EP1049869A1 - Dispositif pour produire un debit variable dans une alimentation en carburant - Google Patents

Dispositif pour produire un debit variable dans une alimentation en carburant

Info

Publication number
EP1049869A1
EP1049869A1 EP99960884A EP99960884A EP1049869A1 EP 1049869 A1 EP1049869 A1 EP 1049869A1 EP 99960884 A EP99960884 A EP 99960884A EP 99960884 A EP99960884 A EP 99960884A EP 1049869 A1 EP1049869 A1 EP 1049869A1
Authority
EP
European Patent Office
Prior art keywords
opening
shaft
groove
inlet
grooves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99960884A
Other languages
German (de)
English (en)
Other versions
EP1049869B1 (fr
Inventor
Hinrich KRÜGER
Martin Werner
Eckbert Zander
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1049869A1 publication Critical patent/EP1049869A1/fr
Application granted granted Critical
Publication of EP1049869B1 publication Critical patent/EP1049869B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • F02M59/361—Valves being actuated mechanically
    • F02M59/362—Rotary valves
    • F02M59/363—Rotary valves arrangements for adjusting the rotary valve
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • F02M41/063—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating the distributor and rotary valve controlling fuel passages to pumping elements being combined
    • 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
    • F02M59/205—Quantity of fuel admitted to pumping elements being metered by an auxiliary metering device
    • 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
    • F02M59/361—Valves being actuated mechanically
    • F02M59/362—Rotary valves
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a device for generating a variable volume flow in a fuel supply, in particular for use in common rail injection systems.
  • Convey fuel from a tank compress it and make the compressed fuel available in a pressure accumulator called a rail for injection by injectors.
  • the pressure in the rail and the amount of fuel drawn from the rail by injection vary with the operating conditions of the engine.
  • a pre-feed pump sucks the fuel through a filter from a tank and supplies the high pressure pump.
  • the compressed fuel is stored in the rail and injected into the combustion chambers by the injectors.
  • This method uses constant pumps that deliver a fixed volume with every revolution of the shaft.
  • a variable delivery rate of the system is achieved by controlling the volume flow that is not required but is already compressed with the aid of a valve.
  • this principle is energetically unfavorable for high-pressure systems.
  • the level can also be changed from the outset by limiting the inlet to the displacement elements.
  • One way to limit the inflow is to throttle the entire volume flow supplied to the pump or the volume flow supplied to each individual displacement element.
  • Adjustable throttle valves are used, which allow a proportional change in the volume flow by changing the throttle cross-section.
  • the maximum cross-section of the throttle valve is designed for the maximum volume flow at full load and rated speed.
  • the interaction of the maximum volume flow that can be conveyed, which is dependent on the pump speed, with the possibility of adjusting the throttle valve results in a relationship between the adjustable volume flow and the manipulated variable as a function of the pump speed.
  • the usable adjustment range of the throttle valve is severely restricted, since only a small area of the throttle cross-sectional area can be effectively used in a throttling manner.
  • the full range of the valve can only be used at maximum speed. For example If a pump is operated with a nominal speed of 3000 rpm and a flow rate of 0.5 ml per revolution, the throttle valve must be designed for a maximum volume flow of 1500 ml / min. At a speed of 300 rpm and the resulting maximum volume flow of 150 ml / min, only 10% of the control range of the throttle valve is used to regulate between zero and full load.
  • the agreement of the characteristic curves of the intake valves is particularly responsible for an equal filling level of the individual cylinders and thus for a uniform flow pulsation.
  • the different characteristic curves of the inlet valves and the resulting differences in the flow rates are particularly noticeable with partial load in uneven flow pulsation.
  • the production of valves with a matching inlet valve characteristic curve is extremely complex, since it is particularly difficult to manufacture springs with identical spring lengths required for the inlet valves.
  • the object of the invention is a device for generating a variable volume flow in a fuel supply Specify at which the flow rate can be set to any volume flow required between zero and full load by limiting the inlet at any speed between idle speed and nominal speed.
  • the advantage of the invention is that a large adjustment range for influencing the variable volume flow is guaranteed for all pump speeds. In addition, by ensuring a uniform distribution of the entire feed to the individual displacement elements, a low and uniform flow pulsation is achieved. Finally, it is advantageous that the high pressure pump can be operated with a very low admission pressure.
  • the invention provides for a meterable, pre-measured volume to be supplied to the delivery elements of the high-pressure pump with each pump revolution.
  • the resulting variable degree of filling of the displacement elements thus results in a volume flow that can be variably adjusted between zero and full load.
  • the setting of the filling level is decoupled from the speed of the high-pressure pump. The consequence of this is that the setting range for influencing the degree of filling has the same size for all speeds.
  • the metering is done by varying the angle between opening and closing the inlets for the individual cylinders at an angle synchronous to the shaft and thus depending on the
  • the inlet to the cylinder of the high-pressure pump is always opened in the area of the top dead center of the piston and closed at any piston position down to the area of the bottom dead center.
  • the cylinders fill up with a defined volume that determines the degree of filling.
  • the shaft which also drives the pistons via cams or eccentrics, for example, is supplied with a continuous volume flow inside by a pre-feed pump. The volume flow is distributed through channels and external grooves.
  • a perforated sleeve is axially adjustable on the shaft.
  • the shape of the grooves on the shaft and the openings in the sleeve are designed so that there are different opening and / or closing angles depending on the axial position of the sleeve.
  • the shape of the openings and grooves can also be interchanged.
  • the shaft and sleeve are located in a housing with additional channels for diverting the volume flow to the individual cylinders.
  • the inlet and outlet can also be placed in any combination in the housing and / or the shaft, which means that both inlet and outlet are accommodated in the shaft or in the housing or that one of the two is in the housing and the other in the shaft is located.
  • the metering of the inlet and thus the opening begins when the groove and opening begin to overlap.
  • the inlet (closing) is interrupted when the groove on the shaft has come out of the overlap with the sleeve opening. If the groove is oriented parallel to the axis, the time of opening advantageously remains constant.
  • phase length of the overlap of groove and opening (angle) changes due to the axial displacement of the sleeve.
  • a defined volume can be let into the cylinder.
  • the axial displacement of the sleeve represents the adjustment range, which is the same for all speeds.
  • the closing time can be fixed and the opening time variable or the opening time fixed and the closing time variable or both variable with respect to the shaft.
  • the inlet to the cylinder or cylinders can be opened at the top dead center of the respective piston and closed at any piston position up to the bottom dead center.
  • control slots in the form of grooves, openings, etc. can be used in the same way on a sleeve, disc or cone or several sleeves, discs or cones, each with a “control slot”, by several Operate pistons in parallel.
  • shafts and / or sleeves and / or housings it is also possible to use conical, disk-shaped or other suitably shaped bodies.
  • inlet and outlet can also be interchanged in all embodiments. Otherwise, the statements applicable to the sliding sleeves also apply accordingly to the other embodiments.
  • All lines and channels as well as the cross sections of the overlapping grooves and openings are designed for maximum flow at maximum speed without throttling.
  • the volume flow limitation thus does not result from throttling, but only by changing the phase length of the open inlet to the displacement elements. In principle no large form is required.
  • the low admission pressure also results in less leakage.
  • Another advantage of the metering of the inlet according to the invention for each individual cylinder compared to throttling the entire pump inlet is to improve the uniform distribution of the inlet to the individual cylinders.
  • the even distribution among the individual cylinders only depends on the correspondence of the geometry and the arrangement of the grooves and openings.
  • the geometrical tolerances required for this are much easier to maintain than, for example, the tolerances of the spring characteristics for identical inlet valves.
  • FIG. 1 shows a first general embodiment of a device according to the invention
  • FIG. 2 shows a first development of the device according to the invention according to FIG. 1
  • FIG. 3 shows a second development of the device according to the invention according to FIG. 1
  • FIG. 4 shows a third development of the device according to the invention according to FIG. 1
  • FIG. 5 shows a fourth development of the invention
  • FIG. 6 shows a general, fifth development of the device according to the invention according to FIG. 1,
  • Figure 7 shows a special embodiment of the training
  • FIG. 6, FIG. 8 a second general embodiment of a device according to the invention
  • FIG. 9 an alternative embodiment of the development according to FIG. 8
  • Figure 10 shows a third general embodiment of a device according to the invention
  • Figure 11 shows a fourth general embodiment of a device according to the invention
  • Figure 12 shows a characteristic field of a device according to the invention.
  • a high-pressure pump 21 is provided, the shaft of which drives its piston 21a via an eccentric 21d.
  • the cylinder 21b also has intake and exhaust valves 21c, respectively.
  • the shaft 1 is led out of the high-pressure pump 21 and comprises in its interior a channel 4 which is connected to a groove 5.
  • the groove 5 breaks through the axially extending circumferential surface of the shaft 1.
  • the channel 4 is connected to the outlet of a prefeed pump 18, the inlet of which is connected to a fuel tank 19 via a filter 20.
  • the outlet of the high pressure pump 21 is connected to a rail 22 which serves to store the fuel under pressure and from which injectors (not shown) are supplied with the fuel under pressure.
  • the inlet of the high-pressure pump is connected to a channel 7, which is inserted into a housing 3 and is connected to a groove 8.
  • the housing 3 has a bore which receives the shaft 1 and a sleeve 2 enclosing the shaft 1.
  • the non-rotating sleeve 2 is arranged axially displaceable on the shaft.
  • the groove 8 accommodated in the housing 3 and the groove 5 located in the shaft 1 are arranged in such a way that they lie opposite one another.
  • the sleeve 2 is located between the two grooves 5 and 8.
  • the groove 8 can also extend over the entire circumference of the housing 3.
  • the groove 5 could extend over the entire circumference of the shaft 1.
  • the opening 6 in the sleeve 2 is designed so that it depends result in different opening and closing angles from the axial position of the sleeve 2.
  • the exemplary embodiments each relate to a high-pressure pump with three cylinders, so that the shaft 1 has three grooves 5a, 5b, 5c and the sleeve 2 has three openings 6a, 6b, 6c.
  • the grooves 5a, 5b, 5c and the openings 6a, 6b, 6c are designed as elongated slots.
  • the grooves 5a, 5b, 5c are arranged in a step-like manner on the lateral surface of the shaft 1 and extend in the axial direction, ie the grooves 5a, 5b, 5c are offset from one another in the axial direction and in the circumferential direction in each case by a certain distance.
  • the openings 6a, 6b, 6c of the sleeve 2 are oriented at a certain angle between the circumferential direction and the axial direction and are displaced parallel to one another in the axial direction and offset by a certain distance in the circumferential direction.
  • the axial displacement of the sleeve 2 changes the angle (phase length) of the overlap of the groove 5a and the opening 6a. By linking these overlaps with the position of the respective piston 21a, a defined volume can be let into the respective cylinder 21b.
  • the axial displacement of the sleeve 2 represents the adjustment range, which is the same for all speeds. Due to the use of straight grooves and slots, there is a non-linear relationship between the axial displacement of the sleeve and the degree of filling of the displacement elements.
  • the Zusa - is menhang for all speeds between a minimum speed n m i n and a maximum speed n max same.
  • the embodiment of the sleeve 2 and the shaft 1 shown in FIG. 3 arises from the embodiment according to FIG. 2 in such a way that the configuration and orientation of the slot-shaped grooves 5d, 5e, 5f or the openings 6d, 6e, 6f are interchanged .
  • the opening and closing behavior is retained.
  • the embodiment described in FIG. 3 therefore acts in the same way as that described in FIG. 2.
  • FIGS. 4 and 5 emerge from the embodiments according to FIGS. 2 and 3 in that the angle between the respective slot-shaped groove 5g to 51 and the respective slot-shaped opening 6g to 61 is no longer positive but negative.
  • the embodiment according to FIG. 4 corresponds to that according to FIG. 2
  • the embodiment according to FIG. 5 corresponds to that according to FIG. 3
  • the movement and adjustment directions and orientations shown in FIGS. 2 and 3 result in a fixed opening angle and a closing angle which is variable between 180 ° and 0 °.
  • the grooves and openings are designed as parallel slots.
  • these elements can also be given a different shape.
  • an edge 10b of a groove or an opening can be rotated until it lies parallel to an edge 9a of an assigned opening or an assigned groove.
  • Any shape of the opening or the groove within the respective triangle shown in dashed lines is possible. Consequently, the rear edge 9b of the groove or of the opening can be rotated around the lower right corner in the same way until it lies parallel to the edge 10a. Any other shape is also conceivable here as long as it lies within the associated dashed triangle.
  • Figure 7 shows a possible variant.
  • a groove or an opening 11 is arranged at a positive angle between 0 ° and 90 ° to an opening or a groove 12. While the opening or the groove 12 is a straight-line slot, the groove or the opening 11 has a serpentine shape. This can be used, for example, to achieve a linear relationship between the adjustment path of the respective sleeve, not shown, and the degree of filling of the associated cylinder.
  • a positive angle between the groove and the opening it is also possible a negative angle and any other shape can be used instead of the snake shape or the slot shape in order to achieve a control-related connection.
  • FIG. 8 Another embodiment of a metering device with a metering controlled by the phase length is obtained if, in addition to the outlet to the cylinders, the inlet from the prefeed pump is also fixed in the metering device housing. Such an embodiment is shown in FIG. 8. On a shaft 13 there is one with the shaft
  • axially displaceable sleeve 17 rotating in a housing.
  • the inlet 14 from the prefeed pump 18 and the outlet 15 to the high-pressure pump 21 are introduced in a housing as fixed channels.
  • the sleeve 17 could be omitted if the shaft is axially displaceable relative to the housing and the groove 16 is introduced into the shaft 13 with the edge 23.
  • FIG. 9 An approximately triangular groove 25 with an inclined edge 26 is located in a shaft 24.
  • an inlet 28 and an outlet 29 are introduced as channels directed radially onto the shaft 24 in the end region.
  • the shaft 24 is axially displaceable relative to the housing 27.
  • the mode of operation corresponds to the embodiment shown in FIG. 8 due to the same relative movement and shape.
  • control slots described so far in the cylindrical shafts or sleeves can also be axially touching Disks, nested cones or other shaped bodies can be incorporated.
  • a disk 31, which is applied or molded onto a shaft 30, is provided with an aperture 32 penetrating the disk 31 in the direction parallel to the shaft axis.
  • a channel which can be displaced in the radial direction parallel to the plane of the disk forms the inlet 33 and is arranged such that it meets the opening 32 or not, depending on its axial position.
  • a channel parallel to the shaft axis as outlet 34 is arranged in a stationary manner on the side of disk 31 opposite inlet 33 such that the maximum possible overlap is achieved during one revolution of shaft 30 for a given breakthrough shape between outlet 34 and opening 32.
  • the inlet 33 is accommodated in a slide 35, which in turn, like the shaft 30, the disk 31 and the outlet 34, are located in a housing 36.
  • the breakthrough in the present exemplary embodiment is based on a shape which surrounds the shaft in a semicircular shape, the breakthrough widening in the radial direction with increasing disk angle.
  • any other suitable shape can also be used.
  • the phase length of the overlap of inlet 33, outlet 34 and disk 31 and thus the phase length of the open inlet to the conveying elements can in turn be varied by radial displacement of the slide 35 and thus the inlet 33.
  • the inlet and outlet can be accommodated together in the slide, in which case an appropriately shaped groove is machined in the disk instead of the opening.
  • FIG. 11 shows an exemplary embodiment with a conical base body which is applied or molded onto a shaft 37 and is referred to below as cone 38.
  • a groove 39 is provided on the lateral surface, which is provided with an inclined edge 40 and is connected to a channel 41 leading to the base surface of the cone.
  • the mouth opening of the channel 41 in the area of the base of the cone has approximately the shape of a semicircular opening around the shaft, for example of constant width, the opening being designed such that between a stationary outlet 42 running parallel to the shaft and the Opening the maximum overlap occurs.
  • An inlet 43 is integrated in a slide 44, which is displaceable in the direction between the cone tip and the base surface along the lateral surface. Depending on the position of the slide 44, a certain phase length occurs
  • a housing 45 is provided for receiving the shaft 37, the cone 38, the outlet 42 and the slide 44.
  • the drain can also be integrated into the slide and a groove can be provided instead of the opening.
  • inlet and outlet can also be interchanged in all of the exemplary embodiments.
  • the statements made for the displaceable sleeves also apply analogously to the remaining exemplary embodiments.
  • only one "control slot” is shown in the exemplary embodiments in FIGS. 10 and 11, in the same way several "control slots” in the form of grooves, openings, etc. on a sleeve, disk or cone or several sleeves, disks or cones with each a "control slot" can be used.
  • a characteristic curve to illustrate an exemplary relationship between the manipulated variable (for example displacement of the sleeve relative to the shaft) and volume flow V is shown in FIG.
  • the manipulated variable for example displacement of the sleeve relative to the shaft
  • volume flow V volume flow

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif pour produire un débit variable dans une alimentation en carburant. Ce dispositif comprend une pompe à haute pression (21), qui présente au moins une arrivée, au moins un cylindre (21b), au moins un piston (21a) pouvant se déplacer à l'intérieur de ce dernier, et un arbre (1) entraînant le ou les pistons (21a), ainsi qu'une unité de dosage (2-8) qui est placée dans l'arrivée ou les arrivées de la pompe à haute pression (21), est synchronisée avec l'arbre (1) et qui, à chaque rotation de l'arbre (1), achemine au(x) cylindre(s) (21b) un volume de carburant pouvant être dosé de façon variable. Le dosage s'effectue par modification de l'angle d'ouverture et de fermeture dans l'arrivée ou les arrivées.
EP99960884A 1998-11-25 1999-11-10 Dispositif pour produire un debit variable dans une alimentation en carburant Expired - Lifetime EP1049869B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19854509A DE19854509C2 (de) 1998-11-25 1998-11-25 Vorrichtung zum Erzeugen eines variablen Volumenstromes bei einer Kraftstoffzuführung
DE19854509 1998-11-25
PCT/DE1999/003581 WO2000031409A1 (fr) 1998-11-25 1999-11-10 Dispositif pour produire un debit variable dans une alimentation en carburant

Publications (2)

Publication Number Publication Date
EP1049869A1 true EP1049869A1 (fr) 2000-11-08
EP1049869B1 EP1049869B1 (fr) 2004-02-25

Family

ID=7889059

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99960884A Expired - Lifetime EP1049869B1 (fr) 1998-11-25 1999-11-10 Dispositif pour produire un debit variable dans une alimentation en carburant

Country Status (4)

Country Link
US (2) US6293250B1 (fr)
EP (1) EP1049869B1 (fr)
DE (2) DE19854509C2 (fr)
WO (1) WO2000031409A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19952000C2 (de) * 1999-10-28 2001-08-16 Siemens Ag Vorrichtung zum Erzeugen eines variablen Volumenstroms für eine Pumpe
DE19951999B4 (de) * 1999-10-28 2004-11-18 Siemens Ag Einspritzanlage für eine Brennkraftmaschine
DE10029420B4 (de) * 2000-06-15 2006-05-04 Siemens Ag Vorrichtung zum Zuführen von Fluid zu einer Pumpe
US6596617B1 (en) 2000-06-22 2003-07-22 Progressant Technologies, Inc. CMOS compatible process for making a tunable negative differential resistance (NDR) device

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1429936A (en) * 1972-06-10 1976-03-31 Simms Group Research Dev Ltd Liquid fuel injection pumping apparatus
WO1980002183A1 (fr) * 1979-04-10 1980-10-16 A Takacs Dispositif de commande d'injection de combustible
US5058553A (en) * 1988-11-24 1991-10-22 Nippondenso Co., Ltd. Variable-discharge high pressure pump
DE3844363A1 (de) * 1988-12-30 1990-07-05 Bosch Gmbh Robert Elektrisch gesteuerte kraftstoffeinspritzpumpe
DE3927742A1 (de) * 1989-08-23 1991-02-28 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5099814A (en) * 1989-11-20 1992-03-31 General Motors Corporation Fuel distributing and injector pump with electronic control
US5123393A (en) * 1991-09-04 1992-06-23 Stanadyne Automotive Corp. Timing control system for fuel injection pump
DE4141699A1 (de) * 1991-12-18 1993-07-01 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0643220B1 (fr) * 1993-09-14 1998-04-22 Lucas Industries Public Limited Company Système de carburant
GB9509609D0 (en) * 1995-05-12 1995-07-05 Lucas Ind Plc Fuel supply apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0031409A1 *

Also Published As

Publication number Publication date
DE19854509C2 (de) 2000-11-23
US6293250B1 (en) 2001-09-25
WO2000031409A1 (fr) 2000-06-02
DE59908649D1 (de) 2004-04-01
EP1049869B1 (fr) 2004-02-25
DE19854509A1 (de) 2000-06-08
USRE38192E1 (en) 2003-07-22

Similar Documents

Publication Publication Date Title
EP0678166B1 (fr) Dispositif de commande pour une pompe a volume de remplissage variable
DE60203130T2 (de) Hybridsteuerverfharen für kraftstoffpumpe unter verwendung intermittierender rezirkulation bei niedrigen und hohen motordrehzahlen
DE2430733A1 (de) Brennstoffeinspritzpumpe
DE69013283T2 (de) Hochdruck-Kraftstoffeinspritzeinheit mit Steuerung des Druckes der Kammer für den Spritzzeitpunkt.
DE3545052A1 (de) Brennstoff-einspritzpumpe fuer eine wenigstens vierzylindrige brennkraftmaschine
EP0150471B1 (fr) Pompe d'injection de combustible
EP0960275B1 (fr) Pompe haute pression destinee a l'alimentation en carburant des systemes a injection de carburant de moteurs a combustion interne
EP0273225B1 (fr) Pompe d'injection de combustible pour moteurs à combustion interne
DE3911160C2 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
EP1049869B1 (fr) Dispositif pour produire un debit variable dans une alimentation en carburant
DE3128975A1 (de) Kraftstoffeinspritzpumpe
DE4441506A1 (de) Kraftstoffeinspritzpumpe
WO1998023858A1 (fr) Systeme d'injection de carburant
EP1306553A2 (fr) Pompe à carburant, système de distribution, procédé d'exploitation dudit système et moteur à combustion interne
DE3236828A1 (de) Brennstoffeinspritzvorrichtung
WO1989010479A1 (fr) Unite de cylindre et piston a haute pression
DE3524241A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2503300A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2937222A1 (de) Kraftstoff-einspritzpumpvorrichtung
DE2911097A1 (de) Fluessigkraftstoff-einspritzeinrichtung
EP1096148B1 (fr) Dispositif pour variation de débit d'une pompe
DE3615919A1 (de) Kraftstoffeinspritzpumpe fuer eine brennkraftmaschine
DE68906515T2 (de) Brennstoffeinspritzpumpe.
DE2918867A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2647973A1 (de) Brennstoffeinspritzvorrichtung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20000719

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 59908649

Country of ref document: DE

Date of ref document: 20040401

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20040319

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20041126

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20110825 AND 20110831

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20151130

Year of fee payment: 17

Ref country code: GB

Payment date: 20151118

Year of fee payment: 17

Ref country code: IT

Payment date: 20151125

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20151119

Year of fee payment: 17

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59908649

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20161110

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20170731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170601

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110