EP0067368A2 - Pompe d'injection de carburant - Google Patents

Pompe d'injection de carburant Download PDF

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Publication number
EP0067368A2
EP0067368A2 EP82104850A EP82104850A EP0067368A2 EP 0067368 A2 EP0067368 A2 EP 0067368A2 EP 82104850 A EP82104850 A EP 82104850A EP 82104850 A EP82104850 A EP 82104850A EP 0067368 A2 EP0067368 A2 EP 0067368A2
Authority
EP
European Patent Office
Prior art keywords
fuel
fuel injection
pump
control
injection pump
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.)
Ceased
Application number
EP82104850A
Other languages
German (de)
English (en)
Other versions
EP0067368A3 (fr
Inventor
Max Dr. Straubel
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 EP0067368A2 publication Critical patent/EP0067368A2/fr
Publication of EP0067368A3 publication Critical patent/EP0067368A3/fr
Ceased 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
    • 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
    • F02M41/14—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 rotary distributor supporting pump pistons
    • F02M41/1405—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 rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—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 rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
    • 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

Definitions

  • the invention relates to a fuel injection pump according to the preamble of the main claim.
  • the amount of fuel which is to be injected during the delivery stroke of the pump piston of the injection pump is metered by a solenoid valve which is clocked or controlled analogously during the suction stroke of the pump piston.
  • the metered quantity is determined by the opening time of the solenoid valve, the opening phase of this valve lying exclusively in the suction stroke area of the pump piston.
  • the pressure conditions in the working space of the fuel injection pump influence the metered amount. Depending on the opening point of the solenoid valve, there is a more or less reduced pressure in the work area.
  • the speed and the injection timing must be taken into account in this known device for dimensioning the opening times of the solenoid valve.
  • Further disadvantages result from the limited switching speed of a solenoid valve.
  • the two switching operations of the solenoid valve that take place during the metering phase during the suction stroke thus influence the accuracy of the metering result.
  • the speed or the injection pump speed are limited by the switching time of the solenoid valve.
  • the metering stroke of the solenoid valve begins with the suction stroke of the associated pump pistons.
  • a spray start adjustment requires a change in the suction stroke start, so that this suction stroke start must be entered exactly when calculating the opening time of the solenoid valve. It is also the dynamic situation at the turning point of the pump piston at the transition from the delivery stroke to the suction stroke is difficult to control.
  • the fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the metering of the amount of fuel to be injected can be controlled electrically and that only one switching operation, the opening or closing of the fuel supply line, via which the amount of fuel to be metered in the working area of the fuel injection pump comes from the switching time, for. B. a solenoid valve is influenced.
  • the other switching operation is advantageously mechanically controlled and carried out sufficiently quickly at any pump speed. This is made possible by the fact that the control times of the control edge, which is guided synchronously with the pump speed, on the one hand, and the solenoid valve, on the other hand, overlap and the fuel supply line is only open when the control edge and the solenoid valve, which are in series, have opened.
  • the overlap of the control times of the control edge and the solenoid valve also permits a relative displacement of the control point of the fuel supply line by the control edge with respect to the control point of the fuel supply line of the solenoid valve, so that spray adjustment is possible without influencing the accuracy of the fuel quantity control.
  • the above measure allows the injection pump to be controlled with sufficient accuracy even at high speeds.
  • FIG. 1 shows the exemplary embodiment in a basic illustration
  • FIG. 2a shows a diagram of the control times at which the fuel supply line is opened by the control edge, plotted against the angle of rotation ⁇
  • FIG. 2b shows the control times of the solenoid valve plotted against the angle of rotation ⁇
  • Fig. 2c the resulting opening time of the fuel supply line
  • Fig. 3a the timing of the control edge in the event that the opening by the control edge of the opening by the solenoid valve leads
  • Fig. 3b the associated control time
  • Fig. 3c the resulting opening time of the fuel supply line in this case
  • Fig. 4 shows the use of two solenoid valves in each of a 90 0 offset fuel supply pipe opening into the pump housing
  • Fig. 5 a first section of the fuel injection pump according to Fig. 4 in the plane of the first fuel supply conduit opening into the pump body
  • Fig. 6 shows a second Section through the fuel feed 4 in the plane of the second junction of a second fuel supply line in the pump body.
  • FIG. 1 shows a basic illustration of a known radial piston pump, in which a rotating distributor 2 is mounted in a pump housing 1 and is driven synchronously with the engine speed.
  • a radial through-bore is provided, from which a delivery channel 5 leads off in the axis of the distributor, which contains a check valve 6 and whose end merges into a radially extending distributor bore 7.
  • the pump housing 1 has injection lines 8 which, starting from the cylinder bore 9 in which the distributor 2 is guided in the housing 1, leads to the individual injection points of the internal combustion engine.
  • the injection lines are distributed according to the number of injection points to be supplied and in the sequence corresponding to them on the circumference of the pump housing.
  • two pump pistons 10 are arranged, which, working against each other, enclose a pump work chamber 11 in the center, which is in constant communication with the delivery channel 5.
  • the other side of the pump piston is acted upon by rollers 12 which roll on a cam ring 14 lying in the radial plane.
  • the pistons 4 are subject to the centrifugal force and are carried to the outside during the rotary movement of the distributor as far as the fuel filling in the pump work chamber 11 permits, and are moved inwards again when the rollers 12 hit a cam of the cam ring.
  • the pump pistons perform the pumping movement, due to which fuel is conveyed through the delivery channel 5 via the check valve 6, the distributor bore 7 into one of the injection lines 8.
  • the fuel in the pump work space is carried out via a fuel supply line 16, which connects to a feed pump 17. This sucks fuel from a fuel reservoir 18 and delivers it under pressure into the fuel supply line 16.
  • the delivery pressure is set with the aid of a pressure control valve 19.
  • a solenoid valve 20 is provided in the fuel supply line. see that is controlled by a control device 21.
  • the fuel supply line opens radially into the cylinder 9 and, when the distributor is in a corresponding rotational position, is connected to the pump working space 11 via a radially extending supply bore 22.
  • the supply bore 22 opens into the delivery channel 5 between the pump work chamber and the breakdown valve.
  • the outlet opening of the supply bore 22 into the cylinder 9 is designed as a control edge 23.
  • curve 23 shows the opening time over the angle of rotation during which the connection between supply bore 22 and the fuel supply line is established via control edge 23.
  • the dashed curve 23 ' shows how the curve 23 relates to the rotation position or the angle of rotation ⁇ shifts when the cam ring 14 is rotated to adjust the injection timing.
  • Such devices for spray timing adjustment are generally known and are not described in detail here.
  • FIG. 2b shows the opening times of the solenoid valve 20 on the basis of curve 20. While the opening time according to curve 23 in FIG. 2a is unchangeable in length, the opening time of the solenoid valve according to curve 20 can now be made variable, which is indicated by the different closing times according to curves 20 'and 20 "is shown. Both curves are assigned to each other in accordance with the angle of rotation and it turns out that the solenoid valve is opened much earlier than the supply bore 22 via the control edge 23.
  • FIG. 2c shows the remaining opening time of the fuel supply line 16 corresponding to the overlap of the opening times according to FIGS. 2a and 2b.
  • this opening time can now be varied. If the start of injection is adjusted and thus a relative displacement of curve 23 to curve 23 'by the angle of rotation ⁇ 1, this displacement must be compensated for by the time the solenoid valve closes.
  • the thus changed opening time of the fuel supply line 16 ' is shown in dashed lines in FIG. 2c.
  • the control device 21 controls the solenoid valve in a conventional manner as a function of the amount of fuel to be metered, which essentially results from the load and other engine parameters. Corrections are necessary according to the spray adjustment. Furthermore, the control device receives signals for the speed or for the position of a reference point, which characterizes a specific rotational angle position of the distributor 2.
  • both supply bores 25 and 26 are provided in parallel radial planes.
  • the fuel supply line 16 also splits into a partial line 16a and a partial line 16b, which open into the cylinder bore 9 of the pump housing 1 in the radial plane identified by the supply bores 25 and 26.
  • Each of the sub-lines 16a and 16b is assigned a solenoid valve 20a and 20b, which are controlled alternately by a control unit 27.
  • both supply bores 25 and 26 open into the delivery channel 5, but are offset from one another by 90 °. 5 and 6 each show a section in the radial plane characterized by the supply bores 25 and 26 through the fuel injection pump in the position shown.
  • This configuration makes it possible to carry out a higher number of injections per revolution of the distributor. It is ensured that the solenoid valves can be opened long enough before opening the supply bores 25 or 26 or, in the other case, can be closed sufficiently long after the supply bores 25 or 26 have been closed in order to enable long spray adjustment times. With only two junction points of the fuel supply line in the cylinder bore 9, four injection cycles per revolution of the distributor can be carried out in this way.
  • the main advantage of the described method of fuel metering is that the influence of the fuel metering amount by the finite switching times of a solenoid valve, which are the same in amount but would cause a proportionally increasing error with increasing speed, is reduced.
  • the switching time error is now only included in the metering result with an edge of the switching of the solenoid valve.
  • Fast-switching valves are used as the valve, which can be controlled electrically and z. B. can be designed as solenoid valves.
  • other valves are also possible / by which the supply line is closed or opened in response to an electrical signal (piezo valves).

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
EP82104850A 1981-06-11 1982-06-03 Pompe d'injection de carburant Ceased EP0067368A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3123138 1981-06-11
DE19813123138 DE3123138A1 (de) 1981-06-11 1981-06-11 Kraftstoffeinspritzpumpe

Publications (2)

Publication Number Publication Date
EP0067368A2 true EP0067368A2 (fr) 1982-12-22
EP0067368A3 EP0067368A3 (fr) 1983-12-14

Family

ID=6134435

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104850A Ceased EP0067368A3 (fr) 1981-06-11 1982-06-03 Pompe d'injection de carburant

Country Status (4)

Country Link
US (1) US4767288A (fr)
EP (1) EP0067368A3 (fr)
JP (1) JPS5879660A (fr)
DE (1) DE3123138A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4446836A (en) * 1981-10-23 1984-05-08 Lucas Industries Public Limited Company Fuel injection pumping apparatus
DE3424881C2 (de) * 1984-07-06 1997-08-14 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE3437973A1 (de) * 1984-10-17 1986-04-17 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US4698550A (en) * 1985-05-06 1987-10-06 Hamamatsu Photonics Kabushiki Kaisha Hollow cathode lamp
DE3719833C2 (de) * 1987-06-13 1996-05-30 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
US5133645A (en) * 1990-07-16 1992-07-28 Diesel Technology Corporation Common rail fuel injection system
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
DE4113957A1 (de) * 1991-04-29 1992-11-05 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzvorrichtung
GB2275307B (en) * 1993-02-18 1996-06-05 Bosch Gmbh Robert A fuel-injection system for internal combustion engines
EP0643221B1 (fr) * 1993-09-14 1998-04-22 Lucas Industries Public Limited Company Dispositif d'alimentation de carburant
US6358024B1 (en) * 1998-02-27 2002-03-19 Stanadyne Automotive Corp. High capacity supply pump with simultaneous directly actuated plungers
DE10129449A1 (de) * 2001-06-19 2003-01-02 Bosch Gmbh Robert Kraftstoffhochdruckpumpe für Brennkraftmaschine mit verbessertem Teillastverhalten
EP1855669A4 (fr) * 2005-01-28 2010-07-07 Bc Cancer Agency Compositions liposomales pour administration parenterale d'agents
DE102005033638A1 (de) * 2005-07-19 2007-01-25 Robert Bosch Gmbh Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1156607B (de) * 1961-10-28 1963-10-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen
DE1919707A1 (de) * 1969-04-18 1970-11-12 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer mehrzylindrige Brennkraftmaschinen
DE1919969C2 (de) * 1969-04-19 1983-10-27 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE2107371A1 (de) * 1970-02-20 1971-09-23 Nippon Denso Co Kraftstoffsteuersystem
DE2503346C2 (de) * 1975-01-28 1986-04-03 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen
US4037574A (en) * 1976-05-21 1977-07-26 Stanadyne, Inc. Timing control for fuel injection pump
JPS6032021B2 (ja) * 1976-12-26 1985-07-25 株式会社デンソー 噴射ポンプ制御装置
JPS5430315A (en) * 1977-08-10 1979-03-06 Automob Antipollut & Saf Res Center Injection fuel controller of distribution fuel injector
US4241714A (en) * 1979-06-25 1980-12-30 General Motors Corporation Solenoid valve controlled fuel injection pump
DE3000977A1 (de) * 1980-01-12 1981-07-23 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen, insbesondere fuer dieselmotoren
JPS5756660A (en) * 1980-09-22 1982-04-05 Hitachi Ltd Fuel injection pump
US4446836A (en) * 1981-10-23 1984-05-08 Lucas Industries Public Limited Company Fuel injection pumping apparatus
JPS5920558A (ja) * 1982-07-26 1984-02-02 Hitachi Ltd 噴射ポンプ燃料計量供給装置

Also Published As

Publication number Publication date
EP0067368A3 (fr) 1983-12-14
DE3123138A1 (de) 1982-12-30
DE3123138C2 (fr) 1991-01-10
US4767288A (en) 1988-08-30
JPH0364709B2 (fr) 1991-10-08
JPS5879660A (ja) 1983-05-13

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

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Effective date: 19860815

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Inventor name: STRAUBEL, MAX, DR.