EP0020249A1 - Einspritzpumpe für Brennkraftmaschine - Google Patents

Einspritzpumpe für Brennkraftmaschine Download PDF

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Publication number
EP0020249A1
EP0020249A1 EP80400720A EP80400720A EP0020249A1 EP 0020249 A1 EP0020249 A1 EP 0020249A1 EP 80400720 A EP80400720 A EP 80400720A EP 80400720 A EP80400720 A EP 80400720A EP 0020249 A1 EP0020249 A1 EP 0020249A1
Authority
EP
European Patent Office
Prior art keywords
piston
fuel
groove
chamber
delivery
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
EP80400720A
Other languages
English (en)
French (fr)
Other versions
EP0020249B1 (de
Inventor
Dirk Bastenhof
Roger Brisson
Claude Bonniot
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
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=26221181&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0020249(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from FR7913486A external-priority patent/FR2457987A1/fr
Application filed by Societe dEtudes de Machines Thermiques SEMT SA filed Critical Societe dEtudes de Machines Thermiques SEMT SA
Publication of EP0020249A1 publication Critical patent/EP0020249A1/de
Application granted granted Critical
Publication of EP0020249B1 publication Critical patent/EP0020249B1/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
    • 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
    • F02M45/066—Having specially arranged spill port and spill contour on the piston
    • 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
    • F02M59/22—Varying quantity or timing by adjusting cylinder-head space

Definitions

  • the invention relates to an injection pump for injecting fuel into a cylinder of an internal combustion engine.
  • the invention particularly relates to an injection pump comprising a fuel receiving chamber defined in a cylindrical body, and variable in volume by the movement in this body, of a piston, according to an alternating back and forth movement , between a top dead center position and a bottom dead center position, this chamber being provided with at least one fuel inlet orifice, connected to a source of fuel of relatively low pressure and closable during the movement of said piston from its bottom dead center position to its top dead center position, to allow fuel to be discharged from said chamber to an injector associated with an engine cylinder, and the piston comprising at least one helical ramp at its periphery , which results in an axial groove and a circular groove connected by said axial groove inside said receiving chamber.
  • the known injection pumps of this structure have the disadvantage that the quantity of fuel injected into a cylinder, before ignition, can become relatively large in the event of a long ignition delay caused by too cold air or poor quality fuel.
  • ignition finally occurs a large amount of fuel ignites, which results in a sharp increase in pressure inside the combustion chamber causing great stresses in the component parts of the engine, such as the jacket, in the shaft bearings, sealing problems, for example at the head gasket, and noise.
  • the object of the invention is to propose an injection pump which makes it possible to carry out the pre-injection by means of an appropriate configuration, of the injection pump of the type described above.
  • the piston of the injection pump comprises a passage opening at one end into said fuel receiving chamber and capable of coming into communication, through its other end, with at least one channel opening into space inside the body coming from said fuel source, to interrupt at a predetermined time and for a predetermined period the delivery of fuel from said chamber to The injector during the displacement of the piston in the direction of its top dead center, the first delivery phase allowing a pre-injection of fuel into said cylinder and the second delivery phase ensuring a main injection.
  • the piston comprises below said first groove a second peripheral groove communicating with the first groove
  • the body of the injection pump comprises at least one aforementioned inlet channel, located below inlet orifices and closable by the peripheral surface of the piston, the inlet channel and said second groove being arranged so that the groove is capable of coming opposite said channel at a predetermined instant after the obturation of the orifices arrival by said piston, during the displacement displacement of the latter in the direction of its top dead center.
  • the injection pump according to the invention further comprises a fuel accumulator device allowing a variation in the quantity of pre-injection fuel without influencing the start of the main injection.
  • Figures 1 to 4 are longitudinal sectional views of a first embodiment of an injection pump according to the invention and illustrate specific steps in the operation of the pump;
  • Figure 5 is a sectional view along line V-V of Figure 2;
  • FIG. 6 illustrates the fuel delivery phases out of the injection pump chamber, as a function of the position of the piston of the engine cylinder, expressed in angular position of the crankshaft;
  • Figure 7 is a longitudinal sectional view of a second embodiment of an injection pump according to the invention;
  • Figure 8 is a sectional view along line VIII-VIII of Figure 7;
  • Figure 9 shows in a sectional view and schematically the accumulator device according to the invention, and
  • Figures 10 and 11 illustrate two concrete embodiments of an accumulator according to the invention.
  • the injection pump shown in Figures 1 to 5 comprises a cylindrical body 1 and a piston 2 movably mounted in this body 1 in a reciprocating rectilinear reciprocating movement, between a position of bottom dead center and a position of top dead center, under the effect of a control cam (not shown) secured to a shaft driven by the motor.
  • a fuel intake chamber 3 into which open fuel inlet orifices 4. These orifices are located at a level such that they allow the filling of the chamber 3 by the fuel, when the piston occupies its bottom dead center position.
  • a fuel delivery orifice in the direction of arrow F1, towards an injector associated with a cylinder of an internal combustion engine. This discharge orifice can be closed off by a discharge member, in a manner known per se.
  • the piston 2 has a first circular groove 5 delimited at its lower part by a straight edge 6 and at its upper part by a helical edge 7 forming a helical ramp and ending in a groove 8 which extends parallel to the axis of the piston .
  • This groove establishes permanent communication between the inlet chamber 3 and the groove 5.
  • the piston 2 is provided with a second circular groove 9, limited, in the example shown, above by a straight edge 10 and below by a straight edge 11.
  • This second groove 9 communicates with the first groove 5 through axial passages, formed in the example represented by two flats 12 formed on the flange 13 which is delimited between the two grooves 5 and 9.
  • the edges 6, 7, 10 and 11 each have a sharp angle of 90 °.
  • fuel inlet holes 14 are made in the wall of the body 1 of the pump, at a predetermined distance below the inlet ports 4.
  • the holes 14 and the ports 4 are connected to a relatively low pressure fuel source.
  • the distance, in the axial direction of the piston, between the inlet orifices 4 and the inlet holes 14, the distance between the upper surface 15 of the piston 2, on the one hand, and the edges of the two grooves 5 and 9 , on the other hand, as well as the axial height of the flange 13 and the width of the second groove 9 are chosen to ensure the specific operating steps of the pump shown in FIGS. 1 to 4.
  • the intake chamber 3 communicates with the inlet orifices 4, which allows the filling of the chamber 3 with fuel.
  • the piston 2 By moving upwards, that is to say towards its top dead center position, the piston 2 reaches the position illustrated in FIG. 2, in which it begins to close the inlet orifices 4. Since the flange 13 is located opposite the holes for inlet 14 and closes these, no more communication exists between the chamber 3 and a low pressure fuel inlet conduit. This is the start of fuel delivery to the injector in the direction of arrow F1. This beginning of repression is designated in Figure 6 by the letter A.
  • the position of the bottom dead center of the piston 2 relative to the movement of the piston of the engine cylinder is chosen such that the start A of the first phase of injection into the engine cylinder is sufficiently advanced relative to the top dead center of the piston of said engine cylinder so that this first injection can constitute a pre-injection ensuring ignition ? in the combustion chamber of an engine cylinder, the amount of main injection combustion, with practically no ignition delay.
  • the start of preinjection could take place at a time corresponding to an angle of rotation of approximately -30 ° from the crankshaft, before the top dead center of the engine piston and the main injection could be triggered at an angle of about -15 °.
  • these values are given only by way of example.
  • the effect of the pre-injection varies as a function of the speed of rotation of the engine.
  • the illustration of the first repression phase that is to say the pre-injection repression, in the form of a rectangle according to FIG. 6, corresponds to the phenomena which actually occur.
  • the delivery and the pre-injection take on the form of a shower, because the establishment of the relatively high pressure inside the chamber 3 during the delivery of fuel out of the chamber and the drop in pressure in the chamber due to the communication between the latter and the inlet holes 14 require a certain period of time, since the inlet orifices 4 and the inlet holes 14 have cross sections of limited value.
  • the upper and lower edges 10, 11 of the second groove 9 are straight and circular. However, it is possible to configure at least one edge, for example the upper edge, at least partially in a helical ramp. This would make it possible to vary the instant of the end of the pre-injection delivery (B in FIG. 6), by rotation of the piston 2 around its longitudinal axis. An appropriate configuration of the lower edge of the groove 9 would make it possible to modify the start of the main injection delivery (C).
  • FIGS. 2 to 5 comprises a circular groove 9 and twice two inlet holes 14, and this in order to reduce the height of the groove 9 and the diameters of said holes 14, because these two dimensions decide the distance between B and C in Figure 6, that is to say the time of the pre-injection compared to the main injection, on the one hand, and the lifting of the cam corresponding to this period, d 'somewhere else.
  • These measures make it possible to reduce the length of the inactive part, that is to say without the piston stroke being pushed back, advance the start of the main injection delivery and / or delay the start of the pre-injection delivery.
  • FIGS. 7 and 8 show another embodiment of the injection pump according to the invention, in which the inlet holes 14 ′ - two in number in the example shown - are located approximately at the same level as the orifices inlet 4.
  • Two grooves 9 ' which function corresponds to that of the circular groove 9 of the first embodiment are formed in the peripheral surface of the piston, at a predetermined distance from the upper surface 15 of the piston, substantially parallel to that -this.
  • each groove 9 ' opens at one end into a vertical groove 8 and thus communicates, permanently, with the interior of the intake chamber 3.
  • each groove could be in communication with this chamber by its two ends.
  • the operation of this embodiment is the same, in principle, as that illustrated in FIGS. 1 to 4.
  • the pre-injection delivery begins when the orifices 4 are closed by the piston.
  • the inlet holes 14 ' are closed by the part of the peripheral surface 13' of the piston which is located above the grooves 9 '. This discharge is finished at the moment when the grooves 9 'come opposite the holes 14'.
  • the main injection delivery begins after the holes 14 'are closed by the peripheral surface of the piston located below the grooves 9' and ends when the ramp 7 discovers the orifices 4.
  • the injection pump according to the present invention also comprises means which allow the variation of the start of the pre-injection delivery. These means are formed by an accumulator device.
  • the accumulator comprises an accumulator chamber 16 in which is mounted a piston 17 movable against a return spring 18.
  • the chamber 16 communicates permanently with the chamber inlet 3 of the injection pump through a passage 19 which opens into the chamber 3 at a level above the top dead center of the piston.
  • the rear part 20 of the chamber, which houses the spring 18, is in permanent communication with the space 21 from which the inlet orifices leave. This ensures that a relatively low pressure acts on the rear face of the piston 17.
  • the stroke of the piston 17 is limited by a stop 22 formed for example by a shoulder of the wall of the chamber 16.
  • the piston 17 is movable over a length e.
  • the stop 22 is shaped as a sealed seat to produce a sealing barrier between the chamber 16 and the part 20 of the chamber containing the spring 18, when the piston is pushed against the stop under the effect of the high pressure prevailing in chamber 3 of the pump and chamber 16,, during the delivery of fuel to the injector.
  • This accumulator operates as follows: When after closing the inlet orifices 4, the piston 2 continues its upward stroke, the pressure inside the receiving chamber 3 increases only slowly since the decrease in the volume of the receiving chamber 3 is compensated by an increase in the volume of the accumulating chamber 16 because the piston 17 moves back under the effect of the increase in the pressure. Consequently, the pressure which is necessary for the opening of the discharge valve 23 can only be established after the piston has come into contact on its sealed seat stop 22. This means that point A, in the figure 6, moves to point B and the amount of pre-injection fuel delivered decreases. On the other hand, the interruption of the discharge at point B is independent of the accumulator and determined only by the communication of the additional holes 14 and the throat 9 of interruption of the discharge. Although the pressure inside the chamber 3 falls, it remains however, due to the piston which continues its upward stroke, at a value sufficient for the maintenance on its seat of the piston 17 of the accumulator.
  • the accumulator has no influence on the start of the main injection delivery, but makes it possible to vary the start of the pre-injection delivery (point A in FIG. 6), and thus the quantity of the pre-injection fuel.
  • FIGS 7 and 8 illustrate two embodiments of the accumulator 15 according to the invention.
  • the accumulator is placed next to the device forming a discharge member 23, above the inlet chamber 3 of the injection pump.
  • the accumulator is perfectly incorporated into the structure of the pump.
  • the accumulator shown in Figure 11 is made to allow adjustment of the outside of the start of the pre-injection delivery.
  • a rod 24 is fixed to the rear face of the piston 17. The free end of said rod comes out of the pump. Rod 24 can be controlled from outside the pump, which makes it easy to vary the final position of the piston 17. It is also possible to deactivate the pre-injection.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP80400720A 1979-05-28 1980-05-22 Einspritzpumpe für Brennkraftmaschine Expired EP0020249B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR7913486A FR2457987A1 (fr) 1979-05-28 1979-05-28 Pompe d'injection pour un moteur a combustion interne
FR7913486 1979-05-28
FR8011046 1980-05-16
FR8011046A FR2482669A2 (fr) 1979-05-28 1980-05-16 Perfectionnement a une pompe d'injection pour un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0020249A1 true EP0020249A1 (de) 1980-12-10
EP0020249B1 EP0020249B1 (de) 1984-08-22

Family

ID=26221181

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80400720A Expired EP0020249B1 (de) 1979-05-28 1980-05-22 Einspritzpumpe für Brennkraftmaschine

Country Status (12)

Country Link
US (1) US4426198A (de)
EP (1) EP0020249B1 (de)
JP (1) JPS55161958A (de)
KR (1) KR840001289B1 (de)
AU (1) AU544751B2 (de)
CS (1) CS243455B2 (de)
DD (1) DD151205A5 (de)
DE (1) DE3069004D1 (de)
ES (1) ES491946A0 (de)
FR (1) FR2482669A2 (de)
PL (1) PL136603B1 (de)
YU (1) YU42508B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2504203A1 (fr) * 1981-04-16 1982-10-22 Semt Pompe d'injection pour moteur a combustion interne comprenant un dispositif de reglage de l'instant de refoulement du combustible d'injection
FR2582355A1 (fr) * 1985-05-24 1986-11-28 Orbital Eng Pty Perfectionnements aux appareils d'alimentation en carburant des moteurs a combustion interne
FR2612569A1 (fr) * 1987-03-21 1988-09-23 Volkswagen Ag Injecteur-pompe
FR2630166A1 (fr) * 1988-04-18 1989-10-20 Hatz Motoren Pompe d'injection de carburant pour moteurs a combustion interne a pre-injection
EP0363088A1 (de) * 1988-10-06 1990-04-11 LUCAS INDUSTRIES public limited company Pumpe
FR2649758A1 (fr) * 1989-07-14 1991-01-18 Daimler Benz Ag Pompe d'injection de carburant commandee par chants inclines, pour moteurs a combustion interne

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL131829B1 (en) * 1982-01-18 1985-01-31 Wyzsza Szkola Inzynierska Gagari Surgical strut for treating spine anomalies
DE3307828A1 (de) * 1983-03-05 1984-09-06 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen
DE3307826A1 (de) * 1983-03-05 1984-09-06 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen
DE3330774A1 (de) * 1983-08-26 1985-03-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung mit vor- und haupteinspritzung bei brennkraftmaschinen
DE3424989C2 (de) * 1984-07-06 1994-09-29 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
JPS6137462U (ja) * 1984-08-09 1986-03-08 株式会社ボッシュオートモーティブ システム 燃料噴射ポンプ
CH667899A5 (de) * 1985-10-18 1988-11-15 Sulzer Ag Brennstoffeinspritzvorrichtung fuer eine dieselbrennkraftmaschine.
CH671073A5 (de) * 1986-09-09 1989-07-31 Nova Werke Ag
DE4029159A1 (de) * 1990-01-03 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung fuer einspritzbrennkraftmaschinen
DE4022226A1 (de) * 1990-07-12 1992-01-16 Man Nutzfahrzeuge Ag Brennstoffeinspritzvorrichtung fuer luftverdichtende brennkraftmaschinen
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
US5133645A (en) * 1990-07-16 1992-07-28 Diesel Technology Corporation Common rail fuel injection system
DE4105168A1 (de) * 1990-12-10 1992-06-11 Man Nutzfahrzeuge Ag Einspritzsystem fuer luftverdichtende brennkraftmaschinen
DE4106813A1 (de) * 1991-03-04 1992-09-10 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4137072A1 (de) * 1991-11-12 1993-05-13 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0962648A1 (de) * 1998-06-04 1999-12-08 Wolfgang Dr. Heimberg Kraftstoffeinspritzvorrichtung
US6799602B2 (en) * 2001-12-28 2004-10-05 Visteon Global Technologies, Inc. Combination fitting
EP1612394B1 (de) * 2004-06-30 2011-04-27 C.R.F. Società Consortile per Azioni Kraftstoffeinspritzsystem für Brennkraftmaschine mit common rail
KR100992227B1 (ko) * 2008-10-27 2010-11-05 현대중공업 주식회사 디젤엔진 연료분사펌프의 캐비테이션 손상방지장치

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE572711C (de) * 1931-07-03 1933-03-22 Maschf Augsburg Nuernberg Ag Brennstoffpumpe
DE585014C (de) * 1932-06-22 1933-09-27 Robert Bosch Akt Ges Einspritzpumpe fuer Brennkraftmaschinen mit Voreinspritzung
FR838688A (fr) * 1937-11-25 1939-03-13 Andre Citroe N Dispositif d'injection à injection franctionnée
DE689545C (de) * 1933-02-17 1940-03-27 Bosch Gmbh Robert ffmenge bei Fahrzeugdieselmotoren
US2237347A (en) * 1938-11-30 1941-04-08 Borg Warner Pump control
GB571485A (en) * 1942-09-16 1945-08-27 Bendix Aviat Corp Improvements in or relating to fuel injection apparatus
GB641575A (en) * 1948-01-03 1950-08-16 Cav Ltd Improvements relating to liquid fuel injection pumps
FR1037219A (fr) * 1950-05-24 1953-09-15 Cav Ltd Pompe à injection de combustible pour moteurs à combustion interne
DE923400C (de) * 1941-04-03 1955-02-10 Versuchsanstalt Fuer Luftfahrt Regelung der Kraftstoffmenge von Einspritzbrennkraftmaschinen nach dem Otto-Verfahren bei aufgeteilter Einspritzung
US2713310A (en) * 1951-11-20 1955-07-19 Cav Ltd Liquid fuel injection pumps
US2810375A (en) * 1953-04-13 1957-10-22 Nordberg Manufacturing Co Injection pump for internal combustion engines
US3792692A (en) * 1972-03-22 1974-02-19 Teledyne Ind Fuel injection device
DE2501764A1 (de) * 1975-01-17 1976-07-22 Guenther Kuske Brennstoffeinspritzelement mit zwischenabsteuerung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5221639Y2 (de) * 1973-07-18 1977-05-18
JPS50157721A (de) * 1974-06-10 1975-12-19
JPS525391Y2 (de) * 1974-10-03 1977-02-03

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE572711C (de) * 1931-07-03 1933-03-22 Maschf Augsburg Nuernberg Ag Brennstoffpumpe
DE585014C (de) * 1932-06-22 1933-09-27 Robert Bosch Akt Ges Einspritzpumpe fuer Brennkraftmaschinen mit Voreinspritzung
DE689545C (de) * 1933-02-17 1940-03-27 Bosch Gmbh Robert ffmenge bei Fahrzeugdieselmotoren
FR838688A (fr) * 1937-11-25 1939-03-13 Andre Citroe N Dispositif d'injection à injection franctionnée
US2237347A (en) * 1938-11-30 1941-04-08 Borg Warner Pump control
DE923400C (de) * 1941-04-03 1955-02-10 Versuchsanstalt Fuer Luftfahrt Regelung der Kraftstoffmenge von Einspritzbrennkraftmaschinen nach dem Otto-Verfahren bei aufgeteilter Einspritzung
GB571485A (en) * 1942-09-16 1945-08-27 Bendix Aviat Corp Improvements in or relating to fuel injection apparatus
GB641575A (en) * 1948-01-03 1950-08-16 Cav Ltd Improvements relating to liquid fuel injection pumps
FR1037219A (fr) * 1950-05-24 1953-09-15 Cav Ltd Pompe à injection de combustible pour moteurs à combustion interne
US2713310A (en) * 1951-11-20 1955-07-19 Cav Ltd Liquid fuel injection pumps
US2810375A (en) * 1953-04-13 1957-10-22 Nordberg Manufacturing Co Injection pump for internal combustion engines
US3792692A (en) * 1972-03-22 1974-02-19 Teledyne Ind Fuel injection device
DE2501764A1 (de) * 1975-01-17 1976-07-22 Guenther Kuske Brennstoffeinspritzelement mit zwischenabsteuerung

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2504203A1 (fr) * 1981-04-16 1982-10-22 Semt Pompe d'injection pour moteur a combustion interne comprenant un dispositif de reglage de l'instant de refoulement du combustible d'injection
EP0063523A1 (de) * 1981-04-16 1982-10-27 Societe D'etudes De Machines Thermiques S.E.M.T. Einspritzpumpe für Brennkraftmaschinen mit einer Regeleinrichtung zum Steuern des Kraftstofförderzeitpunkts
US4705006A (en) * 1981-04-16 1987-11-10 Dirk Bastenhof Fuel injection pump for an internal combustion engine comprising a device for adjusting the instant of injection fuel delivery
FR2582355A1 (fr) * 1985-05-24 1986-11-28 Orbital Eng Pty Perfectionnements aux appareils d'alimentation en carburant des moteurs a combustion interne
FR2612569A1 (fr) * 1987-03-21 1988-09-23 Volkswagen Ag Injecteur-pompe
FR2630166A1 (fr) * 1988-04-18 1989-10-20 Hatz Motoren Pompe d'injection de carburant pour moteurs a combustion interne a pre-injection
EP0363088A1 (de) * 1988-10-06 1990-04-11 LUCAS INDUSTRIES public limited company Pumpe
FR2649758A1 (fr) * 1989-07-14 1991-01-18 Daimler Benz Ag Pompe d'injection de carburant commandee par chants inclines, pour moteurs a combustion interne
GB2235955A (en) * 1989-07-14 1991-03-20 Daimler Benz Ag Sloping-edge-controlled fuel injection pump for internal combustion engines
GB2235955B (en) * 1989-07-14 1993-08-04 Daimler Benz Ag Sloping-edge-controlled fuel injection pump for internal combustion engines

Also Published As

Publication number Publication date
DE3069004D1 (en) 1984-09-27
JPS55161958A (en) 1980-12-16
CS243455B2 (en) 1986-06-12
KR840001289B1 (ko) 1984-09-07
CS375080A2 (en) 1985-08-15
FR2482669A2 (fr) 1981-11-20
EP0020249B1 (de) 1984-08-22
FR2482669B2 (de) 1984-07-06
KR830003002A (ko) 1983-05-31
US4426198A (en) 1984-01-17
YU42508B (en) 1988-10-31
ES8103592A1 (es) 1981-03-16
AU544751B2 (en) 1985-06-13
AU5882880A (en) 1980-12-04
JPH0214542B2 (de) 1990-04-09
YU142580A (en) 1983-01-21
DD151205A5 (de) 1981-10-08
PL136603B1 (en) 1986-03-31
PL224562A1 (de) 1981-02-27
ES491946A0 (es) 1981-03-16

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