US3779225A - Reciprocating plunger type fuel injection pump having electromagnetically operated control port - Google Patents

Reciprocating plunger type fuel injection pump having electromagnetically operated control port Download PDF

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Publication number
US3779225A
US3779225A US00260882A US3779225DA US3779225A US 3779225 A US3779225 A US 3779225A US 00260882 A US00260882 A US 00260882A US 3779225D A US3779225D A US 3779225DA US 3779225 A US3779225 A US 3779225A
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United States
Prior art keywords
port
relief port
pumping chamber
chamber
fuel
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Expired - Lifetime
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US00260882A
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English (en)
Inventor
E Watson
H Fuller
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Bendix Corp
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Bendix Corp
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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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically

Definitions

  • ABSTRACT [22] Filed; June 8 1972 A fuel injection system for an internal combustion engine of the type having a reciprocating piston pressure PP N04 260,882 pump that includes an electromechanically operated relief or control valve that is arranged so that the face [52 US. (:1. 123/139 E, 123/32 AE vaive is not subjected to the Pressurized fluid in 51 Int. Cl.
  • FIGURE 2 FIGURE 3 RECIPROCATING PLUNGER TYPE FUEL INJECTION PUMP HAVING ELECTROMAGNETICALLY OPERATED CONTROL PORT BACKGROUND OF THE INVENTION
  • This invention relates to an internal combustion engine fuel injection system of the type having a source of fuel, a fuel pump for pressu'rizing the fuel, and one or more injectors or nozzle assemblies for injecting fuel into the engine cylinders.
  • the invention is more particularly related to an improved pump of the type having a reciprocating piston for pressurizing fluid and a solenoid-operated control valve for controlling the amount of fluid dispensed by the pump.
  • Mechanical fuel injection systems for internal combustion engines generally include a fuel tank; the fuel pump that receives fuel from the tank and pressurizes the fuel; and one or more nozzle valve assemblies that receive the pressurized fuel and inject it into the engine cylinder.
  • the fuel pump which pressurizes the fuel to be supplied to the engine cylinders may be of the rotary or reciprocating piston or plunger type.
  • An example of a rotary injection fuel pump may be found in U.S. Pat. No. 3,489,091 entitled Rotary Distributor Pump, issued Jan. 13 1970 to P. Becker.
  • Examples of fuel injection pumps that operate on the principle of a reciprocating piston or plunger may be found in U.S. Pat. Nos. 2,922,581 entitled Fuel Injection Apparatusissued Jan. 26, 1960 to L. J. Garday; 3,146,715 entitled Fuel Injection Pump, issued Sept. 1, 1964 to G. J. Knudson; and 3,190,561 entitled Fuel Injector, issued June 22, 1965 to H. I. Fuller e
  • Fuel pumps of the reciprocating piston type generally include a housing; a piston mounted for reciprocating movement within the housing, the piston cooperatively linked to the crankshaft or camshaft of an internal combustion engine so that rotation of the camshaft causes reciprocation of the piston within the pump housing; and a pressure chamber, one wall of which is the face of the reciprocating piston, the pressure chamber having an inlet port, a relief (bypass) port and an injection port.
  • the piston includes a passageway (generally a groove or passage in the piston) that periodically links the pressure chamber to the relief port during the stroke of the piston.
  • the shape and arrangement of the passage and the piston are designed so that radial adjustment of the piston (by rotating the piston) from one position to another affects the periodic linking of the relief port to the pressure chamber, thereby controlling injection time and hence the volume of fuel injected into an engine cylinder. Therefore, the quantity of fuel injected into the engine is determined by radially adjusting (rotating) the reciprocating pistons which are mechanically linked to the camshaft of the engine. Because the piston is mechanically linked to the camshaft, the point in time at which fuel is injected into the engine cylinders is generally fixed with respect to the degree of rotation of the camshaft from a common reference point.
  • the reciprocating piston determines the beginning of the injection cycle, i.e., the piston starts the beginning of the injection cycle when it closes the inlet port and the piston begins to build up pressure in the pressure chamber until the pressure reaches a point that causes the injection port to be opened and fuel to be injected into the engine cylinder.
  • the reciprocating piston is mechanically linked to the engine camshaft or crankshaft so that the inlet port always closes when the camshaft reaches the same degree of rotation.
  • a common approach of making the closing of the inlet port vary with respect to the degree of rotation of the camshaft is to introduce a mechanical translator between the engine camshaft and the pump piston.
  • This invention provides a mechanical fuel injection control system that utilizes a reciprocating piston type fuel pump that is capable of varying the amount of fuel injected into the engine cylinder at fixed and/or at different speeds of rotation of the engine cam and/or crank-shaft.
  • the invention is a fuel injection pump for an internal combustion engine characterized by an electromechanically operated control or relief valve assembly (27) that is controlled independently of a reciprocating piston (31) in the pump that pressurizes the fluid.
  • the invention is also characterized by an electromechanical relief (control) valve (20) that has a valve face (23) that is not subject to the pressure in a pressure chamber so that the valve requires less electromechanical energy to open and close.
  • the fuel injection system for an internal combustion engine of the type having a camshaft comprises: a pump housing (I) having a pressure chamber (10) that communicates with an inlet passage (6), a relief passage (3) and an injection passage (15), the injection passage communicating with the engine; means for supplying fuel to the pumping chamber through said inlet passage; means for closing the injection passage (15), the closing means including biasing means (52), for keeping the injection passage closed until a predetermined fuel pressure is attained in the pumping chamber; means (30) responsive to the rotation of the engine camshaft or crank shaft for periodically pressurizing the fuel in the chamber (10) whereby fuel entering the chamber through the inlet passage periodically flows out of the pumping chamber through the relief (bypass) passage; and electro-mechanical valves means (27) operative to open and close the relief passage (3) at predetermined intervals in response to at least one operating parameter of the engine whereby each time the relief (bypass) passage (3) is closed and fuel is being pressurized, the fuel pressure in the pumping chamber attains a predetermined pressure level
  • FIG. 1 illustrates a fuel pump for an internal combustion engine that incorporates the principles of this invention.
  • FIG. 2 is an enlarged partial diagrammatic view showing the valve portion of the solenoid and the reciprocating plunger.
  • FIG. 3 is a diagrammatic top view of the pressure chamber taken along lines III--III in FIG. 2.
  • FIG. 1 illustrates a fuel injection pump ll of the type having a reciprocating piston assembly 30 for pressurizing the fuel in response to rotation of an internal combustion engine (not shown), a solenoid-operated relief or control valve assembly 27 that is controlled independently of the reciprocating piston assembly 30, and an injection or delivery valve assembly 50 that communicates with the engine cylinder.
  • the reciprocating piston assembly 30 comprises: a can follower 32 that follows the camshaft or crankshaft of an internal combustion engine (not shown); a spring assembly 33 which maintains the cam follower 32 in contact with the camshaft; and a piston 31 which reciprocates in the bore of housing 60.
  • the electromegnetic valve assembly 27 comprises: a coil of wire 24 which receives power from a source (not shown); and a valve or solenoid core 20 which is axially movable in response to energization of the coil 24.
  • Spring 28 biases valve 20 axially in the open position so that energization of the solenoid coil 24 is required to close the valve 20.
  • the movable valve 20 includes a hollow portion 21, the purpose of which is to decrease the mass of the core so that less electromagnetic energy is required to move the valve 20.
  • the valve 20 includes an end face 23 which terminates within the housing 60.
  • An important feature of the valve 20 is the annular groove 2 therein which links relief passage 3 with the bore 10 in the housing when the valve 20 is extended to its farthest position from the coil 24. Obviously, portions of the core 20 not required to be responsive to the solenoid can be fabricated from materials other than iron.
  • the pump assembly 1 further includes a source or supply chamber 5 which supplies fuel to a-pressure chamber 10 through (inlet) passage 6.
  • the supply chamber 5 also communicates with the pressure chamber 10 through (relief) passage 3 and the passage formed by the annular groove 2 of the valve 20 when the valve 20 is in the position shown.
  • passage 6 is closed because of the position of piston 31 and the relief passage 3 is open because of the position of the solenoid valve 20. Therefore, the inlet passage 6 of the pressure chamber 10 is closed and the relief passage 3 is open, preventing pressurizing of the fuel in chamber 10 by the piston 31.
  • the fuel injection pump 1 further includes an injection valve assembly 50 which includes: a delivery valve 51; a valve seat 49 for receiving valve 51; a spring assembly 52 for maintaining the valve 51 in a closed position until a predetermined pressure is attained in chamber 10, the valve 51 and valve seat 49 being disposed in a chamber 15 that communicates with passages 56 and 57 that lead to the engine cylinder.
  • the valve 51 is shown in the closed position which prevents fuel in pressure chamber 10 from communicating with the fluid in chamber 15 and thereby injecting fuel into the engine.
  • the valve 51 is biased closed by spring 52 so that valve 51 does not open until the pressure in the passage 10 reaches a predetermined pressure level which is much greater than any pressure level of the fluid in the supply chamber 5.
  • FIG. 1 illustrates the pressurizing piston 31 at the top of its stroke and the solenoid valve positioned so that the pumping chamber 10 communicates with the supply chamber 5 through passage 3 so that the pressure in chamber 10 is not appreciably greater than the pressure within the supply chamber 5.
  • FIG. 2 is an enlarged cross-sectional diagrammatic view of the pump assembly shown in FIG. 1.
  • the supply chamber 5 communicates with the pressure chamber 10 only through the inlet passage 6 because the iron core 20 of the solenoid valve has been moved to a position to block the relief passage 3 that would otherwise communicate with the pressure chamber 10.
  • This diagrammatic view illustrates that as piston 31 rises to point A, it closes the inlet port connected to the supply chamber 5, thereby allowing the fuel in the chamber 10 to be pressurized as the volume of the chamber decreases.
  • valve 51 (FIG. 1) opens, allowing fluid to flow around the valve body 20 through the injector valve assembly (50, FIG. 1) and to the internal combustion engine (not shown).
  • FIG. 2 Another feature of the invention which can be seen in FIG. 2 is the fact that the face 23 of the valve 20 is not subject to the pressure in chamber 10. If the electromagnetic valve face 23 terminated within chamber 10, it would be subject to pressures that would require additional electromagnetic force to move the valve body 20. Further, since the movement of the valve 20 is independent of the operation of the reciprocating piston 31, control and injection of fuel into an engine cylinder may be started and stopped at any point in time regardless of the angle of rotation of the camshaft. This is an important feature of this invention in that prior art reciprocating type fuel injection pumps were not capable of obtaining this feature.
  • FIG. 3 is a diagrammatic view looking into pressure chamber along lines [IL-Ill in FIG. 2.
  • This FIGURE illustrates the shape of the pressure chamber 10 that allows pressurized fluid to flow around the valve body 20.
  • the valve body is shown in the open position so that fluid in the pressure chamber 10 may flow through the bypass or relief passage 3 to the supply chamber 5.
  • This view further illustrates how axial movement of the valve 20 in an axial direction opens and closes the communicating link between the pressure chamber 10 and the bypass passage 3.
  • This FIGURE further illustrates that the face of the valve 20 is not at any time located within the pressure chamber 10 and therefore is not subjected to any axial forces caused by the fluid in the chamber when the valve 20 is closed or open. Movement of the body 20 in either axial direction is in the order of .005 inches or less, allowing a maximum flow rate to be obtained in a minimum amount of time.
  • the fuel pump 1 operates as follows: a sensing device (not shown) senses one of the operating parameters of the internal combustion engine (not shown) to control the axial movement of the solenoid core or valve 20.
  • the control signal has the effect of causing the body 20 to oscillate at various magnitudes and/or frequencies.
  • the piston 31 reciprocates in response to the action of the spring 33 and cam follower 32 which is following the rotating camshaft of the internal combustion engine. Once the piston 31 has risen to a point in the bore of the housing 60 past the passage 6, fluid in the chamber 10 will or will not be pressurized, depending upon the location of the iron core 20.
  • the movement of the valve 20 is controlled independently of the movement of the reciprocating pis-' ton 31, it is possible to open and/or close the communicating link between the pressure chamber 10 and the supply chamber 5 at any particular point during the upward stroke of the piston 31. Therefore, it can now readily be appreciated that the injection of fuel into the engine may be controlled by the electromagnetically operated valve 20 which in turn is controlled independently of the reciprocating piston 31. Therefore, the quantity of fuel injected into the engine is a function of the interval of time between the opening and closing of the relief passage 3 by the movement of valve 20.
  • the piston 31 when the relief port is closed (no communicating link between pressure chamber 10 and supply chamber 5), the piston 31 will pressurize fuel in the chamber 10 causing it to open injection valve 51 and inject fuel into the engine.
  • the independently controlled valve 20 can be moved into a position that will establish a communicating link between the pressure chamber 10 and the supply chamber 5, thereby relieving the pressure in chamber 10 resulting in the closing of the injector or delivery valve 51.
  • a pump for supplying pressurized fluid which comprises:
  • a pump housing having a pumping chamber that has an inlet port, a relief port, an injection port communicating with said engine, and means for receiv ing a fluid, said fluid receiving means communicating with said inlet port, said relief port and said pumping chamber;
  • electromechanical valve means operative to open and close said relief port at predetermined intervals in response to at least one operating parameter of said engine
  • said electromechanical valve means including a solenoid valve having a core that has a first portion having an axial cross-sectional area that matches the configuration and size of said relief port and a second portion having a second axial cross-sectional area that is smaller than the relief port, said solenoid core mounted for axially reciprocating movement in said relief port so that in one position said first portion of said solenoid core closes said relief port and in a second position said second portion of said solenoid core opens said relief port, said solenoid core mounted so that neither end thereof terminates within said pumping chamber whereby the axial movement of said solenoid core that opens and closes said relief port is not biased by pressurized fluid within said pumping chamber, whereby each time said relief port closes,
  • the fluid pressure in said pumping chamber attains the first predetermined pressure at which said injection port opens, whereby pressurized fluid flows from said injection port.
  • piston mounted for reciprocating movement within said pump housing, said piston operable to periodically open and close said inlet port and thereby periodically apply pressure to said fluid in said pumping chamber as said plunger reciprocates, whereby when said relief port is open, fluid is pumped through said relief port and when said relief port is closed, fluid is pumped through said injection port.
  • a fuel injection system for an internal combustion engine of the type having a cam shaft comprising: v
  • a pump housing having a pumping chamber that has an inlet port, a relief port and an injection port, said injection port communicating with said engine;
  • said closing means including biasing means for keeping said injection port closed until a predetermined fuel pressure is attained in said pumping chamber;
  • said electromechanical valve means operative to open and close said relief port at predetermined intervals in response to at least one operating parameter of said engine whereby each time said relief port is closed the fuel pressure in said pressure chamber attains the predetermined pressure level at which said injection port opens, thereby injecting fuel into said engine, and each time said relief port is open, said injection port is closed, said electromechanical valve means is a solenoid valve having a plunger that has a first portion having an axial cross-sectional area that matches the configuration and size of said relief port and a second portion having a second axial cross-sectional area that is smaller than the relief port, said plunger mounted for axially reciprocating movement in said relief port so that in one position said first portion of said plunger closes said relief port and in a second position said second portion of said plunger opens said relief port, said solenoid core mounted so that neither end thereof terminates within said pumping chamber whereby the axial movement of said solenoid core that opens and closes said relief port is not biased by pressurized fluid within said pumping 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)
US00260882A 1972-06-08 1972-06-08 Reciprocating plunger type fuel injection pump having electromagnetically operated control port Expired - Lifetime US3779225A (en)

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US (1) US3779225A (fi)
JP (1) JPS5641821B2 (fi)
CA (1) CA969829A (fi)
DE (1) DE2328563A1 (fi)
FR (1) FR2188065B1 (fi)
GB (1) GB1400656A (fi)
IT (1) IT993566B (fi)

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US3859972A (en) * 1973-06-28 1975-01-14 Bendix Corp Fuel injection system for an internal combustion engine
US3880131A (en) * 1973-06-28 1975-04-29 Bendix Corp Fuel injection system for an internal combustion engine
US3913537A (en) * 1973-08-21 1975-10-21 Bosch Gmbh Robert Electromechanically controlled fuel injection valve for internal combustion engines
US3989021A (en) * 1974-03-22 1976-11-02 Diesel Kiki Co., Ltd. Dash pot arrangement for distribution type fuel injection pump cut off barrel
US4033314A (en) * 1975-08-08 1977-07-05 Eaton Corporation Metering control
US4033310A (en) * 1972-10-04 1977-07-05 C.A.V. Limited Fuel pumping apparatus with timing correction means
US4050856A (en) * 1974-03-22 1977-09-27 Diesel Kiki Co., Ltd. Dash pot arrangement for distribution-type fuel injection pump cut off barrel
US4073275A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump
US4211202A (en) * 1977-09-21 1980-07-08 Daimler-Benz Aktiengesellschaft Pump nozzle for air-compressing injection internal combustion engine
US4241714A (en) * 1979-06-25 1980-12-30 General Motors Corporation Solenoid valve controlled fuel injection pump
WO1981000431A1 (en) * 1979-08-08 1981-02-19 Caterpillar Tractor Co Rotary fuel injection apparatus
JPS5791371A (en) * 1980-10-06 1982-06-07 Ford Motor Co Bypass port type fuel injection pump
US4343280A (en) * 1980-09-24 1982-08-10 The Bendix Corporation Fuel delivery control arrangement
JPS57173554A (en) * 1981-03-28 1982-10-25 Bosch Gmbh Robert Fuel injector for multi-cylinder internal combustion engine
US4357925A (en) * 1980-12-17 1982-11-09 The Bendix Corporation Distributor injection pump for diesel engines
US4367715A (en) * 1980-12-17 1983-01-11 The Bendix Corporation Distribution injection pump for diesel engines
US4379442A (en) * 1980-10-06 1983-04-12 Ford Motor Company Electromagnetically controlled fuel injection pump
US4406267A (en) * 1981-09-02 1983-09-27 Ford Motor Company Electromagnetically controlled fuel injection pump spill port valve assembly
US4407245A (en) * 1980-09-20 1983-10-04 Robert Bosch Gmbh Shutoff apparatus for fuel injection pumps
US4422424A (en) * 1981-06-23 1983-12-27 The Bendix Corporation Electronically controlled fuel injection pump
US4445484A (en) * 1980-04-30 1984-05-01 Renault Vehicules Industriels Mechanical fuel injection devices, mainly for diesel engines
US4474158A (en) * 1981-11-11 1984-10-02 Lucas Industries Public Limited Company Liquid fuel pumping apparatus
US4475514A (en) * 1981-12-23 1984-10-09 Hans List Fuel injection pump for internal combustion engines
US4580540A (en) * 1979-10-17 1986-04-08 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4619239A (en) * 1983-01-25 1986-10-28 Klockner-Humboldt-Deutz Aktiengesellschaft Fuel injection arrangement for internal combustion engines
US4708116A (en) * 1985-02-23 1987-11-24 Motoren-Werke Mannheim Aktiengesellschaft Injection system for a diesel engine with a high pressure injection pump for each cylinder
US4785787A (en) * 1986-04-29 1988-11-22 Kloeckner-Humboldt-Deutz Ag Fuel injection mechanism for an internal combustion engine
US4793313A (en) * 1986-04-10 1988-12-27 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
US4870940A (en) * 1987-08-25 1989-10-03 Weber S.R.L. Injection pump for fuel injection systems with control led injectors for i.c. engines
US4881504A (en) * 1987-02-13 1989-11-21 Lucas Industries Public Limited Company Fuel injection pump
US4917068A (en) * 1987-12-29 1990-04-17 Toyoto Jidosh Kabushiki Kaisha Unit injector for an engine
US5125807A (en) * 1989-04-04 1992-06-30 Kloeckner-Humboldt-Deutz Ag Fuel injection device
DE4142940A1 (de) * 1991-12-24 1993-07-01 Bosch Gmbh Robert Elektrisch gesteuerte pumpeduese
US5287833A (en) * 1991-04-12 1994-02-22 Yamaha Hatsudoki Kabushiki Kaisha Lubricating oil supplying system for two cycle engine
US5355851A (en) * 1992-02-10 1994-10-18 Yamaha Hatsudoki Kabushiki Kaisha Lubricating oil supplying system for two cycle engine
US5390635A (en) * 1992-03-16 1995-02-21 Yamaha Hatsudoki Kabushiki Kaisha Lubricating oil supplying system for engine
US5501190A (en) * 1993-08-09 1996-03-26 Yamaha Hatsudoki Kabushiki Kaisha Lubricating system for engine
US5526783A (en) * 1992-06-29 1996-06-18 Yamaha Hatsudoki Kabushiki Kaisha Lubricant control
US5537959A (en) * 1993-08-09 1996-07-23 Yamaha Hatsudoki Kabushiki Kaisha Lubricating system for engine
US5542387A (en) * 1994-08-09 1996-08-06 Yamaha Hatsudoki Kabushiki Kaisha Component layout for engine
WO1996026360A1 (en) 1995-02-21 1996-08-29 Diesel Technology Company Fuel pumping and injection systems
WO1997012145A1 (en) * 1995-09-12 1997-04-03 Diesel Technology Company Fuel injection pump having a solenoid operated control valve
US5954487A (en) * 1995-06-23 1999-09-21 Diesel Technology Company Fuel pump control valve assembly
US6089470A (en) * 1999-03-10 2000-07-18 Diesel Technology Company Control valve assembly for pumps and injectors
US6145493A (en) * 1996-10-11 2000-11-14 Daimlerchrysler Ag Fuel guidance system for a multicylinder internal combustion engine having inlet bores for connector pumps
US6158419A (en) * 1999-03-10 2000-12-12 Diesel Technology Company Control valve assembly for pumps and injectors
US6224351B1 (en) * 1998-09-11 2001-05-01 Robert Bosch Gmbh Radial pistol pump
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
US7066151B1 (en) * 2005-04-07 2006-06-27 Robert Bosch Gmbh Fuel injector with spill chamber
US20130284275A1 (en) * 2011-01-12 2013-10-31 Delphi Technologies Holdings, S.A.R.L. Valve assembly
CN104775958A (zh) * 2010-02-26 2015-07-15 洋马株式会社 燃料喷射泵

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US4276000A (en) * 1978-01-31 1981-06-30 Lucas Industries Limited Liquid fuel pumping apparatus
DE3111837A1 (de) * 1980-06-21 1982-01-14 Robert Bosch Gmbh, 7000 Stuttgart "kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen, insbesondere fuer dieselmotoren"
DE3148671A1 (de) * 1981-12-09 1983-07-21 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzvorrichtung fuer brennkraftmaschinen, insbesondere fuer dieselmotoren
AT384654B (de) * 1981-12-23 1987-12-28 List Hans Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US4392612A (en) * 1982-02-19 1983-07-12 General Motors Corporation Electromagnetic unit fuel injector
IT1150843B (it) * 1982-04-19 1986-12-17 Spica Spa Regolatore di mandata per pompa di iniezione del combustibile
US4482094A (en) * 1983-09-06 1984-11-13 General Motors Corporation Electromagnetic unit fuel injector
DE3427421A1 (de) * 1984-07-25 1986-01-30 Klöckner-Humboldt-Deutz AG, 5000 Köln Steuerventil fuer eine kraftstoffeinspritzvorrichtung
DE3536828A1 (de) * 1985-10-16 1987-04-16 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzvorrichtung mit einem elektromagnetischen steuerventil zwischen einspritzpumpe und einspritzduese
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Cited By (61)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4033310A (en) * 1972-10-04 1977-07-05 C.A.V. Limited Fuel pumping apparatus with timing correction means
US3859972A (en) * 1973-06-28 1975-01-14 Bendix Corp Fuel injection system for an internal combustion engine
US3880131A (en) * 1973-06-28 1975-04-29 Bendix Corp Fuel injection system for an internal combustion engine
US3913537A (en) * 1973-08-21 1975-10-21 Bosch Gmbh Robert Electromechanically controlled fuel injection valve for internal combustion engines
US3989021A (en) * 1974-03-22 1976-11-02 Diesel Kiki Co., Ltd. Dash pot arrangement for distribution type fuel injection pump cut off barrel
US4050856A (en) * 1974-03-22 1977-09-27 Diesel Kiki Co., Ltd. Dash pot arrangement for distribution-type fuel injection pump cut off barrel
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Also Published As

Publication number Publication date
FR2188065A1 (fi) 1974-01-18
GB1400656A (en) 1975-07-23
JPS5641821B2 (fi) 1981-09-30
FR2188065B1 (fi) 1975-08-22
IT993566B (it) 1975-09-30
JPS4956029A (fi) 1974-05-30
DE2328563A1 (de) 1973-12-20
CA969829A (en) 1975-06-24

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