the intermediate shaft 70 can be adjusted, for example, by means of a hydraulic one
VerStelleinrichtung 74 erfolgen, durch die die die Lagerung der Zwischenwelle 70 verschoben wird. Alternativ kann die Versteileinrichtung 74 auch als Exzenter ausgebildet sein, durch den die Lagerung der Zwischenwelle 70 verschoben wird.Adjustment device 74 take place, by which the mounting of the intermediate shaft 70 is shifted. Alternatively, the adjusting device 74 can also be designed as an eccentric through which the bearing of the intermediate shaft 70 is displaced.
Nachfolgend wird die Funktion der Kraftstoffeinspritzeinrichtung gemäß dem ersten Ausführungsbeispiel erläutert. Beim Saughub des Pumpenkolbens 18 ist das Steuerventil 23 geöffnet, so daß Kraftstoff aus dem Kraftstoffvorratsbehälter 24 in den Pumpenarbeitsraum 22 gelangt. Beim Förderhub des Pumpenkolbens 18 wird der Beginn der Kraftstoffeinspritzung dadurch festgelegt, daß das Steuerventil 23 schließt, so daß der Pumpenarbeitsraum 22 vom Entlastungsraum getrennt ist und sich im Pumpenarbeitsraum 22 Hochdruck aufbaut. Abhängig von Betriebsparametern der Brennkraftmaschine wird durch die Versteileinrichtung 74 die Zwischenwelle 70 in die erforderliche Lage eingestellt. Wenn der Pumpenkolben 18 seine in Figur 1 in seiner rechten Hälfte dargestellte Ausgangshubstellung aufweist, so ist der Steuerraum 50 mit dem Pumpenarbeitsraum 22 verbunden, so daß in diesem ein hoher Steuerdruck herrscht. Wenn der Druck im Pumpenarbeitsraum 22 und damit im Druckraum 40 des Kraftstoffeinspritzventils 12 so hoch ist, daß die durch diesen über die Druckschulter 42 auf das erste Einspritzventilglied 28 erzeugte Druckkraft größer ist als die Kraft der ersten Schließfeder 44, so öffnet das Kraftstoffeinspritzventil 12 indem das erste Einspritzventilglied 28 mit seiner Dichtfläche 34 vom Ventilsitz 36 abhebt und die wenigstens eine erste Einspritzöffnung 32 freigibt. Der Steuerdruck im Steuerraum 50 wirkt über den Federteller 147 auf das zweite Einspritzventilglied 128 und unterstützt die Schließfeder 144, so daß die durch den im Druckraum 40 herrschenden Druck über die Druckfläche 142 auf das zweite Einspritzventilglied 128 wirkende Druckkraft nicht ausreicht, um das zweite Einspritzventilglied 128 zu öffnen. AmThe function of the fuel injection device according to the first exemplary embodiment is explained below. During the suction stroke of the pump piston 18, the control valve 23 is opened, so that fuel reaches the pump working chamber 22 from the fuel reservoir 24. During the delivery stroke of the pump piston 18, the start of the fuel injection is determined by the control valve 23 closing, so that the pump work chamber 22 is separated from the relief chamber and high pressure builds up in the pump work chamber 22. Depending on the operating parameters of the internal combustion engine, the adjusting shaft 74 sets the intermediate shaft 70 into the required position. If the pump piston 18 has its initial stroke position shown in its right half in FIG. 1, the control chamber 50 is connected to the pump working chamber 22, so that there is a high control pressure in the latter. If the pressure in the pump work chamber 22 and thus in the pressure chamber 40 of the fuel injection valve 12 is so high that the pressure force generated by it via the pressure shoulder 42 on the first injection valve member 28 is greater than the force of the first closing spring 44, the fuel injection valve 12 opens by the first Injection valve member 28 lifts with its sealing surface 34 from the valve seat 36 and the at least one first injection opening 32 opens. The control pressure in the control chamber 50 acts on the second injection valve member 128 via the spring plate 147 and supports the closing spring 144, so that the pressure force acting on the second injection valve member 128 via the pressure surface 142 through the pressure surface 142 is not sufficient for the second injection valve member 128 to open. At the
Kraftstoffeinspritzventil 12 wird somit mit den ersten Einspritzöffnungen 32 nur ein Teil des gesamten Einspritzquerschnitts geöffnet, so daß entsprechend nur eine geringe Kraftstoffmenge eingespritzt wird.Fuel injection valve 12 is thus opened with the first injection openings 32 only a part of the entire injection cross section, so that correspondingly only a small amount of fuel is injected.
Wenn der Pumpenkolben 18 weiter seinen Förderhub ausführt, so gelangt der Kanal 60 im Pumpenkolben 18 aus der Überdeckung mit der Ringnut 62, so daß der Steuerraum 50 vom Pumpenarbeitsraum 22 getrennt ist. Der Steuerraum 50 ist vorzugsweise über wenigstens eine Drosselstelle mit einem Entlastungsraum verbunden, so daß sich der Druck im Steuerraum 50 abbaut. In diesem Fall wirkt auf das zweite Einspritzventilglied 128 nur noch die Kraft der zweiten Schließfeder 144 sowie gegebenenfalls eine geringe Druckkraft, so daß die durch den im Druckraum 40 herrschenden Druck über die Druckfläche 142 auf das zweite Einspritzventilglied 128 wirkende Druckkraft ausreicht, um auch das zweite Einspritzventilglied 128 zu öffnen, so daß auch die wenigstens eine zweite Einspritzöffnung 132 freigegeben wird. Somit ist am Kraftstoffeinspritzventil 12 der gesamte Einspritzquerschnitt freigegeben und es wird eine größere Kraftstoffmenge eingespritzt. Das Ende der Kraftstoffeinspritzung wird durch das Öffnen des Steuerventils 23 bestimmt, wodurch der Pumpenarbeitsraum 22 mit dem Entlastungsraum verbunden ist und sich in diesem kein Hochdruck mehr aufbauen kann . Der Pumpenkolben 18 kann einen weiteren Kanal 65 aufweisen, der bei maximalem Hub des Pumpenkolbens 18 in den Pumpenarbeitsraum 22 hinein mit der Ringnut 62 in Überdeckung kommt und eine Verbindung zu einem Entlastungsraum herstellt. Bei maximalem Hub des Pumpenkolbens 18 ist der Steuerraum 50 somit mit einem Entlastungsraum verbunden und druckentlastet.If the pump piston 18 continues its delivery stroke, the channel 60 in the pump piston 18 comes out of the overlap with the annular groove 62, so that the control chamber 50 is separated from the pump working chamber 22. The control chamber 50 is preferably connected to a relief chamber via at least one throttle point, so that the pressure in the control chamber 50 decreases. In this case, only the force of the second closing spring 144 and possibly a small pressure force acts on the second injection valve member 128, so that the pressure force acting on the second injection valve member 128 through the pressure surface 142 through the pressure surface 142 is sufficient to also cover the second To open injection valve member 128 so that the at least one second injection opening 132 is also released. Thus, the entire injection cross section is released at the fuel injection valve 12 and a larger amount of fuel is injected. The end of the fuel injection is determined by the opening of the control valve 23, as a result of which the pump work chamber 22 is connected to the relief chamber and no high pressure can build up in it. The pump piston 18 can have a further channel 65, which comes into overlap with the annular groove 62 when the pump piston 18 is at a maximum stroke into the pump working chamber 22 and establishes a connection to a relief chamber. With a maximum stroke of the pump piston 18, the control chamber 50 is thus connected to a relief chamber and pressure-relieved.
Es kann vorgesehen sein, daß die durch die ersten Einspritzöffnungen 32 und die zweiten Einspritzöffnungen 132 gebildeten Einspritzquerschnitte zumindest annähernd gleich groß sind, so daß bei der Öffnung nur des ersten Einspritzventilglieds 28 der halbe gesamteIt can be provided that the injection cross sections formed by the first injection openings 32 and the second injection openings 132 are at least approximately the same size, so that when only the first injection valve member 28 is opened, half of the total
Einspritzquerschnitt freigegeben wird. Alternativ kann auch vorgesehen sein, daß die ersten Einspritzöffnungen 32 einen größeren oder kleineren Einspritzquerschnitt bilden als die zweiten Einspritzöffnungen 132.Injection cross section is released. Alternatively, it can also be provided that the first injection openings 32 form a larger or smaller injection cross section than the second injection openings 132.
Wenn sich der Pumpenkolben 18 in seiner in Figur 1 in der linken Hälfte dargestellten Ausgangshubstellung befindet, so ist der Kanal 60 des Pumpenkolbens 18 nicht in Überdeckung mit der Ringnut 62, so daß der Steuerraum 50 vom Pumpenarbeitsraum 22 getrennt ist. In diesem Fall öffnen bei Erreichen des Öffnungsdrucks im Pumpenarbeitsraum 22 beide Einspritzventilglieder 28 und 128 zumindest annähernd gleichzeitig und es wird der gesamte Einspritzquerschnitt am Kraftstoffeinspritzventil 12 freigegeben.When the pump piston 18 is in its initial stroke position shown in FIG. 1 in the left half, the channel 60 of the pump piston 18 is not in register with the annular groove 62, so that the control chamber 50 is separated from the pump working chamber 22. In this case, when the opening pressure in the pump work chamber 22 is reached, both injection valve members 28 and 128 open at least approximately simultaneously and the entire injection cross section on the fuel injection valve 12 is released.
Die Änderung der Lage der Zwischenwelle 70 und damit der Ausgangshubstellung des Pumpenkolbens 18 durch die VerStelleinrichtung 74 erfolgt abhängig vonThe change in the position of the intermediate shaft 70 and thus the initial stroke position of the pump piston 18 by the adjusting device 74 is dependent on
Betriebsparametern der Brennkraftmaschine wie beispielsweise Drehzahl, Last, Temperatur sowie gegebenenfalls weiteren Betriebsparametern. Die Versteileinrichtung 74 wird dabei von einer elektrischen Steuereinrichtung 76 angesteuert, durch die auch das Steuerventil 23 angesteuert wird. Wenn unter Berücksichtigung dieser Betriebsparameter zu Beginn der Kraftstoffeinspritzung nur eine geringe Kraftstoffmenge eingespritzt werden soll, so wird durch die Steuereinrichtung 76 die VerStelleinrichtung 74 derart angesteuert, daß sich die Zwischenwelle 70 und somit der Pumpenkolben 18 in seine in Figur 1 in der rechten Hälfte dargestellte Ausgangshubstellung befindet und zu Beginn der Kraftstoffeinspritzung nur das erste Einspritzventilglied 2£ des Kraftstoffeinspritzventils 12 öffnet. Wenn unter Berücksichtigung dieser Betriebsparameter schon zu Beginn der Kraftstoffeinspritzung nur eine größere Kraftstoffmenge eingespritzt werden soll, so wird durch die Steuereinrichtung 76 die Versteileinrichtung 74 derart angesteuert, daß sich die Zwischenwelle 70 und somit der Pumpenkolben 18 in seine in Figur 1 in der linken Hälfte dargestellte Ausgangshubstellung befindet und bereits zu Beginn der Kraftstoffeinspritzung beide Einspritzventilglieder 28 und 128 des Kraftstoffeinspritzventils 12 öffnen. Wenn die Brennkraftmaschine mehrere Zylinder aufweist, so ist für jeden Zylinder eine Kraftstoffhochdruckpumpe 10 vorgesehen, wobei für deren Antrieb jedoch nur eine Nockenwelle 20 und eine Zwischenwelle 70 vorgesehen ist. Für die Änderung der Lage der Zwischenwelle 70 und der Aufgangshubstellung der Pumpenkolben 18 sämtlicher Kraftstoffhochdruckpumpen 10 ist dabei nur eine VerStelleinrichtung 74 erforderlich.Operating parameters of the internal combustion engine such as speed, load, temperature and possibly other operating parameters. The adjusting device 74 is controlled by an electrical control device 76, which also controls the control valve 23. If taking into account these operating parameters at the beginning of the fuel injection, only a small amount of fuel is to be injected, the adjusting device 74 is controlled by the control device 76 in such a way that the intermediate shaft 70 and thus the pump piston 18 are in the starting stroke position shown in FIG. 1 in the right half and at the beginning of fuel injection, only the first injection valve member 2 £ of the fuel injection valve 12 opens. If, taking these operating parameters into account, only a larger quantity of fuel is to be injected at the start of fuel injection, the adjusting device 74 is controlled by the control device 76 such that the intermediate shaft 70 and thus the pump piston 18 are shown in the left half in FIG. 1 Starting stroke position is and both injection valve members 28 and 128 of the fuel injection valve 12 open at the beginning of the fuel injection. If the internal combustion engine has a plurality of cylinders, a high-pressure fuel pump 10 is provided for each cylinder, but only one camshaft 20 and one intermediate shaft 70 are provided for driving it. In order to change the position of the intermediate shaft 70 and the initial stroke position of the pump pistons 18 of all high-pressure fuel pumps 10, only one adjusting device 74 is required.
In Figur 3 ist die Kraftstoffeinspritzeinrichtung gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der grundsätzliche Aufbau gleich wie beim ersten Ausführungsbeispiel ist. Abweichend zum ersten Ausführungsbeispiel wird beim zweiten Ausführungsbeispiel jedoch nicht der Pumpenarbeitsraum 22 als Druckquelle für die Steuerung des Drucks im Steuerraum 50 verwendet sondern ein KraftstoffZulauf , durch den beim Saughub des Pumpenkolbens 18 Kraftstoff dem Pumpenarbeitsraum 22 zugeführt wird. Mit dem Kraftstoffzulauf ist ein im Pumpenkörper 14 ausgebildeter Kraftstoffkanal 80 verbunden, der am Mantel der Zylinderbohrung 16, in der der Pumpenkolben 18 geführt ist, mündet. In einem zur Mündung des Kraftstoffkanals 80 in Umfangsrichtung versetzten Bereich mündet am Mantel der Zylinderbohrung 16 der Kanal 63, der zum Steuerraum 50 führt. Im Pumpenkolben 18 ist ein Kanal 82 ausgebildet, der beispielsweise radial zur Längsachse des Pumpenkolbens 18 verläuft und der jeweils am Mantel des Pumpenkolbens 18 mündet. Durch den Pumpenkolben 18 wird abhängig von dessen Hubstellung durch dessen Kanal 82 die Verbindung des Kraftstoffkanals 80 mit dem Kanal 63 zum Steuerraum 50 gesteuert. In Figur 3 ist wiederum die Zwischenwelle 70 mit dem Pumpenkolben 18 in unterschiedlichen Stellungen dargestellt. In einer in Figur 3 in der rechten Hälfte des Pumpenkolbens 18 dargestellten Ausgangshubstellung befindet sich der Kanal 82 des Pumpenkolbens 18 in Überdeckung mit der Mündung des Kraftstoffkanals 80 und der Mündung des zum Steuerraum 50 führenden Kanals 63, so daß der Steuerraum 50 mit dem Kraftstoffkanal 80 verbunden ist. Im Steuerraum 50 wirkt somit der erhöhte Druck im Kraftstoffkanal 80, so daß beim Kraftstoffeinspritzventil 12 das zweite Einspritzventilglied 128 in seiner geschlossenen Stellung verbleibt und nur das erste Einspritzventilglied 28 öffnet. Bei der für die linke Hälfte des Pumpenkolbens 18 dargestellten Ausgangshubstellung befindet sich der Kanal 82 des Pumpenkolbens 18 nicht in Überdeckung mit der Mündung des Kraftstoffkanals 80 und der Mündung des zum Steuerraum 50 führenden Kanals 63 sondern ist zu diesen versetzt angeordnet, so daß der Steuerraum 50 vom Kraftstoffkanal 80 getrennt ist. Im Steuerraum 50 wirkt somit kein erhöhter Druck, so daß beim Kraftstoffeinspritzventil 12 beide Einspritzventilglieder 28 und 128 öffnen. FIG. 3 shows the fuel injection device according to a second exemplary embodiment, in which the basic structure is the same as in the first exemplary embodiment. In contrast to the first exemplary embodiment, the pump working chamber 22 is not used as the pressure source for controlling the pressure in the control chamber 50 in the second exemplary embodiment, but rather a fuel inlet, through which fuel flows into the pump working chamber 22 during the suction stroke of the pump piston 18 is fed. A fuel channel 80 formed in the pump body 14 is connected to the fuel inlet and opens at the jacket of the cylinder bore 16 in which the pump piston 18 is guided. In a region offset in the circumferential direction for the opening of the fuel channel 80, the channel 63, which leads to the control chamber 50, opens at the jacket of the cylinder bore 16. A channel 82 is formed in the pump piston 18, which extends, for example, radially to the longitudinal axis of the pump piston 18 and which opens into the jacket of the pump piston 18. The connection of the fuel channel 80 with the channel 63 to the control chamber 50 is controlled by the pump piston 18 depending on its stroke position through its channel 82. In Figure 3, the intermediate shaft 70 is again shown with the pump piston 18 in different positions. In an initial stroke position shown in FIG. 3 in the right half of the pump piston 18, the channel 82 of the pump piston 18 is in register with the mouth of the fuel channel 80 and the mouth of the channel 63 leading to the control chamber 50, so that the control chamber 50 with the fuel channel 80 connected is. The increased pressure in the fuel channel 80 thus acts in the control chamber 50, so that in the fuel injection valve 12 the second injection valve member 128 remains in its closed position and only the first injection valve member 28 opens. In the initial stroke position shown for the left half of the pump piston 18, the channel 82 of the pump piston 18 is not in overlap with the opening of the fuel channel 80 and the opening of the channel 63 leading to the control chamber 50, but is arranged offset to these, so that the control chamber 50 is separated from the fuel channel 80. No increased pressure thus acts in the control chamber 50, so that both injection valve members 28 and 128 open in the fuel injection valve 12.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzeinrichtung für eine1. Fuel injector for one
Brennkraftmaschine mit einer Kraftstoffhochdruckpumpe (10) und einem mit dieser verbundenen Kraftstoffeinspritzventil (12) für jeden Zylinder der Brennkraftmaschine, wobei die Kraftstoffhochdruckpumpe (10) einen durch die Brennkraftmaschine in einer Hubbewegung angetriebenen Pumpenkolben (18) aufweist, der einen Pumpenarbeitsraum (22) begrenzt, der mit einem Druckraum (40) des Kraftstoffeinspritzventils (12) verbunden ist, wobei das Kraftstoffeinspritzventil (12) wenigstens ein erstes Einspritzventilglied (28) aufweist, durch das wenigstens eine erste Einspritzöffnung (32) gesteuert wird und das durch den im Druckraum (40) herrschenden Druck gegen eine Schließkraft in einer Öffnungsrichtung (29) bewegbar ist, und mit einem ersten elektrisch gesteuerten Steuerventil (23), durch das eine Verbindung des Pumpenarbeitsraums (22) mit einem Entlastungsraum gesteuert wird, dadurch gekennzeichnet, daß das Kraftstoffeinspritzventil (12) ein zweites, innerhalb des hohl ausgebildeten ersten Einspritzventilglieds (28) verschiebbar geführtes zweites Einspritzventilglied (128) aufweist, durch das wenigstens eine zweite Einspritzöffnung (132) gesteuert wird und das durch den im Druckraum (40) herrschenden Druck gegen eine Schließkraft in einer Öffnungsrichtung (29) bewegbar ist und daß das zweite Einspritzventilglied (128) zumindest mittelbar von dem in einem kraftstoffgefüllten Steuerraum (50) herrschenden Druck beaufschlagt ist, der abhängig von Betriebsparametern der Brennkraftmaschine derart steuerbar ist, daß das zweite Einspritzventilglied (128) durch den im Steuerraum (50) herrschenden Druck unabhängig von einer Öffnungsbewegung des ersten Einspritzventilglieds (28) in einer die wenigstens eine zweite Einspritzöffnung (132) verschließenden Stellung blockierbar ist.Internal combustion engine with a high-pressure fuel pump (10) and a fuel injection valve (12) connected thereto for each cylinder of the internal combustion engine, the high-pressure fuel pump (10) having a pump piston (18) driven by the internal combustion engine in a stroke movement, which delimits a pump working space (22), which is connected to a pressure chamber (40) of the fuel injection valve (12), the fuel injection valve (12) having at least one first injection valve member (28) through which at least one first injection opening (32) is controlled and which through the in the pressure chamber (40) prevailing pressure against a closing force can be moved in an opening direction (29), and with a first electrically controlled control valve (23), by means of which a connection between the pump work chamber (22) and a relief chamber is controlled, characterized in that the fuel injection valve (12) is on second, inside the hollow first E Injection valve member (28) slidably guided second injection valve member (128) through which at least one second injection opening (132) is controlled and which can be moved in an opening direction (29) by the pressure prevailing in the pressure chamber (40) against a closing force and that the second Injection valve member (128) is acted upon at least indirectly by the pressure prevailing in a fuel-filled control chamber (50), which pressure can be controlled as a function of operating parameters of the internal combustion engine in such a way that the second injection valve member (128) is actuated by the Control chamber (50) prevailing pressure can be blocked regardless of an opening movement of the first injection valve member (28) in a position closing the at least one second injection opening (132).
2. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Steuerraum (50) zur Steuerung des in diesem herrschenden Drucks mit einer Druckquelle (22,-80) verbindbar ist.2. Fuel injection device according to claim 1, characterized in that the control chamber (50) for controlling the pressure prevailing in this can be connected to a pressure source (22, -80).
3. Kraftstoffeinspritzeinrichtung nach Anspruch 2, dadurch gekennzeichnet, daß durch den Pumpenkolben (18) der Kraftstoffhochdruckpumpe (10) abhängig von dessen Hub eine Verbindung des Steuerraums (50) mit der Druckquelle (22; 80) gesteuert wird.3. Fuel injection device according to claim 2, characterized in that a connection of the control chamber (50) with the pressure source (22; 80) is controlled by the pump piston (18) of the high-pressure fuel pump (10) depending on its stroke.
4. Kraftstoffeinspritzeinrichtung nach Anspruch 3, dadurch gekennzeichnet, daß durch den Pumpenkolben (18) bei geringem Hub die Verbindung des Steuerraums (50) mit der Druckquelle (22; 80) geöffnet ist und bei größerem Hub getrennt ist.4. Fuel injection device according to claim 3, characterized in that the connection of the control chamber (50) to the pressure source (22; 80) is opened by the pump piston (18) with a small stroke and is separated with a larger stroke.
5. Kraftstoffeinspritzeinrichtung nach Anspruch 3 oder 4, dadurch gekennzeichnet, daß im Antrieb zwischen der Brennkraftmaschine und dem Pumpenkolben (18) der5. Fuel injection device according to claim 3 or 4, characterized in that the drive between the internal combustion engine and the pump piston (18)
Kraftstoffhochdruckpumpe (10) eine Versteileinrichtung (74) vorgesehen ist, durch die eine Ausgangshubstellung des Pumpenkolbens (18) änderbar ist, ausgehend von der der Pumpenkolben (18) seine Hubbewegung ausführt.A high-pressure fuel pump (10) is provided with an adjusting device (74) by means of which an initial stroke position of the pump piston (18) can be changed, starting from which the pump piston (18) executes its lifting movement.
6. Kraftstoffeinspritzeinrichtung nach Anspruch 5, dadurch gekennzeichnet, daß der Antrieb eine Nockenwelle (20) der Brennkraftmaschine und eine Zwischenwelle (70) mit einem durch die Nockenwelle (20) betätigten und auf den Pumpenkolben (18) wirkenden Übertragungselement (71) aufweist und daß zur Änderung der Ausgangshubstellung des Pumpenkolbens (18) die Lage der Zwischenwelle (70) durch die Versteileinrichtung (74) änderbar ist.6. Fuel injection device according to claim 5, characterized in that the drive has a camshaft (20) of the internal combustion engine and an intermediate shaft (70) with an actuated by the camshaft (20) and acting on the pump piston (18) transmission element (71) and that to change the initial stroke position of the Pump piston (18) the position of the intermediate shaft (70) can be changed by the adjusting device (74).
7. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, daß die Druckquelle der Pumpenarbeitsraum (22) der Kraftstoffhochdruckpumpe (10) ist .7. Fuel injection device according to one of claims 2 to 6, characterized in that the pressure source of the pump working chamber (22) of the high-pressure fuel pump (10).
8. Kraftstoffeinspritzeinrichtung nach Anspruch 7, dadurch gekennzeichnet, daß im Pumpenkolben (18) ein einerseits in den Pumpenarbeitsraum (22) und andererseits am Umfang des Pumpenkolbens (18) mündender Kanal (60) ausgebildet ist und daß der Pumpenkolben (18) in einer Zylinderbohrung (16) geführt ist, in der eine den Pumpenkolben (18) umgebende Ringnut (62) ausgebildet ist, die über einen Kanal (63) mit dem Steuerraum (50) verbunden ist.8. Fuel injection device according to claim 7, characterized in that in the pump piston (18) on the one hand in the pump working chamber (22) and on the other hand on the circumference of the pump piston (18) opening channel (60) is formed and that the pump piston (18) in a cylinder bore (16) is guided, in which an annular groove (62) is formed which surrounds the pump piston (18) and which is connected to the control chamber (50) via a channel (63).
9. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, daß die Druckquelle ein9. Fuel injection device according to one of claims 2 to 6, characterized in that the pressure source
Kraftstoffzulauf (80) ist, über den beim Saughub des Pumpenkolbens (18) Kraftstoff in den Pumpenarbeitsraum (22) zugeführt wird. There is a fuel inlet (80) via which fuel is fed into the pump work chamber (22) during the suction stroke of the pump piston (18).
EP02758168A 2001-08-25 2002-08-23 Fuel injection device for an internal combustion engine Expired - Lifetime EP1423599B1 (en)

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DE10141679A DE10141679A1 (en) 2001-08-25 2001-08-25 Fuel injection device for an internal combustion engine
PCT/DE2002/003140 WO2003018991A1 (en) 2001-08-25 2002-08-23 Fuel injection device for an internal combustion engine

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DE50212607D1 (en) 2008-09-18
RU2003113559A (en) 2005-01-20
EP1423599B1 (en) 2008-08-06
KR20040028663A (en) 2004-04-03
US6901915B2 (en) 2005-06-07
DE10141679A1 (en) 2003-03-06
BR0205941A (en) 2003-08-05
US20040232256A1 (en) 2004-11-25
PL360296A1 (en) 2004-09-06
WO2003018991A1 (en) 2003-03-06
JP2005500468A (en) 2005-01-06
CN1466655A (en) 2004-01-07

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