WO2005088125A1 - High pressure pump, particularly for a fuel injection device of an internal combustion engine - Google Patents
High pressure pump, particularly for a fuel injection device of an internal combustion engine Download PDFInfo
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- WO2005088125A1 WO2005088125A1 PCT/EP2005/050124 EP2005050124W WO2005088125A1 WO 2005088125 A1 WO2005088125 A1 WO 2005088125A1 EP 2005050124 W EP2005050124 W EP 2005050124W WO 2005088125 A1 WO2005088125 A1 WO 2005088125A1
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- WIPO (PCT)
- Prior art keywords
- drive shaft
- rotation
- axis
- cylinder bore
- pressure pump
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Classifications
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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
- 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
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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
- 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
- F04B1/0439—Supporting or guiding means for the pistons
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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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
Definitions
- High-pressure pump in particular for a fuel injection device of an internal combustion engine
- the invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine.
- Such a high pressure pump is known from DE 199 07 311 AI.
- This high-pressure pump has a rotatingly driven drive shaft and at least one pump element.
- the Pu penelement has an at least indirectly driven by the drive shaft in a stroke pump piston which is slidably guided in a cylinder bore of a housing of the high pressure pump.
- the longitudinal axis of the cylinder bore extends perpendicular to the axis of rotation of the drive shaft and in a radial plane containing the axis of rotation.
- the drive shaft has a cam on which a cylindrical roller rolls, which is rotatably mounted in a roller shoe connected to the pump piston.
- the roller shoe is slidably mounted in a bore in the housing of the high-pressure pump and the bearing of the roller shoe absorbs transverse forces transmitted from the cam to the roller during the rotation of the drive shaft, so that these do not act on the pump piston.
- the roller shoe is made much larger in diameter than the pump piston, so that the lateral forces cause only small surface pressures of the roller shoe in the bore.
- a disadvantage of this known high-pressure pump is that it is because of the additional roller shoe and the one for guiding it required bore in the pump housing, which must be exactly aligned with the cylinder bore, is complex to manufacture and has a high weight.
- the high-pressure pump according to the invention with the features according to claim 1 has the advantage that the lateral force generated during rotation of the drive shaft on the pump piston causes only small forces acting on the guidance of the pump piston in the cylinder bore, so that this directly from the pump piston and its Guide can be accommodated in the cylinder bore without causing impermissibly high surface pressure and excessive wear. There is therefore no need for an additional component to absorb the transverse force, which simplifies the manufacture of the high-pressure pump and reduces its weight.
- the transverse force generates a torque on the pump piston, by means of which the pump piston is pressed at both end regions on the same side of the cylinder bore, the sum of the forces acting on the pump piston in its end regions on the support in the cylinder bore is equal to the shear force to be supported. It can be achieved that the greatest supporting forces act on the pump piston only in the area of its dead center, where the pump piston executes only a small stroke. In the embodiment according to claim 5 it can be achieved that only a small supporting force acts in the cylinder bore on the pump piston over a substantial part of its stroke.
- the training according to claim 6 enables transmission of Rotary movement of the drive shaft in the stroke movement of the pump piston with low friction.
- FIG. 1 shows a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
- FIG. 2 shows a section of the high-pressure pump in a cross section according to a first exemplary embodiment
- FIG. 3 shows the high-pressure pump in a cross section according to a second exemplary embodiment
- FIG. 4 shows the high-pressure pump in a cross section according to a third embodiment.
- the high-pressure pump has a multi-part housing 10, in which a drive shaft 12, which can be driven in rotation by the internal combustion engine, is arranged.
- the drive shaft 12 is rotatably mounted in the housing 10 via two bearing points spaced apart in the direction of the axis of rotation 13 of the drive shaft 12.
- the drive shaft 12 has at least one cam 14, wherein the cam 14 can also be designed as a multiple cam.
- the high-pressure pump has at least one or more pump elements 16 arranged in the housing 10, each with a pump piston 20, which is driven by the cam 14 of the drive shaft 12 in a lifting movement.
- the pump piston 20 is guided so as to be tightly displaceable in a cylinder bore 22 formed in the housing 10 and delimits a pump work chamber 24 with its end face facing away from the drive shaft 12 in the cylinder bore 22.
- the pump work chamber 24 has a connection to a fuel feed, for example a feed pump, via a fuel feed channel 26 running in the housing 10.
- An inlet valve 28 opening into the pump working chamber 24 is arranged in the fuel working channel 26 in the pump working chamber 24.
- the pump work chamber 24 also has a connection to an outlet via a fuel drain channel 30 running in the housing 10, said outlet being connected, for example, to a high-pressure accumulator 110.
- One or, preferably, a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, and are used to inject fuel into the cylinders of the internal combustion engine.
- An outlet valve 32 opening out of the pump work chamber 24 is arranged at the mouth of the fuel drain channel 30 into the pump work chamber 24.
- the pump piston 20 can be supported directly on the cam 14 of the drive shaft 12 with a piston foot protruding from the cylinder bore 22 toward the drive shaft 12. However, the pump piston 20 is preferably supported on the cam 14 via a roller 34.
- the roller 34 is at least approximately cylindrical and its axis of rotation 35 extends at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
- the roller 34 is rotatably mounted in a concave recess 36 of a roller shoe 38, the roller shoe 38 being formed in one piece with the pump piston 20 can or is connected to the pump piston 20 as a separate part.
- the roller shoe 38 has a larger cross section than the part of the pump piston 20 arranged in the cylinder bore 22.
- FIG. 2 shows a section of the high-pressure pump in a cross section according to a first exemplary embodiment.
- a radial plane containing the axis of rotation 13 of the drive shaft 12 is designated by the reference number 40.
- the roller 34 is arranged in such a way that its axis of rotation 35 extends at least approximately in the radial plane 40.
- the cylinder bore 22 is arranged such that its longitudinal axis 23 does not run in the radial plane 40 but, based on an arrangement of the longitudinal axis 23 in the radial plane 40, runs inclined with respect to the radial plane 40 such that the longitudinal axis 23 increases in the direction of rotation with increasing distance from the drive shaft 12 18 leads the drive shaft 12 of the radial plane 40.
- the longitudinal axis 23 of the cylinder bore 22 extends at least approximately perpendicular to the axis of rotation
- the roller 34 can also be arranged such that the longitudinal axis 23 of the cylinder bore 22 does not intersect the axis of rotation 35 of the roller 34.
- the longitudinal axis 23 of the cylinder bore 22 does not intersect the axis of rotation 13 of the drive shaft 12.
- the longitudinal axis 23 of the cylinder bore 22 is equal to the direction of the stroke movement of the pump piston 20.
- the pump piston 20 is shown when it is arranged in its inner dead center.
- the angle ⁇ between the longitudinal axis 23 of the cylinder bore 22 and the radial plane 40 is, for example, between approximately 0 ° and approximately 20 °.
- the angle ⁇ can preferably be selected such that the force application angle ⁇ between the Cam 14 and the roller 34 during the rotation of the drive shaft 12 with an average stroke of the pump piston 20 is at least approximately equal to ⁇ , so that only a force acts on the roller 34 and the pump piston 20 in the direction of the longitudinal axis 23 of the cylinder bore 22.
- the direction of the force application angle ⁇ between the cam 14 and the roller 34 is opposite during the delivery stroke of the pump piston 20 to the direction during the suction stroke of the pump piston 20. Due to the supporting forces acting on the pump piston 20 in the area of the inner dead center and in the area of the outer dead center However, cylinder bore 22 only has a small amount of friction work, since the pump piston 20 only executes a small stroke when these supporting forces occur.
- FIG. 3 shows the high-pressure pump according to a second exemplary embodiment, in which the basic structure is the same as described above, but the arrangement of the cylinder bore 22 has been modified.
- FIG. 3 again shows the radial plane 40 which contains the axis of rotation 13 of the drive shaft 12.
- the position of the cylinder bore 22 is changed such that its longitudinal axis 23 is at least approximately parallel to the radial plane 40, but in FIG Direction of rotation 18 of the drive shaft 12 extends offset to the radial plane 40.
- the roller 34 is arranged in such a way that its axis of rotation 35 extends at least approximately in the radial plane 40.
- the longitudinal axis 23 of the cylinder bore 22 does not intersect the axis of rotation 13 of the drive shaft 12 and the axis of rotation 35 of the roller 34.
- the normal force Fn acting on the roller 34 in the direction of the longitudinal axis 23 generates a torque on the pump piston 20, by means of which the pump piston 20 in its inner and outer end region with its rotational direction 18 of the drive shaft
- the longitudinal axis 23 of the cylinder bore 22 is preferably offset from the radial plane 40 in such a way that the forces Fa and Fi are at least approximately the same size and each half the transverse force Fq.
- FIG. 4 shows the high-pressure pump according to a third exemplary embodiment, in which the structure is essentially the same as in the second exemplary embodiment, but additionally the roller 34 is arranged offset.
- the roller 34 is arranged such that its axis of rotation 35 in one the axis of rotation
- the 13 of the drive shaft 12 includes radial plane 42 which is inclined at an angle ⁇ to the longitudinal axis 23 of the cylinder bore 22, the angle ⁇ being between approximately 0 ° and approximately 20 °.
- the pump working chamber 24 becomes through the fuel inlet channel 26 with the inlet valve 28 open filled with fuel, the exhaust valve 32 is closed.
- the pump piston 20 delivers fuel under high pressure through the fuel drain channel 30 to the high-pressure accumulator 110 with the outlet valve 32 open, wherein the inlet valve 28 is closed.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer BrennkraftmaschineHigh-pressure pump, in particular for a fuel injection device of an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung es Anspruchs 1.The invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine.
Eine solche Hochdruckpumpe ist durch die DE 199 07 311 AI bekannt. Diese Hochdruckpumpe weist eine rotierend angetriebene Antriebswelle und wenigstens ein Pumpenelement auf. Das Pu penelement weist einen zumindest mittelbar durch die Antriebswelle in einer Hubbewegung angetriebenen Pumpenkolben auf, der in einer Zylinderbohrung eines Gehäuses der Hochdruckpumpe verschiebbar geführt ist. Die Längsachse der Zylinderbohrung verläuft dabei senkrecht zur Drehachse der Antriebswelle und in einer die Drehachse enthaltenden Radialebene. Die Antriebswelle weist einen Nocken auf, auf dem eine zylindrische Rolle abrollt, die in einem mit dem Pumpenkolben verbundenen Rollenschuh drehbar gelagert ist. Der Rollenschuh ist in einer Bohrung des Gehäuses der Hochdruckpumpe verschiebbar gelagert und durch die Lagerung des Rollenschuhs werden bei der Rotation der Antriebswelle vom Nocken auf die Rolle übertragene Querkräfte aufgenommen, so dass diese nicht auf den Pumpenkolben wirken. Der Rollenschuh ist dabei im Durchmesser wesentlich größer ausgeführt als der Pumpenkolben, so dass durch die Querkräfte nur geringe Flächenpressungen des Rollenschuhs in der Bohrung verursacht werden. Nachteilig bei dieser bekannten Hochdruckpumpe ist jedoch, dass diese wegen des zusätzlichen Rollenschuhs und der für dessen Führung erforderlichen Bohrung im Pumpengehäuse, die exakt zur Zylinderbohrung ausgerichtet sein muss, in der Herstellung aufwendig ist und ein hohes Gewicht aufweist.Such a high pressure pump is known from DE 199 07 311 AI. This high-pressure pump has a rotatingly driven drive shaft and at least one pump element. The Pu penelement has an at least indirectly driven by the drive shaft in a stroke pump piston which is slidably guided in a cylinder bore of a housing of the high pressure pump. The longitudinal axis of the cylinder bore extends perpendicular to the axis of rotation of the drive shaft and in a radial plane containing the axis of rotation. The drive shaft has a cam on which a cylindrical roller rolls, which is rotatably mounted in a roller shoe connected to the pump piston. The roller shoe is slidably mounted in a bore in the housing of the high-pressure pump and the bearing of the roller shoe absorbs transverse forces transmitted from the cam to the roller during the rotation of the drive shaft, so that these do not act on the pump piston. The roller shoe is made much larger in diameter than the pump piston, so that the lateral forces cause only small surface pressures of the roller shoe in the bore. A disadvantage of this known high-pressure pump, however, is that it is because of the additional roller shoe and the one for guiding it required bore in the pump housing, which must be exactly aligned with the cylinder bore, is complex to manufacture and has a high weight.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch die bei der Rotation der Antriebswelle auf den Pumpenkolben erzeugten Querkraft nur geringe auf die Führung des Pumpenkolbens in der Zylinderbohrung wirkende Kräfte verursacht wird, so dass diese direkt vom Pumpenkolben und dessen Führung in der Zylinderbohrung aufgenommen werden kann, ohne dass unzulässig hohe und zu starkem Verschleiß führende Flächenpressungen auftreten. Es ist somit kein zusätzliches Bauteil zur Aufnahme der Querkraft erforderlich, wodurch die Herstellung der Hochdruckpumpe vereinfacht ist und deren Gewicht verringert ist.The high-pressure pump according to the invention with the features according to claim 1 has the advantage that the lateral force generated during rotation of the drive shaft on the pump piston causes only small forces acting on the guidance of the pump piston in the cylinder bore, so that this directly from the pump piston and its Guide can be accommodated in the cylinder bore without causing impermissibly high surface pressure and excessive wear. There is therefore no need for an additional component to absorb the transverse force, which simplifies the manufacture of the high-pressure pump and reduces its weight.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben . Bei der Ausbildung gemäß Anspruch 3 wird durch die Querkraft ein Drehmoment auf den Pumpenkolben erzeugt, durch das der Pumpenkolben an beiden Endbereichen an dieselbe Seite der Zylinderbohrung gepresst wird, wobei die Summe der auf den Pumpenkolben in seinen Endbereichen an der Abstützung in der Zylinderbohrung wirkenden Kräfte gleich der abzustützenden Querkraft ist. Durch die Ausbildung gemäß Anspruch 4 kann erreicht werden, dass die größten Stützkräfte auf den Pumpenkolben nur im Bereich von dessen Totpunkten wirken, wo der Pumpenkolben nur einen geringen Hub ausführt. Bei der Ausführung gemäß Anspruch 5 kann erreicht werden, dass auf den Pumpenkolben über einen wesentlichen Teil seines Hubs nur geringe Stützkräfte in der Zylinderbohrung wirken. Die Ausbildung gemäß Anspruch 6 ermöglicht eine Übertragung der Drehbewegung der Antriebswelle in die Hubbewegung des Pumpenkolbens mit geringer Reibung.Advantageous refinements and developments of the high-pressure pump according to the invention are specified in the dependent claims. In the embodiment according to claim 3, the transverse force generates a torque on the pump piston, by means of which the pump piston is pressed at both end regions on the same side of the cylinder bore, the sum of the forces acting on the pump piston in its end regions on the support in the cylinder bore is equal to the shear force to be supported. It can be achieved that the greatest supporting forces act on the pump piston only in the area of its dead center, where the pump piston executes only a small stroke. In the embodiment according to claim 5 it can be achieved that only a small supporting force acts in the cylinder bore on the pump piston over a substantial part of its stroke. The training according to claim 6 enables transmission of Rotary movement of the drive shaft in the stroke movement of the pump piston with low friction.
Zeichnungdrawing
Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine in einem Längsschnitt, Figur 2 die Hochdruckpumpe ausschnittsweise in einem Querschnitt gemäß einem ersten Ausführungsbeispiel, Figur 3 die Hochdruckpumpe in einem Querschnitt gemäß einem zweiten Ausführungsbeispiel und Figur 4 die Hochdruckpumpe in einem Querschnitt gemäß einem dritten Ausführungsbeispiel.Several embodiments of the invention are shown in the drawing and explained in more detail in the following description. 1 shows a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section, FIG. 2 shows a section of the high-pressure pump in a cross section according to a first exemplary embodiment, FIG. 3 shows the high-pressure pump in a cross section according to a second exemplary embodiment, and FIG. 4 shows the high-pressure pump in a cross section according to a third embodiment.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In den Figuren 1 bis 4 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein mehrteiliges Gehäuse 10 auf, in dem eine durch die Brennkraftmaschine rotierend antreibbare Antriebswelle 12 angeordnet ist. Die Antriebswelle 12 ist im Gehäuse 10 über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen drehbar gelagert. In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 12 wenigstens einen Nocken 14 auf, wobei der Nocken 14 auch als Mehrfachnocken ausgebildet sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere im Gehäuse 10 angeordnete Pumpenelemente 16 mit jeweils einem Pumpenkolben 20 auf, der durch den Nocken 14 der Antriebswelle 12 in einer Hubbewegung angetrieben wird.1 to 4 show a high-pressure pump for a fuel injection device of an internal combustion engine. The high-pressure pump has a multi-part housing 10, in which a drive shaft 12, which can be driven in rotation by the internal combustion engine, is arranged. The drive shaft 12 is rotatably mounted in the housing 10 via two bearing points spaced apart in the direction of the axis of rotation 13 of the drive shaft 12. In an area lying between the two bearing points, the drive shaft 12 has at least one cam 14, wherein the cam 14 can also be designed as a multiple cam. The high-pressure pump has at least one or more pump elements 16 arranged in the housing 10, each with a pump piston 20, which is driven by the cam 14 of the drive shaft 12 in a lifting movement.
Der Pumpenkolben 20 ist in einer im Gehäuse 10 ausgebildeten Zylinderbohrung 22 dicht verschiebbar geführt und begrenzt mit seiner der Antriebswelle 12 abgewandten Stirnseite in der Zylinderbohrung 22 einen Pumpenarbeitsraum 24. Der Pumpenarbeitsraum 24 weist über einen im Gehäuse 10 verlaufenden KraftstoffZulaufkanal 26 eine Verbindung mit einem Kraftstoffzulauf, beispielsweise einer Förderpumpe auf. An der Mündung desThe pump piston 20 is guided so as to be tightly displaceable in a cylinder bore 22 formed in the housing 10 and delimits a pump work chamber 24 with its end face facing away from the drive shaft 12 in the cylinder bore 22. The pump work chamber 24 has a connection to a fuel feed, for example a feed pump, via a fuel feed channel 26 running in the housing 10. At the mouth of the
Kraftstoffzulaufkanals 26 in den Pumpenarbeitsraum 24 ist ein in den Pumpenarbeitsraum 24 öffnendes Einlassventil 28 angeordnet. Der Pumpenarbeitsraum 24 weist ausserdem über einen im Gehäuse 10 verlaufenden Kraftstoffablaufkanal 30 eine Verbindung mit einem Auslass auf, der beispielsweise mit einem Hochdruckspeicher 110 verbunden ist. Mit dem Hochdruckspeicher 110 sind ein oder vorzugsweise mehrere an den Zylindern der Brennkraftmaschine angeordnete Injektoren 120 verbunden, durch die Kraftstoff in die Zylinder der Brennkraftmaschine eingespritzt wird. An der Mündung des Kraftstoffablaufkanals 30 in den Pumpenarbeitsraum 24 ist ein aus dem Pumpenarbeitsraum 24 öffnendes Auslassventil 32 angeordnet .An inlet valve 28 opening into the pump working chamber 24 is arranged in the fuel working channel 26 in the pump working chamber 24. The pump work chamber 24 also has a connection to an outlet via a fuel drain channel 30 running in the housing 10, said outlet being connected, for example, to a high-pressure accumulator 110. One or, preferably, a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, and are used to inject fuel into the cylinders of the internal combustion engine. An outlet valve 32 opening out of the pump work chamber 24 is arranged at the mouth of the fuel drain channel 30 into the pump work chamber 24.
Der Pumpenkolben 20 kann sich direkt mit einem aus der Zylinderbohrung 22 zur Antriebswelle 12 hin herausragenden Kolbenfuß am Nocken 14 der Antriebswelle 12 abstützen. Vorzugsweise stützt sich der Pumpenkolben 20 jedoch über eine Rolle 34 am Nocken 14 ab. Die Rolle 34 ist dabei zumindest annähernd zylinderförmig ausgebildet und deren Drehachse 35 verläuft zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12. Die Rolle 34 ist in einer konkaven Vertiefung 36 eines Rollenschuhs 38 drehbar gelagert, wobei der Rollenschuh 38 einstückig mit dem Pumpenkolben 20 ausgebildet sein kann oder als separates Teil mit dem Pumpenkolben 20 verbunden ist. Der Rollenschuh 38 weist einen größeren Querschnitt auf als der in der Zylinderbohrung 22 angeordnete Teil des Pumpenkolbens 20. Bei der Rotation der Antriebswelle 12 um ihre Drehachse 13 rollt die Rolle 34 auf dem Nocken 14 ab und bewirkt die Hubbewegung des Pumpenkolbens 20 und damit eine Kraftstoffförderung unter Hochdruck in den Speicher 110. Der Pumpenkolben 20 und der Rollenschuh 38 werden durch eine vorgespannte Feder 39 zum Nocken 14 der AntriebswelleThe pump piston 20 can be supported directly on the cam 14 of the drive shaft 12 with a piston foot protruding from the cylinder bore 22 toward the drive shaft 12. However, the pump piston 20 is preferably supported on the cam 14 via a roller 34. The roller 34 is at least approximately cylindrical and its axis of rotation 35 extends at least approximately parallel to the axis of rotation 13 of the drive shaft 12. The roller 34 is rotatably mounted in a concave recess 36 of a roller shoe 38, the roller shoe 38 being formed in one piece with the pump piston 20 can or is connected to the pump piston 20 as a separate part. The roller shoe 38 has a larger cross section than the part of the pump piston 20 arranged in the cylinder bore 22. When the drive shaft 12 rotates about its axis of rotation 13, the roller 34 rolls on the cam 14 and causes this Stroke movement of the pump piston 20 and thus a delivery of fuel under high pressure into the accumulator 110. The pump piston 20 and the roller shoe 38 become a cam 14 of the drive shaft by means of a prestressed spring 39
12 hin beaufschlagt.12 acted out.
In Figur 2 ist die Hochdruckpumpe ausschnittsweise in einem Querschnitt gemäß einem ersten Ausführungsbeispiel dargestellt. In Figur 2 ist eine die Drehachse 13 der Antriebswelle 12 enthaltende Radialebene mit der Bezugszahl 40 bezeichnet. Die Rolle 34 ist derart angeordnet, dass deren Drehachse 35 zumindest annähernd in der Radialebene 40 verläuft. Die Zylinderbohrung 22 ist derart angeordnet, dass deren Längsachse 23 nicht in der Radialebene 40 verläuft sondern ausgehend von einer Anordnung der Längsachse 23 in der Radialebene 40 derart bezüglich der Radialebene 40 geneigt verläuft, dass die Längsachse 23 mit zunehmendem Abstand von der Antriebswelle 12 in Drehrichtung 18 der Antriebswelle 12 der Radialebene 40 vorauseilt. Die Längsachse 23 der Zylinderbohrung 22 verläuft dabei zumindest annähernd senkrecht zur DrehachseFIG. 2 shows a section of the high-pressure pump in a cross section according to a first exemplary embodiment. In FIG. 2, a radial plane containing the axis of rotation 13 of the drive shaft 12 is designated by the reference number 40. The roller 34 is arranged in such a way that its axis of rotation 35 extends at least approximately in the radial plane 40. The cylinder bore 22 is arranged such that its longitudinal axis 23 does not run in the radial plane 40 but, based on an arrangement of the longitudinal axis 23 in the radial plane 40, runs inclined with respect to the radial plane 40 such that the longitudinal axis 23 increases in the direction of rotation with increasing distance from the drive shaft 12 18 leads the drive shaft 12 of the radial plane 40. The longitudinal axis 23 of the cylinder bore 22 extends at least approximately perpendicular to the axis of rotation
13 der Antriebswelle 12 und schneidet die Drehachse 35 der Rolle 34. Die Rolle 34 kann alternativ wie in Figur 2 mit gestrichelten Linien dargestellt auch derart angeordnet sein, dass die Längsachse 23 der Zylinderbohrung 22 die Drehachse 35 der Rolle 34 nicht schneidet. Die Längsachse 23 der Zylinderbohrung 22 schneidet die Drehachse 13 der Antriebswelle 12 nicht. Die Längsachse 23 der Zylinderbohrung 22 ist gleich der Richtung der Hubbewegung des Pumpenkolbens 20. In Figur 2 ist der Pumpenkolben 20 bei Anordnung in seinem inneren Totpunkt dargestellt.13 of the drive shaft 12 and intersects the axis of rotation 35 of the roller 34. As an alternative, as shown in FIG. 2 with dashed lines, the roller 34 can also be arranged such that the longitudinal axis 23 of the cylinder bore 22 does not intersect the axis of rotation 35 of the roller 34. The longitudinal axis 23 of the cylinder bore 22 does not intersect the axis of rotation 13 of the drive shaft 12. The longitudinal axis 23 of the cylinder bore 22 is equal to the direction of the stroke movement of the pump piston 20. In FIG. 2, the pump piston 20 is shown when it is arranged in its inner dead center.
Der Winkel α zwischen der Längsachse 23 der Zylinderbohrung 22 und der Radialebene 40 beträgt beispielsweise zwischen etwa 0° und etwa 20°. Der Winkel α kann vorzugsweise derart gewählt sein, dass der Kraftangriffswinkel φ zwischen dem Nocken 14 und der Rolle 34 bei der Rotation der Antriebswelle 12 bei mittlerem Hub des Pumpenkolbens 20 zumindest annähernd gleich α ist, so dass auf die Rolle 34 und den Pumpenkolben 20 nur eine Kraft in Richtung der Längsachse 23 der Zylinderbohrung 22 wirkt. Im Bereich des inneren Totpunkts des Pumpenkolbens 20, in dem der Pumpenkolben 20 am weitesten zur Antriebswelle 12 hin aus der Zylinderbohrung 22 ausgetaucht ist und die Rolle 34 am tiefsten Punkt des Nockens 14 anliegt, und im Bereich des äußeren Totpunkts des Pumpenkolbens 20, in dem der Pumpenkolben 20 am weitestens von der Antriebswelle 12 weg in die Zylinderbohrung 22 eingetaucht ist und die Rolle 34 am höchsten Punkt des Nockens 14 anliegt, ergibt sich dabei ein Kraftangriffswinkel φ zwischen dem Nocken 14 und der Rolle 34, der ungleich α ist, so dass auf die Rolle 34 und den Pumpenkolben 20 sowohl eine Kraft in Richtung der Längsachse 23 der Zylinderbohrung 22 als auch senkrecht zur Längsachse 23 wirkt. Die Richtung des Kraftangriffswinkels φ zwischen dem Nocken 14 und der Rolle 34 ist beim Förderhub des Pumpenkolbens 20 entgegengesetzt zu der Richtung beim Saughub des Pumpenkolbens 20. Durch die im Bereich des inneren Totpunkts und im Bereich des äußeren Totpunkts auf den Pumpenkolben 20 wirkenden Stützkräfte in der Zylinderbohrung 22 wird jedoch nur eine geringe Reibarbeit geleistet, da der Pumpenkolben 20 beim Auftreten dieser Stützkräfte nur einen geringen Hub ausführt.The angle α between the longitudinal axis 23 of the cylinder bore 22 and the radial plane 40 is, for example, between approximately 0 ° and approximately 20 °. The angle α can preferably be selected such that the force application angle φ between the Cam 14 and the roller 34 during the rotation of the drive shaft 12 with an average stroke of the pump piston 20 is at least approximately equal to α, so that only a force acts on the roller 34 and the pump piston 20 in the direction of the longitudinal axis 23 of the cylinder bore 22. In the area of the inner dead center of the pump piston 20, in which the pump piston 20 is most distant to the drive shaft 12 out of the cylinder bore 22 and the roller 34 rests against the lowest point of the cam 14, and in the area of the outer dead center of the pump piston 20, in which the pump piston 20 is immersed as far as possible from the drive shaft 12 into the cylinder bore 22 and the roller 34 abuts the highest point of the cam 14, this results in a force application angle φ between the cam 14 and the roller 34, which is not equal to α, so that both a force in the direction of the longitudinal axis 23 of the cylinder bore 22 and perpendicular to the longitudinal axis 23 acts on the roller 34 and the pump piston 20. The direction of the force application angle φ between the cam 14 and the roller 34 is opposite during the delivery stroke of the pump piston 20 to the direction during the suction stroke of the pump piston 20. Due to the supporting forces acting on the pump piston 20 in the area of the inner dead center and in the area of the outer dead center However, cylinder bore 22 only has a small amount of friction work, since the pump piston 20 only executes a small stroke when these supporting forces occur.
In Figur 3 ist die Hochdruckpumpe gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der grundsätzliche Aufbau gleich ist wie vorstehend beschrieben, jedoch die Anordnung der Zylinderbohrung 22 modifiziert ist. In Figur 3 ist wiederum die die Drehachse 13 der Antriebswelle 12 enthaltende Radialebene 40 dargestellt. Die Zylinderbohrung 22 ist ausgehend von einer Anordnung in der Radialebene 40 derart in ihrer Lage verändert, dass deren Längsachse 23 zumindest annähernd parallel zur Radialebene 40, jedoch in Drehrichtung 18 der Antriebswelle 12 zur Radialebene 40 versetzt verläuft. Die Rolle 34 ist derart angeordnet, dass deren Drehachse 35 zumindest annähernd in der Radialebene 40 verläuft. Die Längsachse 23 der Zylinderbohrung 22 schneidet die Drehachse 13 der Antriebswelle 12 und die Drehachse 35 der Rolle 34 nicht. Bei dieser Anordnung der Längsachse 23 der Zylinderbohrung 22 wird durch die auf die Rolle 34 in Richtung der Längsachse 23 wirkende Normalkraft Fn ein Drehmoment auf den Pumpenkolben 20 erzeugt, durch das der Pumpenkolben 20 in seinem inneren und äußeren Endbereich mit seiner in Drehrichtung 18 der AntriebswelleFIG. 3 shows the high-pressure pump according to a second exemplary embodiment, in which the basic structure is the same as described above, but the arrangement of the cylinder bore 22 has been modified. FIG. 3 again shows the radial plane 40 which contains the axis of rotation 13 of the drive shaft 12. Starting from an arrangement in the radial plane 40, the position of the cylinder bore 22 is changed such that its longitudinal axis 23 is at least approximately parallel to the radial plane 40, but in FIG Direction of rotation 18 of the drive shaft 12 extends offset to the radial plane 40. The roller 34 is arranged in such a way that its axis of rotation 35 extends at least approximately in the radial plane 40. The longitudinal axis 23 of the cylinder bore 22 does not intersect the axis of rotation 13 of the drive shaft 12 and the axis of rotation 35 of the roller 34. In this arrangement of the longitudinal axis 23 of the cylinder bore 22, the normal force Fn acting on the roller 34 in the direction of the longitudinal axis 23 generates a torque on the pump piston 20, by means of which the pump piston 20 in its inner and outer end region with its rotational direction 18 of the drive shaft
12 weisenden Mantelfläche gegen die Zylinderbohrung 22 gepresst wird. Die Summe der auf den Pumpenkolben 20 in der Zylinderbohrung 22 zur Abstützung der Querkraft Fq im äußeren und inneren Endbereich des Pumpenkolbens 20 wirkenden Kräfte Fa und Fi ist dabei etwa gleich der Querkraft Fq. Vorzugsweise ist die Längsachse 23 der Zylinderbohrung 22 derart zur Radialebene 40 versetzt, dass die Kräfte Fa und Fi zumindest annähernd gleich groß und jeweils halb so groß wie die Querkraft Fq sind.12 facing outer surface is pressed against the cylinder bore 22. The sum of the forces Fa and Fi acting on the pump piston 20 in the cylinder bore 22 for supporting the transverse force Fq in the outer and inner end region of the pump piston 20 is approximately equal to the transverse force Fq. The longitudinal axis 23 of the cylinder bore 22 is preferably offset from the radial plane 40 in such a way that the forces Fa and Fi are at least approximately the same size and each half the transverse force Fq.
In Figur 4 ist die Hochdruckpumpe gemäß einem dritten Ausführungsbeispiel dargestellt, bei dem der Aufbau im wesentlichen gleich ist wie beim zweiten Ausführungsbeispiel, jedoch zusätzlich die Rolle 34 versetzt angeordnet ist. Die Rolle 34 ist dabei derart angeordnet, dass deren Drehachse 35 in einer die DrehachseFIG. 4 shows the high-pressure pump according to a third exemplary embodiment, in which the structure is essentially the same as in the second exemplary embodiment, but additionally the roller 34 is arranged offset. The roller 34 is arranged such that its axis of rotation 35 in one the axis of rotation
13 der Antriebswelle 12 enthaltenden Radialebene 42 verläuft, die unter einem Winkel ß geneigt zu der Längsachse 23 der Zylinderbohrung 22 angeordnet ist, wobei der Winkel ß zwischen etwa 0° und etwa 20° betragen kann.13 of the drive shaft 12 includes radial plane 42 which is inclined at an angle β to the longitudinal axis 23 of the cylinder bore 22, the angle β being between approximately 0 ° and approximately 20 °.
Beim Saughub des Pumpenkolbens 20, bei dem sich dieser bewirkt durch die Feder 39 in der Zylinderbohrung 22 nach innen bewegt, wird der Pumpenarbeitsraum 24 durch den Kraftstoffzulaufkanal 26 bei geöffnetem Einlassventil 28 mit Kraftstoff befüllt, wobei das Auslassventil 32 geschlossen ist. Beim Förderhub des Pumpenkolbens 20, bei dem sich dieser bewirkt durch den Nocken 14 gegen die Kraft der Feder 39 in der Zylinderbohrung 22 nach aussen bewegt, wird durch den Pumpenkolben 20 Kraftstoff unter Hochdruck durch den Kraftstoffablaufkanal 30 bei geöffnetem Auslassventil 32 zum Hochdruckspeicher 110 gefördert, wobei das Einlassventil 28 geschlossen ist. During the suction stroke of the pump piston 20, during which it is moved inward by the spring 39 in the cylinder bore 22, the pump working chamber 24 becomes through the fuel inlet channel 26 with the inlet valve 28 open filled with fuel, the exhaust valve 32 is closed. During the delivery stroke of the pump piston 20, during which it is moved outwards by the cam 14 against the force of the spring 39 in the cylinder bore 22, the pump piston 20 delivers fuel under high pressure through the fuel drain channel 30 to the high-pressure accumulator 110 with the outlet valve 32 open, wherein the inlet valve 28 is closed.
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004011284.3 | 2004-03-09 | ||
| DE200410011284 DE102004011284A1 (en) | 2004-03-09 | 2004-03-09 | High-pressure pump, in particular for a fuel injection device of an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2005088125A1 true WO2005088125A1 (en) | 2005-09-22 |
Family
ID=34895045
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP2005/050124 Ceased WO2005088125A1 (en) | 2004-03-09 | 2005-01-13 | High pressure pump, particularly for a fuel injection device of an internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE102004011284A1 (en) |
| WO (1) | WO2005088125A1 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008037745A3 (en) * | 2006-09-28 | 2008-08-14 | Continental Automotive Gmbh | Radial piston pump for a high-pressure fuel supply |
| WO2012059315A1 (en) * | 2010-11-05 | 2012-05-10 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump |
| WO2012156137A1 (en) * | 2011-05-18 | 2012-11-22 | Robert Bosch Gmbh | Piston pump |
| US8662864B2 (en) | 2010-12-09 | 2014-03-04 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
| USD706397S1 (en) | 2011-08-19 | 2014-06-03 | S.P.M. Flow Control, Inc. | Portion of fluid end |
| USD706833S1 (en) | 2012-04-27 | 2014-06-10 | S.P.M. Flow Control, Inc. | Center portion of a fluid cylinder for a pump |
| US20150211454A1 (en) * | 2014-01-24 | 2015-07-30 | Denso Corporation | High pressure fuel pump |
| WO2016058736A1 (en) * | 2014-10-14 | 2016-04-21 | Continental Automotive Gmbh | Fuel pump |
| US9945362B2 (en) | 2012-01-27 | 2018-04-17 | S.P.M. Flow Control, Inc. | Pump fluid end with integrated web portion |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007019261A1 (en) * | 2007-04-17 | 2008-10-23 | Golle Motor Ag | Radial piston pump, esp. For Common Rail (CR) injection systems |
| DE102008007342A1 (en) * | 2008-02-04 | 2009-08-06 | Robert Bosch Gmbh | Shear force-free cams for common-rail high-pressure pumps |
| DE102008050661A1 (en) | 2008-09-22 | 2010-03-25 | Vladimir Volchkov | Drive device i.e. high pressure pump, for fuel injection to reciprocating piston engine, has return spring component consisting of pairs of helical compression springs, and pistons provided on supporting element |
| DE102009002488A1 (en) | 2009-04-20 | 2010-10-21 | Robert Bosch Gmbh | Cam drive in an internal combustion engine and a high-pressure pump driven by it |
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| DE3505176C1 (en) * | 1985-02-15 | 1986-04-24 | Hauhinco Maschinenfabrik G. Hausherr, Jochums Gmbh & Co Kg, 4300 Essen | Radial-piston pump for hydraulic media |
| DE3942223C1 (en) * | 1989-12-21 | 1991-06-20 | Asea Brown Boveri Ag, 6800 Mannheim, De | Piston-cylinder for electrical switching drive unit - has piston driven against spring by eccentric to off set piston axis w.r.t. eccentric centre point |
| DE4310062A1 (en) * | 1993-03-27 | 1994-09-29 | Teves Gmbh Alfred | Radial piston machine |
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Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008037745A3 (en) * | 2006-09-28 | 2008-08-14 | Continental Automotive Gmbh | Radial piston pump for a high-pressure fuel supply |
| CN103201499B (en) * | 2010-11-05 | 2016-10-05 | 罗伯特·博世有限公司 | Pump |
| WO2012059315A1 (en) * | 2010-11-05 | 2012-05-10 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump |
| CN103201499A (en) * | 2010-11-05 | 2013-07-10 | 罗伯特·博世有限公司 | Pump, in particular high-pressure fuel pump |
| US8662864B2 (en) | 2010-12-09 | 2014-03-04 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
| US8668470B2 (en) | 2010-12-09 | 2014-03-11 | S.P.M. Flow Control, Inc. | Offset valve bore for a reciprocating pump |
| US9989044B2 (en) | 2010-12-09 | 2018-06-05 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
| US9784262B2 (en) | 2010-12-09 | 2017-10-10 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
| WO2012156137A1 (en) * | 2011-05-18 | 2012-11-22 | Robert Bosch Gmbh | Piston pump |
| USD706397S1 (en) | 2011-08-19 | 2014-06-03 | S.P.M. Flow Control, Inc. | Portion of fluid end |
| US9945362B2 (en) | 2012-01-27 | 2018-04-17 | S.P.M. Flow Control, Inc. | Pump fluid end with integrated web portion |
| US10330097B2 (en) | 2012-01-27 | 2019-06-25 | S.P.M. Flow Control, Inc. | Pump fluid end with integrated web portion |
| USD706833S1 (en) | 2012-04-27 | 2014-06-10 | S.P.M. Flow Control, Inc. | Center portion of a fluid cylinder for a pump |
| US20150211454A1 (en) * | 2014-01-24 | 2015-07-30 | Denso Corporation | High pressure fuel pump |
| WO2016058736A1 (en) * | 2014-10-14 | 2016-04-21 | Continental Automotive Gmbh | Fuel pump |
| US10054090B2 (en) | 2014-10-14 | 2018-08-21 | Continental Automotive Gmbh | High-pressure fuel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102004011284A1 (en) | 2005-09-29 |
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