US3677256A - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine Download PDF

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Publication number
US3677256A
US3677256A US67173A US3677256DA US3677256A US 3677256 A US3677256 A US 3677256A US 67173 A US67173 A US 67173A US 3677256D A US3677256D A US 3677256DA US 3677256 A US3677256 A US 3677256A
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Prior art keywords
fuel
piston
engine
injection
deducting
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Expired - Lifetime
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US67173A
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English (en)
Inventor
Marcel Regneault
Maurice Le Creurer
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Automobiles Peugeot SA
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Automobiles Peugeot SA
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    • 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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure

Definitions

  • the present invention relates to fuel injection devices for pressure ignited internal combustion engines.
  • the object of the present invention is to provide means for achieving the same result in the case of an injection device having pumps in line.
  • An assembly in line or series having injection pumps comprises a cylinder in which is received a piston whose reciprocating motion is usually controlled by a cam.
  • the chamber defined by the cylinder communicates, first, by way of at least one supply orifice, with a source such as a fuel feed pump and, secondly, with an injection pipe connected to an injector.
  • a source such as a fuel feed pump
  • an injection pipe connected to an injector.
  • means are provided for regulating the amount of fuel injected for each delivery stroke in accordance with the load and speed of operation of the engine.
  • These means may comprise a governor which adjusts, through a simple mechanism, the angular position of the piston.
  • the latter has on its periphery a helical groove which determines the end of the injection when it faces the supply orifices. It will be understood that a modification of the orientation of the piston results in a modification of the total amount of fuel injected.
  • the invention provides a fuel injection device for a pressure-ignited internal combustion engine of the type having in line or series injection pumps, said device comprising in each piston-cylinder assembly of the pump complementary means adapted to cooperate in at least one given angular position and in at least one part of the delivery stroke of the piston so as to deduct a part of the fuel displaced in the course of said delivery stroke.
  • said complementary means comprise a cavity which is formed in the lateral wall of the piston and communicates with the delivery chamber of the pump and a constricted passage in the wall of the delivery chamber.
  • This improvement enables the fuel injection law to be substantially modified for given conditions of operation of the engine.
  • the piston when the piston is in an angular position in which the cavity formed in its lateral wall and the calibrated orifice are disposed in facing relation to each other, a part of the fuel delivery is deducted or taken off.
  • the deduction of fuel is compensated by prolonging the duration of the injection.
  • the engine thus receives the required amount of fuelbut the injection of this amount is efi'ected in accordance with a law which is such that the combustion is controlled under better conditions and is less brutal 50 that the engine is more flexible and silent in operation.
  • FIG. 1 is a diagrammatic sectionalview of a part of an injection device according to the invention
  • FIG. 2 is a sectional view of the injection pump of this device taken along line 2-2 of FIG. 1
  • FIG. 3 is a perspective view of the piston of the pump shown in FIGS. 1 and 2
  • FIGS. 4a, 4b, 4c are three diagrams representing respectively a conventional injection law and two laws obtained in accordance with the invention
  • FIGS. 5, 6, and 7 are views of a modification of the invention which correspond to FIGS. 1, 2, and 3 respectively
  • FIG. 8 is a partial axial sectional view of a modification of the injection pump
  • FIG. 9 is a side elevational view of the piston of the pump shown in FIG. 8
  • FIG. 10 is a diagram representing the injection law obtained with the device shown in FIGS. 8 and 9
  • FIGS. 11 and 12 are two views, corresponding respectively to those of FIGS. 8 and 9, of a modification of the invention
  • FIG. 13 is a diagrammatic sectional view of another embodiment of the device according to the invention.
  • FIGS. 14 and 15 are two partial sectional views of two other modifications of the injection pump.
  • the part of the invention device shown in FIG. 1 comprises an injection pump P and an injector I connected to the pump by an injection conduit c.
  • the other component parts of this device necessary for a comprehension of the invention have not been shown.
  • the pump P has a body 1 in which is provided a chamber 2 connected to the outlet of a fuel supply pump (not shown).
  • the pump I receives a cylinder 3 provided with a first orifice 4 having a relatively large section and a second orifice 5 which has a small or constricted section 5a constituting a jet, and a larger section 5b.
  • the body 1 receives a bushing 6 defining a seat 6a for a valve 7 and a plug 8 which maintains the cylinder and bushing in position and aflords a support face for a spring 9 which biases the valve 7 against the seat 60.
  • the plug 8 constitutes a connection for the injection conduit c.
  • the cylinder 3 receives a piston I0, shown in perspective in FIG. 3.
  • a very small clearance is provided between the piston and the cylinder.
  • the piston 10 has a head 10a in which is formed a cavity 10b defined by a ramp having a roughly helical profile. This cavity communicates with the upper face of the piston by way of a longitudinal recess 11 known as a stop recess.
  • a longitudinal recess 11 known as a stop recess.
  • Formed in the lateral face of the head 10a of the piston is an additional cavity constituted, in the embodiment shown in FIGS. I to 3, by a recess 12 having a roughly constant depth and a height h which is adapted, as will be described hereinafter in detail, to cooperate with the jet 5.
  • the cylinder 3 and the piston 10 define a delivery chamberl3.
  • the piston 10 is shifted by a camshaft through a pushrod. These members have not been shown in the drawing.
  • the piston 10 can be shifted angularly by a rack 14 whose movement in translation is controlled by a governor. The latter is responsive to the load and the speed of operation of the engine.
  • the resulting angular movement of the piston determines, owing to the effect of the profile of the ramp 10c, the part of the stroke of the piston during which the fuel is delivered to the injector.
  • the injection device just described operates in the following manner:
  • FIGS. 40 to 40 represent, with respect to time, the amount of fuel injected under identical conditions of load and speed of the engine, first, in the case of a conventional injection pump (FIG. 4a) and, secondly, in the case of two improved pumps according to the invention (FIGS. 4b and 4c).
  • the segment ab 1 corresponds to the rising of the needle valve of the injector, the segment be to the normal injection and the segment cd to the return of the needle to its seat.
  • the total duration of the injection corresponds to the length ad and the total amount of fuel injected corresponds to the cross-hatched area of the trapezium abcd;
  • the diagram shown in FIG. 4b represents the injection law in the case where the height h of the recess 12 is less than the delivery stroke of the piston 10.
  • the part 0,, b,, c, corresponds to the reduced injection with a controlled escape of a part of the fuel through the jet 5.
  • the segment c d corresponds to the closure of the jet and the segment d e to normal injection with a flow equal to that of the pump.
  • the height h of the recess 12 is at least equal to the effective delivery stroke of the piston for a given selected angular position of the latter, so that the controlled escape-of the fuel through the jet 5 occurs throughout the period a d of the injection and the injected flow is at each instant equal to the difference between the flow of the pump (shownby the dotted line a b 'c 'd and the escape flow.
  • the duration a,d is therefore longer than the corresponding duration a l, of the preceding case, so that the total amount of fuel injected is unchanged.
  • the function performed by the stop recess 11 and the supply orifice 4 cannot be compared with the function of the recess 12 and the jet 5. Indeed, when the recess 1 l is brought into alignment with the orifice 4 when the engine is stopped, the pressure in the delivery chamber 13 is too weak to open the valve 7 and all the fuel displaced is discharged to the supply chamber 2. On the other hand, when the recess 12 and the jet 5 are in facing relation, owing to the small section of this jet, the pressure established in the chamber 13 is sufficient to open the valve 7 and result in the supply of fuel to the injector I.
  • the modification of the invention shown in FIGS. 5 to 7 differs from the embodiment just described only in respect of the shape of the cavity on the periphery of the head of the piston.
  • the piston of this modification carries the reference numeral 15 and the cavity is constituted by a recess having a greater circumferential extent, the depth of the recess varying.
  • the depth of the recess in the region of the jet 5 is maximum for the position of the piston corresponding to an idling engine or an engine under low load, and decreases progressively when the piston is shifted angularly in response to an increased engine speed or load and finally becomes nil after a given rotation of the piston.
  • FIGS. 8 and 9 are detail views of another modification of the invention also concerning the construction of the piston of the injection pump.
  • the cavity on the periphery of the piston 16 does not directly communicate with the delivery chamber 13.
  • This cavity is formed by an oblong recess 16:: which is separated from the delivery chamber by a bearing portion 16b and the inner end of the recess is connected to the delivery chamber through two passages 16c, 16d which extend radially and axially respectively.
  • This arrangement afiords an injection law which differs from those described hereinbefore and is represented in FIG. 10.
  • the piston starts to deliver fuel to the injector and the pressure established is sufficient to produce the injection.
  • This corresponds to the part a b of the diagram shown in FIG. 10.
  • the recess 16a comes in front of the orifice 5, a part of the fuel is transferred to the supply chamber 2 and a pressure drop occurs in the injection circuit which is such that injection ceases.
  • This phase corresponds to the part b c d of the diagram.
  • FIGS. 11 and 12 differs from that just described only in that the recess 17a formed in the piston 17 has a circumferential extent exeeding that of the recess 16a of the preceding embodiment. This arrangement also results in a double injection similar to that represented in FIG. 10.
  • FIG. 13 is more complex and in which the piston of the injection pump, designated by the reference numeral 18, may be identical to one of the previously described pistons 10, 15, 16, and 17. It is illustrated as being identical to the piston 10 andconsequently has a recess 18a which opens into the delivery chamber 13.
  • a fuel deducting device D comprising a body- 19 which is screwthreadedly engaged in the body of the pump and has a cylindrical portion 20 engaged in a fiuidtight manner in a cavit y 21 in the cylinder 3.
  • a sealing element 22 affords a seal between the cylindrical portion 20 and the cavity 21.
  • a screwthreaded connection 26 connects the device D of each pump assembly with a conduit 27 connected to a common device D It is assumed that the engine equipped with the device according to the invention has four cylinders.
  • the conduit 27 is connected through a ball check-valve 28 to the supply chamber of the pump so as to ensure, between'each injection cycle, an equilibrium between the pressures of the supply chamber 2, the conduit 27 and the cylindrical cavities 23b so that any possible leakage is compensated.
  • the device D is similar to one of the auxiliary fuel deducting devices described in the US. Pat. No. 3,456,629 completed by a closing member 29 constituted by a key or a rotary member, for example actuated by the acceleration lever of the engine.
  • This closing member can be shifted by mechanical, hydraulic or electrical means as a function of at least one parameter of the operation of the engine.
  • the device D will not be described in detail. It will merely be mentioned that it comprises a piston 30 movable in opposition to the action of a spring 31.
  • the assembly shown in FIG. 13 operates in the following manner:
  • the recess 18a of the piston 18 faces the orifice 5
  • the closing member 29 of the device D is open, and the device is able to exert a modifying effect on the injection law of the pump in the following manner
  • the fuel discharged by the pump piston 18 from the chamber 13 is sent, on one hand, to the injector and, on the other hand, to the chamber 21 by way of the orifice 5 and causes both the opening of the injector and the shifting of the piston 24 off its seat 23a.
  • the volume of fuel displaced by the movement of the piston 24 causes the piston 30 of the device D to move so that the device can modify the injection law ofthe pump.
  • the helical ramp of the piston 18 opens or unmasks the supply orifice 4, results in a pressure relief in the chamber 13 and, under the effect of this relief, the injector and the valve, corresponding to the valve 7 shown in FIG. 1, close.
  • the piston 24 is no longer exposed to pressure, it returns to its conical seat under the action of the spring 25.
  • the same is true of the piston 30 of the device D The fuel in the chamber 21 is returned to the chamber 13.
  • the injection is effected normally without being subjected to the effect of the flow modifying device.
  • This effect is eliminated, in accordance with the load, by the shifting of the recess 18 with respect to the orifice 5 and, in accordance with the engine speed, by the closure of the closing member 29.
  • FIG. 13 The injection device assembly shown in FIG. 13 can moreover be employed with the modifications shown in FIGS. 14 and 15, which will now be described.
  • the device D is replaced by a device D in which the fuel deducting chamber is a chamber 32 defined by an elastic bag 33.
  • the amount of fuel deducted in the course of each injection is absorbed by the elastic deformation of the bag of this chamber under the effect of the injection pressure.
  • FIG. 15 shows a device D in which the fuel deducting chamber is a chamber 34 having a movable wall formed by a membrane 35 which is subjected to the pressure of a compressrble fluid on the srde opposed to the chamber 34. This fluid is disposed in a chamber 36 which communicates with the atmosphere by way of a ball check-valve 37.
  • the amount of fuel deducted upon each injection is absorbed by the increase in the volume in the chamber 34 as a result of the deformation of the membrane 35, the fluid in the chamber 36 being compressed.
  • a fuel injection device for a pressure-ignited internal combustion engine having series injection pumps that is, in which each injection pump supplies fuel to one cylinder of the engine, said device comprising, in each piston and cylinder assembly of the injection pump, complementary means adapted to cooperate in at least one given angular position of, and in at least one part of the delivery stroke of, the piston so as to define a discharge path for the fuel and deduct a part of the fuel displaced in the course of said delivery stroke, said device further comprising a first fuel deducting device having a varia- I ble capacity chamber defined by a piston for receiving said deducted fuel and a second fuel deducting device [said two fuel deducting devices being] connected in series relation with said first deducting device, and a closing member controlled in v accordance with a parameter of the operation of the engine such as the speed and/or the load of the engine to selectively allow and preclude communication between the two fuel deducting devices.
  • said second fuel deducting device comprises a variable-capacity chamber defined by a piston biased by elastically yieldable means.
  • the second fuel deducting device comprises a variable-capacity chamber defined by a membrane having a face which is opposed to said variable capacity chamber and subjected to the action of a compressible fluid.
  • said means comprises a cavity in a lateral wall of the piston, communicating with a delivery chamber of the pump and a throttling orifice in the wall of the delivery chamber, opening in said variable capacity chamber, said cavity being a recess which opens directly into said delivery chamber.
  • said means comprises a cavity in a lateral wall of the piston, communicating with a delivery chamber of the pump and a throttling orifice in the wall of the delivery chamber, opening in said variable capacity chamber, said cavity being a recess which is separated from said delivery chamber by a portion of said lateral wall of the piston, a conduit being formed in the piston between an inner end of said recess and said delivery chamber.

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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)
US67173A 1969-11-20 1970-08-26 Fuel injection device for an internal combustion engine Expired - Lifetime US3677256A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR6939888A FR2067883A5 (ja) 1969-11-20 1969-11-20

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US67173A Expired - Lifetime US3677256A (en) 1969-11-20 1970-08-26 Fuel injection device for an internal combustion engine

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US (1) US3677256A (ja)
JP (1) JPS4826090B1 (ja)
AT (1) AT314906B (ja)
DE (1) DE2045556C3 (ja)
FR (1) FR2067883A5 (ja)
GB (1) GB1326074A (ja)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3929113A (en) * 1973-05-07 1975-12-30 Diesel Kiki Co Fuel injection pump
US4073275A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump
US4271807A (en) * 1978-01-25 1981-06-09 Robert Bosch Gmbh Pump/nozzle for internal combustion engines
US4448167A (en) * 1981-08-01 1984-05-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4526149A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4526150A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4681080A (en) * 1984-11-23 1987-07-21 A V L Gesellschaft fur Verbrennungskraftmaschinen und Messtechnik mbh Prof. Dr.Dr. h.c. Hans List Device for the temporary interruption of the pressure build-up in a fuel injection pump
US4881506A (en) * 1987-06-10 1989-11-21 Kloeckner-Humboldt-Deutz Ag Injection pump with preinjection
US5029568A (en) * 1990-01-10 1991-07-09 Cummins Engine Company, Inc. Injection rate control injector
US5209208A (en) * 1989-08-08 1993-05-11 Robert Bosch Gmbh Fuel injection pump for diesel internal combustion engines
US5315978A (en) * 1992-03-25 1994-05-31 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Fuel injection system
EP0971123A3 (de) * 1998-07-10 2001-04-18 L'orange Gmbh Kraftstoffeinspritzpumpe
US20020168274A1 (en) * 2001-04-02 2002-11-14 Anthony Williams Fuel system
US20040079818A1 (en) * 2001-07-07 2004-04-29 Michael Lindner Fuel supply system for internal combustion engines

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ZA795088B (en) * 1978-11-17 1980-09-24 Lucas Industries Ltd Fuel injection nozzles
DE2855539A1 (de) * 1978-12-22 1980-07-03 Daimler Benz Ag Pumpe - duese fuer luftverdichtende einspritzbrennkraftmaschinen
EP0027790A1 (de) * 1979-10-15 1981-04-29 Friedmann & Maier Aktiengesellschaft Einspritzpumpe
DE3044254A1 (de) * 1980-11-25 1982-06-24 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg Brennstoffeinspritzvorrichtung fuer brennkraftmaschinen
DE3310049A1 (de) * 1983-03-19 1984-09-20 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung zur einspritzung einer aus mindestens zwei komponenten bestehenden kraftstoffmischung
DE3444234A1 (de) * 1984-01-11 1985-07-18 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
GB2160595A (en) * 1984-06-19 1985-12-24 Zahnradfabrik Friedrichshafen Reciprocating pump
US4674461A (en) * 1984-10-02 1987-06-23 Diesel Kiki Co., Ltd. Unit injector for internal combustion engines
AT407429B (de) * 1986-04-01 2001-03-26 Friedmann & Maier Ag Einspritzpumpe für brennkraftmaschinen
DE3624092C2 (de) * 1986-07-17 1998-01-29 Guenter Stein Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US4811715A (en) * 1987-11-02 1989-03-14 Stanadyne, Inc. Electronic unit injector
US5033443A (en) * 1988-06-27 1991-07-23 Nippondenso Co., Ltd. Pilot injection device for fuel injection pump
US5144925A (en) * 1990-02-21 1992-09-08 Automotive Diesel Gesellschaft M.B.H. Fuel injection device for fuel-injected internal combustion engines
DE4225803A1 (de) * 1992-08-05 1994-02-10 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE4443860B4 (de) * 1994-12-09 2004-05-13 Robert Bosch Gmbh Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Citations (6)

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Publication number Priority date Publication date Assignee Title
US1993759A (en) * 1932-06-21 1935-03-12 Bosch Robert Fuel injection pump
US2565681A (en) * 1945-11-01 1951-08-28 Caterpillar Tractor Co Fuel injection for internal combustion engines
US2575955A (en) * 1947-07-10 1951-11-20 James W Hatch Fuel injection pump
GB725585A (en) * 1952-06-23 1955-03-09 Burmeister & Wain S Maskin & S Improvements in and relating to fuel injection systems in internal combustion engines
US2794397A (en) * 1952-04-19 1957-06-04 Bosch Arma Corp Fuel injection pump
US3456629A (en) * 1966-08-01 1969-07-22 Peugeot Fuel injection devices for compression ignited internal combustion engines

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1993759A (en) * 1932-06-21 1935-03-12 Bosch Robert Fuel injection pump
US2565681A (en) * 1945-11-01 1951-08-28 Caterpillar Tractor Co Fuel injection for internal combustion engines
US2575955A (en) * 1947-07-10 1951-11-20 James W Hatch Fuel injection pump
US2794397A (en) * 1952-04-19 1957-06-04 Bosch Arma Corp Fuel injection pump
GB725585A (en) * 1952-06-23 1955-03-09 Burmeister & Wain S Maskin & S Improvements in and relating to fuel injection systems in internal combustion engines
US3456629A (en) * 1966-08-01 1969-07-22 Peugeot Fuel injection devices for compression ignited internal combustion engines

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3929113A (en) * 1973-05-07 1975-12-30 Diesel Kiki Co Fuel injection pump
US4073275A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump
US4271807A (en) * 1978-01-25 1981-06-09 Robert Bosch Gmbh Pump/nozzle for internal combustion engines
US4448167A (en) * 1981-08-01 1984-05-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4526149A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4526150A (en) * 1983-03-05 1985-07-02 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4681080A (en) * 1984-11-23 1987-07-21 A V L Gesellschaft fur Verbrennungskraftmaschinen und Messtechnik mbh Prof. Dr.Dr. h.c. Hans List Device for the temporary interruption of the pressure build-up in a fuel injection pump
US4881506A (en) * 1987-06-10 1989-11-21 Kloeckner-Humboldt-Deutz Ag Injection pump with preinjection
US5209208A (en) * 1989-08-08 1993-05-11 Robert Bosch Gmbh Fuel injection pump for diesel internal combustion engines
US5029568A (en) * 1990-01-10 1991-07-09 Cummins Engine Company, Inc. Injection rate control injector
US5315978A (en) * 1992-03-25 1994-05-31 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Fuel injection system
EP0971123A3 (de) * 1998-07-10 2001-04-18 L'orange Gmbh Kraftstoffeinspritzpumpe
US20020168274A1 (en) * 2001-04-02 2002-11-14 Anthony Williams Fuel system
US6648610B2 (en) * 2001-04-02 2003-11-18 Delphi Technologies, Inc. Fuel injection system with structurally biased relief valve
US20040079818A1 (en) * 2001-07-07 2004-04-29 Michael Lindner Fuel supply system for internal combustion engines
US7143965B2 (en) * 2001-07-07 2006-12-05 Robert Bosch Gmbh Fuel supply for internal combustion engines

Also Published As

Publication number Publication date
FR2067883A5 (ja) 1971-08-20
AT314906B (de) 1974-04-25
DE2045556A1 (de) 1971-06-03
JPS4826090B1 (ja) 1973-08-06
DE2045556B2 (de) 1979-10-04
GB1326074A (en) 1973-08-08
DE2045556C3 (de) 1980-07-10

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