EP1283366A2 - Radialkolbenpumpe und Verfahren zum Betreiben dieser Pumpe - Google Patents
Radialkolbenpumpe und Verfahren zum Betreiben dieser Pumpe Download PDFInfo
- Publication number
- EP1283366A2 EP1283366A2 EP02015316A EP02015316A EP1283366A2 EP 1283366 A2 EP1283366 A2 EP 1283366A2 EP 02015316 A EP02015316 A EP 02015316A EP 02015316 A EP02015316 A EP 02015316A EP 1283366 A2 EP1283366 A2 EP 1283366A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- adjusting
- ring
- piston pump
- radial piston
- 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
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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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
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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
- 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
- F04B49/12—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 varying the length of stroke of the working members
- F04B49/123—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
- F04B49/125—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
- F04B49/126—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts with a double eccenter mechanism
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/06—Control
- F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
Definitions
- the invention first relates to a radial piston pump for High-pressure fuel generation in fuel systems from Internal combustion engines, especially in a common rail injection system, with a housing with at least one Cylinder, with a drive shaft in the housing is stored and at least one eccentric section has, with a cam ring, which around the Eccentric section is arranged around and with at least a piston which is received in the cylinder and is supported on the cam ring.
- Such a radial piston pump is known from DE 198 58 862 A1 known. With her, three cylinders are star-shaped around one Eccentric section of a centrally arranged drive shaft arranged. There is a cam ring on the eccentric section placed with the radially inner ends of the in the Cylinder piston is connected. The cam ring itself does not rotate, but moves in its Level along a circular path. This way, in the Cylinders picked up pistons alternately in a back and forth Moved here.
- Such a radial piston pump is called a high pressure fuel pump used in a fuel system. you fuel is fed from a pre-feed pump and it feeds the fuel further into a fuel manifold, commonly referred to as "rail". Of there the fuel reaches the combustion chambers via injectors the internal combustion engine.
- the present invention has the task of a Radial piston pump of the type mentioned educate that the fuel system in which they is used, manufactured easier and cheaper can be.
- This task is the beginning of a radial piston pump mentioned kind in that between Eccentric section and cam ring arranged an adjusting ring is, the inner opening opposite the outer contour is eccentric and which is about the central axis of the Opposite inner opening in a desired angular position the eccentric section can be rotated.
- Radial piston pump is that for controlling it the amount of fuel delivered no pressure and / or Volume control valves are required more. Instead the quantity is controlled by adjusting the stroke the piston or pistons of the radial piston pump.
- the radial piston pump according to the invention is therefore simpler to build.
- the amount of fuel delivered by the radial piston pump can be set very precisely, can be done on the Fuel line existing pressure relief valve and the corresponding return line turn out smaller, or it can possibly even completely on such a pressure relief valve to be dispensed with. Also for example to the fuel tank returning leakage line is when using the Radial piston pump according to the invention no longer required. By the radial piston pump according to the invention thus become costs when building a fuel system saved and the fuel system builds overall easier, because it has fewer components.
- the Radial piston pump according to the invention includes an adjustment shaft, which has a Gearing works together with the adjusting ring.
- a such adjustment shaft is space-saving in the To accommodate radial piston pump and enables a reliable and precise adjustment of the adjustment ring.
- the adjusting shaft arranged coaxially to the axis of rotation of the drive shaft and on an end face of the eccentric section of the drive shaft, eccentric to the axis of rotation of the drive shaft a gear is stored, which on the one hand with external teeth on the adjusting shaft and on the other hand with a Internal toothing on the adjusting ring works together.
- An adjusting device for the adjusting ring becomes created, which on the one hand builds small and on the other hand due to the between the adjusting shaft and the Adjustment ring arranged gear a cheap Translation, possibly also a self-locking between Adjustment ring and adjustment shaft enables.
- Adjustment ring there is a stop, which is a such angular position of the adjusting ring relative to the Drive shaft defined in which the cam ring at least is approximately coaxial with the axis of rotation of the drive shaft.
- the radial piston pump works with Zero discharge.
- the stop becomes this operating point the radial piston pump defined in a simple manner.
- the stop can be formed by the Internal teeth on the adjusting ring in the circumferential direction in one Range of approximately 185 ° to 195 °, preferably over one Range of approximately 190 °, and the Internal toothing opposite an axis, which is in the plane of the adjustment ring lies through the center of the Inner opening of the adjustment ring goes and orthogonal to Axis of symmetry of the adjusting ring is symmetrical.
- the So stop is only through the arrangement and training the internal toothing formed on the adjusting ring, so that on an additional stop element can be dispensed with.
- An electrical adjustment device is preferred provided, which works on the adjusting shaft.
- a such a device can be easily controlled.
- the electrical adjustment device can be an electric motor, preferably a stepper motor.
- the corresponding supply lines are possible to save space.
- a electrical adjustment device, in particular a Stepper motor also work very precisely and build relatively small. In principle, it is also conceivable the use of an electromagnetic or a hydraulic actuator.
- the stator of the Electric motor with the drive shaft and the rotor of the Electric motor rotatably connected to the adjusting shaft are.
- the drive shaft, the adjusting shaft rotate and correspondingly the stator and the rotor of the electric motor synchronous. Only if the adjustment ring is adjusted can be required by the arrangement according to the invention in a simple way a speed difference between the drive shaft and the adjusting shaft are generated, which leads to the adjustment of the adjustment ring.
- the invention also relates to a method for operating an internal combustion engine in which the fuel is at least is also promoted by a radial piston pump, with a Housing with at least one cylinder, one drive shaft, which is stored in the housing and at least one Has eccentric section, with a cam ring, which around the eccentric section is arranged around and with at least one piston which is in the cylinder is recorded and is supported on the cam ring.
- Radial piston pump delivered fuel amount very much quickly to a changed operating state of the Internal combustion engine to be adjusted. This will essentially allows only that amount of fuel is promoted to the fuel rail, which of the Injectors finally passed into the combustion chambers becomes. Excess the usual return Fuel from the fuel rail can thus omitted or the components required for this can at least turn out smaller.
- the amount of fuel to be delivered is the desired torque and the instantaneous speed of the internal combustion engine. This is the case with that further development of the invention Process taken into account in which a desired Torque and a speed of the internal combustion engine Parameter is determined which for setting a such eccentricity of the cam ring with respect to the axis of rotation the drive shaft is required, in which the Radial piston pump that the torque request and the speed appropriate amount of fuel promotes.
- the invention further relates to a computer program which is suitable for performing the above method if it is running on a computer. It becomes special preferred if the computer program is on a memory, is stored in particular on a flash memory.
- the present invention also relates to a control and / or Control device for control and / or regulation at least one function of an internal combustion engine. at such a control and / or regulating device suggested that it work with a computer program above type is provided.
- a fuel system has the reference number 10 in FIG. 1.
- a fuel tank 12 from which one electric fuel pump 14 via a filter 16 Fuel promotes. Via a low pressure fuel line 18 is the electric fuel pump 14 with a High pressure fuel pump 20 connected. Between electric fuel pump 14 and high pressure pump 20 branches off from the low pressure fuel line 18 Branch line 22 in which a pressure control valve 24 is arranged.
- the high pressure fuel pump 20 pumps the fuel in a fuel manifold 26. In this is the Fuel stored under very high pressure. To the Fuel rail 26 is a plurality of injectors 28 connected, the fuel directly into combustion chambers 30 inject.
- the High-pressure fuel pump 20 for the fuel rail 26 delivered fuel quantity can be changed.
- the high pressure fuel pump 20 includes an electric motor 32, which of a control and / or regulating device 34th is controlled. This is on the input side with a Sensor 36, which taps the speed of the internal combustion engine and a sensor 38, which is a target torque Internal combustion engine delivers corresponding signals, connected.
- the High-pressure fuel pump 20 is a Radial piston pump with three arranged in a star shape Cylinders 40a, 40b and 40c ( Figure 3). Cylinder heads 42a, 42b and 42c close the cylinders 40a, 40b and 40c radially outside. In the cylinder heads 42a, 42b and 42c contain bushings 44a, 44b and 44c in which Pistons 46a, 46b and 46c are slidably received.
- the cylinders 40a, 40b and 40c are part of a housing 48.
- a drive shaft 50 In the center between the cylinders 40a, 40b and 40c is in Housing 48 received a drive shaft 50. Over a Coupling 52 is this with a camshaft (not shown) connected to the internal combustion engine. That in figure 2 left end of the drive shaft 50 is opposite the housing 48 supported by a ball bearing 53.
- the drive shaft 50 has in the region of the cylinders 40a, 40b and 40c an eccentric section 54. This is with respect to the axis of rotation 56 of the drive shaft 50 by one Eccentricity 58 replaced ( Figure 5). Radial outside is open the eccentric portion 54 of the drive shaft 50 Adjustment ring 60 put on. Radially outside is on the Adjustment ring 60 in turn a lifting ring 62 placed. The The cam ring 62 bears one around its cam ring bore 63 radially inner extending circumferential collar 65th By this is the cam ring 62 between the adjusting ring 60 and a shaft collar 67 present on the drive shaft 50 held axially.
- the outer lateral surface of the cam ring 62 has three 120 ° offset flattened areas 64a, 64b and 64c on.
- a sliding shoe 66a, 66b or 66c is against this by a spring 68a, 68b or 68c, which is located on the Bushing 44a, 44b and 44c supported, pressed.
- the Slide shoe 66a, 66b and 66c is with the radially inner End of the piston 46a, 46b and 46c connected.
- the drive shaft 50 is in its right in Figure 2 Hollow area. In this recess is one Adjustment shaft 70 introduced. On her left in Figure 2 At the end, the adjusting shaft 70 has circumferential teeth 72nd
- the central axis 81 of the inner opening 80 is opposite that circular outer contour of the adjusting ring 60 by a Eccentricity 82 arranged offset ( Figure 5).
- On one Area of the inner lateral surface of the inner opening 80 of the Adjustment ring 60 has an internal toothing 84.
- the Gear 76 is also with this internal toothing 84 in Intervention.
- the internal toothing 84 on the adjusting ring 60 extends in the circumferential direction over a range of about 190 °.
- the internal toothing 84 is opposite an axis 86 which is in the plane of the adjusting ring 60 lies through the center 81 of the inner opening of the Adjustment ring goes and orthogonal to the axis of symmetry 88 des Adjustment ring 60 is symmetrical ( Figure 5). How to continue set out below, formed the ends of the Internal toothing stops, one of which is shown in FIGS. 4 and 5 bears reference number 89.
- a shaft journal 90 to the right in FIG. 2 a bearing bush 92 is pressed on.
- the associated one Bearing ring 94 is pressed with the housing 48.
- the Bearing bush 92 and the bearing ring 94 together form one Slide bearing, over which the right end in Figure 2 supports the drive shaft 50 relative to the housing 48.
- the adjusting shaft 70 is also the axis of the Electric motor 32. To this extent, a rotor 102 of the Electric motor 32 at the right end in FIG Adjustment shaft 70 fixed in rotation. A stator 104 of the Electric motor 32 surrounds rotor 102. Stator 104 is via a disk-shaped holding plate 106 rotatably with the Bearing bush 92 connected. The disc-shaped holding plate 106 can be injection molded onto the bearing bush 92, for example. On in this way, the stator 104 is rotationally fixed to the Drive shaft 50 connected. The stator 104 is one of Cover hood 108, the edge of which in the housing 48th is crimped pressure-tight. In the cover 108 are Plug contacts 110 inserted, which via sliding contacts Power the stator 104 (without reference numerals) can.
- the fuel system 10 with the radial piston pump 20 works as follows: Before starting the Internal combustion engine, for example when the ignition is actuated the electric motor 32 from the control and / or regulating device 34 so controlled that the gear 76 against the stop 89 of the Internal toothing 84 on the adjusting ring 60 runs.
- the adjustment ring 60 is adjusted by a relative rotation of the rotor 102 with respect to the stator 104. This also rotates the adjusting shaft 70 and that Gear 76. This in turn leads to a relative rotation of the Adjustment ring 60 with respect to the eccentric section 54 Drive shaft 50.
- every angular position of the adjusting ring 60 with respect to the eccentric section 54 of the drive shaft 50 a very specific delivery rate of the high pressure fuel pump 20 corresponds. These are angular positions with the associated delivery rates in the control unit 34 saved.
- the ones that correspond to the user's request Performance of the internal combustion engine, in particular torque and speed, are from the control unit 34 in the required fuel quantity and the corresponding Angular position of the adjusting ring 60 relative to that Eccentric section 54 of the drive shaft 50 converted and the electric motor 32 is controlled accordingly.
Abstract
Description
- Figur 1
- eine schematische Darstellung eines Kraftstoffsystems mit einer Radialkolbenpumpe;
- Figur 2
- eine teilweise geschnittene Ansicht der Radialkolbenpumpe von Figur 1;
- Figur 3
- eine Schnittdarstellung längs der Linie III-III der Radialkolbenpumpe von Figur 2;
- Figur 4
- eine Detailansicht der Radialkolbenpumpe von Figur 3, in einem Betriebszustand der Radialkolbenpumpe, in dem diese keinen Kraftstoff fördert; und
- Figur 5
- eine Ansicht ähnlich Figur 4, in einem Betriebszustand der Radialkolbenpumpe, in dem diese die maximal mögliche Kraftstoffmenge fördert.
Claims (15)
- Radialkolbenpumpe (20) zur Kraftstoffhochdruckerzeugung bei Kraftstoffsystemen (10) von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Einspritzsystem, mit einem Gehäuse (48) mit mindestens einem Zylinder (40a, 40b, 40c), mit einer Antriebswelle (50), die in dem Gehäuse (48) gelagert ist und mindestens einen Exzenterabschnitt (54) aufweist, mit einem Hubring (62), welcher um den Exzenterabschnitt (54) herum angeordnet ist, und mit mindestens einem Kolben (46a, 46b, 46c), welcher in dem Zylinder (40a, 40b, 40c) aufgenommen ist und sich am Hubring (62) abstützt, dadurch gekennzeichnet, dass zwischen Exzenterabschnitt (54) und Hubring (62) ein Verstellring (60) angeordnet ist, dessen Innenöffnung (80) gegenüber der Außenkontur exzentrisch ist und welcher um die Mittelachse (81) der Innenöffnung (80) in eine gewünschte Winkelposition gegenüber dem Exzenterabschnitt (54) verdreht werden kann.
- Radialkolbenpumpe (20) nach Anspruch 1, dadurch gekennzeichnet, dass sie eine Verstellwelle (70) umfasst, welche über eine Verzahnung (72) mit dem Verstellring (60) zusammenarbeitet.
- Radialkolbenpumpe (20) nach Anspruch 2, dadurch gekennzeichnet, dass die Verstellwelle (70) koaxial zur Drehachse (56) der Antriebswelle (50) angeordnet ist, und dass an einer Stirnseite des Exzenterabschnitts (54) der Antriebswelle (50), exzentrisch zur Drehachse (56) der Antriebswelle (50), ein Zahnrad (76) gelagert ist, welches einerseits mit einer Außenverzahnung (72) auf der Verstellwelle (70) und andererseits mit einer Innenverzahnung (84) am Verstellring (60) zusammenarbeitet.
- Radialkolbenpumpe (20) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Exzentrizität (82) der Innenöffnung (80) des Verstellrings (60) und die Exzentrizität (58) des Exzenterabschnitts (54) der Antriebswelle (50) im Wesentlichen gleich sind.
- Radialkolbenpumpe (20) nach Anspruch 4, dadurch gekennzeichnet, dass am Verstellring (60) ein Anschlag (89) vorhanden ist, welcher eine solche Winkelposition des Verstellrings (60) gegenüber der Antriebswelle (50) definiert, in der der Hubring (62) wenigstens ungefähr koaxial zur Drehachse (56) der Antriebswelle (50) ist.
- Radialkolbenpumpe (20) nach den Ansprüchen 3 und 5, dadurch gekennzeichnet, dass sich die Innenverzahnung (84) am Verstellring (60) in Umfangsrichtung über einen Bereich von ungefähr 185° bis 195°, vorzugsweise über einen Bereich von ungefähr 190°, erstreckt, und die Innenverzahnung (84) gegenüber einer Achse (86), welche in der Ebene des Verstellrings (60) liegt, durch den Mittelpunkt (81) der Innenöffnung (80) des Verstellrings (60) geht und orthogonal zur Symmetrieachse (88) des Verstellrings (60) ist, symmetrisch ist.
- Radialkolbenpumpe (20) nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, dass sie eine elektrische Verstellvorrichtung (32) umfasst, welche auf die Verstellwelle (70) arbeitet.
- Radialkolbenpumpe (20) nach Anspruch 7, dadurch gekennzeichnet, dass die elektrische Verstellvorrichtung einen Elektromotor (32), vorzugsweise einen Schrittmotor, umfasst.
- Radialkolbenpumpe (20) nach Anspruch 8, dadurch ekennzeichnet, dass der Stator (104) des Elektromotors (32) mit der Antriebswelle (50) und der Rotor (102) des Elektromotors (32) mit der Verstellwelle (70) drehfest verbunden sind.
- Verfahren zum Betreiben einer Brennkraftmaschine, bei dem der Kraftstoff mindestens auch von einer Radialkolbenpumpe (20) gefördert wird, mit einem Gehäuse (48) mit mindestens einem Zylinder (40a, 40b, 40c), mit einer Antriebswelle (50), die in dem Gehäuse (48) gelagert ist und mindestens einen Exzenterabschnitt (54) aufweist, mit einem Hubring (62), welcher um den Exzenterabschnitt (54) herum angeordnet ist, und mit mindestens einem Kolben (46a, 46b, 46c), welcher in dem Zylinder (40a, 40b, 40c) aufgenommen ist und sich am Hubring (62) abstützt, dadurch gekennzeichnet, dass die Exzentrizität des Hubrings (62) gegenüber der Drehachse (56) der Antriebswelle (50) in Abhängigkeit von mindestens einem Betriebsparameter der Brennkraftmaschine verstellt wird.
- Verfahren nach Anspruch 10, dadurch gekennzeichnet, dass vor dem Starten der Brennkraftmaschine ein Verstellring (60) gegen einen mechanischen Anschlag (81) verstellt wird, welcher eine solche Winkelposition des Verstellrings (60) gegenüber der Antriebswelle (50) definiert, in der der Hubring (62) wenigstens ungefähr koaxial zur Drehachse (56) der Antriebswelle (50) ist, und dass in dieser Position ein Abgleich einer Steuerelektronik (34) durchgeführt wird.
- Verfahren nach einem der Ansprüche 10 oder 11, dadurch gekennzeichnet, dass aus einem gewünschten Drehmoment und einer Drehzahl der Brennkraftmaschine ein Parameter ermittelt wird, welcher für die Einstellung einer solchen Exzentrizität des Hubrings (62) gegenüber der Drehachse (56) der Antriebswelle (50) erforderlich ist, bei der die Radialkolbenpumpe (20) die dem Drehmomentwunsch und der Drehzahl entsprechende Kraftstoffmenge fördert.
- Computerprogramm, dadurch gekennzeichnet, dass es zur Durchführung des Verfahrens nach einem der Ansprüche 10 bis 12 geeignet ist, wenn es auf einem Computer ausgeführt wird.
- Computerprogramm nach Anspruch 13, dadurch gekennzeichnet, dass es auf einem Speicher, insbesondere auf einem Flash-Memory, abgespeichert ist.
- Steuer- und/oder Regelgerät (34) zur Steuerung und/oder Regelung mindestens einer Funktion einer Brennkraftmaschine, dadurch gekennzeichnet, dass es mit einem Computerprogramm nach einem der Ansprüche 13 oder 14 versehen ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10139519 | 2001-08-10 | ||
DE10139519A DE10139519A1 (de) | 2001-08-10 | 2001-08-10 | Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung, sowie Verfahren zum Betreiben einer Brennkraftmaschine, Computerprogramm und Steuer- und/oder Regelgerät |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1283366A2 true EP1283366A2 (de) | 2003-02-12 |
EP1283366A3 EP1283366A3 (de) | 2004-05-12 |
EP1283366B1 EP1283366B1 (de) | 2005-11-09 |
Family
ID=7695149
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02015316A Expired - Lifetime EP1283366B1 (de) | 2001-08-10 | 2002-07-10 | Radialkolbenpumpe und Verfahren zum Betreiben dieser Pumpe |
Country Status (4)
Country | Link |
---|---|
US (1) | US6872056B2 (de) |
EP (1) | EP1283366B1 (de) |
JP (1) | JP2003097383A (de) |
DE (2) | DE10139519A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102006000832A1 (de) * | 2006-01-05 | 2007-07-12 | Siemens Ag | Radialkolbenpumpe mit Fördermengenregelung |
EP2093421A1 (de) * | 2008-02-22 | 2009-08-26 | Robert Bosch GmbH | Hochdruckpumpe zur Lieferung von Kraftstoff an ein Kraftstoffeinspritzsystem |
WO2010094367A1 (de) * | 2009-02-18 | 2010-08-26 | Robert Bosch Gmbh | Hochdruckkraftstoffpumpe für eine brennkraftmaschine |
CN105179218A (zh) * | 2015-10-12 | 2015-12-23 | 杭州电子科技大学 | 一种数字式径向柱塞变量泵 |
Families Citing this family (42)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10349310B3 (de) | 2003-10-23 | 2005-05-19 | Siemens Ag | Radialkolbenpumpe für Common Rail Einspritzsysteme |
JP4297859B2 (ja) * | 2004-09-28 | 2009-07-15 | 三洋電機株式会社 | 電動車輪用ハブユニット及び該ハブユニットを具えた乗物 |
DE102005061456B4 (de) * | 2005-12-22 | 2015-09-24 | Magna Powertrain Bad Homburg GmbH | Zylinderblock einer Hubkolbenmaschine mit durch Spannring gehaltenen Zylinderköpfen |
DE102006006823B3 (de) * | 2006-02-14 | 2007-03-15 | Siemens Ag | Verfahren und Vorrichtung zum Einspritzen von Kraftstoff |
JP4624961B2 (ja) * | 2006-06-13 | 2011-02-02 | 株式会社ニッキ | 燃料供給システム |
US8122811B2 (en) * | 2007-11-12 | 2012-02-28 | Denso Corporation | Fuel injection pump and method for assembling the same |
CN102472262A (zh) * | 2009-08-11 | 2012-05-23 | 卓越剂量技术有限公司 | 用于使正排量机械摆动的驱动装置 |
DE102009049354A1 (de) * | 2009-10-14 | 2011-04-21 | Robert Bosch Gmbh | Hydromaschine |
US9618129B2 (en) * | 2010-10-07 | 2017-04-11 | Vanderbilt University | Normally closed microvalve and applications of the same |
WO2013010458A1 (en) * | 2011-07-14 | 2013-01-24 | Neo Mechanics Limited | Diesel engine fuel injection pump which pistons are sealed with all metal seal rings |
DE102015214837A1 (de) * | 2015-08-04 | 2017-02-09 | Zf Friedrichshafen Ag | Hydraulische Radialkolbenmaschine |
JP6305480B2 (ja) * | 2016-09-01 | 2018-04-04 | 日機装株式会社 | 無脈動ポンプ |
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DE19858862A1 (de) | 1998-12-19 | 2000-03-02 | Bosch Gmbh Robert | Radialkolbenpumpe |
DE19956092A1 (de) * | 1999-11-22 | 2000-10-26 | Siemens Ag | Kolbenpumpe, insbesondere Hochdruck-Radialkolbenpumpe |
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2002
- 2002-07-10 EP EP02015316A patent/EP1283366B1/de not_active Expired - Lifetime
- 2002-07-10 DE DE50204834T patent/DE50204834D1/de not_active Expired - Fee Related
- 2002-08-09 JP JP2002232760A patent/JP2003097383A/ja active Pending
- 2002-08-12 US US10/216,352 patent/US6872056B2/en not_active Expired - Fee Related
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GB608234A (en) * | 1944-07-03 | 1948-09-13 | Olaer Marine | Improvements in pumps, motors, compressors and analogous machines |
US2900839A (en) * | 1954-01-26 | 1959-08-25 | Donald D R Mackintosh | Variable throw radial pump |
US5944493A (en) * | 1990-06-29 | 1999-08-31 | Whitemoss, Inc. | Radial piston fluid machine and/or adjustable rotor |
EP1111234A2 (de) * | 1999-12-20 | 2001-06-27 | Hydraulik-Ring GmbH | Kraftstoffpumpe |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006000832A1 (de) * | 2006-01-05 | 2007-07-12 | Siemens Ag | Radialkolbenpumpe mit Fördermengenregelung |
DE102006000832B4 (de) * | 2006-01-05 | 2011-12-01 | Continental Automotive Gmbh | Radialkolbenpumpe mit Fördermengenregelung |
EP2093421A1 (de) * | 2008-02-22 | 2009-08-26 | Robert Bosch GmbH | Hochdruckpumpe zur Lieferung von Kraftstoff an ein Kraftstoffeinspritzsystem |
WO2010094367A1 (de) * | 2009-02-18 | 2010-08-26 | Robert Bosch Gmbh | Hochdruckkraftstoffpumpe für eine brennkraftmaschine |
CN102325994A (zh) * | 2009-02-18 | 2012-01-18 | 罗伯特·博世有限公司 | 用于内燃机的高压燃料泵 |
CN102325994B (zh) * | 2009-02-18 | 2015-10-21 | 罗伯特·博世有限公司 | 用于内燃机的高压燃料泵 |
CN105179218A (zh) * | 2015-10-12 | 2015-12-23 | 杭州电子科技大学 | 一种数字式径向柱塞变量泵 |
CN105179218B (zh) * | 2015-10-12 | 2016-11-30 | 杭州电子科技大学 | 一种数字式径向柱塞变量泵 |
Also Published As
Publication number | Publication date |
---|---|
US6872056B2 (en) | 2005-03-29 |
EP1283366A3 (de) | 2004-05-12 |
DE50204834D1 (de) | 2005-12-15 |
JP2003097383A (ja) | 2003-04-03 |
US20030031568A1 (en) | 2003-02-13 |
DE10139519A1 (de) | 2003-02-27 |
EP1283366B1 (de) | 2005-11-09 |
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