EP0336926A1 - Pumpedüse für Dieselmotoren - Google Patents

Pumpedüse für Dieselmotoren Download PDF

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Publication number
EP0336926A1
EP0336926A1 EP89890093A EP89890093A EP0336926A1 EP 0336926 A1 EP0336926 A1 EP 0336926A1 EP 89890093 A EP89890093 A EP 89890093A EP 89890093 A EP89890093 A EP 89890093A EP 0336926 A1 EP0336926 A1 EP 0336926A1
Authority
EP
European Patent Office
Prior art keywords
pump
sleeve
control sleeve
control
nozzle according
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.)
Ceased
Application number
EP89890093A
Other languages
German (de)
English (en)
French (fr)
Inventor
Heinz Ing. Rathmayr
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.)
Voestalpine Metal Forming GmbH
Original Assignee
Voestalpine Metal Forming GmbH
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
Application filed by Voestalpine Metal Forming GmbH filed Critical Voestalpine Metal Forming GmbH
Publication of EP0336926A1 publication Critical patent/EP0336926A1/de
Ceased 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • F02M59/246—Mechanisms therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention relates to a pump nozzle for diesel engines, in which an injection pump element having a pump piston driven by a camshaft and an element sleeve is combined with an injection nozzle to form a unit to be assigned to a respective engine cylinder, the pump piston being enclosed by a control sleeve which is non-rotatably mounted relative to the element sleeve , which is adjustable in the direction of the axis of the pump piston in order to change the start of injection as a function of operating variables of the engine, and wherein the pump piston can be rotated relative to the control sleeve to adjust the delivery rate.
  • a control sleeve usually has a control edge which lies in a normal plane to the pump axis and which controls the start of injection.
  • a sloping control edge of the control sleeve or of the pump piston determines the end of injection and thus the injection quantity as a function of the rotational position of the pump piston relative to the control sleeve.
  • Such a pump nozzle has become known from DE-A1-31 43 073, in which the control sleeve is axially adjustable for the purpose of changing the start of injection.
  • the control sleeve is adjusted directly by a hydraulic piston. Since the control sleeve is adjusted directly by the hydraulic piston, the adjustment travel of the control sleeve is equal to the adjustment travel of the hydraulic piston. Since the adjustment path of the control sleeve is small, only small adjustment paths of the hydraulic piston are available for the adjustment of the control sleeve, and such a regulation is therefore not sensitive and precise.
  • the hydraulic piston is connected to the control sleeve via a linkage.
  • the adjustment of the control sleeve becomes even less precise.
  • the control sleeve is guided directly on the pump piston, so that wear between the control sleeve and the pump piston is promoted.
  • the control sleeve is guided on the pump piston over a relatively small guide length and there is therefore a risk of the control sleeve being covered on the pump piston, which increases the wear on the pump piston and control sleeve and further reduces the precision of the control.
  • the axially adjustable hydraulic piston surrounds the pump piston and is itself designed as a control sleeve. It is therefore also in this embodiment, the adjustment of the hydraulic piston equal to the adjustment of the control sleeve and therefore very small and also complicated seals are required, which also affect the precision and sensitivity of the control due to the friction.
  • the object of the invention is to provide a pump nozzle in which the start of delivery can be set individually and independently of the other pump nozzles precisely and reproducibly and the setting can be adjusted easily and without stopping the pump test bench or the motor, the setting device also being suitable for electronic control is.
  • the invention consists essentially in the fact that the control sleeve is non-rotatably connected to a separating sleeve surrounding it and cannot be displaced in the axial direction, the inner side of the separating sleeve being axially displaceable at both ends of the control sleeve on guide surfaces of the element sleeve and being non-rotatable relative to the latter , wherein the element sleeve between the guide surfaces has a space for receiving the control sleeve has, which also forms the control chamber, that the separating sleeve has at its end facing away from the injection nozzle a hook-like extension which is transverse to the axis, at least partially inclined to a normal plane perpendicular to the axis of the pump piston and parallel to this normal plane in the direction of its Scanning inclined surface scans, and that the adjusting force causing the axial adjustment movement of the control sleeve acts on the inclined surface.
  • control sleeve is guided by means of the separating sleeve on the element sleeve, and in that this separating sleeve is in turn displaceably guided on both sides of the control sleeve on the element sleeve, there is a large guide length of the separating sleeve and thus a precise guidance of the control sleeve, whereby the guide surfaces are only slightly stressed and therefore hardly show any wear.
  • the guidance of the control sleeve on the pump piston is thus largely relieved, whereby abrasion on the pump piston and on the control sleeve is avoided, so that the control function is precisely maintained.
  • the separating sleeve at its end facing away from the injection nozzle has a hook-like extension, by means of which the height adjustment of the separating sleeve and thus the control sleeve is carried out, stray stresses acting on the separating sleeve and the control sleeve are reduced.
  • the hook-like extension scans an inclined and displaceable surface lying transversely to the axis, a large displacement movement of this inclined surface can be used for a small height adjustment of the control sleeve. This large gear ratio enables great control precision.
  • the inclined surface can enclose an angle of 3 ° to 22 ° with the normal plane, etc.
  • control sleeve is mounted between the two guide points of the separating sleeve on the element sleeve in a recess of the element sleeve, the control sleeve and the control chamber is completely shielded by the separating sleeve.
  • the inclined surface can advantageously lie above the control sleeve and can be displaced in a straight line, the direction of displacement of which is tangential to a circle concentric with the axis of the pump piston. Characterized in that the inclined surface lies above the control sleeve, the control sleeve is pulled during its height adjustment movement, which already counteracts hiding, and it is further achieved that the adjustment device is made easily accessible for adjustment during operation.
  • the inclined surface can be moved in a manner known per se by means of a hydraulic piston.
  • the inclined surface can also be formed on the hydraulic piston itself, which saves a separate component. For this purpose, this inclined surface can be formed by flattening the hydraulic piston and the hydraulic piston itself could also be conical in the region of the inclined surface.
  • the inclined surface can also be formed by a helically running path which concentrically surrounds the axis of the pump piston and can be rotated about the axis of the pump piston in the direction of displacement.
  • a Such training has the advantage that the force is applied to the hook near the guide of the separating sleeve and thus a risk of jamming is excluded.
  • the path forming the inclined surface can be incorporated on part of the circumference of the jacket of the rotor of an electric actuator. In this way, the adjustment accuracy of the control sleeve is increased.
  • the control device exhibits less inertia behavior and a lower overall height of the pump nozzle is also made possible, since the inclined surface can be designed as a groove in the jacket of the rotor.
  • the inclined surface can have sections arranged one behind the other in the direction of displacement with differently sized and / or differently directed inclinations.
  • the slope of the inclined surface and in different sections can decrease and the angle of inclination or slope can be zero in one or more sections. In this way, an additional possibility is created to adapt the regulation of the start of injection to different requirements.
  • the control sleeve is supported against a support surface of the separating sleeve and is pressed against the support surface by at least one compression spring supported against the end of the element sleeve facing away from the injection nozzle.
  • this compression spring also forms a return spring which presses the hook-like extension against the inclined surface.
  • this compression spring can lie in the control chamber.
  • the pressure in the control chamber can be reduced in a damped manner and this has the advantage that fewer impacts act on the control sleeve and, subsequently, on the sloping surface via the separating sleeve and the hook. Pressure fluctuations in the pump suction chamber are avoided and a complete and regular filling of the high pressure chamber and thus a reproducible fuel supply is achieved even at high speeds.
  • the suction space can be connected to the pump spring space and the fuel supply to the suction space can be guided via the pump spring space, a check valve being arranged in the fuel inlet to the pump spring space and in the fuel return line from the suction space.
  • the guide sleeve causes a dynamic pressure increase of the fuel in the pump spring chamber during the working stroke, so that the high pressure chamber of the pump piston is better filled during the suction stroke.
  • the setting of the filling pressure can be determined by appropriately designed valves and / or throttling points in the inlet and outlet.
  • the hydraulic piston is supplied with fuel from a pressure-controlled space in which the pressure is regulated depending on the operating variables of the engine, for example by a valve controlled by an electronic regulator.
  • the fuel can be fed to this pressure-controlled space from the pump control space or from the pump spring space connected to the suction space. It is only essential that the space from which the fuel is supplied to the pressure-controlled space is under a pressure which is higher than the pressure to which the pressure-controlled space is to be set. This occurs when fuel from the pump control chamber or fuel from the pump spring chamber, if it is connected to the intake chamber, is supplied to the pressure-controlled chamber.
  • the fuel is supplied to the pressure-controlled space via a throttle point or a throttle valve. In this way, a separate pressure generator can be saved.
  • the switching valve controlled by an electronic controller for modulating the pressure level in the pressure-controlled space can be integrated in the housing of the pump nozzle.
  • a further embodiment of the invention consists in that the pump spring chamber and a chamber containing an electrical actuator which actuates the crank arm for rotating the pump piston communicate with one another and are sealed off from the chamber containing the camshaft, rocker arm and tappet for the pump drive, and in that a fuel supply line to the the actuator-containing space and a fuel return line to the tank are connected to the pump spring space.
  • the electrical windings are cooled by the amount of fuel flowing through and, moreover, fuel leaks from the high-pressure chamber into the pump spring chamber are discharged without mixing with the engine oil in the space containing the camshaft, rocker arm and tappet.
  • FIG. 1 to 4 show an embodiment of the pump nozzle, wherein FIG. 1 shows a section along line II of FIG. 2, FIG. 2 shows a section along line II-II of FIG. 1, FIG. 3 shows a section along line III-III 1 and FIG. 4 shows a section along line IV-IV of FIG. 1.
  • Fig. 5 shows a detail.
  • Fig. 6 shows a variant in the same representation as Fig. 1.
  • Fig. 7 shows a horizontal Partial section through a variant of the pump nozzle with a switching valve integrated in the housing of the pump nozzle.
  • 8 shows a variant of a pump nozzle in axial section, in which the fuel is led to the suction chamber via the pump spring chamber.
  • Fig. 1 shows a section along line II of FIG. 2
  • FIG. 3 shows a section along line III-III 1
  • FIG. 4 shows a section along line IV-IV of FIG. 1.
  • Fig. 5 shows a detail.
  • Fig. 6 shows a variant in the same representation
  • FIGS. 12 and 13 show a detail of the control sleeve or the arrangement thereof on a larger scale, FIG. 12 showing an axial section along line XII-XII in FIG 13 and 13 show a cross section along line XIII-XIII of FIG.
  • FIG. 14 shows the installation of the control sleeve in the separating sleeve in a section along the line XIII-XIII of FIG. 12.
  • 1 represents the pump piston which is driven by a camshaft (not shown) via a rocker arm 2 and a tappet 3.
  • the pump spring 4 engages the pump piston 1 via a spring plate 5 and is guided in a guide sleeve 6.
  • 7 is the high pressure chamber of the pump and 8 is the injection nozzle.
  • 9 is the suction space and 9 'is the suction hole.
  • 10 is a crank arm for the rotation of the pump piston.
  • 11 is the element can.
  • the piston 1 has an axial bore 13 from which a radial bore 14 extends. Via this axial bore 13, the radial bore 14 is in open communication with the working space 7 of the pump piston 1. As soon as the radial stroke of the piston 1, the radial bore 14 is completed by the control edge 15, the promotion begins. As soon as the inclined edge 16 clears the transverse bore 14 of the piston 1, the delivery stroke is ended and the fuel is discharged from the high-pressure chamber 7.
  • the control sleeve 12 is connected to a separating sleeve 17 by an extension 18 engaging in a recess in the separating sleeve 17 and pressed against a support surface 20 of the separating sleeve 17 by two compression springs 19. In this way, the control sleeve is connected to the separating sleeve 17 without play in the vertical direction.
  • This separating sleeve 17 is rotatably connected to the control sleeve 12 and above and below the control sleeve 12 with its inside on the element sleeve 11 on guide surfaces 11a and 11b of the same in a height-adjustable manner, so that the control sleeve 12 is properly guided without the pump piston 1 and the is loaded with the pump piston 1 cooperating inner surface of the control sleeve, so that there is little wear.
  • control sleeve 12 and 13 the detail of the control sleeve 12 with the separating sleeve 17 is shown on a larger scale.
  • the control sleeve is secured against rotation relative to the element sleeve 11 by a pin 55 inserted into the element sleeve 11, which engages in a slot 56 of the control sleeve 12. Since the separating sleeve 17 is also secured against rotation, the control sleeve 12 is therefore non-rotatable relative to the separating sleeve 17.
  • the control sleeve 12 is again pressed down by the springs 19, which are supported against the element sleeve 11.
  • control sleeve 12 is supported in the axial direction against the separating sleeve 17 by the extension 18, which engages in an annular groove 57 extending over part of the inner surface of the separating sleeve 17.
  • the element sleeve 11 has a space 29 for receiving the control sleeve, which at the same time forms the control chamber.
  • Fig. 14 it is shown how the control sleeve 12 in the Separating sleeve 17 is installed.
  • the control sleeve 12 With the piston 1 removed, the control sleeve 12 is displaced relative to the separating sleeve 17 to the right, so that the bore 58 of the control sleeve 12, in which the pump piston 1 is guided, reaches the relative position 58 '.
  • the separating sleeve 17 has a downwardly open groove 59, so that when the control sleeve is shifted to the right, the separating sleeve 17 can be pushed over the foot 60 of the control sleeve, which has the extension 18.
  • the pin 55 engages in the slot 56.
  • the control sleeve is then pushed back into the central position, in which the extension 18 now engages in the annular groove segment 57.
  • the separating sleeve is then rotated into the position according to FIG. 13.
  • the separating sleeve 17, as shown in FIG. 1, has at its upper end a hook-like extension 21 which scans with its hook arm 22 a surface 23 lying transversely to the pump axis, which is slightly inclined towards a normal plane to the pump axis and can be displaced parallel to this normal plane is.
  • a surface 23 lying transversely to the pump axis, which is slightly inclined towards a normal plane to the pump axis and can be displaced parallel to this normal plane is.
  • the inclined surface 23 scanned by the hook-like part 21 can be relatively long in its direction of inclination.
  • the stroke of the control sleeve 12 for the purpose of adjusting the start of injection is very small. A considerable translation can therefore be achieved between the displacement of the inclined surface 23 and the stroke of the control sleeve 12, which considerably improves the sensitivity of the control.
  • FIG. 5 shows in detail the inclined surface 23 scanned by the hook-like part 21.
  • the slope of this inclined surface is indicated at 28. It can be seen from this that the slope is very small in relation to the scanned length of this area.
  • the control chamber in which the regulator sleeve is housed is designated by 29.
  • the pressure springs 19 are also located in this control chamber. From the control chamber, the controlled fuel is supplied via bores 30 separately from the intake chamber 9 to the return line, so that the pressure in the intake chamber 9 is not impaired by the controlled fuel and therefore a calmed down pressure for the intake Available. If the fuel required for the working space 25 of the piston 24 displacing the inclined surface is branched off from the suction space 9, pressure fluctuations in the suction space up to the inclined surface 23 scanned by the hook-like extension 21 can have an effect and the injection time can be set again influence point. The fact that the controlled fuel does not get into the intake space increases the precision of the control of the start of injection. 31 is the pump spring chamber, which is surrounded by the housing 32 of the pump nozzle. Leakage oil that has penetrated into this pump spring chamber can also be discharged through a return line.
  • the hook-like part 33 protrudes vertically upward from the separating sleeve 17 and engages in a helical groove in the jacket of the rotor 35 of an electrical actuator, the lower limit 34, which is similar to a helical surface that the inclined surface constituting web.
  • This track can also have differently sized and / or differently directed gradients in different sections.
  • 36 is an electronic controller for the electrical actuator for the stroke movement of the controller sleeve 12.
  • In the housing 61 there is also an actuator, not shown, for the rotary adjustment of the pump piston 1.
  • FIG. 7 shows, in a section similar to FIG. 3, an example in which the electronically controlled switching valve 26 is integrated in the housing of the pump nozzle.
  • 62 is an electromagnet actuating the switching valve 26, which is controlled by an electronic controller 27, as shown in FIG. 3.
  • 63 is the line connecting the electromagnet 62 to the electronic regulator 27.
  • FIG. 8 shows a variant in which the fuel is supplied to the intake chamber 9 via a chamber 41 containing an electrical actuator that actuates the crank arm for rotating the pump piston and the pump spring chamber 31.
  • a check valve 38 is switched on in the supply line 37 and a pressure-maintaining valve 40 is switched on in the discharge line 39.
  • the guide sleeve 6 of the pump spring 4 exerts a certain pumping action from, whereby the pressure of the fuel supplied by the backing pump is increased.
  • the embodiment according to FIG. 9 shows an example in which the pressure of the deactivated fuel is used.
  • the controlled fuel is fed to the pressure-controlled chamber 43 via the bore 30 and a line 42.
  • a throttle cross section or a throttle valve 44 is switched into line 42.
  • a switching valve 46 controlled by an electronic controller 27 is switched into a drain line 45, so that the pressure in the space 43 can be adjusted in accordance with the operating parameters of the engine.
  • the fuel pressure set in this way is made effective from the space 43 on the hydraulic piston 24 via a line 47.
  • the 10 shows a variant in which the pressure from the pump spring chamber 31 is used to act on the hydraulic piston.
  • the pressure-controlled space 43 is connected by a line 48 to the pump spring space 31 via a throttle valve 44.
  • a switching valve 46 controlled by the electronic regulator 27 regulates the outflow to the tank 49 and thus the pressure in the pressure-controlled space 43.
  • This pressure is made effective from the pressure-controlled space 43 on the hydraulic piston 24 via a line 50.
  • the pump spring chamber 31 is connected to the suction chamber 9 here, just as in the arrangement according to FIG. 8.
  • the fuel is supplied from the backing pump, not shown, into the intake chamber 9 or into the pump spring chamber through a line, not shown.
  • the space 41 which contains the electrical actuator 54 which actuates the crank arm 10 for rotating the pump piston 1 and the pump spring space 31 which is in open communication therewith are of a quantity of fuel which is not injected flushed, which is fed through a fuel feed line 37 and flows through a fuel return line 39 into the tank 49.
  • This causes cooling of the electrical winding 53 of the actuator located in the housing 54 for the rotary adjustment of the pump piston, and fuel leak quantities reaching the pump spring chamber 31 are also removed.
  • the spaces 31 and 41 are sealed by means of a seal 52.

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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)
EP89890093A 1988-04-08 1989-04-05 Pumpedüse für Dieselmotoren Ceased EP0336926A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3811845 1988-04-08
DE3811845A DE3811845A1 (de) 1988-04-08 1988-04-08 Pumpeduese fuer dieselmotoren

Publications (1)

Publication Number Publication Date
EP0336926A1 true EP0336926A1 (de) 1989-10-11

Family

ID=6351641

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89890093A Ceased EP0336926A1 (de) 1988-04-08 1989-04-05 Pumpedüse für Dieselmotoren

Country Status (4)

Country Link
US (1) US4907559A (enrdf_load_stackoverflow)
EP (1) EP0336926A1 (enrdf_load_stackoverflow)
JP (1) JPH0723707B2 (enrdf_load_stackoverflow)
DE (1) DE3811845A1 (enrdf_load_stackoverflow)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5566660A (en) * 1995-04-13 1996-10-22 Caterpillar Inc. Fuel injection rate shaping apparatus for a unit fuel injector
US5730104A (en) * 1997-02-19 1998-03-24 Caterpillar Inc. Injection rate shaping device for a fill metered hydraulically-actuated fuel injection system
CN106555678B (zh) * 2016-12-02 2022-10-14 斯太尔动力（常州）发动机有限公司 柴油发动机泵喷嘴供油装置

Citations (3)

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Publication number Priority date Publication date Assignee Title
US3847126A (en) * 1973-10-01 1974-11-12 Allis Chalmers Injection timing modulator
DE3143073A1 (de) * 1981-10-30 1983-05-11 Robert Bosch Gmbh, 7000 Stuttgart Einspritzpumpe mit einstellbarem spritzzeitpunkt
DE3325479A1 (de) * 1982-07-14 1984-01-19 Steyr-Daimler-Puch AG, 1011 Wien Kraftstoff-einspritzaggregat fuer je einen zylinder eines dieselmotors

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US30189A (en) * 1860-10-02 Improvement in making emery-wheels
US2147390A (en) * 1934-04-17 1939-02-14 Provencale De Const Aeronautiq Fuel feed pump
DE1910112C3 (de) * 1969-02-28 1974-07-18 Robert Bosch Gmbh, 7000 Stuttgart Regeleinrichtung für die Fördermenge einer Einspritzpumpe für Brennkraftmaschinen
USRE30189E (en) 1973-07-02 1980-01-15 Cummins Engine Company Fuel injection system for diesel engines
NL7403916A (nl) * 1974-03-22 1975-09-24 Holec Nv Injekteur voor het afgeven van brandstof aan een verbrandingsmotor.
US3999529A (en) * 1975-05-19 1976-12-28 Stanadyne, Inc. Multiple plunger fuel injection pump
US4146178A (en) * 1977-05-18 1979-03-27 Caterpillar Tractor Co. Unit fuel injector
JPS55164773A (en) * 1979-06-11 1980-12-22 Diesel Kiki Co Ltd Fuel injection device for internal combustion engine
JPS619182Y2 (enrdf_load_stackoverflow) * 1981-03-04 1986-03-22
DE3428174A1 (de) * 1984-07-31 1986-02-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3447374A1 (de) * 1984-12-24 1986-07-10 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3447375A1 (de) * 1984-12-24 1986-07-03 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3724409A1 (de) * 1986-10-31 1988-05-19 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3870748D1 (de) * 1987-07-25 1992-06-11 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen.

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3847126A (en) * 1973-10-01 1974-11-12 Allis Chalmers Injection timing modulator
DE3143073A1 (de) * 1981-10-30 1983-05-11 Robert Bosch Gmbh, 7000 Stuttgart Einspritzpumpe mit einstellbarem spritzzeitpunkt
DE3325479A1 (de) * 1982-07-14 1984-01-19 Steyr-Daimler-Puch AG, 1011 Wien Kraftstoff-einspritzaggregat fuer je einen zylinder eines dieselmotors

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 7 (M-350)(1730) 12 Januar 1985, & JP-A-59 158368 (HINO JIDOSHA KOGYO K.K.) 07 September 1984, *

Also Published As

Publication number Publication date
JPH0723707B2 (ja) 1995-03-15
DE3811845A1 (de) 1989-10-19
DE3811845C2 (enrdf_load_stackoverflow) 1991-06-06
US4907559A (en) 1990-03-13
JPH01315662A (ja) 1989-12-20

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