EP0063523B2 - Einspritzpumpe für Brennkraftmaschinen mit einer Regeleinrichtung zum Steuern des Kraftstofförderzeitpunkts - Google Patents

Einspritzpumpe für Brennkraftmaschinen mit einer Regeleinrichtung zum Steuern des Kraftstofförderzeitpunkts Download PDF

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Publication number
EP0063523B2
EP0063523B2 EP82400665A EP82400665A EP0063523B2 EP 0063523 B2 EP0063523 B2 EP 0063523B2 EP 82400665 A EP82400665 A EP 82400665A EP 82400665 A EP82400665 A EP 82400665A EP 0063523 B2 EP0063523 B2 EP 0063523B2
Authority
EP
European Patent Office
Prior art keywords
valve
injection pump
fuel
piston
engine
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
Application number
EP82400665A
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English (en)
French (fr)
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EP0063523B1 (de
EP0063523A1 (de
Inventor
Dirk Bastenhof
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.)
MAN Energy Solutions France SAS
Original Assignee
Societe dEtudes de Machines Thermiques SEMT SA
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Filing date
Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=9257492&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0063523(B2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Societe dEtudes de Machines Thermiques SEMT SA filed Critical Societe dEtudes de Machines Thermiques SEMT SA
Priority to AT82400665T priority Critical patent/ATE9606T1/de
Publication of EP0063523A1 publication Critical patent/EP0063523A1/de
Publication of EP0063523B1 publication Critical patent/EP0063523B1/de
Application granted granted Critical
Publication of EP0063523B2 publication Critical patent/EP0063523B2/de
Expired 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
    • 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
    • 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
    • F02M59/365—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages valves being actuated by the fluid pressure produced in an auxiliary pump, e.g. pumps with differential pistons; Regulated pressure of supply pump actuating a metering valve, e.g. a sleeve surrounding the pump piston

Definitions

  • the present invention relates to an injection pump for an internal combustion engine, comprising a fuel intake chamber that can be filled with fuel through intake orifices connected to a space communicating with a fuel source, this admission chamber being of variable volume by the displacement of a piston of the head type with helical ramp of interruption of delivery, according to a rectilinear movement back and forth between a position of bottom dead center and a position of point dead high, this piston closing said intake orifices at the start of each stroke towards its top dead center position, and the pump comprising a device for adjusting the instant of the delivery of fuel from the pump to the injector.
  • Injection pumps of this type are already known (EP-A-0-020 249), which are equipped with a device allowing the adjustment of the moment of delivery of injection fuel.
  • These devices essentially comprise an accumulator chamber, of a predetermined quantity of fuel discharged by the piston after the intake orifices have been blocked.
  • a piston is slidably mounted in this chamber which moves back as the delivery piston advances, to prevent the establishment in this chamber of sufficient pressure to open the outlet valve of the pump. This opening takes place when the accumulator piston reaches its extreme position.
  • the extreme position of the piston must be variable.
  • This adjustment device is complex and bulky. The complexity increases considerably if the adjustment has to be made according to certain engine parameters.
  • the object of the present invention is to provide an adjustment of the fuel delivery time from the pump, which is very simple and compact, even if the adjustment must be made according to different parameters of the engine.
  • the adjustment device is characterized in that it comprises a bypass channel connecting the intake chamber to the space communicating with the source of fuel for filling the chamber, a valve located at the inlet of the channel in the inlet chamber and allowing the closing and opening of this channel, and a control member preventing the closing of the valve for a determined time until a closing control signal occurs depending on the angular position of a rotary member of the engine, such as the crankshaft, the valve being arranged in such a way that the flow of fuel from the inlet chamber into the bypass channel causes the valve to close, and the opening of the valve is determined by the vacuum in the intake chamber caused by the movement of the piston to its bottom dead center position after the fuel is discharged from the injection pump.
  • the adjustment device comprises a hydraulic circuit connected with the control member and provided with a valve member, and an electrical circuit comprising a sensor of the angular position of the rotary member of the engine.
  • the adjustment device comprises a solenoid capable of being excited by an electrical signal produced by a sensor of the angular positions of the rotary member of the motor.
  • the single figure is an axial sectional view of the injection pump according to the invention.
  • the injection pump shown in the figure essentially comprises a hollow cylindrical body 1 in which is axially sliding a piston 2 provided with a head of the helical ramp type 3.
  • the piston 2 is displaceable inside the body 1 , following a straight back and forth movement, between a bottom dead center position and a top dead center position.
  • the body 1 defines, above the discharge surface 4 of the piston 2, a fuel intake chamber 5.
  • This chamber is filled with fuel, using orifices 6 which pass through the cylindrical walls of the body 1 , near the bottom dead center of the piston 2, in order to be closable by this piston at the start of the ascent stroke thereof.
  • the reference numeral 7 generally designates the discharge member intended to open or close the fuel delivery channel 8 out of the intake chamber 5 and therefore out of the injection pump, towards the injector.
  • an envelope 9 surrounds the part of the injection pump, which has just been described, forming an internal annular space 10 into which the inlet orifices 6 open out.
  • This space 10 communicates with the outside , by a channel 11 which ensures its fuel supply.
  • the device for adjusting the fuel delivery instant to the injector, through the outlet channel 8, is essentially formed by a valve 13 for opening and closing a bypass channel 14 intended to connect the chamber 5 in space 10.
  • the valve 13 is provided with a control piston 15 slidably mounted in a sealed manner in a cylindrical bore 16 formed in the upper part of the pump.
  • the part of the bore 16 which is located above the piston 15 communicates with a hydraulic control circuit 17 which comprises a solenoid valve 18 making it possible to connect the upper part of the bore 16 alternately to a a source of hydraulic fluid 19 of low pressure and a source of hydraulic fluid 20 of relatively high pressure.
  • the electric circuit 22 for controlling the solenoid valve 18 essentially comprises, connected in series a sensor 23, a delay device 24 and a switch 25 in the event of overspeed.
  • the sensor 23 cooperates with a member 26 forming part of a rotary flywheel 27 associated with the crank shaft (not shown).
  • the delay device 24 is designed to delay electrical signals produced by the sensor 23, according to one or more engine parameters, such as the air pressure before the engine, the position of the rack of the fuel pumps. or the maximum pressure of the combustion cycle, or the speed of the engine.
  • the low pressure source 19 can supply a fluid at a pressure of 1 to 5 bars.
  • the pressure of the fluid coming from the relatively high pressure source 20 can be of the order of 20 bars.
  • the piston 2 By moving towards its top dead center position, the piston 2 closes the intake orifices 6 and continues its climb stroke.
  • the solenoid valve 18 is in a position such that the fluid coming from the source 20 of relatively high pressure acts on the piston 15 of the valve 13. The latter is therefore kept open .
  • the fuel discharged by the piston 2 therefore flows into the space 10.
  • the pressure in the chamber 5 remains at a relatively low value, insufficient for the opening of the closure member 7 located in the outlet channel 8 leading to the injector.
  • the valve 13 opens again when the delivery piston 2 descends to its bottom dead center position, when the orifices 6 are again closed, under the effect of the vacuum thus created in the chamber 5. This opening of the valve 13 during the descent of the delivery piston 2 contributes to a good filling of the chamber 5 between the fuel deliveries. The high pressure above the piston 15 of the valve 13 is then smoothly restored to lock the valve 13 again in its open position.
  • the instant of production by the sensor 23, of the control signal of the solenoid valve 18 can be chosen relatively close to the instant of the start of delivery determined by the cooperation of the piston 2 and the intake orifices 6. To then be able vary within a relatively large range, the instant of the beginning of the discharge, following the closing of the valve 13, it suffices to introduce, by means of the delay device 24, a delay between the moment of production of the signal by the sensor 23 and of the instant of the pressure drop above the valve piston 13. This delay can be chosen as a function of the speed of the engine, as a function of the air pressure before the engine , the position of the rack of the injection pump, the maximum pressure of the combustion cycle or as a function of any other parameter of the engine.
  • the device according to the invention can also operate in the event of overspeed. It is then sufficient to prevent the pressure above the valve piston 15 from falling.
  • the system can be put out of service by disconnecting the hydraulic circuit from the source of relatively high pressure.
  • the time of delivery of the fuel to the injector is then determined by the cooperation of the delivery piston 2 and the inlet orifices 6, that is to say the engine operates with the obviously greater advance which is determined mechanically.
  • Mechanical means adjustable during a short stop, allow in this case to shift this advance backwards and ensure that the motor continues to run, although the advance is fixed.
  • An important feature of this invention is that the moving parts only move in the presence of low pressures, which is especially important for reliability.
  • the purpose of adjusting the moment of the delivery mainly lies in optimizing the operating conditions of the engine to reduce specific consumption by adjusting the maximum cycle pressure by adjusting the injection time.
  • control piston 15 need not necessarily be slidably mounted in a sealed manner in the cylindrical bore 16. Sealing is not necessary in the event of fuel in the hydraulic system 17, 19, 20. Even if oil is used in the hydraulic system, a small leak can be tolerated. One could consider eliminating the hydraulic control circuit and controlling the valve directly by an electrical signal, for example, using a solenoid.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Management, Administration, Business Operations System, And Electronic Commerce (AREA)
  • Measuring Or Testing Involving Enzymes Or Micro-Organisms (AREA)
  • Bakery Products And Manufacturing Methods Therefor (AREA)
  • Macromonomer-Based Addition Polymer (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Claims (9)

1. Einspritzpumpe für eine Brennkraftmaschine mit einer Brennstoffeinlaßkammer (5), die durch Einlaßbohrungen (6) hindurch, welche mit einem Raum (10) verbunden sind, der mit einer Brennstoffquelle in Verbindung steht, mit Brennstoff gefüllt werden kann, wobei diese Einlaßkammer einen veränderlichen Rauminhalt durch die Verschiebung eines Kolbens (2) mit schraubenförmiger Rampe am Kolbenkopf zur Unterbrechung des Ausstoßes gemäß einer geradlinigen Hin-und Herbewegung zwischen einer unteren Totpunktlage und einer oberen Totpunktlage besitzt, wobei der Kolben die Einlaßbohrungen (6) am Anfang jedes Hubes zu seiner oberen Totpunktlage hin verschliaßen und die Pumpe eine Vorrichtung zur Regelung des Zeitpunkts des Brennstoffausstoßes aus der Pumpe zur Einspritzdüse hin aufweist, dadurch gekennzeichnet, daß die Regelvorrichtung einen Umgehungskanal (14), der die Einlaßkammer (5) mit dem mit der Brennstoffquelle zur Füllung der Kammer in Verbindung stehenden Raum (10) verbindet, ein Ventil (13), das am Eingang des Kanals (14) in die Einlaßkammer angeordnet ist und das Schließen und Öffnen des Kanals erlaubt, und ein Steuerorgan (15) aufweist, das das Schließen des Ventils während einer bestimmten Zeit verhindert, bis in Abhängigkeit von der Winkellage eines drehbaren Glieds (27) des Motors, wie der Kurbelwelle, ein Steuersignal zum Schließen entsteht, wobei das Ventil (13) derart ausgebildet ist, daß die Brennstoffströmung von der Einlaßkammer in den Umgehungskanal das Schließen des Ventils (13) zur Folge hat und daß das Öffnen des Ventils (13) durch den durch die Bewegung des Kolbens zu seiner unteren Totpunktlage hin nach dem Ausstoß des Brennstoffs aus der Einspritzpumpe verursachten Unterdruck in der Einlaßkammer bestimmt wird.
2. Einspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Regelvorrichtung einen Hydraulikkreislauf, der mit dem Steuerorgan (15) verbunden und mit einem ein Ventilschutz (18) bildenden Glied versehen ist, und eine elektrische Schaltung aufweist, die einen Meßfühler (23) für die Winkelstellung des drehbaren Glieds (27) des Motors aufweist.
3. Einspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, daß das ein Ventilschütz (18) bildende Glied aus einem mehrwegigen Magnetventil oder einem piezoelektrischen Ventil besteht.
4. Einspritzpumpe nach Anspruch 2, dadurch gekennzeichnet, daß der Hydraulikkreis eine Quelle (19) für ein Fluid unter schwachem Druck und eine Quelle (20) für ein Fluid unter verhältnismäßig hohem Druck aufweist, wobei diese beiden Quellen (19 - 20) abwechselnd mit der Arbeitskammer eines Kolbens (15) zur Steuerung des Ventils (13) über das Ventilschütz (18) verbindbar sind.
5. Einspritzpumpe nach Anspruch 4, dadurch gekennzeichnet, daß der Zeitpunkt zum Schließen des Ventils durch die Verbindung der Arbeitskammer des Steuerkolbens (15) mit der Quelle (19) des Fluids unter schwachem Druck bestimmt.
6. Einspritzpumpe nach Anspruch 4, dadurch gekennzeichnet, daß das Ventil offen ist, wenn die Arbeitskammer des Steuerkolbens (15) mit der Quelle (20) für das Fluid unter verhältnismäßig hohem Druck verbunden ist.
7. Einspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Regelvorrichtung eine durch ein von einem Meßfühler (23) für die Winkellagen des drehbaren Glieds (27) des Motors erzeugtes elektrisches Signal erregbare Zylinderspule aufweist.
8. Einspritzpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß eine Vorrichtung (24) zur Verzögerung in Abhängigkeit von einem Betriebskennwert des Motors in der Schaltung für das durch den Meßfühler (23) erzeugte Signal angeordnet ist.
9. Einspritzpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß ein Unterbrechungsglied (25) die Aufrechterhaltung der Öffnungsdauerstellung des Ventils bei mit Überdrehzahl laufendem Motor bewirkt.
EP82400665A 1981-04-16 1982-04-14 Einspritzpumpe für Brennkraftmaschinen mit einer Regeleinrichtung zum Steuern des Kraftstofförderzeitpunkts Expired EP0063523B2 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82400665T ATE9606T1 (de) 1981-04-16 1982-04-14 Einspritzpumpe fuer brennkraftmaschinen mit einer regeleinrichtung zum steuern des kraftstoffoerderzeitpunkts.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8107685 1981-04-16
FR8107685A FR2504203B1 (fr) 1981-04-16 1981-04-16 Pompe d'injection pour moteur a combustion interne comprenant un dispositif de reglage de l'instant de refoulement du combustible d'injection

Publications (3)

Publication Number Publication Date
EP0063523A1 EP0063523A1 (de) 1982-10-27
EP0063523B1 EP0063523B1 (de) 1984-09-26
EP0063523B2 true EP0063523B2 (de) 1989-10-04

Family

ID=9257492

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82400665A Expired EP0063523B2 (de) 1981-04-16 1982-04-14 Einspritzpumpe für Brennkraftmaschinen mit einer Regeleinrichtung zum Steuern des Kraftstofförderzeitpunkts

Country Status (19)

Country Link
US (1) US4705006A (de)
EP (1) EP0063523B2 (de)
JP (1) JPS57181967A (de)
KR (1) KR880001501B1 (de)
AT (1) ATE9606T1 (de)
AU (1) AU549787B2 (de)
BR (1) BR8202126A (de)
CS (1) CS261858B2 (de)
DD (1) DD202197A5 (de)
DE (1) DE3260819D1 (de)
DK (1) DK155290C (de)
ES (1) ES8304266A1 (de)
FI (1) FI70300C (de)
FR (1) FR2504203B1 (de)
IN (1) IN157868B (de)
NO (1) NO156801C (de)
PL (1) PL137665B1 (de)
SU (1) SU1192636A3 (de)
YU (1) YU45861B (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0111200B1 (de) * 1982-11-25 1988-02-03 Kawasaki Jukogyo Kabushiki Kaisha Kraftstoffeinspritzbeginnkontrollsystem
DE3248086C2 (de) * 1982-12-24 1986-10-16 L'Orange GmbH, 7000 Stuttgart Kraftstoffeinspritzpumpe für Brennkraftmaschinen, insbesondere für Dieselmotoren
DE3506392A1 (de) * 1985-02-23 1986-09-04 Motoren-Werke Mannheim AG vorm. Benz Abt. stationärer Motorenbau, 6800 Mannheim Einspritzsystem fuer einen dieselmotor mit einer hochdruck-einspritzpumpe fuer jeden zylinder
GB8828159D0 (en) * 1988-12-02 1989-01-05 Lucas Ind Plc Fuel injection pump
DE4010450A1 (de) * 1990-03-31 1991-10-02 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung fuer einspritzbrennkraftmaschinen
DE4113957A1 (de) * 1991-04-29 1992-11-05 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzvorrichtung
GB9306603D0 (en) * 1993-03-30 1993-05-26 Lucas Ind Plc Fuel pump
JP3936119B2 (ja) * 2000-04-18 2007-06-27 トヨタ自動車株式会社 高圧ポンプおよび高圧ポンプの組み付け構造
JP3905282B2 (ja) * 2000-04-18 2007-04-18 トヨタ自動車株式会社 高圧ポンプ

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR693493A (fr) * 1930-04-07 1930-11-20 Usines De La Chaleassiere Soc Pompe à combustible pour moteurs à combustion interne et à injection mécanique
DE6610398U (de) * 1967-05-03 1973-11-29 Winkelhofer & Soehne Joh Kette.
DE1917927A1 (de) * 1969-04-09 1970-10-29 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen
JPS506043B1 (de) * 1969-05-19 1975-03-10
BE795479A (fr) * 1972-02-17 1973-08-16 Sulzer Ag Pompe d'injection de carburant pour moteur diesel
JPS5425328A (en) * 1977-07-28 1979-02-26 Mitsui Eng & Shipbuild Co Ltd Fuel injection time changer
DE2742466C2 (de) * 1977-09-21 1986-11-27 Daimler-Benz Ag, 7000 Stuttgart Pumpdüse zur Kraftstoffeinspritzung in eine luftverdichtende Brennkraftmaschine
GB2041577B (en) * 1979-01-31 1983-04-13 Lucas Industries Ltd Fuel system for internal combustion engines
US4385614A (en) * 1979-04-06 1983-05-31 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
FR2482669A2 (fr) * 1979-05-28 1981-11-20 Semt Perfectionnement a une pompe d'injection pour un moteur a combustion interne
US4343280A (en) * 1980-09-24 1982-08-10 The Bendix Corporation Fuel delivery control arrangement
US4364351A (en) * 1981-05-18 1982-12-21 General Motors Corporation Diesel engine fuel limiting system

Also Published As

Publication number Publication date
US4705006A (en) 1987-11-10
DK155290C (da) 1989-08-07
PL236003A1 (de) 1982-11-08
DK161982A (da) 1982-10-17
FI821295A0 (fi) 1982-04-13
DE3260819D1 (en) 1984-10-31
EP0063523B1 (de) 1984-09-26
JPS57181967A (en) 1982-11-09
CS274782A2 (en) 1988-07-15
FR2504203B1 (fr) 1985-05-31
IN157868B (de) 1986-07-12
KR830010291A (ko) 1983-12-30
NO821235L (no) 1982-10-18
ES511459A0 (es) 1983-02-16
NO156801C (no) 1987-11-25
KR880001501B1 (ko) 1988-08-16
ES8304266A1 (es) 1983-02-16
CS261858B2 (en) 1989-02-10
FI70300C (fi) 1986-09-15
YU45861B (sh) 1992-09-07
DK155290B (da) 1989-03-20
AU549787B2 (en) 1986-02-13
JPH0413552B2 (de) 1992-03-10
BR8202126A (pt) 1983-03-22
EP0063523A1 (de) 1982-10-27
FI70300B (fi) 1986-02-28
AU8267482A (en) 1982-10-21
FI821295L (fi) 1982-10-17
SU1192636A3 (ru) 1985-11-15
DD202197A5 (de) 1983-08-31
ATE9606T1 (de) 1984-10-15
PL137665B1 (en) 1986-07-31
NO156801B (no) 1987-08-17
YU84482A (en) 1989-02-28
FR2504203A1 (fr) 1982-10-22

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