EP1091120A2 - Verfahren zum Ermitteln oder Steuern eines Betriebsparameters einer Pumpe - Google Patents
Verfahren zum Ermitteln oder Steuern eines Betriebsparameters einer Pumpe Download PDFInfo
- Publication number
- EP1091120A2 EP1091120A2 EP00121761A EP00121761A EP1091120A2 EP 1091120 A2 EP1091120 A2 EP 1091120A2 EP 00121761 A EP00121761 A EP 00121761A EP 00121761 A EP00121761 A EP 00121761A EP 1091120 A2 EP1091120 A2 EP 1091120A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pressure
- angular position
- fuel
- volume
- 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
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
- F04B49/065—Control using electricity and making use of computers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1208—Angular position of the shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/06—Pressure in a (hydraulic) circuit
- F04B2205/063—Pressure in a (hydraulic) circuit in a reservoir linked to the pump outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/13—Pressure pulsations after the pump
Definitions
- the invention relates to a method for determining or controlling an operating parameter of a pump according to the preamble of claim 1.
- fuel is supplied by one Prefeed pump removed from a tank and a high pressure pump fed.
- the high pressure pump supplies a fuel reservoir, the so-called common rail, with fuel.
- On injectors are connected to the fuel accumulator, which are controlled by a control unit and accordingly inject fuel into an internal combustion engine.
- the Amount of fuel that is in the high pressure accumulator from the High pressure pump is pumped through a volume flow control valve in the suction area of the high pressure pump.
- Superfluous Fuel is drawn from the fuel reservoir via a Pressure control valve returned to the tank. Warmed up when relaxing the fuel, so that the temperature of the Fuel in the fuel tank increases.
- a power loss represents.
- the object of the invention is a method for determining or to provide control of an operating parameter of a pump, which is an improved mode of operation of the pump enables.
- An advantage of the invention is that the location of Extreme pressure during a compression process of the pump in the volume into which the pump pumps medium and that based on the temporal position and / or angular position the extreme pressure determines an operating parameter of the pump and / or the pump is controlled.
- Fig. 1 shows a fuel tank 1, from which a prefeed pump 2 takes fuel and via a volume flow control valve 3 and a feed line 19 to a high pressure pump 4.
- the high pressure pump 4 compresses the supplied fuel and delivers the compressed fuel through a drain 20 on to a fuel accumulator 5.
- injection valves 6 are connected, the Controlled by a control unit 8 via a third control line 16 become. According to the control by the control unit 8 give the injectors 6 fuel from the fuel accumulator 5 in the internal combustion engine 17.
- a pressure control valve 7 connected via an output line communicates with the fuel tank 1.
- the Pressure control valve 7 is connected to a second control line 12 with the control unit 8 in connection.
- a pressure sensor 14 arranged on the fuel accumulator 5, which has a second data line 13 with the control unit 8 in connection stands.
- Sensors 15 are assigned to internal combustion engine 17, which are connected to the control unit 8 via a fourth data line 18 are.
- the control unit 8 is also above a first one Data line 10 with a data memory 9 in connection. Furthermore, the control device 8 is via a first control line 11 connected to the volume flow control valve 3.
- the pre-feed pump 2 and the high pressure pump 4 become mechanical driven by the internal combustion engine 17.
- the speed the pre-feed pump 2 and the speed of the high pressure pump 4 are proportional to the speed of the internal combustion engine 17.
- Die High-pressure pump 4 is, for example, a radial piston pump with three pistons 22, as shown in Fig. 2.
- Fig. 2 shows schematically the piston arrangement of a radial piston pump with three pistons.
- Each piston 22 is over a first one Check valve 23 in the inlet and via a second check valve 25 in the process with the feed line 19 or with the Derivation 20 connected.
- the piston 22 of the radial piston pump are star-shaped around a rotary shaft 21 of the high pressure pump 4 arranged, which is driven by the internal combustion engine 17 becomes.
- the rotary shaft 21 is surrounded by an eccentric ring 26, which the eccentric rotational movement of the rotary shaft 21 in implements a radial stroke movement of the pistons 22.
- the piston 22 is the 360 ° during an entire revolution Rotary shaft 21 from its bottom dead center to top dead center moved and then from top dead center back to bottom dead center moves.
- the piston 22 is from the upper Dead center moved to bottom dead center and over a first one Check valve 23 fuel from the feed line 19 in the Cylinder chamber 24 sucked.
- the piston 22 is positively guided so that regardless of the amount of fuel that over the first check valve 23 is sucked in, always from the lower Dead center to top dead center and then to bottom Dead center moves during one revolution of the rotary shaft 21.
- the first check valve 23 is biased by a spring 27.
- the spring 27 ensures that a vacuum is always in the cylinder chamber 24 and not in the feed line 19. Vacuum can arise, for example, when the volume flow control valve 3 less fuel supplied to the piston 22 is considered due to the size of the cylinder chamber 24 a suction process between the top dead center and the bottom Dead center could be sucked in by the piston 22.
- the piston 22 is from the lower Dead center shifted to top dead center.
- the degree of filling of the cylinder chamber 24 defines that of the piston 22 Amount of fuel delivered during a compression process firmly.
- the piston 22 pushes during a compression process each the amount of fuel in the discharge line 20 that during of the suction process was sucked into the cylinder chamber 24.
- High pressure pump 4 is in by pushing out fuel the fuel accumulator 5 a pressure wave in the fuel accumulator 5 generated.
- the pressure waves generated by the three pistons 22 are due to the phase shift of the movements of the three pistons 22 with the same delivery of the three pistons by 120 ° each transferred.
- 3A and Fig. 3B show the delivery volume flow V of the piston 22 as a function of of the angle of rotation ⁇ of the rotary shaft 21 for different Filling levels.
- the piston 22 moves from the bottom Dead center UT to top dead center OT.
- 3A and FIG. 3B shows the front of the control unit 8 measured via the pressure sensor 14 Pressure signal p shown for the piston 22. Basically applies that if more fuel from the fuel storage 5 flows as from the high pressure pump 4 in the Fuel storage is promoted, the pressure in the fuel storage drops because the mass balance is negative.
- the pressure in the fuel accumulator 5 increases a positive mass balance, i.e. if more fuel in the fuel storage is promoted as it flows out, on.
- V of the piston 22 is shown in dashed lines, in which the middle Inflow into the fuel accumulator 5 whose mean outflow corresponds.
- N the areas of a negative mass balance and thus a pressure drop in the fuel accumulator or with P the Areas of a positive pressure balance and thus a pressure increase marked in the fuel storage 5.
- the delivery flow of the piston 22 is at a fill level F of the cylinder chamber 24 is represented by 100%, i.e. that the volume flow control valve 3 opened so far by the control unit 8 will that during the suction process of the piston 22 Cylinder chamber 24 is completely filled with fuel.
- the delivery volume flow V of the piston increases 22 first from bottom dead center UT, then to to drop towards top dead center again. Because of this The course of the volume flow is the mass balance in Fuel store 5 first negative, then positive and for Again negative.
- the measurement diagram shown in FIG. 3B corresponds to one Filling degree F of the cylinder chamber 24 of 25%.
- the points of a balanced mass balance are at Transition from the negative mass balance N to the positive mass balance P and from the positive mass balance P back to negative mass balance N over the pumping movement of the piston 22 from bottom dead center UT to top dead center OT towards shifted to the top dead center.
- Fig. 3A 3B shows fluctuations in the mass balance and thus remain in the pressure of the fuel accumulator 5.
- the position of the multi-piston pumps also shifts Extreme pressure with different filling levels of the cylinder chambers. 4 is the shift of the pressure maximum for simulates a three-piston pump, as shown in Fig. 3 is.
- the graphic clearly shows that the situation of the pressure maximum with decreasing delivery rate and thus decreasing Degree of filling of the cylinder chambers towards larger pump angles and thus moves towards top dead center OT.
- FIG. 5 shows a method for operating a pump according to Figures 1 and 2 described.
- Starts at program point 40 the engine 17 by a starter and rotates the pre-feed pump 2 and the high pressure pump 4 with predetermined Initial speeds.
- the control unit 8 opens it Volume flow control valve 3 to a cross section, for the Starting process is stored in the data memory 9.
- the opening cross section of the volume flow control valve 3 selected as large as possible when starting the internal combustion engine 17, so that the high pressure pump 4 as quickly as possible the operation of the internal combustion engine 17 required fuel pressure builds up in the fuel accumulator 5.
- the control unit 8 determines at program point 41 the angular position of the pressure tip in relation to the rotational position the rotary shaft 21.
- the bottom and top dead center UT, TDC of the piston 22 are predetermined angular values of the rotating shaft 21 assigned.
- control unit 8 determines the angle difference to the top dead center of the piston 22, from which the pressure peak was generated.
- the angular position of the pressure tip can So also directly from the evaluation of an amplitude and one Phase response of the pressure curve can be obtained.
- the control unit 8 calculates from the angular position the pressure peak the fuel volume delivered by the piston 22.
- a table is stored in the data memory 9, in which 4 values for the pistons 22 of the high pressure pump the fuel volume delivered depending on the angular position the pressure peak are stored.
- the delivery volume of Pump 4 per revolution of the rotary shaft 21 depending on the angular positions of the pressure peaks generated in the pressure accumulator 5 measured during one revolution of the rotary shaft 21 and as a function of the angular positions of the pressure peak in the data memory 9 filed.
- the pressure peaks of the three Piston 22 of the pump 4 evaluated during one revolution the rotary shaft 21 are generated.
- a Type of calculation averaged the angular positions of the pressure peaks, generated during one revolution of the rotary shaft 21 become.
- a mean Delivery rate read from the table from the data memory 9, which multiplied by the number of three pistons and thus the delivery rate of the high pressure pump 4 per revolution the rotating shaft 21 is calculated.
- 22 is used for each piston measured the angular position of the pressure wave and based on the three angular positions each calculated the delivery of the pistons, the fuel during one revolution of the rotary shaft 21 promote. The sum of the three production quantities becomes the Flow rate of the high pressure pump 4 calculated for one revolution.
- control unit 8 Quantity of fuel delivered via the fuel injection valves 6 determined.
- that of the high pressure pump 4 fuel quantity delivered over a certain period of time determined and the over the same period of the amount of fuel delivered to the injection valves 6 is determined. This is done from the fuel pressure that occurs during the injection processes prevailed in the fuel store 5 and the opening times of the injection valves 6, the injection valves 6 amount of fuel delivered during the specified period calculated.
- the control unit compares the data from the Period from the high pressure pump 4 to the fuel accumulator 5 amount of fuel delivered with the via the injection valves 6 amount of fuel delivered over the same period and checks whether the pressure in the fuel accumulator 5 changes accordingly the difference has increased or decreased. Is that true Change in fuel pressure in the fuel accumulator 5 not with the high pressure pump 4 and the Injectors 6 discharged fuel amount match, so a defect such as increased leakage in the injection system recognized.
- the control unit 7 shows a method for controlling the volume flow control valve 3 depending on the angular position of the pressure peaks, generated by the pistons 22 in the fuel accumulator 5 become.
- the control unit determines at program point 60 8 the angular position of the pressure extremes of the piston 22. From the The control unit 8 calculates the table in the data memory 9 correspondingly from the high pressure pump 4 into the fuel accumulator 5 amount of fuel delivered. The amount of fuel delivered compares control unit 8 at program point 61 a target delivery rate specified by a control program.
- An embodiment of the method according to FIG. 7 is based on that the volume flow control valve based on one of one Control program predetermined target angle position for the pressure peak is controlled.
- the control program depends on this a desired angular position of operating parameters of the internal combustion engine for the pressure peak.
- the control unit 8 measures via the pressure sensor 14 the position of the pressure peak and compares the measured position with the target position of the Pressure peak.
- the measured angular position of the pressure peak is in comparison to the target angular position too close to the top dead center of the promoting piston, then the opening cross section of the Volume flow control valve 3 enlarged by a predetermined value.
- the predetermined value is preferably proportional to the difference angle between the target angular position and the measured angular position of the pressure peak.
- the measured angular position of the pressure peak is in comparison to the target angular position too far from top dead center, then the opening cross section of the volume flow control valve reduced by a predetermined value.
- the specified value is proportional to the difference angle between the target angular position and the measured Angle position of the pressure tip.
- a preferred embodiment of the method according to FIG. 7 is based on the fact that the control unit 8 determines the angular position of the Pressure peaks of at least two pistons delivering one after the other 22 determined and the angular position of the pressure peaks used to the volume flow control valve 3 in the way control that the angular positions of the successive conveying Pistons 22 are identical, so that equal funding by the piston 22 is reached. It will be the same size Flow through the piston 22 of the high pressure pump 4 thereby achieved that the volume flow control valve 3 controlled in this way is that the angular positions of the pressure peaks of the different pistons 22 are the same. This procedure allows a simple process for controlling equal opportunities several pistons 22 of a high pressure pump 4.
- the method described can be applied to any type of pump and not limited to the system described.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Computer Hardware Design (AREA)
- Fuel-Injection Apparatus (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
Description
Claims (9)
- Verfahren zum Ermitteln oder Steuern eines Betriebsparameters einer Pumpe,
wobei der Pumpe Pumpmedium zugeführt wird, und
wobei wenigstens ein Verdrängerelement von einer Drehwelle der Pumpe angetrieben wird, das während eines Verdichtungsvorgangs Pumpmedium in ein Volumen pumpt,
dadurch gekennzeichnet,daß die Lage eines Druckextremums in dem Volumen (20, 5) während des Pumpvorgangs ermittelt wird, unddaß abhängig von der zeitlichen Position und/oder Winkelposition des Druckextremums ein Betriebsparameter der Pumpe (4) ermittelt und/oder ein Betriebsparameter der Pumpe (4) gesteuert wird. - Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß abhängig von der zeitlichen Position und/oder Winkelposition des Druckextremums die von wenigstens einem Verdrängerelement (22) in das Volumen (20, 5) geförderte Menge an Pumpmedium bestimmt wird.
- Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß die der Pumpe (4) zugeführte Menge an Pumpmedium eingestellt wird, oder daß der Winkelbereich, in dem das Verdrängerelement (22) während des Verdichtungsvorganges Pumpmedium in das Volumen (20, 5) pumpt, abhängig von der Menge des zugeführten Pumpmediums eingestellt wird,daß die Winkelposition des Druckextremums erfaßt wird, unddaß in Abhängigkeit von der Winkelposition des Druckextrema die vom Verdrängerelement (22) in das Volumen (20, 5) gepumpte Menge an Pumpmedium ermittelt wird.
- Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß von abhängig von der zeitlichen Position und/oder Winkelposition des Druckextremums die Zufuhr an Pumpmedium zur Pumpe (4) gesteuert wird.
- Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß die der Pumpe (4) zugeführte Menge an Pumpmedium eingestellt wird, oder daß der Winkelbereich, in dem das Verdrängerelement (22) während des Verdichtungsvorganges Pumpmedium in das Volumen (20, 5) pumpt, abhängig von der Menge des zugeführten Pumpmediums eingestellt wird,daß die Winkelposition des Druckextrema erfaßt wird, unddaß abhängig von der Winkelposition des Druckextremums die der Pumpe zugeführte Menge an Pumpmedium eingestellt wird.
- Verfahren nach Anspruch 2, dadurch gekennzeichnet, daß eine Tabelle verwendet wird, in der abhängig von der Winkelposition des Druckextremums die Fördermenge des Verdrängerelementes abgelegt ist, unddaß anhand der Werte in der Tabelle die Fördermenge des Verdrängerelementes (22) bestimmt wird.
- Verfahren nach Anspruch 2, dadurch gekennzeichnet, daß die Fördermenge der Pumpe (4) abhängig von der Drehzahl der Pumpe (4), abhängig vom Hubvolumen der Pumpe (4) pro Umdrehung der Drehwelle (21) und abhängig von der Winkelposition der Druckextrema berechnet wird, wobei eine Tabelle verwendet wird, in der das Fördervolumen der Pumpe (4) abhängig von der Winkelposition der Druckextrema abgelegt ist.
- Verfahren nach Anspruch 4, dadurch gekennzeichnet, daß die zeitlichen Positionen und/oder die Winkelpositionen der Druckextrema zweier beliebiger aufeinanderfolgender Verdrängerelemente (22) der Pumpe (4) bestimmt werden, unddaß die der Pumpe (4) zugeführte Menge an Pumpmedium in Abhängigkeit von der Winkelposition der zwei Druckextrema in der Weise so eingestellt wird, daß die zwei Verdrängerelemente eine nahezu gleich große Menge an Medium in das Volumen (20, 5) pumpen.
- Verfahren nach Anspruch 2, dadurch gekennzeichnet, daß als Pumpe (4) eine Kraftstoffpumpe verwendet wird, wobei an das als Leitung (20) und Kraftstoffspeicher (5) ausgebildete Volumen ein Einspritzventil (6) angeschlossen ist,daß die während eines Vergleichszeitraums vom Einspritzventil (6) abgegebene Kraftstoffmenge ermittelt wird,daß die abgegebene Kraftstoffmenge mit dem Fördervolumen verglichen wird, unddaß aufgrund des Vergleichs eine Aussage über die Funktionsweise der Einspritzanlage getroffen wird.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19947890 | 1999-10-05 | ||
DE19947890A DE19947890B4 (de) | 1999-10-05 | 1999-10-05 | Verfahren zum Betreiben einer Pumpe in einer Kraftstoffeinspritzanlage |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1091120A2 true EP1091120A2 (de) | 2001-04-11 |
EP1091120A3 EP1091120A3 (de) | 2002-07-03 |
EP1091120B1 EP1091120B1 (de) | 2005-02-16 |
Family
ID=7924524
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00121761A Expired - Lifetime EP1091120B1 (de) | 1999-10-05 | 2000-10-05 | Verfahren zum Ermitteln oder Steuern eines Betriebsparameters einer Pumpe |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1091120B1 (de) |
DE (2) | DE19947890B4 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004015618A1 (de) * | 2004-03-30 | 2005-10-20 | Zexel Valeo Compressor Europe | Hubraumvariabler Verdichter sowie Verfahren zur Regelung des Kolbenhubs in einem solchen |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4964985A (en) * | 1986-09-17 | 1990-10-23 | U.S. Philips Corporation | Liquid chromatograph |
EP0501459A2 (de) * | 1991-02-27 | 1992-09-02 | Nippondenso Co., Ltd. | System und Verfahren zur Kraftstoffeinspritzung mit gemeinsamer Brennstoffleitung |
US5197438A (en) * | 1987-09-16 | 1993-03-30 | Nippondenso Co., Ltd. | Variable discharge high pressure pump |
WO1997032128A1 (en) * | 1996-02-27 | 1997-09-04 | Amersham Pharmacia Biotech Ab | Pump |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS506043B1 (de) * | 1969-05-19 | 1975-03-10 | ||
DE3935325C1 (de) * | 1989-10-24 | 1991-05-23 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De |
-
1999
- 1999-10-05 DE DE19947890A patent/DE19947890B4/de not_active Expired - Fee Related
-
2000
- 2000-10-05 EP EP00121761A patent/EP1091120B1/de not_active Expired - Lifetime
- 2000-10-05 DE DE50009538T patent/DE50009538D1/de not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4964985A (en) * | 1986-09-17 | 1990-10-23 | U.S. Philips Corporation | Liquid chromatograph |
US5197438A (en) * | 1987-09-16 | 1993-03-30 | Nippondenso Co., Ltd. | Variable discharge high pressure pump |
EP0501459A2 (de) * | 1991-02-27 | 1992-09-02 | Nippondenso Co., Ltd. | System und Verfahren zur Kraftstoffeinspritzung mit gemeinsamer Brennstoffleitung |
WO1997032128A1 (en) * | 1996-02-27 | 1997-09-04 | Amersham Pharmacia Biotech Ab | Pump |
Also Published As
Publication number | Publication date |
---|---|
DE19947890B4 (de) | 2005-10-27 |
DE50009538D1 (de) | 2005-03-24 |
EP1091120B1 (de) | 2005-02-16 |
DE19947890A1 (de) | 2001-04-19 |
EP1091120A3 (de) | 2002-07-03 |
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