EP2414675B1 - Pompe à haute pression - Google Patents
Pompe à haute pression Download PDFInfo
- Publication number
- EP2414675B1 EP2414675B1 EP10702693.2A EP10702693A EP2414675B1 EP 2414675 B1 EP2414675 B1 EP 2414675B1 EP 10702693 A EP10702693 A EP 10702693A EP 2414675 B1 EP2414675 B1 EP 2414675B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cam
- pump
- piston
- pressure pump
- suction phase
- 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.)
- Active
Links
- 239000000446 fuel Substances 0.000 claims description 23
- 230000001133 acceleration Effects 0.000 claims description 11
- 238000002485 combustion reaction Methods 0.000 claims description 7
- 238000002347 injection Methods 0.000 claims description 5
- 239000007924 injection Substances 0.000 claims description 5
- 238000010586 diagram Methods 0.000 description 10
- 230000008901 benefit Effects 0.000 description 4
- 238000004088 simulation Methods 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- NCGICGYLBXGBGN-UHFFFAOYSA-N 3-morpholin-4-yl-1-oxa-3-azonia-2-azanidacyclopent-3-en-5-imine;hydrochloride Chemical compound Cl.[N-]1OC(=N)C=[N+]1N1CCOCC1 NCGICGYLBXGBGN-UHFFFAOYSA-N 0.000 description 1
- 101100042630 Caenorhabditis elegans sin-3 gene Proteins 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- 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
- F04B1/0413—Cams
-
- 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
Definitions
- the present invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
- High-pressure pumps are used, for example, in common-rail systems of motor vehicles to provide or supply pressurized fuel to a high-pressure accumulator under all operating conditions.
- Such high-pressure diesel pumps usually have either eccentric drives or cam drives.
- cam-driven high-pressure pumps is that in this case it is possible to design for a desired application a cam profile adapted thereto, which represents the piston stroke via a rotation angle of the drive shaft or the camshaft.
- a slow delivery phase and a fast suction phase of the high pressure pump can be realized via an asymmetric cam profile, whereby an advantage is achieved by the resulting low maximum drive torque, which must apply the motor to drive the high pressure pump.
- cam contours designed in this way can therefore also be used both for the right-handed and for the anti-clockwise rotation.
- the EP 1 101 939 A2 shows a piston pump for fluid delivery with a plurality of preferably similar piston-cylinder units, in whose cylinder chamber in each case an associated displacer piston is arranged.
- Each piston performs an oscillation with a suction and delivery interval.
- the delivery interval occupies a larger part of the oscillation period than the suction interval.
- variable supply fuel supply device comprises a piston and a cylinder, wherein the pressure in a pressure chamber at a position which is set to a certain value before the top dead center is reached in the course of the exhaust stroke, in which the piston of the fuel pump is from the bottom dead center is moved to the top dead center, is drained.
- a high-pressure pump for a fuel injection device of an internal combustion engine, in particular for a common rail injection system, which has a cam engine in which the rotational movement of a camshaft is converted via at least one cam into a stroke movement of a pump piston of the high-pressure pump, wherein the at least one Cam has an asymmetric cam contour, wherein a cam contour of the cam is designed so that in a suction phase of the high-pressure pump in a range from a top dead center to a bottom dead center, in which fuel is sucked into a pump chamber, the piston stroke of the pump piston as a function of Cam rotation angle follows a sinusoidal course.
- the cam contour is designed such that in a delivery phase of the high-pressure pump, in which the fuel is compressed in the pump working space and supplied to a delivery valve, an acceleration of the pump piston as a function of the cam rotation angle follows a course composed of sinusoidal and linear sections.
- the sinusoidal curve in the suction phase corresponds to a falling edge of a sinusoidal function, which starts at a top dead center of the cam and ends at a bottom dead center of the cam.
- the falling edge is formed from a sum of harmonic functions.
- the performance of the high pressure pump is further optimized.
- the lift-off properties of the plunger body of the high-pressure pump are improved, and depending on the acceleration curve of the rising flank in the delivery phase, larger acceleration stages in the transition region to the suction phase are avoided.
- this refinement improves the speed and acceleration profile of the pump piston as well as the Hertzian pressure.
- the sinusoidal curve in the suction phase at the top dead center of the cam corresponds to a maximum delivery stroke of the pump piston.
- the suction phase is further optimized, the course or the cam contour of which takes place before the suction phase promotion phase is irrelevant and can follow an already optimized cam contour.
- the sinusoidal characteristic is characterized by a slow and harmonic decrease or increase in the piston stroke, the piston speed and the piston acceleration after and before the dead centers.
- the high piston speed in the mid-range of the delivery phase was previously the reason for high drive torques of the high-pressure pump and was not enforceable in the requirements previously placed on the high-pressure pumps in the prior art.
- the slow, harmonic decay after top dead center results in an improved suction phase and lower negative torques during pressure build-up. Due to the slow approach to the bottom dead center, the suction valve of the high-pressure pump can begin earlier with its closing operation and delivery losses due to a late closing of the suction valve are significantly reduced.
- the sinusoidal curve in the suction phase at the bottom dead center of the cam corresponds to a minimum delivery stroke of the pump piston.
- the cam contour is designed so that in the suction phase of the high-pressure pump, the piston speed of the pump piston performing a downward movement follows a sinusoidal course as a function of the cam rotation angle.
- Fig. 1 is a section through a high-pressure pump 1 for a fuel injection device of an internal combustion engine shown, as is known in the prior art.
- the high-pressure pump 1 has a multipart pump housing 2 in which a drive shaft or camshaft 3 driven in rotation by the internal combustion engine is arranged.
- the camshaft 3 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 4 of the camshaft 3.
- the bearings can be arranged in different parts of the pump housing 2, for example, a first bearing point in a base body 5 of the pump housing 2 and a second bearing point can be arranged in a connected to the base body 5 flange 6.
- the camshaft 3 has a cam 7, which may also be designed as a multiple cam.
- the high pressure pump 1 has at least one or more arranged in the housing 2 pump elements 8, each with a pump piston 9 which is driven by the cam 7 of the camshaft 3 in a lifting movement in at least approximately radial direction to the axis of rotation 4 of the camshaft 3.
- the pump piston 9 is set in a reciprocating or upward and downward movement. This results in a cyclical change in the volume of a pump working chamber 14 bounded by the pump piston 9.
- a pump housing part 10 which is connected to the main body 5 and which is designed as a cylinder head.
- the pump housing part 10 has a voltage applied to an outer side of the main body 5 flange 11 and a through an opening in the base body 5 to the camshaft 3 out, at least approximately cylindrical projection 12 with respect to the flange 11 of smaller diameter.
- the pump piston 9 is guided tightly displaceably in a neck 12 formed in the cylinder bore 13 in the pump housing part 10 and limited with its side facing away from the camshaft 3 end face in the cylinder bore 13 the pump chamber 14.
- the cylinder bore 13 may extend into the flange 11, in the then the pump working space 14 is arranged.
- the pump working chamber 14 has a connection with a fuel feed, for example a feed pump (not shown), via a fuel feed channel 15 running in the pump housing 2.
- the pump working chamber 14 also has, via a fuel outlet channel 17 running in the pump housing 2, a connection to an outlet, which is connected to a high-pressure accumulator 18, for example.
- One or more injectors 19 arranged on cylinders of the internal combustion engine are connected to the high-pressure accumulator 18, through which fuel is injected into the cylinders of the internal combustion engine.
- an outlet valve or delivery valve 20 opening out of the pump working chamber 14 is arranged.
- the pump working chamber 14 is filled with fuel through the fuel inlet channel 15 with open inlet valve 16, which acts as a suction valve, wherein the delivery valve 20 is closed .
- fuel is conveyed under high pressure through the pump piston 9 through the fuel outlet channel 17 with open delivery valve 20 to the high-pressure accumulator 18, wherein the inlet valve 16 is closed.
- a plunger 21 is arranged, via which the pump piston 9 is at least indirectly supported on the cam 7 of the camshaft 3.
- the plunger 21 is hollow cylindrical with a round outer cross-section and is guided in a bore 22 of the main body 5 of the pump housing 2 in the direction of the longitudinal axis 23 of the pump piston 20 slidably.
- the longitudinal axis of the plunger 21 is thus at least substantially identical to the longitudinal axis 23 of the pump piston 9.
- a support member 24 is inserted, in which a roller 25 is rotatably mounted on the cam 7 of Camshaft 3 rolls off.
- the axis of rotation 26 of the roller 25 is at least approximately parallel to the axis of rotation 4 of the camshaft 3.
- the support member 24 has on its side facing the camshaft 3 a recess 27 in which the roller 25 is rotatably mounted.
- the support member 24 and the plunger 21 may also be integrally formed.
- the pump piston 9 may be coupled to the plunger 21, at least in the direction of its longitudinal axis 23. Alternatively, the pump piston 9 may not be connected to the plunger 21, then by the return spring 28, the system of the pump piston 9 is secured to the plunger 21.
- the return spring 28 engages, for example via a spring plate 29 on an enlarged diameter piston base of the pump piston 9, which is thereby held in contact with a on the plunger 21 by the jacket inwardly projecting flange, in turn, in contact with the support element 24 is held, so that the entire composite of pump piston 9, plunger 21 and support member 24 is acted upon with roller 25 to the cam 7 of the camshaft 3 out.
- a support 30 is arranged laterally next to the roller 25 for this purpose, which prevents the roller 25 from moving out of the support element 24 in the direction of its axis of rotation 26.
- the roller 25 may be convexly curved at its side facing the support 30 side surfaces, for example, curved at least approximately spherical.
- the side surfaces of the roller 25 facing surface of the support 30 may be formed at least approximately flat or curved.
- the support 30 may be formed as a ring surrounding the roller 25 or may be arranged only laterally adjacent to the side surfaces of the roller 25.
- Fig. 2 shows a diagram representing the delivery rate of a high pressure pump 1 as a function of the rotational speed of a cam 7 on the one hand according to the prior art and another cam 7 on the other hand, according to an embodiment, which is determined according to a simulation.
- the simulation of the delivery rates or the comparison of the delivery rates was carried out on the basis of the conditions of a pressure of 1800 bar and a temperature of 40 ° C.
- a radial piston pump according to the prior art with a conventional cam 7 with 2 x 6 mm stroke with a radial piston pump compared with a cam 7 according to an embodiment of the invention which has a cam contour with respect to the suction phase, which follows a sinusoidal course.
- the cam 7 according to the embodiment is hereinafter referred to as a half-sine cam.
- the delivery rate of 160 l / h achieved by the conventional cam 7 increases to 178 l / h for the half-sine cam at a speed of about 5000 rpm.
- Fig. 3 shows a diagram of the course of the piston stroke in dependence on the cam rotation angle.
- the delivery phase over a cam rotation angle range of 0 ° to 90 ° is shown, in which the curve is composed of linear, sinusoidal, tangential or arcuate acceleration regions. It is important, however, that in the suction phase, the cam contour follows a sinusoidal course in a cam rotation angle range of 90 ° to 180 °.
- the falling edge 33 of the cam contour can also be formed from a non-pure sine function, the falling edge 33 of the cam contour is then obtained from a sum of harmonic functions, whereby a further optimization latitude in the cam design can be obtained.
- contributions from the 4th order may only be less than 1% of the 1st order A1.
- Fig. 4 shows a further diagram, in which the curve of the piston speed in dependence on the cam rotation angle in a delivery phase and in the suction phase is shown. Again, the piston velocity in the suction phase again follows a sinusoidal course.
- FIG. 5 a diagram of the course of the piston acceleration in dependence on the cam rotation angle. Again, in the suction phase of the following a sinusoidal curve can be seen, while the course of the delivery phase of sinusoidal and linear regions is composed.
- the piston speed and the piston stroke result from appropriate integration of the piston acceleration.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Claims (6)
- Pompe à haute pression (1) pour un dispositif d'injection de carburant d'un moteur à combustion interne, en particulier pour un système de rampe commune, qui présente un entraînement par arbre à cames, dans lequel le mouvement de rotation d'un arbre à cames (3) est converti par au moins une came (7) en un mouvement de course d'un piston de pompe (9) de la pompe à haute pression (1), dans laquelle ladite au moins une came (7) présente un contour de came asymétrique, dans laquelle un contour de came de la came (7) est conçu de telle manière que, dans une phase d'aspiration de la pompe à haute pression (1) dans une plage allant d'un point mort haut (31) à un point mort bas (32), dans laquelle du carburant est aspiré dans une chambre de travail de la pompe (14), la course de piston du piston de pompe (9) en fonction de l'angle de rotation de la came suive un tracé sinusoïdal, caractérisée en ce que le contour de came est conçu de telle manière que dans une phase de refoulement de la pompe à haute pression (1), dans laquelle le carburant est comprimé dans la chambre de travail de la pompe (14) et est envoyé à la soupape de refoulement (20), l'accélération du piston de pompe (9) en fonction de l'angle de rotation de la came suive un tracé qui se compose de parties sinusoïdales et de parties linéaires.
- Pompe à haute pression (1) selon la revendication 1, caractérisée en ce que le tracé sinusoïdal dans la phase d'aspiration correspond à un flanc descendant (33) d'une fonction sinusoïdale, qui commence à un point mort haut (31) de la came (7) et se termine à un point mort bas (32) de la came (7).
- Pompe à haute pression (1) selon la revendication 2, caractérisée en ce que le flanc descendant (33) est formé d'une somme de fonctions harmoniques.
- Pompe à haute pression (1) selon la revendication 2 ou 3, caractérisée en ce que le tracé sinusoïdal dans la phase d'aspiration au point mort haut (31) de la came (7) correspond à une course de refoulement maximale du piston de pompe (9).
- Pompe à haute pression (1) selon une ou plusieurs des revendications 2 à 4, caractérisée en ce que le tracé sinusoïdal dans la phase d'aspiration au point mort bas (32) de la came (7) correspond à une course de refoulement minimale du piston de pompe (9).
- Pompe à haute pression (1) selon une ou plusieurs des revendications 1 à 5, caractérisée en ce que le contour de came est conçu de telle manière que dans la phase d'aspiration de la pompe à haute pression (1), la vitesse de piston du piston de pompe (9) effectuant un mouvement alternatif en fonction de l'angle de rotation de la came suive un tracé sinusoïdal.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200910002132 DE102009002132A1 (de) | 2009-04-02 | 2009-04-02 | Hochdruckpumpe |
PCT/EP2010/051475 WO2010112253A1 (fr) | 2009-04-02 | 2010-02-08 | Pompe à haute pression |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2414675A1 EP2414675A1 (fr) | 2012-02-08 |
EP2414675B1 true EP2414675B1 (fr) | 2019-01-02 |
Family
ID=42101984
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10702693.2A Active EP2414675B1 (fr) | 2009-04-02 | 2010-02-08 | Pompe à haute pression |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2414675B1 (fr) |
CN (1) | CN102378861B (fr) |
DE (1) | DE102009002132A1 (fr) |
WO (1) | WO2010112253A1 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11401883B2 (en) | 2020-04-03 | 2022-08-02 | Ford Global Technologies, Llc | System and method for direct injection fuel pump control |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014225528A1 (de) * | 2014-12-11 | 2016-06-16 | Robert Bosch Gmbh | Verfahren zur Ansteuerung einer Hochdruckpumpe für die Kraftstoffeinspritzung in einen Verbrennungsmotor |
DE102015201452A1 (de) * | 2015-01-28 | 2016-07-28 | Robert Bosch Gmbh | Vorrichtung zum Antreiben einer Kolbenpumpe, Nocken für eine Vorrichtung, Kolbenpumpe und Verfahren zum Auslegen der Vorrichtung |
DE102015218258B4 (de) * | 2015-09-23 | 2017-08-24 | Continental Automotive Gmbh | Verfahren zur Raildruckregelung eines Einspritzsystems |
DE102016216978A1 (de) * | 2016-09-07 | 2018-03-08 | Robert Bosch Gmbh | Verfahren zur Ansteuerung einer Hochdruckpumpe für die Kraftstoffeinspritzung in einen Verbrennungsmotor |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6334344A (ja) * | 1986-07-28 | 1988-02-15 | Yoshida Kogyo Kk <Ykk> | 間欠駆動装置 |
DE3921998A1 (de) * | 1989-07-04 | 1991-01-17 | Bihler Maschf Otto | Kurbelantrieb fuer eine materialeinzugsvorrichtung an einer bearbeitungsmaschine insbesondere einem stanz- und biegeautomaten stichwort: feststehende korrekturkurve |
DE19955778A1 (de) * | 1999-11-19 | 2001-06-13 | Siemens Ag | Mehrzylindrige Kolbenpumpe |
JP2002115623A (ja) * | 2000-10-05 | 2002-04-19 | Mitsubishi Electric Corp | 可変吐出量燃料供給装置 |
-
2009
- 2009-04-02 DE DE200910002132 patent/DE102009002132A1/de not_active Withdrawn
-
2010
- 2010-02-08 EP EP10702693.2A patent/EP2414675B1/fr active Active
- 2010-02-08 CN CN201080015086.5A patent/CN102378861B/zh active Active
- 2010-02-08 WO PCT/EP2010/051475 patent/WO2010112253A1/fr active Application Filing
Non-Patent Citations (1)
Title |
---|
None * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11401883B2 (en) | 2020-04-03 | 2022-08-02 | Ford Global Technologies, Llc | System and method for direct injection fuel pump control |
Also Published As
Publication number | Publication date |
---|---|
CN102378861B (zh) | 2016-03-16 |
EP2414675A1 (fr) | 2012-02-08 |
DE102009002132A1 (de) | 2010-10-07 |
CN102378861A (zh) | 2012-03-14 |
WO2010112253A1 (fr) | 2010-10-07 |
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