EP1201913A2 - Kraftstoffhochdruckpumpe mit veränderlicher Fördermenge - Google Patents
Kraftstoffhochdruckpumpe mit veränderlicher Fördermenge Download PDFInfo
- Publication number
- EP1201913A2 EP1201913A2 EP01123835A EP01123835A EP1201913A2 EP 1201913 A2 EP1201913 A2 EP 1201913A2 EP 01123835 A EP01123835 A EP 01123835A EP 01123835 A EP01123835 A EP 01123835A EP 1201913 A2 EP1201913 A2 EP 1201913A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- rotation angle
- angle range
- fuel pump
- pressure fuel
- 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
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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
- 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
-
- 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
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- 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
-
- 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
- F04B49/24—Bypassing
- F04B49/243—Bypassing by keeping open the inlet valve
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
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- 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
- F04B2205/09—Flow through the pump
Definitions
- the invention relates to a high-pressure fuel pump variable delivery rate for an internal combustion engine, with a piston actuated by a camshaft, the Piston fuel from a low pressure line into one Suction chamber and then into a High pressure line promotes, and with a pumping room and Volume control valve connecting high pressure line.
- the high-pressure fuel pump is the delivery rate regulated that the volume control valve at the beginning of Production stroke is closed and during the production stroke is opened. Has due to the dead volume in the delivery room the piston at the time the exhaust valve opens (Start of funding in high-pressure pipeline and rail) already one high speed. This leads to this due to the Point of liquid standing in the High pressure line that needs to be accelerated to one Pressure surge. This pressure surge complicates the exact Quantity metering when fuel is injected into the Combustion chamber and also leads to swelling the high pressure line and the common rail. Also are the mechanical loads on the high pressure fuel pump and the camshaft due to the shock load Start of fuel delivery in the high pressure line very much high.
- the invention has for its object a High pressure fuel pump with variable delivery rate to provide, in which the pressure surges in the High pressure line and in the common rail compared to the state of the Technology significantly reduced and the mechanical Stresses on the high-pressure fuel pump reduced become.
- a High pressure fuel pump with variable delivery rate for an internal combustion engine with one of a camshaft actuated piston, the piston fuel from a Low pressure line sucks into a delivery chamber and then conveys into a high pressure line, whereby between the delivery chamber and the low pressure line Volume control valve and a separate suction valve in parallel are switched and the regulation of the delivery rate by opening the volume control valve during the delivery stroke of the piston.
- the pressure increase in Delivery chamber always from the bottom dead center (UT) of the piston takes place regardless of the speed and the Operating point of the internal combustion engine the pressure curve in Delivery room and thus also in the high pressure line be designed so that the pressure surges in the High pressure line and in the common rail and the jerky Loads on the high pressure fuel pump can be reduced.
- the level of the pressure surge depends on the Speed of the cam at the time of opening Exhaust valve.
- each cam of the camshaft has at least a first rotation angle range, a second rotation angle range and a third rotation angle range, the bottom dead center (UT) of the piston lying within the first rotation angle range, so that the piston reaches after reaching the UT the piston experiences a positive acceleration in the first rotation angle range, that within the second rotation angle range, the stroke speed V H / ⁇ of the piston is approximately constant, that the outlet valve of the high-pressure pump opens while the cam passes through the second rotation angle range, and that within the third Angle range, the stroke speed of the piston increases until a maximum value is reached.
- the second angle of rotation range with an approximately constant, as low as possible stroke speed V H / ⁇ has the advantage that, regardless of the delivery rate, ie the time at which the exhaust valve opens, the stroke speed V H essentially depends only on the speed of the camshaft. This makes it possible to limit the pressure surge p s to a permissible level by selecting a low lifting speed even at the maximum speed of the high-pressure fuel pump and maximum pressure in the high-pressure line. As a result, the injection quantity can be controlled with greater accuracy and the above-mentioned swelling loads and shock-like loads are reduced.
- the Acceleration of the piston in the first angular range the maximum permissible speed of the high-pressure fuel pump essentially by the mass forces of the piston limited so that the first rotation angle range is as small as can be kept possible.
- the piston experiences no or less positive acceleration in the second rotational angle range at the permissible maximum speed of the high-pressure fuel pump than in the first rotational angle range.
- the stroke speed of the piston can also increase in the second rotation angle range by means of a small positive acceleration - provided the permissible pressure surges p s in the high-pressure line are not exceeded - and the same delivery stroke can thus be achieved within a smaller rotation angle range. This measure allows the maximum stroke speed of the piston to be reduced, which at high speeds of the high-pressure fuel pump leads to a reduction in the flow losses at the quantity control valve during shutdown and thereby increases the pump efficiency.
- High pressure fuel pump will accelerate the Piston in the third range of rotation at the permissible Maximum speed of the high pressure fuel pump through the limited maximum pressure, so that on the one hand the maximum piston speed in the delivery stroke as fast as possible and, on the other hand, no impermissible ones Stresses of the high pressure fuel pump occur.
- the third range of rotation must be the piston against the pressure Do work in the high pressure line.
- each cam has a fourth, a fifth and has a sixth rotation angle range that the top dead center (TDC) of the piston between fourth Angle range and fifth angular range is that the positive acceleration of the piston in the fourth Angular range becomes negative that the piston in the fifth Angular range experiences a negative acceleration, and that within the sixth rotation angle range Piston stroke speed negative and approximate is constant.
- TDC top dead center
- the high pressure fuel pump is the volume control valve is open when de-energized Solenoid valve so that impermissible pressures in the Fuel feed pump even if the Quantity control valve or its control prevented become.
- the Transition from the sixth angle range to the first Angle of rotation slowly decreases the suction speed, see above that the overflow losses due to the valve closing too late Intake valve are reduced.
- Fig. 1 is one of a piston 10 which in one Cylinder 11 guided and by a camshaft 12 with two Cam 13 is driven, existing injection pump shown schematically.
- the piston 10 limits one Delivery chamber 14, in which a low pressure line 15 and a High pressure line 16 open. Between high pressure line 16 and delivery chamber 14, an outlet valve 17 is provided, which causes a backflow of the in the high pressure line 16 located fuel in the delivery chamber 14 prevented.
- the high pressure line 16 can be in a not shown Common rail flow or directly with injectors or Injector to be connected.
- the fuel in the low pressure line 15 can are sucked into the delivery chamber 14 via a suction valve 18, when the piston 10, as shown in Fig. 1a, after moved below and thus enlarged the delivery room 14.
- a quantity control valve 19 hydraulic connection between delivery chamber 14 and Low pressure line 15 are made.
- the quantity control valve 19 designed as a solenoid valve closed. If the piston 10 differs from one in Fig. 1a not shown top dead center (OT) in the direction of Arrow 20 to bottom dead center (UT), which is also in Fig. 1a is not shown, moves, fuel flows from the Low pressure line 15 via the suction valve 18 in the Delivery chamber 14.
- the quantity control valve 19 is during the Suction hubs closed. As soon as the camshaft 12 is so far has rotated that the point 21 touches the piston 10 the UT reached. The delivery stroke then begins.
- FIGS. 1a, 1b and 1c are assigned to the corresponding sections in the above diagram by lines 24, 25 and 26.
- the switching position of the quantity control valve 19 is also shown in the diagram of FIG. 1. It is clear that opening the closed quantity control valve 19 stops the delivery of fuel into the high-pressure line 16.
- the opening of the quantity control valve 19 like shown within a range 27 between UT and OT can be varied.
- the camshaft 12 has two cams 13, so that with one camshaft revolution two suction and delivery strokes be carried out by the piston 10.
- FIG. 3a shows the stroke 23 of the cam 13 in the radial direction and thus also of the piston 10 over the angle of rotation ⁇ NW of the camshaft 12.
- the speed v R of the cam 13 is plotted in the radial direction.
- the speed v R corresponds to the speed of the piston 10.
- the acceleration a of the piston 10 over the angle of rotation über NW of the camshaft 12 is shown in FIG. 3c.
- the position of the outlet valve 18 is shown in FIG. 3d. 3e shows the course of the pressure p F in the delivery chamber 14 over the angle of rotation ⁇ NW , while the switching position of the quantity control valve 19 is shown in FIG. 3f.
- the pressure p F rises steeply in the delivery chamber.
- the liquid column in the line between the high-pressure fuel pump and the rail is suddenly accelerated in accordance with the cam speed at the time of overflow. With increasing speeds, this results in a pressure increase in the delivery chamber 14.
- This pressure increase reaches a maximum, which is marked in FIG. 3e with p s , and runs after the outlet valve 17 has opened as a pressure surge through the high-pressure line 16. If this pressure surge reaches the common rail, an injection nozzle or an injector, this can happen lead to inaccurate fuel metering during injection. In addition, the pressure increase leads to a heavy load on the cam drive of the pump.
- the pressure increase in the delivery chamber 14 should be as small as possible compared to the rail pressure p CR prevailing in the high-pressure line 15. This means that the difference between p s and p CR should be as small as possible. This goal can be achieved with the design of the cam 13 described below.
- the outlet valve 17 opens sooner or later. Because of the volumetric losses between piston 10 and cylinder 11 and the compressibility of the fuel in the delivery chamber and the elasticity of the wall of the injection pump surrounding the delivery chamber 14, not shown in FIG. 1, a certain delivery stroke is necessary in order to build up pressure in the delivery chamber 14. Knowing the properties of a specific high-pressure fuel pump, a rotation angle range can thus be specified within which the exhaust valve 17 does not open under any circumstances. In Fig. 3a, this range of rotation angle is designated 1.
- the angle of rotation range 1 is smaller, the lower the pressure p CR in the high-pressure line and the smaller the volume of the delivery chamber 14 and the greater the elasticity of the wall surrounding the delivery chamber 14.
- the outlet valve 17 opens latest regardless of the speed, otherwise the same boundary conditions, when the pressure p CR present in the high-pressure line 16 corresponds to the maximum permissible operating pressure of the common rail. I.e. For each high-pressure fuel pump, depending on the above parameters, a second rotation angle range 2 can be specified, within which the outlet valve 17 opens.
- the acceleration a in the third rotation angle range 3 is selected such that after reaching the maximum permissible speed and after the transition to a fourth range, the maximum negative acceleration is such that at the contact point between the cam 13 and the piston 11 at the highest permissible pressure P CR the permissible Hertzian pressure is not exceeded.
- the compressive forces acting on the piston 10 and the inertial forces are to be taken into account.
- a fourth rotation angle range 4 begins, which is characterized in that the acceleration a becomes negative.
- the value of the acceleration is limited by the maximum permissible Hertzian pressure.
- the acceleration a is constantly negative during almost the entire fourth rotation angle range 4 and a subsequent fifth rotation angle range 5, which means that the speed of the piston 10 decreases.
- the speed becomes negative, ie the suction stroke begins.
- the piston 10 has a certain negative speed, which it maintains constant over a sixth rotation angle range 6.
- fuel is drawn in from the low-pressure line 15 into the delivery chamber 14.
- the first rotation angle range 1 again follows the sixth rotation angle range 6.
- the range of rotation angle 1 is characterized in that the acceleration a of the piston 10 is chosen to be as large as possible.
- the possible acceleration is essentially limited by the mass forces of the piston 10, since hydraulic forces acting on the piston 10 from the delivery chamber in the area of the UT are comparatively small. For this reason, the maximum acceleration in the first rotation angle range is significantly greater than the maximum acceleration in the third rotation angle range 3.
- the second rotation angle range 2 can be correspondingly larger.
- the piston 10 instead of a constant speed of the piston 10 in the second rotation angle range 2, the piston 10 can also be accelerated slightly. However, it is a prerequisite that the pressure peak p s does not become impermissibly high when the outlet valve 17 is opened in all operating states. In the third angle 3 range, it is advisable to select the acceleration a of the piston 10 as large as possible in order to achieve the required delivery rate with the lowest possible maximum speed v max of the piston 10. The lower the maximum speed v max of the piston 10, the lower the flow losses during shutdown by the quantity control valve 19. The efficiency of the high-pressure fuel pump is improved.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
- Fig. 1:
- eine schematische Darstellung einer Kraftstoffhochdruckpumpe in drei verschiedenen Betriebszuständen mit einem Hub-Drehwinkel-Diagramm;
- Fig. 2:
- die Kontur eines erfindungsgemäßen Nockens und
- Fig. 3:
- den Verlauf von Nockenhub, Nockengeschwindigkeit und Beschleunigung, Auslaßventilhub, Förderraumdruck und Zustand des Mengensteuerungventils über dem Drehwinkel der Nockenwelle.
Alle in der Zeichnung, deren Beschreibung und den Patentansprüchen beschriebenen Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein.
Claims (10)
- Kraftstoffhochdruckpumpe mit veränderlicher Fördermenge für eine Brennkraftmaschine, mit einem von einer Nockenwelle (12) betätigten Kolben (10), wobei der Kolben (10) Kraftstoff aus einer Niederdruck-Leitung (15) in einen Förderraum (14) ansaugt und anschließend in eine Hochdruck-Leitung (16) fördert, und mit einem Förderraum (14) und Niederdruckleitung (15) verbindenden Mengensteuerventil (19), dadurch gekennzeichnet, dass zwischen Niederdruck-Leitung (15) und Förderraum (14) ein separates Saugventil (18) angeordnet ist, und dass die Regelung der Fördermenge durch Öffnen des Mengensteuerventils (19) während des Förderhubs des Kolbens (10) erfolgt.
- Kraftstoffhochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass jeder Nocken (13) der Nockenwelle (12) mindestens einen ersten Drehwinkelbereich (1), einen zweiten Drehwinkelbereich (2) und einen dritten Drehwinkelbereich (3) aufweist, wobei der UT des Kolbens (23) innerhalb des ersten Drehwinkelbereichs (1) liegt, dass der Kolben (10) nach Erreichen des UT durch den Nocken (13) im ersten Drehwinkelbereich (1) eine positive Beschleunigung erfährt, dass innerhalb des zweiten Drehwinkelbereichs (2) die Hubgeschwindigkeit (vR) des Kolbens (10) annähernd konstant ist, dass das Mengensteuerventil (19) öffnet während die Nocke (13) den zweiten Drehwinkelbereich durchläuft, und dass innerhalb des dritten Drehwinkelbereichs (3) die Hubgeschwindigkeit (vR) des Kolbens (10) bis zum Erreichen eines Maximalwerts (vMAX) zunimmt.
- Kraftstoffhochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet, dass die Beschleunigung des Kolbens (10) im ersten Drehwinkelbereich (1) bei der zulässigen Höchstdrehzahl der Kraftstoffhochdruckpumpe im Wesentlichen durch die Massenkräfte des Kolbens (10) begrenzt wird.
- Kraftstoffhochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet, dass der Kolben (10) im zweiten Drehwinkelbereich (2) bei der zulässigen Höchstdrehzahl der Kraftstoffhochdruckpumpe einen gegenüber der Beschleunigung im ersten Drehwinkelbereich (1) geringere positive Beschleunigung erfährt.
- Kraftstoffhochdruckpumpe nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass die Beschleunigung des Kolbens (10) im vierten Drehwinkelbereich (4) bei der zulässigen Höchstdrehzahl der Kraftstoffhochdruckpumpe von der maximal zulässigen Hertz'schen Pressung an der Kontaktstelle zwischen Nocken (13) und Kolben (10) begrenzt wird.
- Kraftstoffhochdruckpumpe nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, dass jeder Nocken (13) einen vierten Drehwinkelbereich (4), einen fünften Drehwinkelbereich (5) und einen sechsten Drehwinkelbereich (6) aufweist, dass der OT des Kolbens (10) zwischen viertem Drehwinkelbereich (4) und fünftem Drehwinkelbereich (5) liegt, dass die positive Beschleunigung des Kolbens (10) durch den Nocken (13) im vierten Drehwinkelbereich (4) auf Null verringert wird, dass der Kolben (10) durch den Nocken (13) im fünften Drehwinkelbereich (5) eine negative Beschleunigung erfährt, und dass innerhalb des sechsten Drehwinkelbereichs (6) die Hubgeschwindigkeit (vR) des Kolbens (10) negativ und annähernd konstant ist.
- Kraftstoffhochdruckpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Änderung der Geschwindigkeit des Kolbens (10) im vierten und im fünften Drehwinkelbereich (4, 5) annähernd konstant ist.
- Kraftstoffhochdruckpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Mengensteuerventil (18) ein stromlos geöffnetes Magnetventil ist.
- Kraftstoffhochdruckpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Mengensteuerventil (19) von einem Steuergerät in Abhängigkeit der Drehzahl, der Last, der Temperatur der Brennkraftmaschine, der Spannung des Bordnetzes und der Temperatur der Ansaugluft und des Drucks im Common-Rail geregelt wird.
- Kraftstoffhochdruckpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass vor dem Übergang vom sechsten Drehwinkelbereich (6) in den ersten Drehwinkelbereich (1) die Sauggeschwindigkeit langsam abnimmt.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10052629 | 2000-10-24 | ||
DE10052629A DE10052629A1 (de) | 2000-10-24 | 2000-10-24 | Kraftstoffhochdruckpumpe mit veränderlicher Fördermenge |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1201913A2 true EP1201913A2 (de) | 2002-05-02 |
EP1201913A3 EP1201913A3 (de) | 2004-01-02 |
EP1201913B1 EP1201913B1 (de) | 2006-04-19 |
Family
ID=7660843
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01123835A Expired - Lifetime EP1201913B1 (de) | 2000-10-24 | 2001-10-05 | Kraftstoffhochdruckpumpe mit veränderlicher Fördermenge |
Country Status (4)
Country | Link |
---|---|
US (1) | US6655362B2 (de) |
EP (1) | EP1201913B1 (de) |
JP (1) | JP2002138923A (de) |
DE (2) | DE10052629A1 (de) |
Cited By (3)
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US5754363A (en) * | 1993-08-17 | 1998-05-19 | Mitsubishi Denki Kabushiki Kaisha | Cassette loading device |
EP1361360A1 (de) * | 2002-05-10 | 2003-11-12 | Delphi Technologies, Inc. | Hochdruck-Kraftstoffpumpe |
WO2008066635A1 (en) * | 2006-11-27 | 2008-06-05 | Caterpillar Inc. | Opposed pumping load high pressure common rail fuel pump |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
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JP4123952B2 (ja) * | 2003-02-06 | 2008-07-23 | トヨタ自動車株式会社 | 内燃機関の燃料供給システム |
JP4106663B2 (ja) * | 2004-03-26 | 2008-06-25 | 株式会社デンソー | 内燃機関の燃料供給装置 |
US7517200B2 (en) * | 2004-06-24 | 2009-04-14 | Caterpillar Inc. | Variable discharge fuel pump |
DE102004053278A1 (de) * | 2004-11-04 | 2006-05-11 | Robert Bosch Gmbh | Verfahren zum Betreiben eines Kraftstoffsystems einer Brennkraftmaschine, sowie Kraftstoffsystem |
DE102004056665A1 (de) * | 2004-11-24 | 2006-06-01 | Robert Bosch Gmbh | Verfahren, Computerprogramm und Steuer- und/oder Regelgerät zum Betreiben einer Brennkraftmaschien, sowie Brennkraftmaschine |
US20090272365A1 (en) * | 2008-04-30 | 2009-11-05 | Kunz Timothy W | Cam lobe profile for driving a mechanical fuel pump |
GB0811385D0 (en) * | 2008-06-20 | 2008-07-30 | Artemis Intelligent Power Ltd | Fluid working machines and method |
DE102008050060A1 (de) | 2008-10-01 | 2010-04-08 | Man Diesel Se | Krafteinspritzsystem mit Hochdruckpumpen mit magnetisch betätigbarem Saugventil |
US8091530B2 (en) | 2008-12-08 | 2012-01-10 | Ford Global Technologies, Llc | High pressure fuel pump control for idle tick reduction |
DE102008054512B4 (de) * | 2008-12-11 | 2021-08-05 | Robert Bosch Gmbh | Verfahren zum Betreiben eines Kraftstoffeinspritzsystems einer Brennkraftmaschine |
DE102011005459A1 (de) | 2011-03-11 | 2012-09-13 | Robert Bosch Gmbh | Fluidpumpe, insbesondere Kraftstoff-Hochdruckpumpe, mit einer Antriebswelle mit mindestens einem ersten Nockenabschnitt |
DE102011089281B4 (de) | 2011-12-20 | 2024-01-04 | Robert Bosch Gmbh | Verfahren zum Betreiben einer Kraftstoffhochdruckpumpe bei Nullförderung |
US9989026B2 (en) * | 2012-02-17 | 2018-06-05 | Ford Global Technologies, Llc | Fuel pump with quiet rotating suction valve |
DE102014206442B4 (de) | 2014-04-03 | 2019-02-14 | Continental Automotive Gmbh | Verfahren und Vorrichtung zum Betreiben eines Druckspeichers, insbesondere für Common-Rail-Einspritzsysteme in der Kfz-Technik |
GB2529909B (en) * | 2014-09-30 | 2016-11-23 | Artemis Intelligent Power Ltd | Industrial system with synthetically commutated variable displacement fluid working machine |
DE102015220374A1 (de) * | 2015-10-20 | 2017-04-20 | Robert Bosch Gmbh | Verfahren zum Betreiben einer Brennkraftmaschine, sowie Computerprogramm und Steuer- und/oder Regeleinrichtung |
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EP0481964B1 (de) | 1988-11-24 | 1995-05-17 | Denso Corporation | Hochdruckpumpe mit veränderlichem Abfluss |
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CH228741A (de) * | 1941-11-15 | 1943-09-15 | Bosch Gmbh Robert | Einspritzpumpe, insbesondere für Brennkraftmaschinen. |
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US5197438A (en) * | 1987-09-16 | 1993-03-30 | Nippondenso Co., Ltd. | Variable discharge high pressure pump |
JP2829639B2 (ja) * | 1989-09-22 | 1998-11-25 | 株式会社ゼクセル | 電子制御式分配型燃料噴射ポンプの送油率可変制御方法 |
US5230613A (en) * | 1990-07-16 | 1993-07-27 | Diesel Technology Company | Common rail fuel injection system |
DE4223728C2 (de) * | 1992-07-18 | 1999-02-18 | Daimler Benz Ag | Ventilgesteuerte Einspritzvorrichtung, insbesondere für eine luftverdichtende Einspritzbrennkraftmaschine |
WO1994027039A1 (en) * | 1993-05-06 | 1994-11-24 | Cummins Engine Company, Inc. | Variable displacement high pressure pump for common rail fuel injection systems |
US5577892A (en) * | 1993-11-26 | 1996-11-26 | Mercedes Benz Ag | Method of injecting fuel including delayed magnetic spill valve actuation |
DE4407166C1 (de) * | 1994-03-04 | 1995-03-16 | Daimler Benz Ag | Kraftstoffeinspritzanlage für eine Brennkraftmaschine |
DE19646581A1 (de) * | 1996-11-12 | 1998-05-14 | Bosch Gmbh Robert | Kraftstoffeinspritzsystem |
JP3237549B2 (ja) * | 1996-11-25 | 2001-12-10 | トヨタ自動車株式会社 | 内燃機関の高圧燃料供給装置 |
JPH11200990A (ja) * | 1998-01-07 | 1999-07-27 | Unisia Jecs Corp | 燃料噴射制御装置 |
JP3110021B2 (ja) * | 1999-04-12 | 2000-11-20 | 株式会社ボッシュオートモーティブシステム | 燃料供給ポンプ |
JP3819208B2 (ja) * | 2000-03-01 | 2006-09-06 | 三菱電機株式会社 | 可変吐出量燃料供給装置 |
-
2000
- 2000-10-24 DE DE10052629A patent/DE10052629A1/de not_active Withdrawn
-
2001
- 2001-10-05 EP EP01123835A patent/EP1201913B1/de not_active Expired - Lifetime
- 2001-10-05 DE DE50109544T patent/DE50109544D1/de not_active Expired - Lifetime
- 2001-10-24 JP JP2001326770A patent/JP2002138923A/ja active Pending
- 2001-10-24 US US09/983,500 patent/US6655362B2/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
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EP0481964B1 (de) | 1988-11-24 | 1995-05-17 | Denso Corporation | Hochdruckpumpe mit veränderlichem Abfluss |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5754363A (en) * | 1993-08-17 | 1998-05-19 | Mitsubishi Denki Kabushiki Kaisha | Cassette loading device |
EP1361360A1 (de) * | 2002-05-10 | 2003-11-12 | Delphi Technologies, Inc. | Hochdruck-Kraftstoffpumpe |
WO2008066635A1 (en) * | 2006-11-27 | 2008-06-05 | Caterpillar Inc. | Opposed pumping load high pressure common rail fuel pump |
US7444989B2 (en) | 2006-11-27 | 2008-11-04 | Caterpillar Inc. | Opposed pumping load high pressure common rail fuel pump |
Also Published As
Publication number | Publication date |
---|---|
JP2002138923A (ja) | 2002-05-17 |
EP1201913B1 (de) | 2006-04-19 |
US20020053338A1 (en) | 2002-05-09 |
DE10052629A1 (de) | 2002-05-08 |
DE50109544D1 (de) | 2006-05-24 |
US6655362B2 (en) | 2003-12-02 |
EP1201913A3 (de) | 2004-01-02 |
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