EP1318293A2 - Système d'injection de carburant pour moteur a combustion interne - Google Patents

Système d'injection de carburant pour moteur a combustion interne Download PDF

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Publication number
EP1318293A2
EP1318293A2 EP02023348A EP02023348A EP1318293A2 EP 1318293 A2 EP1318293 A2 EP 1318293A2 EP 02023348 A EP02023348 A EP 02023348A EP 02023348 A EP02023348 A EP 02023348A EP 1318293 A2 EP1318293 A2 EP 1318293A2
Authority
EP
European Patent Office
Prior art keywords
pump
control
fuel
fuel injection
pump piston
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
EP02023348A
Other languages
German (de)
English (en)
Other versions
EP1318293B1 (fr
EP1318293A3 (fr
Inventor
Friedrich Boecking
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 EP1318293A2 publication Critical patent/EP1318293A2/fr
Publication of EP1318293A3 publication Critical patent/EP1318293A3/fr
Application granted granted Critical
Publication of EP1318293B1 publication Critical patent/EP1318293B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • 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
    • F02M45/06—Pumps 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
    • 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
    • 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

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 injector is due to the EP 0 987 431 A2 is known.
  • This Fuel injector has one High-pressure fuel pump and a connected to it Fuel injector for each cylinder of the Internal combustion engine on.
  • the high-pressure fuel pump has one by the internal combustion engine in one stroke driven pump piston on which a pump work space limited.
  • the fuel injector has one with the Pump work room connected pressure room and a Injection valve member through which at least one Injection opening is controlled and that of that in the pressure chamber prevailing pressure against a closing force in Opening direction to release the at least one Injection opening is movable. It's a first electric actuated control valve provided by one Connection of the pump work room with a relief room is controlled.
  • a control piston turns one Control pressure space limited, the control piston from the in Control pressure chamber is pressurized into Closing direction acts on the injection valve member.
  • the Control pressure chamber has one through a second electrical actuated control valve controlled connection with a Relief space on. It is also a second electric actuated control valve provided by one Connection of a control pressure room with a relief room is controlled. It becomes a fuel injection first control valve closed and the second control valve opened so that there is no high pressure in the control pressure chamber can build up and can open the fuel injector. When the second control valve is open, however, flows out of the Pump working space from the control pressure chamber fuel, so that the available for injection Amount of fuel delivered by the pump piston Fuel quantity is reduced and also that for the Injection available pressure is reduced.
  • the fuel injection device with the Features according to claim 1 has the advantage that due to the connection of the control pressure chamber with the through the second pump piston limited working space at Second control valve and fuel injection open thus opened fuel injector no fuel flows out of the pump work space and thus the entire fuel delivered by the first pump piston and the generated by the first pump piston in the pump work space Undiminished pressure for fuel injection Available.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a longitudinal section in a simplified representation with Pump piston in a first stroke position, Figure 2 a Section II of the fuel injector with Pump piston in a second stroke position and Figure 3 den Pressure curve at an injection port Fuel injector the Fuel injector during one Injection cycle.
  • FIG. 1 and 2 is one Fuel injection device for an internal combustion engine shown a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the Fuel injector is preferably as so-called pump-nozzle unit designed and has for each cylinder of the internal combustion engine one High-pressure fuel pump 10 and a connected thereto Fuel injector 12 on which is a common Form unit.
  • the Fuel injection device also as a so-called pump-line-nozzle system be trained in which the High pressure fuel pump and the fuel injection valve each cylinder arranged separately and over a line are connected.
  • the High-pressure fuel pump 10 has a pump body 14 a cylinder bore 16 in which a first pump piston 18 is tightly guided, at least indirectly by one Cam 20 counter to a camshaft of the internal combustion engine the force of a return spring 19 in one stroke is driven.
  • the first pump piston 18 delimits in the Cylinder bore 16 a pump working space 22, in which Delivery stroke of the pump piston 18 fuel under high pressure is compressed.
  • the pump work space 22 becomes fuel from a fuel tank 24 of the motor vehicle fed.
  • the fuel injection valve 12 has one with the Pump body 14 connected valve body 26, the can be formed in several parts, and in the one Injection valve member 28 in a bore 30 is guided longitudinally.
  • the valve body 26 instructs its the combustion chamber of the cylinder of the internal combustion engine facing end region 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 region trained valve seat 36 cooperates from after or after which the injection openings 32 discharge.
  • valve body 26 in the Valve body 26 is between the injection valve member 28 and an annular space 38 toward the bore 30 toward the valve seat 36 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 by reducing a cross section Pressure shoulder 42 on.
  • Injector member 28 engages a biased one Closing spring 44 through which the injection valve member 28 is pressed towards the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 of the valve body 26, the connects to the bore 30.
  • the closing spring 44 is supported at least indirectly, for example via a spring plate, on the control piston 50.
  • the closing spring 44 is stationary in the spring chamber 46 supports and that the control piston 50 at least indirectly on Injection valve member 28 supports, for example via a piston rod projecting into the spring chamber 46.
  • the bore 48 has a section 49 facing away from the spring chamber 46 smaller diameter, with the control piston 50 through the force of the closing spring 44 against one at the transition of Bore 48 to its section 49 formed annular shoulder 51st is pressed when a low pressure in the control pressure chamber 52 prevails.
  • the control pressure chamber 52 assigns a connection 54 a low pressure range than that, for example, the Fuel reservoir 24 is used.
  • connection 54 is a check valve 56 opening towards the control pressure chamber 52 arranged.
  • the high-pressure fuel pump 10 has a second one Pump piston 60, which is designed as a hollow cylinder and through which the first pump piston 18 passes.
  • the second pump piston 60 is in a pump working chamber 22 facing away, in diameter compared to the area of Cylinder bore 16 in which the first pump piston 18 is tight is enlarged section 116 of the cylinder bore 16 tightly guided in its outer jacket.
  • the first Pump piston 18 passes through the second with little play Pump piston 60 and is relative to the second Pump piston 60 slidable.
  • To section 116 of the Cylinder bore 16 closes pump working space 22 turned away a section reduced in diameter again 216 of the cylinder bore 16.
  • the first pump piston 18 is stepped in diameter formed and has one through the second pump piston 60 passing through and sealed in the cylinder bore 16 led area 118 with a smaller diameter and an area 218 arranged towards the cam 20 larger diameter.
  • At the transition between areas 118 and 218 on the first pump piston 18 is one of the second Pump piston 60 facing annular shoulder 68 is formed.
  • the one Cam portion 20 facing end portion 316 of the cylinder bore 16 is corresponding to the diameter of area 218 of the first Pump piston 18 in diameter opposite section 216 the cylinder bore 16 enlarged so that the first Pump piston 18 with its area 218 in the end section 316 the cylinder bore 16 is guided.
  • the one between the first Pump piston 18 with its annular shoulder 68 and the second Pump piston 60 in section 216 of cylinder bore 16 limited space 70 has a connection 71 with one Low pressure range than, for example, at least indirectly the fuel tank 24 can serve.
  • the first pump piston 18 is in one by the cam 20 Stroke movement driven, the pump piston 18 starting from an outer dead center position at which this is furthest protrudes from the cylinder bore 16 against the force of Return spring 19 to an inner dead center position at which this immerses the most in the cylinder bore 16, is moved.
  • the outer dead center position of the first Pump piston 18 according to Figure 1 is this with his Ring shoulder 68 at a distance a from the second pump piston 60 arranged so that a starting stroke a starting from the outer dead center position only the first pump piston 18 moves becomes.
  • the second pump piston 60 remains caused by the Return spring 64 in contact with the ring shoulder 65 in Section 116 of the cylinder bore 16.
  • connection 76 leads from channel 74 to one Relief area than the at least indirectly the Fuel reservoir 24 or another Low pressure area can serve. Connection 76 is through controls a first electrically operated control valve 78.
  • the control valve 78 can, as shown in FIG. 1, be a 2/2-way valve be trained.
  • the control pressure chamber 52 has a connection 80 to a relief space than that again the fuel tank 24 or another Low pressure area can serve by a second electrically operated control valve 82 is controlled, the can be designed as a 2/2-way valve.
  • connection 67 of the control pressure chamber 52 with the work chamber 66 preferably a throttle point 69 and in connection 80 of the control pressure chamber 52 with the relief chamber 24 preferably a throttle point 81 is provided.
  • a throttle point 81 Through the Throttling points 69.81 can be the inflow of fuel into the Control pressure chamber 52 or the outflow of fuel from the Control pressure chamber 52 can be set.
  • the control valves 78, 82 can be electromagnetic Have actuator or a piezo actuator and are replaced by a controlled electronic control device 84.
  • the Control valves 78, 82 can each have their own actuator have or a common actuator 86, which has a Bridge 87 both control valves 78, 82 each against the force operated a return spring.
  • At a first stroke of the Actuator 86 is only the first control valve 78 of one open to a closed position.
  • Another stroke of the actuator 86 is the second Control valve 82 from a closed to an open Position switched while the first control valve 78 in remains in its closed position.
  • Between the bridge 87 and the first control valve 78 can be a spring be arranged, the further stroke of the actuator 86 is suppressed.
  • the first control valve 78 is preferred pressure-balanced.
  • the first injection phase corresponds to an I in FIG. 3 designated pilot injection of a small amount of fuel.
  • the one in Figure 3 corresponds to the injection phase designated II, that is second control valve 82 by the control device 84 opened by the actuator 86 causing a further stroke.
  • the first control valve 78 remains closed, so that 22 high pressure prevails in the pump workspace.
  • second control valve 82 is the control pressure chamber 52 relieved, so that the control piston 50 back in its outer stroke position in contact with the ring shoulder 51 moves and the bias of the closing spring 44 is reduced. This then opens due to the pressure prevailing in the pressure chamber 40 Injection valve member 28 and there is one Fuel injection. From the second pump piston 60 from the Working space 66 displaced fuel flows over the opened second control valve 82 into the relief chamber 24 from.
  • the second one Control valve 82 through the controller 84 in its closed switching position by the actuator 86 executes a smaller stroke.
  • the control pressure chamber 52 is then separated from the relief space 24 and builds up in this High pressure as in work room 66, through which the Control piston 50 shifted and the bias of Closing spring 44 is increased so that Fuel injector closes.
  • the one in Figure 3 with III corresponds to the injection phase, the second Control valve 82 by the control device 84 again opened so that due to the relief of the control pressure chamber 52 the fuel injection valve 12 opens.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP02023348A 2001-12-07 2002-10-18 Système d'injection de carburant pour moteur à combustion interne Expired - Lifetime EP1318293B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10160258 2001-12-07
DE10160258A DE10160258A1 (de) 2001-12-07 2001-12-07 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP1318293A2 true EP1318293A2 (fr) 2003-06-11
EP1318293A3 EP1318293A3 (fr) 2006-03-22
EP1318293B1 EP1318293B1 (fr) 2007-08-29

Family

ID=7708447

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02023348A Expired - Lifetime EP1318293B1 (fr) 2001-12-07 2002-10-18 Système d'injection de carburant pour moteur à combustion interne

Country Status (3)

Country Link
US (1) US6688541B2 (fr)
EP (1) EP1318293B1 (fr)
DE (2) DE10160258A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102369349A (zh) * 2009-04-02 2012-03-07 瓦锡兰芬兰有限公司 一种活塞式发动机的燃料喷射装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10233101A1 (de) * 2002-07-20 2004-01-29 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
US20070007363A1 (en) * 2005-07-04 2007-01-11 Hitachi, Ltd. Fuel injection valve
DE102006026644A1 (de) * 2006-06-08 2007-12-13 Robert Bosch Gmbh Piezoelektrischer Aktor
FI124743B (fi) * 2012-10-18 2015-01-15 Wärtsilä Finland Oy Polttoaineen ruiskutusjärjestely

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0987431A2 (fr) 1998-09-18 2000-03-22 Lucas Industries Limited Injecteur de carburant

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4004610A1 (de) * 1989-04-21 1990-10-25 Bosch Gmbh Robert Kraftstoffeinspritzanlage, insbesondere pumpeduese, fuer brennkraftmaschinen
GB9614822D0 (en) * 1996-07-13 1996-09-04 Lucas Ind Plc Injector
DE29712502U1 (de) * 1997-07-15 1997-09-18 Fev Motorentech Gmbh & Co Kg Elektromagnetischer Aktuator mit Gehäuse
GB9812901D0 (en) * 1998-06-15 1998-08-12 Lucas Ind Plc Fuel injector
DE19940294A1 (de) * 1999-08-25 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE10042309B4 (de) * 2000-08-29 2005-04-21 Robert Bosch Gmbh Zumessventil
DE10055269B4 (de) * 2000-11-08 2005-10-27 Robert Bosch Gmbh Druckgesteuerter Injektor mit Druckübersetzung
DE10154802A1 (de) * 2001-11-08 2003-05-22 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10155406A1 (de) * 2001-11-10 2003-05-22 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0987431A2 (fr) 1998-09-18 2000-03-22 Lucas Industries Limited Injecteur de carburant

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102369349A (zh) * 2009-04-02 2012-03-07 瓦锡兰芬兰有限公司 一种活塞式发动机的燃料喷射装置
CN102369349B (zh) * 2009-04-02 2013-12-25 瓦锡兰芬兰有限公司 一种活塞式发动机的燃料喷射装置

Also Published As

Publication number Publication date
DE10160258A1 (de) 2003-06-18
US6688541B2 (en) 2004-02-10
EP1318293B1 (fr) 2007-08-29
EP1318293A3 (fr) 2006-03-22
DE50210802D1 (de) 2007-10-11
US20030106948A1 (en) 2003-06-12

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