EP2627903B1 - High-pressure pump for a fuel injection device - Google Patents

High-pressure pump for a fuel injection device Download PDF

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Publication number
EP2627903B1
EP2627903B1 EP11754404.9A EP11754404A EP2627903B1 EP 2627903 B1 EP2627903 B1 EP 2627903B1 EP 11754404 A EP11754404 A EP 11754404A EP 2627903 B1 EP2627903 B1 EP 2627903B1
Authority
EP
European Patent Office
Prior art keywords
tappet
pressure pump
eccentric
pump according
bucket tappet
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.)
Not-in-force
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EP11754404.9A
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German (de)
French (fr)
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EP2627903A1 (en
Inventor
Alfons Schoetz
Markus Schetter
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2627903A1 publication Critical patent/EP2627903A1/en
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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
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • 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

Definitions

  • the present invention relates to a high pressure pump of a fuel injection device, which can be used in particular for a common rail injection device of an internal combustion engine, according to the preamble of claim 1.
  • Such a high-pressure pump is through the WO 03/014569 A1 known.
  • This high-pressure pump comprises a pump shaft which is rotationally rigidly connected to an eccentric, and at least one pump element which is inserted in a housing bore of an engine block.
  • the pump element has an element piston which is drive-connected to the eccentric via a cup tappet and which is guided so as to be movable in a cylinder bore of a shaft section, as well as a tappet spring acting on the tappet.
  • the element piston defines a pump working space connected to a suction valve and a high pressure valve.
  • a drive connection between the bucket tappet and the eccentric comprises a rotatably mounted on the eccentric race on which the bucket tappet is non-positively supported.
  • the bucket tappet includes on the drive side a sliding plate, which forms a contact zone as a contact surface together with a contact surface of the eccentric surrounding race. Lubrication of the contact zone between the bucket tappet and the raceway is effected by the medium surrounding the bucket tappet and the raceway. As a result, under certain circumstances, sufficient lubrication of the contact zone is ensured.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that the lubrication of the contact zone between the tappet and the race is improved by the at least one flood hole in the slide plate.
  • a preferred embodiment of the invention provides that the sliding plate is used as a separate part in the tappets.
  • the preferably pressed into the cup tappet and fixed in position sliding plate is supported with a contact surface on the associated contact surface of the eccentric enclosing race, wherein the contact surfaces together form a contact zone.
  • the sliding plate is made of a material adapted to the given loads and lubricant conditions. To achieve a high wear resistance, it makes sense, for example, to produce the sliding plate made of hard metal or a ceramic material.
  • the tappet with integrated sliding plate is further characterized by a simplified and component-optimized design. Due to the sliding plate, the tappet advantageously requires neither a position-oriented mounting position nor an anti-twist device, which simplifies assembly.
  • the inventive simplified and cost-optimized bucket tappet concept also offers a cost advantage over known solutions of bucket tappets with roller shoe and integrated role.
  • the race is rotatably mounted on the eccentric shaft via a rolling bearing or sliding bearing.
  • a rolling bearing or sliding bearing By the use of commercial Wälz- or Plain bearings can be a robust, proven and inexpensive storage of the race on the eccentric shaft can be realized.
  • roller bearings are preferably cylindrical roller bearings, since the storage has to absorb any axial forces. Due to the small required radial space can preferably be used for the storage of the race needle roller bearings.
  • Another particular embodiment of the invention is characterized in that at least one of the mutually facing contact surfaces of the sliding plate and the race is slightly convex or convex. This measure advantageously compensates for slight angle errors that can occur during production due to permissible position and / or shape tolerances.
  • the convexity also serves to reduce the contact area between the slide plate and the raceway to line contact, thereby advantageously reducing friction.
  • the invention to coat at least one contact surface of the race or the sliding plate with a material of high wear resistance.
  • the invention further includes a coating of at least one contact surface with a friction-reducing material.
  • the high pressure pump designed as a plug-in pump is used as a structural unit with a plug-in pump body in a housing bore of the engine block.
  • a cylinder bore is introduced, which is intended to guide the element piston and at the same time forms the pump working space.
  • the invention offers the possibility to create a high-pressure pump in which the principle of a plug-in pump is combined with a drive connection having a mounted on the eccentric shaft raceway and a bucket tappet with integrated sliding plate.
  • the structural design of the invention further includes different solutions for guiding the bucket tappet.
  • An outer guide of the tappet is preferred, in which a tappet body of the tappet is guided over a lateral surface in the housing bore of the engine block. This outer guide of the tappet prevents deformation of the guide of the element piston in the shaft portion. Alternatively, it is advisable to guide the tappet inside the shaft portion of the plug-in pump body.
  • a space-optimized arrangement of the plunger spring is also provided for the designed as a plug-pump high-pressure pump.
  • the plunger spring is supported on an integrated inside the cup tappet spring plate, wherein the plunger spring is guided over a greater length within the plunger body.
  • the mutual spring end of the plunger spring is enclosed for guiding by a board of the plug-in pump body.
  • At least one preferably circumferential lubrication groove is introduced in a lateral surface of the tappet body, which are connected via associated passage bores with a plunger interior.
  • a high pressure pump 1 is shown for a fuel injection device of an internal combustion engine, which is preferably intended for a common rail injection system of a diesel internal combustion engine.
  • fuel is at high pressure in an in Fig. 1 not shown storage (rail) promoted, from which the fuel is injected via fuel injectors specifically into associated combustion chambers of an internal combustion engine.
  • the high-pressure pump 1 forms a radial piston pump, which is used as a plug-in pump with a plug-in pump body 2 in an engine block 3 or housing.
  • the plug-in pump body 2 is followed by a low-pressure unit 4, which can also be referred to as a cylinder head.
  • a rotatable in the engine block 3 drive shaft with an axis 5 is connected to an eccentric 6, whose central axis 7 has an eccentricity S with respect to the axis 5.
  • the drive shaft may be a shaft of the internal combustion engine, for example, the camshaft or a balancer shaft.
  • the eccentric 6 is surrounded by a race 9, which is rotatably mounted on the eccentric 6 via a rolling bearing 10, in particular a needle bearing, with cylindrical rolling elements 11 and which is drivingly connected to a tappet 13 of a pump element 8.
  • the pump element 8 comprises the cup tappet 13 in which an element piston 12 or pump piston is held and a tappet spring 14.
  • the tappet 13 is guided via a tappet body 15 without rotation in a housing bore 16 of the motor block 3 which extends radially to the axis 5 of the drive shaft.
  • About a form-fitting inserted into a receptacle 17 of the tappet 5 and fixed in position sliding plate 18 of the tappet 13 is supported on the raceway 9 of the eccentric 6. In the operating state causes the rotating eccentric 6 in conjunction with the race 9, an oscillating movement of the tappet 13 and the associated element piston 12 which is guided in a cylinder bore 19 of a shaft portion 20 of the plug-in pump body 2.
  • the element piston 8 defines a pump working space 21 to which a suction valve 22 and a high-pressure valve 23 are assigned.
  • a suction stroke downward movement
  • the suction valve 22 opens, whereby the pump working chamber 21 fuel from the low pressure unit 4 can be supplied.
  • a delivery stroke (upward movement) of the element piston 8 leads to the closure of the suction valve 22 and fuel compression before the fuel is conveyed via a function of a check valve performing high-pressure valve 23 in a further fuel line to a high-pressure accumulator (rail).
  • An eccentricity S between the axis 5 of the drive or pump shaft to the central axis 7 of the eccentric 6 simultaneously determines a maximum stroke of the element piston 12th
  • the restoring force on the tappet 13 triggering plunger spring 14 is supported between the plug-in pump body 2 and a spring plate 24 of the tappet 13 and causes a frictional support of the tappet 13 on the Running ring 9.
  • the plunger spring 14 surrounds the shaft portion 20 of the plug-in pump body 2, wherein a first spring end of the plunger spring 14 is enclosed by a board 25 of the plug-in pump body 2 and the further entering the tappet 13, supported on the spring plate 24 spring end on the outside of the plunger body 15 is enclosed.
  • the eccentric 6 enclosing raceway 9 is supported via a convex, convex contact surface 27 on a correspondingly shaped counter surface, the contact surface 28 of the sliding plate 18 of the tappet 13.
  • a friction-reducing coating on at least one contact surface 27, 28 is additionally suitable.
  • FIG. 2 shows the tappet 13 as a single part in an enlarged view and illustrates more details.
  • the element piston 12 is inserted in a central opening 26 of the spring plate 24 and through an opening 26 cross-end board 35 secured. Since the plunger body 15 are guided in the engine block 3 and the element piston 12 in the shaft portion 20 and thus in separate components, the element piston 12 is preferably performed with a small angular error compensating clearance in the opening 26 of the spring plate 24.
  • a preferably circumferential lubrication 30 introduced circumferentially arranged through holes 31.
  • a lubricant or funded by the high-pressure pump 1 fuel in one of the plunger body 15 and the housing bore 16 radially limited annular gap 32 enter.
  • the lubricant also passes in the direction of the eccentric 6 and applied for lubrication and cooling a contact zone 33 (FIG. Fig. 1 ) between the raceway 9 and the slide plate 18.
  • a plurality of flood bores 34 are introduced in the slide plate 18, which allow a flow of lubricant to selectively lubricate the components of the contact zone 33 and to cool.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)

Description

Die vorliegende Erfindung betrifft eine Hochdruckpumpe einer Kraftstoffeinspritzeinrichtung, die insbesondere für eine Common-Rail-Einspritzeinrichtung einer Brennkraftmaschine eingesetzt werden kann, nach dem Oberbegriff des Anspruchs 1.The present invention relates to a high pressure pump of a fuel injection device, which can be used in particular for a common rail injection device of an internal combustion engine, according to the preamble of claim 1.

Eine solche Hochdruckpumpe ist durch die WO 03/014569 A1 bekannt. Diese Hochdruckpumpe umfasst eine Pumpenwelle, die mit einem Exzenter drehstarr verbunden ist, sowie zumindest ein Pumpenelement, das in einer Gehäusebohrung eines Motorblocks eingesetzt ist. Das Pumpenelement weist einen mit dem Exzenter über einen Tassenstößel antriebsverbundenen Elementkolben auf, der hubbeweglich in einer Zylinderbohrung eines Schaftabschnitts geführt ist, sowie eine den Tassenstößel beaufschlagende Stößelfeder. Der Elementkolben begrenzt einen mit einem Saugventil und einem Hochdruckventil verbundenen Pumpenarbeitsraum. Eine Antriebsverbindung zwischen dem Tassenstößel und dem Exzenter umfasst einen drehbar auf dem Exzenter gelagerten Laufring, an dem der Tassenstößel kraftschlüssig abgestützt ist. Der Tassenstößel schließt antriebsseitig eine Gleitplatte ein, die als Kontaktfläche gemeinsam mit einer Kontaktfläche des den Exzenter umschließenden Laufrings eine Kontaktzone bildet. Eine Schmierung der Kontaktzone zwischen dem Tassenstößel und dem Laufring erfolgt durch das den Tassenstößel und den Laufring umgebendes Medium. Hierdurch ist unter Umständen keine ausreichende Schmierung der Kontaktzone sichergestellt.Such a high-pressure pump is through the WO 03/014569 A1 known. This high-pressure pump comprises a pump shaft which is rotationally rigidly connected to an eccentric, and at least one pump element which is inserted in a housing bore of an engine block. The pump element has an element piston which is drive-connected to the eccentric via a cup tappet and which is guided so as to be movable in a cylinder bore of a shaft section, as well as a tappet spring acting on the tappet. The element piston defines a pump working space connected to a suction valve and a high pressure valve. A drive connection between the bucket tappet and the eccentric comprises a rotatably mounted on the eccentric race on which the bucket tappet is non-positively supported. The bucket tappet includes on the drive side a sliding plate, which forms a contact zone as a contact surface together with a contact surface of the eccentric surrounding race. Lubrication of the contact zone between the bucket tappet and the raceway is effected by the medium surrounding the bucket tappet and the raceway. As a result, under certain circumstances, sufficient lubrication of the contact zone is ensured.

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass die Schmierung der Kontaktzone zwischen dem Tassenstößel und dem Laufring durch die zumindest eine Flutbohrung in der Gleitplatte verbessert ist.The high pressure pump according to the invention with the features of claim 1 has the advantage that the lubrication of the contact zone between the tappet and the race is improved by the at least one flood hole in the slide plate.

Eine bevorzugte Weiterbildung der Erfindung sieht vor, dass die Gleitplatte als separates teil in den Tassenstößel eingesetzt ist. Die vorzugsweise in den Tassenstößel eingepresste und lagefixierte Gleitplatte ist mit einer Kontaktfläche an der zugehörigen Kontaktfläche des den Exzenter umschließenden Laufrings abgestützt, wobei die Kontaktflächen gemeinsam eine Kontaktzone bilden. Vorteilhaft ist die Gleitplatte aus einem an die gegebenen Belastungen und Schmierstoffverhältnisse angepassten Werkstoff hergestellt. Zur Erzielung einer hohen Verschleißfestigkeit bietet es sich beispielsweise an, die Gleitplatte aus Hartmetall oder einem keramischen Werkstoff herzustellen. Der Tassenstößel mit integrierter Gleitplatte zeichnet sich weiterhin aus durch einen vereinfachten und bauteiloptimierten Aufbau. Bedingt durch die Gleitplatte benötigt der Tassenstößel vorteilhaft weder eine lageorientierte Einbaulage noch eine Verdrehsicherung, wodurch sich die Montage vereinfacht. Das erfindungsgemäße vereinfachte und kostenoptimierte Tassenstößelkonzept bietet außerdem gegenüber bekannten Lösungen von Tassenstößeln mit Rollenschuh und integrierter Rolle einen Kostenvorteil.A preferred embodiment of the invention provides that the sliding plate is used as a separate part in the tappets. The preferably pressed into the cup tappet and fixed in position sliding plate is supported with a contact surface on the associated contact surface of the eccentric enclosing race, wherein the contact surfaces together form a contact zone. Advantageously, the sliding plate is made of a material adapted to the given loads and lubricant conditions. To achieve a high wear resistance, it makes sense, for example, to produce the sliding plate made of hard metal or a ceramic material. The tappet with integrated sliding plate is further characterized by a simplified and component-optimized design. Due to the sliding plate, the tappet advantageously requires neither a position-oriented mounting position nor an anti-twist device, which simplifies assembly. The inventive simplified and cost-optimized bucket tappet concept also offers a cost advantage over known solutions of bucket tappets with roller shoe and integrated role.

Zur Reibungsminimierung ist der Laufring über ein Wälzlager oder Gleitlager auf der Exzenterwelle drehbar gelagert. Durch die Verwendung handelsüblicher Wälz- oder Gleitlager kann eine robuste, bewährte und kostengünstige Lagerung des Laufrings auf der Exzenterwelle realisiert werden. Als Wälzlager eignen sich bevorzugt Zylinderrollenlager, da die Lagerung keine axialen Kräfte aufzunehmen hat. Aufgrund des geringen erforderlichen radialen Bauraums können für die Lagerung des Laufrings bevorzugt Nadellager eingesetzt werden.To minimize friction, the race is rotatably mounted on the eccentric shaft via a rolling bearing or sliding bearing. By the use of commercial Wälz- or Plain bearings can be a robust, proven and inexpensive storage of the race on the eccentric shaft can be realized. As roller bearings are preferably cylindrical roller bearings, since the storage has to absorb any axial forces. Due to the small required radial space can preferably be used for the storage of the race needle roller bearings.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass zumindest eine der zueinander gerichteten Kontaktflächen der Gleitplatte sowie des Laufrings leicht ballig oder konvex ausgebildet ist. Diese Maßnahme gleicht vorteilhaft leichte Winkelfehler aus, die bei der Fertigung aufgrund zulässiger Lage- und / oder Formtoleranzen auftreten können. Die konvexe Ausbildung dient außerdem dazu, die Kontaktzone zwischen der Gleitplatte und dem Laufring bis auf einen Linienkontakt zu verkleinern, wodurch sich die Reibung vorteilhaft reduziert.Another particular embodiment of the invention is characterized in that at least one of the mutually facing contact surfaces of the sliding plate and the race is slightly convex or convex. This measure advantageously compensates for slight angle errors that can occur during production due to permissible position and / or shape tolerances. The convexity also serves to reduce the contact area between the slide plate and the raceway to line contact, thereby advantageously reducing friction.

Zur Erzielung einer erhöhten Lebensdauer der Antriebsverbindung ist erfindungsgemäß vorgesehen, zumindest eine Kontaktfläche des Laufrings oder der Gleitplatte mit einem Werkstoff hoher Verschleißfestigkeit zu beschichten. Alternativ oder ergänzend dazu schließt die Erfindung weiterhin eine Beschichtung zumindest einer Kontaktfläche mit einem reibungsmindernden Werkstoff ein.To achieve an increased service life of the drive connection, it is provided according to the invention to coat at least one contact surface of the race or the sliding plate with a material of high wear resistance. Alternatively or additionally, the invention further includes a coating of at least one contact surface with a friction-reducing material.

Gemäß einer weiteren vorteilhaften Ausführungsform ist die als Steckpumpe ausgebildete Hochdruckpumpe als eine Baueinheit mit einem Steckpumpenkörper in einer Gehäusebohrung des Motorblocks eingesetzt. In einem Schaftabschnitt des Steckpumpenkörpers ist eine Zylinderbohrung eingebracht, die zur Führung des Elementkolbens bestimmt ist und die gleichzeitig den Pumpenarbeitsraum bildet. Vorteilhaft bietet die Erfindung die Möglichkeit eine Hochdruckpumpe zu schaffen, bei der das Prinzip einer Steckpumpe mit einer Antriebsverbindung kombiniert ist, die einen auf der Exzenterwelle gelagerten Laufring sowie einen Tassenstößel mit integrierter Gleitplatte aufweist.According to a further advantageous embodiment, the high pressure pump designed as a plug-in pump is used as a structural unit with a plug-in pump body in a housing bore of the engine block. In a shaft portion of the plug-in pump body, a cylinder bore is introduced, which is intended to guide the element piston and at the same time forms the pump working space. Advantageously, the invention offers the possibility to create a high-pressure pump in which the principle of a plug-in pump is combined with a drive connection having a mounted on the eccentric shaft raceway and a bucket tappet with integrated sliding plate.

Der konstruktive Aufbau der Erfindung schließt weiterhin unterschiedliche Lösungen zur Führung des Tassenstößels ein. Bevorzugt ist eine äußere Führung des Tassenstößels, bei der ein Stößelkörper des Tassenstößels über eine Mantelfläche in der Gehäusebohrung des Motorblocks geführt ist. Diese Außenführung des Tassenstößels unterbindet eine Deformation der Führung des Elementkolbens in dem Schaftabschnitt. Alternativ dazu bietet sich an, den Tassenstößel innenseitig an dem Schaftabschnitt des Steckpumpenkörpers zu führen.The structural design of the invention further includes different solutions for guiding the bucket tappet. An outer guide of the tappet is preferred, in which a tappet body of the tappet is guided over a lateral surface in the housing bore of the engine block. This outer guide of the tappet prevents deformation of the guide of the element piston in the shaft portion. Alternatively, it is advisable to guide the tappet inside the shaft portion of the plug-in pump body.

In weiterer Ausgestaltung der Erfindung ist für die als Steckpumpe ausgeführte Hochdruckpumpe außerdem eine bauraumoptimierte Anordnung der Stößelfeder vorgesehen. Dazu ist die Stößelfeder an einem innerhalb des Tassenstößels integrierten Federteller abgestützt, wobei die Stößelfeder über eine größere Länge innerhalb des Stößelkörpers geführt ist. Das gegenseitige Federende der Stößelfeder ist zur Führung von einem Bord des Steckpumpenkörpers umschlossen.In a further embodiment of the invention, a space-optimized arrangement of the plunger spring is also provided for the designed as a plug-pump high-pressure pump. For this purpose, the plunger spring is supported on an integrated inside the cup tappet spring plate, wherein the plunger spring is guided over a greater length within the plunger body. The mutual spring end of the plunger spring is enclosed for guiding by a board of the plug-in pump body.

Zur gezielten und effektiven Schmierung der Führung des Tassenstößels in der Gehäusebohrung ist in einer Mantelfläche des Stößelkörpers zumindest eine bevorzugt umlaufende Schmiernut eingebracht, die über zugehörige Durchtrittsbohrungen mit einem Stößelinnenraum verbunden sind. Diese Maßnahme bewirkt, dass ein Schmierstoff, insbesondere der durch die Hochdruckpumpe geförderte Kraftstoff in den sich zwischen der Gehäusebohrung des Motorblocks und der Mantelfläche des Tassenstößels einstellenden Ringspalt eintritt. Dadurch kann eine optimale, reibungsmindernde Schmierung des Tassenstößels realisiert werden. Weiterhin gelangt der Schmierstoff zur Kühlung und Schmierung in die von dem Laufring und der Gleitplatte definierte Kontaktzone der Antriebsverbindung zwischen dem Exzenter und dem Tassenstößel.For targeted and effective lubrication of the leadership of the tappet in the housing bore at least one preferably circumferential lubrication groove is introduced in a lateral surface of the tappet body, which are connected via associated passage bores with a plunger interior. This measure has the effect that a lubricant, in particular the fuel delivered by the high-pressure pump, enters the annular gap which is established between the housing bore of the engine block and the lateral surface of the cup tappet. As a result, an optimal, friction-reducing lubrication of the bucket tappet can be realized. Furthermore, the lubricant passes for cooling and lubrication in the defined by the race and the sliding plate contact zone of the drive connection between the eccentric and the bucket tappet.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind der Zeichnungsbeschreibung zu entnehmen, in der in den Figuren dargestellte Ausführungsbeispiele der Erfindung näher beschrieben sind.Further advantageous embodiments of the invention are described in the drawings, are described in more detail in the embodiments illustrated in the figures of the invention.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Es zeigen:

Fig. 1
eine Schnittdarstellung einer Hochdruckpumpe mit einer Antriebsverbindung zwischen Exzenter und Tassenstößel;
Fig. 2
als Einzelteilzeichnüng den erfindungsgemäßen Tassenstößel gemäß Fig. 1.
Show it:
Fig. 1
a sectional view of a high-pressure pump with a drive connection between the eccentric and bucket tappets;
Fig. 2
as Einzelteilzeichnüng the bucket tappet according to the invention Fig. 1 ,

In Figur 1 ist eine Hochdruckpumpe 1 für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt, die bevorzugt für ein Common-Rail-Einspritzsystem einer Diesel-Brennkraftmaschine bestimmt ist. Durch die Hochdruckpumpe 1 wird Kraftstoff unter Hochdruck in einen in Fig. 1 nicht abgebildeten Speicher (Rail) gefördert, aus dem der Kraftstoff über Kraftstoffinjektoren gezielt in zugeordnete Brennräume einer Brennkraftmaschine eingespritzt wird. Die Hochdruckpumpe 1 bildet eine Radialkolbenpumpe, die als Steckpumpe mit einem Steckpumpenkörper 2 in einem Motorblock 3 oder Gehäuse eingesetzt ist. An den Steckpumpenkörper 2 schließt sich eine auch als Zylinderkopf zu bezeichnende Niederdruckeinheit 4 an. Eine im Motorblock 3 drehbare Antriebswelle mit einer Achse 5 ist mit einem Exzenter 6 verbunden, dessen Mittelachse 7 eine Exzentrizität S gegenüber der Achse 5 aufweist. Die Antriebswelle kann eine Welle der Brennkraftmaschine sein, beispielsweise deren Nockenwelle oder eine Ausgleichswelle.In FIG. 1 a high pressure pump 1 is shown for a fuel injection device of an internal combustion engine, which is preferably intended for a common rail injection system of a diesel internal combustion engine. By the high-pressure pump 1, fuel is at high pressure in an in Fig. 1 not shown storage (rail) promoted, from which the fuel is injected via fuel injectors specifically into associated combustion chambers of an internal combustion engine. The high-pressure pump 1 forms a radial piston pump, which is used as a plug-in pump with a plug-in pump body 2 in an engine block 3 or housing. The plug-in pump body 2 is followed by a low-pressure unit 4, which can also be referred to as a cylinder head. A rotatable in the engine block 3 drive shaft with an axis 5 is connected to an eccentric 6, whose central axis 7 has an eccentricity S with respect to the axis 5. The drive shaft may be a shaft of the internal combustion engine, for example, the camshaft or a balancer shaft.

Der Exzenter 6 ist von einem Laufring 9 umschlossen, der über ein Wälzlager 10, insbesondere ein Nadellager, mit zylindrischen Wälzkörpern 11 drehbar auf dem Exzenter 6 gelagert ist und der mit einem Tassenstößel 13 eines Pumpenelements 8 antriebsverbunden ist. Das Pumpenelement 8 umfasst den Tassenstößel 13, in dem ein Elementkolben 12 oder Pumpenkolben gehalten ist sowie eine Stößelfeder 14. Über einen Stößelkörper 15 ist der Tassenstößel 13 ohne eine Verdrehsicherung in einer radial zur Achse 5 der Antriebswelle verlaufenden Gehäusebohrung 16 des Motorblocks 3 geführt. Über eine formschlüssig in einer Aufnahme 17 des Tassenstößels 5 eingesetzten und lagefixierten Gleitplatte 18 ist der Tassenstößel 13 an dem Laufring 9 des Exzenters 6 abgestützt. Im Betriebszustand bewirkt der rotierende Exzenter 6 in Verbindung mit dem Laufring 9 eine oszillierende Bewegung des Tassenstößels 13 und des damit verbundenen Elementkolbens 12, der in einer Zylinderbohrung 19 eines Schaftabschnitts 20 des Steckpumpenkörpers 2 geführt ist.The eccentric 6 is surrounded by a race 9, which is rotatably mounted on the eccentric 6 via a rolling bearing 10, in particular a needle bearing, with cylindrical rolling elements 11 and which is drivingly connected to a tappet 13 of a pump element 8. The pump element 8 comprises the cup tappet 13 in which an element piston 12 or pump piston is held and a tappet spring 14. The tappet 13 is guided via a tappet body 15 without rotation in a housing bore 16 of the motor block 3 which extends radially to the axis 5 of the drive shaft. About a form-fitting inserted into a receptacle 17 of the tappet 5 and fixed in position sliding plate 18 of the tappet 13 is supported on the raceway 9 of the eccentric 6. In the operating state causes the rotating eccentric 6 in conjunction with the race 9, an oscillating movement of the tappet 13 and the associated element piston 12 which is guided in a cylinder bore 19 of a shaft portion 20 of the plug-in pump body 2.

Der Elementkolben 8 begrenzt einen Pumpenarbeitsraum 21, dem ein Saugventil 22 sowie ein Hochdruckventil 23 zugeordnet ist. Bei einem Saughub (Abwärtsbewegung) des Elementkolbens 8 öffnet sich das Saugventil 22, wodurch dem Pumpenarbeitsraum 21 Kraftstoff aus der Niederdruckeinheit 4 zugeführt werden kann. Ein Förderhub (Aufwärtsbewegung) des Elementkolbens 8 führt zur Schließung des Saugventils 22 und einer Kraftstoffkomprimierung, bevor der Kraftstoff über ein die Funktion eines Rückschlagventils ausübendes Hochdruckventil 23 in eine weiterführende Kraftstoffleitung zu einem Hochdruckspeicher (Rail) gefördert wird. Eine Exzentrizität S zwischen der Achse 5 der Antriebs- oder Pumpenwelle zu der Mittelachse 7 des Exzenters 6 bestimmt gleichzeitig einen maximalen Hub des Elementkolbens 12.The element piston 8 defines a pump working space 21 to which a suction valve 22 and a high-pressure valve 23 are assigned. During a suction stroke (downward movement) of the element piston 8, the suction valve 22 opens, whereby the pump working chamber 21 fuel from the low pressure unit 4 can be supplied. A delivery stroke (upward movement) of the element piston 8 leads to the closure of the suction valve 22 and fuel compression before the fuel is conveyed via a function of a check valve performing high-pressure valve 23 in a further fuel line to a high-pressure accumulator (rail). An eccentricity S between the axis 5 of the drive or pump shaft to the central axis 7 of the eccentric 6 simultaneously determines a maximum stroke of the element piston 12th

Die eine Rückstellkraft auf den Tassenstößel 13 auslösende Stößelfeder 14 ist zwischen dem Steckpumpenkörper 2 und einem Federteller 24 des Tassenstößels 13 abgestützt und bewirkt eine kraftschlüssige Abstützung des Tassenstößels 13 an dem Laufring 9. Dabei umschließt die Stößelfeder 14 den Schaftabschnitt 20 des Steckpumpenkörpers 2, wobei ein erstes Federende der Stößelfeder 14 von einem Bord 25 des Steckpumpenkörpers 2 umschlossen ist und das weitere in den Tassenstößel 13 eintretende, an dem Federteller 24 abgestützte Federende außenseitig von dem Stößelkörper 15 umschlossen wird.The restoring force on the tappet 13 triggering plunger spring 14 is supported between the plug-in pump body 2 and a spring plate 24 of the tappet 13 and causes a frictional support of the tappet 13 on the Running ring 9. In this case, the plunger spring 14 surrounds the shaft portion 20 of the plug-in pump body 2, wherein a first spring end of the plunger spring 14 is enclosed by a board 25 of the plug-in pump body 2 and the further entering the tappet 13, supported on the spring plate 24 spring end on the outside of the plunger body 15 is enclosed.

Zum Ausgleich von kleinen Winkelfehlern, beispielsweise bedingt durch Fertigungstoleranzen einzelner Bauteile, ist der den Exzenter 6 umschließende Laufring 9 über eine ballige, konvexe Kontaktfläche 27 an einer entsprechend gestalteten Gegenfläche, der Kontaktfläche 28 der Gleitplatte 18 des Tassenstößels 13 abgestützt. Zur Erzielung optimaler Reibungsverhältnisse bietet sich ergänzend dazu eine reibungsmindernde Beschichtung zumindest einer Kontaktfläche 27, 28 an.To compensate for small angular errors, for example due to manufacturing tolerances of individual components, the eccentric 6 enclosing raceway 9 is supported via a convex, convex contact surface 27 on a correspondingly shaped counter surface, the contact surface 28 of the sliding plate 18 of the tappet 13. To achieve optimum friction conditions, a friction-reducing coating on at least one contact surface 27, 28 is additionally suitable.

Die Figur 2 zeigt den Tassenstößel 13 als Einzelteil in einer vergrößerten Darstellung und verdeutlicht weitere Details. Der in dem Tassenstößel 13 eingesetzte, zur Abstützung der Stößelfeder 14 bestimmte Federteller 24 bewirkt gleichzeitig eine Halterung des Elementkolbens 12 an dem Tassenstößel 13. Dazu ist der Elementkolben 12 in einer zentralen Öffnung 26 des Federtellers 24 eingesetzt und durch einen die Öffnung 26 übergreifenden endseitigen Bord 35 gesichert. Da der Stößelkörper 15 im Motorblock 3 und der Elementkolben 12 im Schaftabschnitt 20 und damit in getrennten Bauteilen geführt sind, ist der Elementkolben 12 bevorzugt mit einer kleine Winkelfehler ausgleichenden Spielpassung in der Öffnung 26 des Federtellers 24 geführt. Als Maßnahme um die Reibung des Stößelkörpers 15 in der Gehäusebohrung 16 des Motorblocks 3 zu verbessern ist in einer Mantelfläche 29 des Stößelkörpers 15 eine bevorzugt umlaufende Schmiernut 30 eingebracht mit umfangsverteilt angeordneten Durchtrittsbohrungen 31. Damit kann gezielt ein Schmierstoff oder der von der Hochdruckpumpe 1 geförderte Kraftstoff in einen von dem Stößelkörper 15 und der Gehäusebohrung 16 radial begrenzten Ringspalt 32 (Fig. 1) eintreten. Von dort gelangt der Schmierstoff auch in Richtung des Exzenters 6 und beaufschlagt zur Schmierung und Kühlung eine Kontaktzone 33 (Fig. 1) zwischen dem Laufring 9 und der Gleitplatte 18. Zusätzlich sind in der Gleitplatte 18 mehrere Flutbohrungen 34 eingebracht, die ein Durchströmen von Schmierstoff ermöglichen, um gezielt die Bauteile der Kontaktzone 33 zu schmieren und zu kühlen.The FIG. 2 shows the tappet 13 as a single part in an enlarged view and illustrates more details. The inserted in the tappet 13, for supporting the plunger spring 14 certain spring plate 24 simultaneously causes a support of the element piston 12 on the tappet 13. For this, the element piston 12 is inserted in a central opening 26 of the spring plate 24 and through an opening 26 cross-end board 35 secured. Since the plunger body 15 are guided in the engine block 3 and the element piston 12 in the shaft portion 20 and thus in separate components, the element piston 12 is preferably performed with a small angular error compensating clearance in the opening 26 of the spring plate 24. As a measure to improve the friction of the plunger body 15 in the housing bore 16 of the engine block 3 is in a lateral surface 29 of the plunger body 15, a preferably circumferential lubrication 30 introduced circumferentially arranged through holes 31. Thus targeted a lubricant or funded by the high-pressure pump 1 fuel in one of the plunger body 15 and the housing bore 16 radially limited annular gap 32 (FIG. Fig. 1 ) enter. From there, the lubricant also passes in the direction of the eccentric 6 and applied for lubrication and cooling a contact zone 33 (FIG. Fig. 1 ) between the raceway 9 and the slide plate 18. In addition, a plurality of flood bores 34 are introduced in the slide plate 18, which allow a flow of lubricant to selectively lubricate the components of the contact zone 33 and to cool.

Claims (10)

  1. High-pressure pump (1) of a fuel injection device, in particular for a common-rail injection device of an internal combustion engine, having a pump shaft which is connected rotationally conjointly to an eccentric (6), and having at least one pump element (8) which is inserted into a housing bore (16) of an engine block (3) and which comprises an element piston (12), said element piston being connected in terms of drive to the eccentric (6) by way of a bucket tappet (13) and being guided, such that it can perform stroke movements, in a cylinder bore (19) of a shank section (20), and which comprises a tappet spring (14) which acts on the bucket tappet (13), wherein the element piston (12) delimits a pump working chamber (21) which is connected to a suction valve (22) and to a high-pressure valve (23), wherein a drive connection between the bucket tappet (13) and the eccentric (6) comprises a running ring (9) mounted rotatably on the eccentric (6), on which running ring the bucket tappet (13) is supported in non-positively locking fashion, wherein the bucket tappet (13) comprises, at the drive side, a slide plate (18) which, as contact surface (28), forms a contact zone (33) together with a contact surface (27) of the running ring (9) that surrounds the eccentric (6), characterized in that, for the supply of lubricant to the contact zone (33) between the slide plate (18) and the running ring (9), at least one flood bore (34) is formed in the slide plate (18).
  2. High-pressure pump according to Claim 1, characterized in that the slide plate (18) is inserted, as a separate part, into the bucket tappet (13).
  3. High-pressure pump according to Claim 1, characterized in that the running ring (9) is mounted rotatably on the eccentric (6) by way of a rolling bearing (10) or plain bearing.
  4. High-pressure pump according to Claim 3, characterized in that, as rolling bearing (10), a cylindrical-roller bearing or needle-roller bearing is provided for the mounting of the running ring (9).
  5. High-pressure pump according to Claim 1 or 2, characterized in that the running ring (9) and/or the slide plate (18) have/has a contact surface (27, 28) of spherical or convex form.
  6. High-pressure pump according to Claim 1 or 2, characterized in that the contact surface (27) of the running ring (9) and/or the contact surface (28) of the slide plate (18) have/has a friction-reducing coating.
  7. High-pressure pump according to Claim 1, characterized in that the high-pressure pump (1), which is in the form of a unit pump, is inserted by way of a unit pump body (2) into the housing bore (16) of the engine block (3), and the cylinder bore (19), which is designed for guiding the element piston (12) and for forming a pump working chamber (8), is formed in a shank section (20) of the unit pump body (2).
  8. High-pressure pump according to Claim 1, characterized in that the bucket tappet (13) is guided at the outside, by way of a tappet body (15), in the housing bore (16) of the engine block (3) or at the inside on the unit pump shank (20) of the unit pump body (2).
  9. High-pressure pump according to Claim 1, characterized in that the tappet spring (14) is supported by way of one spring end on a disk spring (24) which is integrated into the bucket tappet (13).
  10. High-pressure pump according to Claim 1, characterized in that, for the supply of lubricant to a guide of the bucket tappet (13), there is provided in the tappet body (15) at least one lubrication groove (30) which is connected via associated passage bores (31) to an interior space of the bucket tappet (13).
EP11754404.9A 2010-10-15 2011-09-07 High-pressure pump for a fuel injection device Not-in-force EP2627903B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010042484 DE102010042484A1 (en) 2010-10-15 2010-10-15 High pressure pump for a fuel injection device
PCT/EP2011/065472 WO2012048961A1 (en) 2010-10-15 2011-09-07 High-pressure pump for a fuel injection device

Publications (2)

Publication Number Publication Date
EP2627903A1 EP2627903A1 (en) 2013-08-21
EP2627903B1 true EP2627903B1 (en) 2016-07-13

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ID=44583058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11754404.9A Not-in-force EP2627903B1 (en) 2010-10-15 2011-09-07 High-pressure pump for a fuel injection device

Country Status (4)

Country Link
EP (1) EP2627903B1 (en)
CN (1) CN103154512B (en)
DE (1) DE102010042484A1 (en)
WO (1) WO2012048961A1 (en)

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Publication number Priority date Publication date Assignee Title
CN107110092B (en) * 2014-12-24 2020-05-05 罗伯特·博世有限公司 Pump unit for feeding fuel, preferably diesel fuel, to an internal combustion engine
DE102015111025A1 (en) 2015-07-08 2017-01-12 Volkswagen Ag Self lubricated high pressure pump
DE102016203768B4 (en) * 2015-11-12 2017-10-26 Robert Bosch Gmbh Pump, in particular high-pressure pump of a fuel injection system, with a mounting assembly of plunger assembly and pump cylinder head, in particular by a latching connection between spring plate and plunger body
CN107939628B (en) * 2017-12-26 2023-07-18 浙江三浪润滑科技有限公司 Multi-head radial plunger pump and application method thereof
DE102018120777A1 (en) * 2018-08-24 2020-02-27 Volkswagen Aktiengesellschaft High-pressure pump comprising pressure lubrication

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Publication number Priority date Publication date Assignee Title
DE4315826C5 (en) * 1993-05-12 2012-04-05 Continental Teves Ag & Co. Ohg Motor-pump assembly
JPH09303252A (en) * 1996-05-13 1997-11-25 Nissan Motor Co Ltd Hydraulic pump device
IT1289796B1 (en) * 1996-12-23 1998-10-16 Elasis Sistema Ricerca Fiat IMPROVEMENTS TO A PUMP DEVICE FOR SUPPLYING FUEL FROM A TANK TO AN INTERNAL COMBUSTION ENGINE.
DE19907311A1 (en) 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulic pump unit
KR20040035730A (en) * 2001-08-08 2004-04-29 씨알티 커먼 레일 테크놀로지스 아게 High pressure feed pump
DE10157076A1 (en) 2001-11-21 2003-05-28 Bosch Gmbh Robert Tappet with piston has axial and/or radial roller guide adjustable on tappet by means of roller shoe fixed to tappet
DE10158768B4 (en) * 2001-11-29 2012-10-25 Schaeffler Technologies AG & Co. KG Radial piston pump
WO2006037676A1 (en) * 2004-10-06 2006-04-13 Siemens Aktiengesellschaft Radial piston pump comprising a roller tappet
DE102006041673A1 (en) * 2006-02-20 2007-08-23 Robert Bosch Gmbh High pressure pump especially for fuel injection in IC engine has the cam follower supported axially by hardened low wear surfaces
DE102006043187B3 (en) * 2006-09-14 2008-04-03 Siemens Ag Fluid pump, in particular high-pressure fuel pump for injection systems of internal combustion engines
DE102006060680A1 (en) * 2006-12-21 2008-06-26 Schaeffler Kg Rolling bearings for a radial piston pump

Also Published As

Publication number Publication date
CN103154512B (en) 2017-03-01
WO2012048961A1 (en) 2012-04-19
EP2627903A1 (en) 2013-08-21
CN103154512A (en) 2013-06-12
DE102010042484A1 (en) 2012-04-19

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