EP0020249B1 - Einspritzpumpe für Brennkraftmaschine - Google Patents

Einspritzpumpe für Brennkraftmaschine Download PDF

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Publication number
EP0020249B1
EP0020249B1 EP80400720A EP80400720A EP0020249B1 EP 0020249 B1 EP0020249 B1 EP 0020249B1 EP 80400720 A EP80400720 A EP 80400720A EP 80400720 A EP80400720 A EP 80400720A EP 0020249 B1 EP0020249 B1 EP 0020249B1
Authority
EP
European Patent Office
Prior art keywords
delivery
chamber
fuel
piston
injection
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
EP80400720A
Other languages
English (en)
French (fr)
Other versions
EP0020249A1 (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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=26221181&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0020249(B1) "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 present invention relates to an injection pump for an internal combustion engine of the type described in the preamble to the main claim.
  • a pump of this type is known from GB-A-571485.
  • This pump allows a quantity of pre-injection fuel to be discharged before the main injection fuel is discharged, but has the disadvantage of not allowing a variation in the start of the pre-injection discharge.
  • US-A-2 810 375 relates to an injection pump which makes it possible to vary the start of the delivery of fuel from the pump to the injector.
  • This device for varying the start of delivery includes a fuel accumulator chamber, in permanent communication with the intake chamber and of variable volume by a piston mounted movably in said accumulator chamber, against a return spring, under the effect of fuel pressure in the intake chamber.
  • the object of the present invention is to propose an injection pump which makes it possible to vary the start of the pre-injection delivery without influencing the start of the main injection delivery.
  • a rod is fixed to the rear face of the aforementioned piston and the free end of said rod is brought out of the pump structure to determine the length of the piston stroke.
  • the injection pump shown in FIGS. 1 to 5 comprises a cylindrical body 1 and a piston 2 mounted movably 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.
  • 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 intake chamber 3 and the groove 5.
  • the piston 2 is provided with a second circular groove 9, limited, in the example shown, at the top by a straight edge 10 and at the bottom 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. It should be noted that 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 opposite the inlet holes 14 and closes these, no more communication exists between the chamber 3 and a conduit low pressure fuel supply. This is the start of fuel delivery to the injector in the direction of arrow F1. This start of delivery is designated in FIG. 6 with the letter A.
  • the piston 2 arrives at the position shown in fig. 3, in which the upper edge 10 of the second circular groove 9 comes at the level of the lower edge of the inlet holes 14, which constitutes the start of the connection of these holes 14 and of the groove 9 and, at through the flats 12, of the groove 5 and of the groove 8, with the chamber 3.
  • This state is indicated in fig. 6 by the letter B.
  • This communication and because of it the low pressure inside the chamber 3 persist until the piston reaches the position shown in FIG. 4, in which the lower edge 11 of the groove 9 comes to the level of the upper edge of the inlet holes 14. These are closed by the cylindrical surface of the piston, which follows the groove 9.
  • the position of the bottom dead center of the piston 2 with respect 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 the ignition, in the combustion chamber of an engine cylinder, of the quantity of main injection combustion, practically without ignition delay.
  • the start of pre-injection could take place at an instant corresponding to an angle of rotation of about -30 ° of the crankshaft, before the top dead center of the driving piston and the main injection could be triggered at an angle d 'around -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 delivery phase that is to say the pre-injection delivery, in the form of a rectangle according to FIG. 6, corresponds to the phenomena that actually occur.
  • the delivery and the pre-injection take on the appearance of a bell, 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 partial 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).
  • the embodiment represented by 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 fig. 6, that is to say the time of the pre-injection with respect to the main injection, on the one hand, and the lifting of the cam corresponding to this period, on the other hand.
  • These measures make it possible to reduce the length of the inactive part, that is to say without the piston stroke being pushed back, to advance the start of the main injection delivery and / or to delay the start of the pre-injection delivery.
  • Figs 7 and 8 show another embodiment of the injection pump, in which the inlet holes 14 '- two in number in the example shown - are located approximately at the same level as the inlet orifices 4.
  • Two grooves 9 ' the function of which 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 the latter.
  • each groove 9 ' opens at one end in 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 starts 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 inlet chamber 3 of the injection pump by 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 due to the fact that the piston 17 moves back under the effect of the increase in 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 FIG . 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 of the groove 9 for interrupting 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 to maintain the piston 17 of the accumulator on its seat.
  • the accumulator has no influence on the start of the main injection delivery, but allows to vary the start of the pre-injection delivery (point A in fig. 6), and thus the quantity of the pre-injection fuel. .
  • Figs 10 and 11 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 fig. 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.
  • the rod 24 can be controlled from outside the pump, which makes it possible to easily vary the final position of the piston 17. It is also possible to deactivate the pre-injection.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (2)

1. Einspritzpumpe für einen Verbrennungsmotor zum Ausstoss einer Voreinspritzkraftstoffmenge vor dem Ausstoss des Kraftstoffs für die Haupteinspritzung, mit einer Brennstoffaufnahmekammer (3), die in einem zylindrischen Körper (1) ausgebildet ist und dessen Volumen durch die geradlinige Hin- und Herbewegung eines Kolbens (2) in diesem Körper verändert wird, wobei die Kammer (3) mit Öffnungen (4) zum Zufluss vom Kraftstoff versehen ist, die mit einer Kraftstoffquelle verhältnismässig niedrigen Drucks verbunden und durch den genannten Kolben (2) während dessen Bewegung zu seinem oberen Todpunkt hin verschliessbar sind, um den Ausstoss des Kraftstoffes aus der genannten Kammer (3) heraus zu erlauben, wobei der Kolben (2) einen Kopf mit wenigstens einer im allgemeinen das Ende des Ausstosses aus der Pumpe bestimmenden schraubenförmigen Rampe (7) und eine Nut (9) zur Unterbrechung des Ausstosses, die mit der genannten Kammer (3) in Verbindung steht, besitzt, wobei die Ausstossunterbrechung stattfindet, wenn diese Nut (9) in eine Stellung gegenüber wenigstens einer mit der genannten Kraftstoffquelle in Verbindung stehenden Durchführung (14) durch den genannten Körper (1) kommt, wobei die Durchführung (14) einen bestimmten Durchströmungsquerschnitt hat, dadurch gekennzeichnet, dass die Pumpe in an sich bekannter Weise eine Vorrichtung zur Veränderung des Beginnes des Ausstosses besitzt, die eine Brennstöffsammelkammer (16) aufweist, die ständig mit der Aufnahmekammer (13) in Verbindung steht und dessen Volumen durch einen Kolben (17) veränderlich ist, der in der genannten Kammer (16) entgegen einer Rückstellfeder (18) unter Bewirkung des Kraftstoffdruckes in der Aufnahmekammer (3) beweglich angebracht ist, und dass dieser Kolben (17) in dichter Weise auf einem Sitz (22) zur Auflage kommt, der einen Begrenzungsanschlag für den Hub des Kolbens (17) während der Voreinspritzung bildet, und auf diesem Sitz (22) unter Wirkung eines Druckes gehalten wird, der gleich dem Druck ist, der während der Ausstossunterbrechung von dem Kolben (2) der Pumpe hervorgerufen wird, wenn dieser seinen Aufwärtshub während der Unterbrechung fortsetzt, ohne den Beginn des Ausstosses für die Haupteinspritzung zu beeinflussen.
2. Einspritzpumpe nach Anspruch 1, dadurch gekennzeichnet, dass eine Stange (24) an der rückwärtigen Fläche des genannten Kolbens (17) befestigt ist, und dass das freie Ende der genannten Stange (24) aus der Struktur der Pumpe herausgeführt ist, um die Länge des Kolbenhubes zu bestimmen.
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
FR8011046A FR2482669A2 (fr) 1979-05-28 1980-05-16 Perfectionnement a une pompe d'injection pour un moteur a combustion interne
FR8011046 1980-05-16

Publications (2)

Publication Number Publication Date
EP0020249A1 EP0020249A1 (de) 1980-12-10
EP0020249B1 true 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) ES8103592A1 (de)
FR (1) FR2482669A2 (de)
PL (1) PL136603B1 (de)
YU (1) YU42508B (de)

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Publication number Priority date Publication date Assignee Title
FR2504203B1 (fr) * 1981-04-16 1985-05-31 Semt Pompe d'injection pour moteur a combustion interne comprenant un dispositif de reglage de l'instant de refoulement du combustible d'injection
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
DE3617241A1 (de) * 1985-05-24 1986-12-11 Orbital Engine Co. Pty. Ltd., Balcatta, Westaustralien Vorrichtung zur dosierung von brennstoff fuer eine verbrennungsmaschine
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
DE3807965C2 (de) * 1987-03-21 1994-08-25 Volkswagen Ag Pumpedüse
DE3812867A1 (de) * 1988-04-18 1989-10-26 Hatz Motoren Kraftstoff-einspritzpumpe fuer brennkraftmaschinen mit vor- und haupteinspritzung des kraftstoffes
GB8823453D0 (en) * 1988-10-06 1988-11-16 Lucas Ind Plc Pump
DE3923306A1 (de) * 1989-07-14 1991-01-24 Daimler Benz Ag Schraegkantengesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen
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
DE602004032429D1 (de) * 2004-06-30 2011-06-09 Fiat Ricerche Kraftstoffeinspritzsystem für Brennkraftmaschine mit common rail
KR100992227B1 (ko) * 2008-10-27 2010-11-05 현대중공업 주식회사 디젤엔진 연료분사펌프의 캐비테이션 손상방지장치

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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
JPS5221639Y2 (de) * 1973-07-18 1977-05-18
JPS50157721A (de) * 1974-06-10 1975-12-19
JPS525391Y2 (de) * 1974-10-03 1977-02-03
DE2501764A1 (de) * 1975-01-17 1976-07-22 Guenther Kuske Brennstoffeinspritzelement mit zwischenabsteuerung

Also Published As

Publication number Publication date
YU142580A (en) 1983-01-21
FR2482669A2 (fr) 1981-11-20
ES491946A0 (es) 1981-03-16
DE3069004D1 (en) 1984-09-27
JPH0214542B2 (de) 1990-04-09
CS243455B2 (en) 1986-06-12
AU544751B2 (en) 1985-06-13
PL136603B1 (en) 1986-03-31
JPS55161958A (en) 1980-12-16
AU5882880A (en) 1980-12-04
KR840001289B1 (ko) 1984-09-07
US4426198A (en) 1984-01-17
ES8103592A1 (es) 1981-03-16
FR2482669B2 (de) 1984-07-06
EP0020249A1 (de) 1980-12-10
KR830003002A (ko) 1983-05-31
DD151205A5 (de) 1981-10-08
YU42508B (en) 1988-10-31
PL224562A1 (de) 1981-02-27
CS375080A2 (en) 1985-08-15

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