EP1483498B1 - Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine - Google Patents

Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Download PDF

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Publication number
EP1483498B1
EP1483498B1 EP02792633A EP02792633A EP1483498B1 EP 1483498 B1 EP1483498 B1 EP 1483498B1 EP 02792633 A EP02792633 A EP 02792633A EP 02792633 A EP02792633 A EP 02792633A EP 1483498 B1 EP1483498 B1 EP 1483498B1
Authority
EP
European Patent Office
Prior art keywords
control
pressure
space
pressure space
control 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.)
Expired - Lifetime
Application number
EP02792633A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1483498A1 (de
Inventor
Peter Boehland
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1483498A1 publication Critical patent/EP1483498A1/de
Application granted granted Critical
Publication of EP1483498B1 publication Critical patent/EP1483498B1/de
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
    • 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
    • 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
    • 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
    • F02M47/027—Electrically actuated valves draining the chamber to release the 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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure

Definitions

  • the invention is based on a Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is characterized by the EP 0 987 431 A2.
  • These Fuel injection device has a High-pressure fuel pump and a connected to this Fuel injector for each cylinder of Internal combustion engine.
  • the high-pressure fuel pump points one by the internal combustion engine in a reciprocating motion powered pump piston having a pump working space limited.
  • the fuel injection valve has one with the Pump work space associated pressure room and one Injection valve member, through which at least one Injection opening is controlled and by the in the Pressure chamber prevailing pressure against a closing force in Opening direction for releasing the at least one Injection opening is movable. It is a first electric actuated control valve provided by the one Connection of pump work space with a discharge chamber is controlled.
  • control pressure chamber is replaced by a Control piston limited, the control piston of the im Control pressure chamber prevailing pressure applied in one Closing direction acts on the injection valve member and is movable together with the injection valve member.
  • the Control pressure chamber has a connection with the Pump workroom on.
  • To a fuel injection is the first control valve closed and the second Control valve open, so that in the control pressure chamber no High pressure can build up and the fuel injector can open.
  • With opened second control valve flows however, from the pump working space via the control pressure chamber Fuel off, so that available for injection standing amount of fuel through the pump piston subsidized fuel quantity is reduced and also the reduced pressure available for injection becomes. It follows that the efficiency of Fuel injector is not optimal.
  • the fuel injection device with the Features according to claim 1 has the advantage that in its open position Injection valve member a smaller area of the control piston acted upon by the pressure prevailing in the control pressure chamber is and thus a lower force in the closing direction the injection valve member acts as in his in his closed injection valve member, so that the second control valve during the Fuel injection can be closed and no Fuel quantity and fuel pressure loss during the Injection occurs and thus the efficiency of Fuel injection device is improved.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation
  • Figure 2 a in Figure 1 with II designated section of the Fuel injection device in an enlarged view when in a closed position Injection valve member
  • Figure 3 the cutout II at in an open position injection valve member
  • Figure 4 shows the detail II of the fuel injection device according to a modified embodiment in a Injection valve member located in the closed position
  • Figure 5 shows the detail II according to the modified embodiment the Krafftscherinspritz worn in a open position befindlichem injection valve member
  • FIG. 6 shows a profile of a pressure at injection openings a fuel injection valve of Fuel injector.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the Fuel injection device is preferably as So-called pump-nozzle unit is designed and has for each cylinder of the internal combustion engine one each High-pressure fuel pump 10 and connected to this Fuel injection valve 12, which has a common Form building unit.
  • the Fuel injection device as a so-called pump-line-nozzle system be trained in which the High-pressure fuel pump and the fuel injection valve each cylinder is arranged separately from each other and over a line are connected together.
  • the High-pressure fuel pump 10 has a pump body 14 with a cylinder bore 16 in which a pump piston 18th is tightly guided, at least indirectly by a Cam 20 of a camshaft of the internal combustion engine opposite the force of a return spring 19 in a lifting movement is driven.
  • the pump piston 18 limited in the Cylinder bore 16 a pump working chamber 22, in the at Delivery stroke of the pump piston 18 Fuel under high pressure is compressed.
  • the pump working chamber 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 may be formed in several parts, and in the one Injection valve member 28 in a bore 30th is guided longitudinally displaceable.
  • the valve body 26 indicates its the combustion chamber of the cylinder of the internal combustion engine facing end region at least one, preferably a plurality Injection openings 32.
  • the injection valve member 28 has at its the combustion chamber end facing a For example, about conical sealing surface 34, which with one in the valve body 26 in the combustion chamber facing End region formed valve seat 36 cooperates, from or after which the injection openings 32 dissipate.
  • valve body 26 is between the injection valve member 28 and the bore 30 to the valve seat 36 toward an annular space 38th present, in its the valve seat 36 facing away End region by a radial extension of the bore 30 in a pressure chamber 40 surrounding the injection valve member 28 passes.
  • the injection valve member 28 has the height of the Pressure chamber 40 by a cross-sectional reduction a Pressure shoulder 42 on.
  • a biased Closing spring 44 At the end of the combustion chamber facing away from the Injector member 28 engages a biased Closing spring 44, through which the injection valve member 28th is pressed toward the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 of the valve body 26, the adjoins the bore 30.
  • a control piston 50 is tightly guided, with the injection valve member 28 is connected.
  • the control piston 50 is over a diameter smaller than this piston rod 51 connected to the injection valve member 28.
  • the Control piston 50 may be integral with the injection valve member 28 is formed, however, for reasons of assembly preferably as a separate part with the injection valve member 28 connected.
  • a channel 60 to the pressure chamber 40 of the Fuel injection valve 12.
  • a channel 62 leads to the control pressure chamber 52.
  • the control pressure chamber 52 also opens a channel 64, the makes a connection to a relief room when the at least indirectly, the fuel tank 24 or another area may serve in which a low pressure prevails.
  • From the pump chamber 22 or channel 60 leads a connection 66 to a discharge space 24 from, through a first electrically operated control valve 68 controlled becomes.
  • the control valve 68 may be as shown in FIG be designed as a 2/2-way valve.
  • the connection 64 of Control pressure chamber 52 with the discharge chamber 24 is through controlling a second electrically operated control valve 70, which can be designed as a 2/2-way valve.
  • a throttle point 63 In the Connection 62 of the control pressure chamber 52 with the Pump workspace 22 may be provided a throttle point 63 be and in the connection of the control pressure chamber 52 with the Relief space 24, a throttle body 71 may be provided be.
  • the control valves 68,70 can a having electromagnetic actuator or a piezoelectric actuator and are by an electronic control device 72nd driven.
  • the pressure prevailing in the control pressure chamber 52 pressure acted upon end face of the control piston 50 is such measured that with closed second control valve 70, when the control pressure chamber 52 from the relief space 24th is separated and the delivery stroke of the pump piston 18 in the Pump working chamber 22 and thus also in the control pressure chamber 52nd High pressure builds up, in addition to the force of the closing spring 44 in the closing direction of the injection valve member 28th acting force that is greater than that on the Injection valve member 28 acting force in the opening direction 29 is when the injection valve member 28 is in his closed position or as above explained only with a partial lift open and with his Sealing surface 34 is lifted from the valve seat 36. In this Case remains the fuel injection valve 12th closed.
  • FIG. 2 and 3 is a section II of Fuel injection device shown enlarged, wherein the injection valve member 28 and the control piston 50 in FIG 2 in its closed position naval injection valve member are shown and in Figure 3 at in its open position with maximum lift injection valve member 28 are shown.
  • the Channel 62 as a connection to the pump working chamber 22
  • the Channel 64 as a connection to the discharge chamber 24 open into the Control pressure chamber 52 in the direction of the longitudinal axis 49th each considered near the edge of the control pressure space 52, for example, opposite each other.
  • Control piston 50 in the direction of the longitudinal axis 49th frontally opposite boundary 53 of the Control pressure space 52 is at least approximately coaxial with Control piston 50 a recess 54 formed, one of which Connection 55 leads to a discharge space 24, in the a throttle point 56 is arranged.
  • the recess 54 is in cross-section preferably circular and on whose edge is at the transition to the boundary 53 a seat 57th educated.
  • a projection 58 protruding in the direction of the longitudinal axis 49 of the control piston 50 tapers toward the restriction 53 and For example, at least approximately conical is.
  • a sealing surface 59 is formed with the seat 57 cooperates.
  • the second control valve 70 must be opened to to relieve the control pressure chamber 52, since the entire End face of the control piston 50 is pressurized. If the fuel injection valve 12, starting from a with Maximum stroke open position of the injection valve member 28 is to be closed, it must be closed when the second Control valve 70, the first control valve 68 are opened, so that the prevailing in the pressure chamber 40 and a in Opening direction 29 acting on the injection valve member 28 Pressure is less than the sum of the force of the closing spring 44 and by the ruling in the control pressure chamber 52 Pressure generated force in the closing direction.
  • FIGS. 4 and 5 the detail II of FIG Fuel injection device according to a modified Execution shown.
  • the control pressure chamber 152 points a reduced in diameter extension 154, in the the channel 62 as a connection to the pump working chamber 22 and the Channel 64 open as a connection to the discharge chamber 24.
  • Extension 154 is at least approximately coaxial with Control piston 150 arranged.
  • annular boundary 153 of the control pressure chamber 152 educated.
  • the boundary 153 is transverse, preferably at least approximately perpendicular to the longitudinal axis 49 of the Spool 150, is flat and forms one Flat seat 157.
  • control piston 150 On the control piston 150 is of the End face to the boundary 153 toward an annular approach 158 from, on the front side of an annular sealing surface 159 is formed.
  • the outside the sealing surface 159 lying part of the control pressure chamber 152nd is then separated from the extension 154, so that the part 152 of Control pressure chamber no connection with the pump work space 22 more.
  • the part 152 of the control pressure space is relieved of pressure and with a discharge space 24 connected, for example, one between the Control piston 150 and the bore 48 existing gap 155, which forms a throttle point, or via a separate Connection in which a throttle point is provided. From the pressure prevailing in the extension 154 of the control pressure chamber pressure is only the inside of the annular sealing surface 159th lying part of the end face of the control piston 150th applied.
  • control piston 50 with the approach 58 with the conical sealing surface 59 according to FIGS. 2 and 3 can also in the embodiment according to Figures 4 and 5 instead of the annular projection 158 provided there be used.
  • training of the Control piston 150 with the annular projection 158 and the annular sealing surface 159 according to Figures 4 and 5 also in the embodiment according to Figures 2 and 3 instead of provided there approach 58 are used.
  • FIG. 6 the Course of the pressure p at the injection openings 32 of the Fuel injection valve 12 over the time t during a Injection cycle shown.
  • the suction stroke of the pump piston 18 gets this fuel from the fuel tank 24 supplied.
  • the delivery stroke of the pump piston 18 begins the fuel injection with a pilot injection, wherein the first control valve 68 by the controller 72nd is closed, so that the pump chamber 22 from Relief space 24 is disconnected.
  • the second control valve 70 is also opened so that the control pressure chamber 52 or 152 with the discharge space 24th connected is. In this case, can in the control pressure chamber 52 or 152 do not build high pressure, as this for Relief space 24 is relieved.
  • the Injection valve member 28 opens only with a partial stroke, so that the control piston 50 or 150 with its sealing surface 59 or 159 does not come into contact with seat 57 or 157.
  • On the end face of the injection valve member 28 only acts relatively low pressure in the opening direction 29 and the entire end face of the control piston 50 and 150 is of the pressure prevailing in the control pressure chamber 52 and 152, respectively applied.
  • the second control valve 70th closed, so that the control pressure chamber 52 and 152 of Relief space 24 is disconnected.
  • the first control valve 68 stays in its closed position. In the control pressure room 52 or 152 builds up high pressure as in Pumping work chamber 22, so that on the control piston 50th or 150 a large pressure force acts in the closing direction.
  • the second control valve 70 by the controller 72nd open.
  • the fuel injection valve 12 then opens due to the reduced pressure force on the control piston 50 or 150 and the injection valve member 28 moves over its maximum opening stroke until the control piston 50 or 150 with its sealing surface 59 and 159 on the seat 57 and 157th comes to the plant.
  • the seat 57 or 157 thus also forms a stop for limiting the stroke of the control piston 50th or 150 and thus the opening stroke of the Injection valve member 28.
  • the first Control valve 68 by the controller 72 in his opened switch position, so that the Pump working space 22 connected to the discharge chamber 24 is and on the injection valve member 28 in the opening direction 29 only a small pressure force acts and that Fuel injection valve 12 due to the force of Closing spring 44 and by the in the control pressure chamber 52 and 152 prevailing residual pressure generated force, which after lifting of the control piston 50 and 150 with its sealing surface 59 or 159 from the seat 57 or 157 again on the entire face the control piston 50 and 150 acts, closes.
  • the second Control valve 70 may terminate the Main injection in its open or closed Position.
EP02792633A 2002-02-08 2002-12-05 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Expired - Lifetime EP1483498B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10205185A DE10205185A1 (de) 2002-02-08 2002-02-08 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10205185 2002-02-08
PCT/DE2002/004455 WO2003067070A1 (de) 2002-02-08 2002-12-05 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1483498A1 EP1483498A1 (de) 2004-12-08
EP1483498B1 true EP1483498B1 (de) 2005-07-20

Family

ID=27618432

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02792633A Expired - Lifetime EP1483498B1 (de) 2002-02-08 2002-12-05 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine

Country Status (7)

Country Link
US (1) US6981653B2 (ja)
EP (1) EP1483498B1 (ja)
JP (1) JP2005517118A (ja)
AT (1) ATE299993T1 (ja)
DE (2) DE10205185A1 (ja)
ES (1) ES2243786T3 (ja)
WO (1) WO2003067070A1 (ja)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005014180A1 (de) * 2005-03-29 2006-10-05 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
US20070163243A1 (en) * 2006-01-17 2007-07-19 Arvin Technologies, Inc. Exhaust system with cam-operated valve assembly and associated method
US7415969B2 (en) * 2006-02-28 2008-08-26 Caterpillar Inc. Fuel injector having recessed check top
EP2085604A1 (de) * 2008-02-04 2009-08-05 Robert Bosch GmbH Injektor zum Einspritzen von Kraftstoff
US10982635B2 (en) 2012-05-29 2021-04-20 Delphi Technologies Ip Limited Fuel injector and method for controlling the same
EP2669503A1 (en) * 2012-05-29 2013-12-04 Delphi Technologies Holding S.à.r.l. Fuel Injector
DE102013210036A1 (de) * 2013-05-29 2014-12-04 Robert Bosch Gmbh Hochdruckpumpe für ein Kraftstoffeinspritzsystem
WO2014210148A1 (en) * 2013-06-26 2014-12-31 Cummins Inc. Fuel injector including features to reduce viscous heating in a control valve and a drain circuit
DE102016220364A1 (de) * 2016-10-18 2018-04-19 Robert Bosch Gmbh Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil
US11933257B2 (en) * 2022-03-18 2024-03-19 Caterpillar Inc. Fuel injector lift control

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5860597A (en) * 1997-03-24 1999-01-19 Cummins Engine Company, Inc. Injection rate shaping nozzle assembly for a fuel injector
DE19732802A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
GB9820237D0 (en) * 1998-09-18 1998-11-11 Lucas Ind Plc Fuel injector
DE59903599D1 (de) * 1998-11-10 2003-01-09 Ganser Hydromag Ag Zuerich Brennstoffeinspritzventil für verbrennungskraftmaschinen
DE19939424A1 (de) * 1999-08-20 2001-03-08 Bosch Gmbh Robert Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE19946766C2 (de) * 1999-09-29 2001-07-26 Siemens Ag Injektor für eine Brennkraftmaschine mit Direkteinspritzung

Also Published As

Publication number Publication date
ATE299993T1 (de) 2005-08-15
JP2005517118A (ja) 2005-06-09
DE10205185A1 (de) 2003-08-21
EP1483498A1 (de) 2004-12-08
US20040169092A1 (en) 2004-09-02
US6981653B2 (en) 2006-01-03
DE50203709D1 (de) 2005-08-25
ES2243786T3 (es) 2005-12-01
WO2003067070A1 (de) 2003-08-14

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