EP0910739B1 - Kraftstoffeinspritzsystem - Google Patents

Kraftstoffeinspritzsystem Download PDF

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Publication number
EP0910739B1
EP0910739B1 EP98912246A EP98912246A EP0910739B1 EP 0910739 B1 EP0910739 B1 EP 0910739B1 EP 98912246 A EP98912246 A EP 98912246A EP 98912246 A EP98912246 A EP 98912246A EP 0910739 B1 EP0910739 B1 EP 0910739B1
Authority
EP
European Patent Office
Prior art keywords
injection
pump
cam
sub area
valve
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
EP98912246A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0910739A1 (de
Inventor
Stuart-William Nicol
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 EP0910739A1 publication Critical patent/EP0910739A1/de
Application granted granted Critical
Publication of EP0910739B1 publication Critical patent/EP0910739B1/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
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • 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
    • 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
    • F02M45/063—Delivery stroke of piston being divided into two or more parts, e.g. by using specially shaped cams

Definitions

  • the invention is based on a fuel injection system the genus of claim 1.
  • a fuel injection pump a distributor injection pump is provided, with a back and forth driven and at the same time rotating pump piston which rotates during its and its pump stroke one of several injection lines, that each lead to a fuel injector Injection brought fuel supplied.
  • the electrically controlled Valve which is a solenoid valve, opened briefly, and so on relieve the pump workspace and the fuel pressure achieved dismantle briefly. This means that a very fast switching solenoid valve is required, the one considerable effort on the electrical control and on the Construction of the valve requires.
  • the solution according to the invention ensures a safe one Interruption of injection between pre-injection and main injection with low demands on speed of a time-controlled valve. Doing so during the interruption the injection between pre and Main injection no or only a very small part of the available cam stroke. Through the constructive Support the interruption of the Injection is achieved even at higher speeds a safe interruption of injection between pre and main injection is observable without it becoming a Loss of those available for high-pressure production Cam stroke is coming. The speed-independent influence of the switching time is through the second portion of the cam compensated, so that no overly large requirements the speed of the electrically controlled valve must be asked.
  • FIG. 1 shows a basic illustration of a Fuel injection pump controlled by a solenoid valve 2 shows a course of the invention Cam track in the form of a cam elevation curve over the angle of rotation with a first control sequence of the valve low speed of the internal combustion engine and Figure 3 a Course of the cam track according to the invention over the angle of rotation with a second control sequence of the valve at high Speed of the internal combustion engine.
  • Embodiment based on a distributor injection pump realized as shown schematically in Figure 1 is. It is a distributor injection pump the axial piston type, even if the object the invention also in other fuel injection pumps is usable such.
  • the invention is in a distributor injection pump feasible because here the available cam stroke because of the limited length of the cam track is smaller than e.g. an in-line injection pump.
  • a pump piston 1 is provided, which is displaceable and rotatable in a cylinder bore 2 is arranged and there on the front a pump work space 10 includes.
  • the pump piston is included a cam 6, the axially downward facing cam 5 of the embodiment according to the invention, for. B. about a spring, not shown, coupled.
  • the cam disc becomes rotating, especially synchronous to the speed the internal combustion engine supplied by the injection pump a drive shaft not shown in known Way driven, the cam disc under the influence of Spring on a known axially fixed roller ring expires and subsequently the rotating pump and Distributor piston in a reciprocating promotional and sucking movement offset.
  • the time or angle of rotation dependent The course of the rollers on the cam flank is determined thus the stroke position of the pump piston.
  • the pump piston When it rotates in association with a pump delivery stroke in which from the pump work space 10 fuel is displaced under high pressure, the pump piston comes with one of several injection lines 7 via a distributor groove 8 in the lateral surface of the Pump and distributor pistons in connection.
  • the distributor groove is constantly connected to the pump workspace via a longitudinal channel 9 connected.
  • the injection line introduces via Pressure valve 12 to a fuel injection valve 13, the assigned to the respective cylinder of an internal combustion engine is.
  • the pump work space 10 is supplied with fuel via a suction line 15, which is separated from a suction space 17, which is essentially only shown in dashed lines and enclosed within the housing of the fuel injection pump is supplied.
  • the suction chamber receives fuel from a fuel feed pump 18, which is synchronous with the fuel injection pump, e.g. B. driven by the drive shaft and therefore fuel in speed-dependent quantities promotes in the suction chamber.
  • a fuel feed pump 18 is usually the pressure in the suction chamber controlled speed-dependent, if with the help of this Pressure additional functions of the fuel injection pump controlled should be.
  • An overflow throttle 22 flows continuously Fuel back to the reservoir 23, so that for cooling the injection pump or degassing the Suction chamber is taken care of.
  • the suction line 15 leads through Check valve 16 in the pump work space, which Check valve opens towards the pump work area.
  • an electrically controlled one Valve 24 is provided which has a bypass line 21 controls to the pressure valve 16 and with its help when opening the valve a connection between the pump work space 10 and suction chamber 17 is made and when the valve is closed the pump work space 10 is closed. That as a solenoid valve symbolized electrically controlled valve 24 is controlled by a control device 25 according to operating parameters controlled in a manner known per se. With enough large flow cross section of the valve 24 can, however Check valve 16 is also omitted. In this case the Pump work space during the suction stroke only via the electrically controlled Valve filled.
  • the valve can also be used to control the start of spraying become.
  • the start of spraying through a separate injection start adjustment device be adjusted, which is known to be relative to the Cam-sensing pump piston rotatable cam drive part having.
  • the cam 5 designed so that it as in the Figure 2 or 3 shown a stroke over time of the pump piston, which is divided into one first area V which begins with the delivery stroke of the piston ends after a small delivery stroke, in a second area P in which the piston then not at all or only so slightly is moved in the conveying direction that he is in this area for high-pressure delivery is not effective and an injection break arises and finally into a third Area H in which the cam flank rises again and the Pump piston for further delivery of the main injection quantity moves further.
  • area P the cam can be horizontal, slightly rising or falling.
  • the pilot injection is continued by the electric controlled valve controlled so that it is closed is when the roles in the second area P come.
  • the diagram is in FIG. 2 shows that the electrically controlled valve, e.g. a solenoid valve or one from a piezo actuated valve, for controlling the start of the pre-injection quantity delivery in U.T., i.e. before the rise of Cam curve is closed from a base circle and in which Cam area V again before reaching cam area P. is opened.
  • the electrically controlled valve e.g. a solenoid valve or one from a piezo actuated valve
  • the electrically controlled valve e.g. a solenoid valve or one from a piezo actuated valve, for controlling the start of the pre-injection quantity delivery in U.T., i.e. before the rise of Cam curve is closed from a base circle and in which Cam area V again before reaching cam area P. is opened.
  • a spray break in area P follows then a reclosing of the valve 24 with the start of the high pressure delivery for the main injection in the following Cam flank part H, where thereafter by opening valve 24 the high-pressure
  • valve 24 becomes like this controlled that it is only in the region of the cam flank part P is closed so that it is securely closed when the Fuel delivery for the now main injection in the area of the cam flank part adjoining area P. H is done.
  • the end of the injection will turn controlled by opening the valve, which then usually even before the top dead center of the cam of the injection pumps he follows.
  • This control has the advantage that at high speeds the pump workspace of the injection pump is sufficient Fuel can be filled because the filling phase is now against is extended above the control at low speed and the piston movement in the filling direction, i.e. during the suction stroke only must reach the stroke range on which the second Area P is located. Because of the only starting from area P. High-pressure delivery is the required filling quantity of the pump working room reduced.
  • the electric The controlled valve therefore closes only in the region P Cam flank so that the suction stroke for sucking fuel fully exploited via the trailing cam flank V. can be.
  • the inflow filling effect still affects the beginning part of the cam flank in front of area P as long the valve is not yet closed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP98912246A 1997-04-25 1998-02-17 Kraftstoffeinspritzsystem Expired - Lifetime EP0910739B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19717493A DE19717493A1 (de) 1997-04-25 1997-04-25 Kraftstoffeinspritzsystem
DE19717493 1997-04-25
PCT/DE1998/000452 WO1998049442A1 (de) 1997-04-25 1998-02-17 Kraftstoffeinspritzsystem

Publications (2)

Publication Number Publication Date
EP0910739A1 EP0910739A1 (de) 1999-04-28
EP0910739B1 true EP0910739B1 (de) 2001-10-04

Family

ID=7827733

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98912246A Expired - Lifetime EP0910739B1 (de) 1997-04-25 1998-02-17 Kraftstoffeinspritzsystem

Country Status (8)

Country Link
US (1) US6079388A (zh)
EP (1) EP0910739B1 (zh)
JP (1) JP2000513783A (zh)
CN (1) CN1089854C (zh)
CZ (1) CZ291627B6 (zh)
DE (2) DE19717493A1 (zh)
RU (1) RU2196246C2 (zh)
WO (1) WO1998049442A1 (zh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10101107A1 (de) * 2001-01-12 2002-07-25 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
JP2003343396A (ja) * 2002-05-22 2003-12-03 Mitsubishi Electric Corp 高圧燃料供給装置
FI119120B (fi) * 2004-01-23 2008-07-31 Waertsilae Finland Oy Laitteisto ja menetelmä polttoaineen ruiskutuspaineen muokkaamiseksi
DE102010027745A1 (de) * 2010-04-14 2011-10-20 Robert Bosch Gmbh Hochdruckpumpe

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3690768A (en) * 1969-02-28 1972-09-12 Mitsubishi Motors Corp Diesel fuel injection system with improved starting performance
US4838232A (en) * 1984-08-14 1989-06-13 Ail Corporation Fuel delivery control system
JPS62110566U (zh) * 1985-12-27 1987-07-14
JPS635140A (ja) * 1986-06-24 1988-01-11 Diesel Kiki Co Ltd 燃料噴射ポンプの噴射制御方法
DE3629751C2 (de) * 1986-09-01 1998-07-02 Bosch Gmbh Robert Voreinspritzvorrichtung für Brennkraftmaschinen
DE3929747A1 (de) * 1989-09-07 1991-03-14 Bosch Gmbh Robert Verfahren und einrichtung zum steuern der kraftstoffeinspritzung
US5325837A (en) * 1992-11-19 1994-07-05 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US5443047A (en) * 1993-04-09 1995-08-22 Zexel Corporation Fuel injection system
GB9509610D0 (en) * 1995-05-12 1995-07-05 Lucas Ind Plc Fuel system

Also Published As

Publication number Publication date
CZ419598A3 (cs) 1999-06-16
CN1089854C (zh) 2002-08-28
RU2196246C2 (ru) 2003-01-10
JP2000513783A (ja) 2000-10-17
DE59801622D1 (de) 2001-11-08
EP0910739A1 (de) 1999-04-28
DE19717493A1 (de) 1998-10-29
WO1998049442A1 (de) 1998-11-05
CZ291627B6 (cs) 2003-04-16
CN1224484A (zh) 1999-07-28
US6079388A (en) 2000-06-27

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