EP3014107B1 - Pumping device, in particular high pressure fuel pumping device for a fuel injection device - Google Patents

Pumping device, in particular high pressure fuel pumping device for a fuel injection device Download PDF

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Publication number
EP3014107B1
EP3014107B1 EP14720621.3A EP14720621A EP3014107B1 EP 3014107 B1 EP3014107 B1 EP 3014107B1 EP 14720621 A EP14720621 A EP 14720621A EP 3014107 B1 EP3014107 B1 EP 3014107B1
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EP
European Patent Office
Prior art keywords
drive shaft
cam
eccentric
outer contour
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.)
Active
Application number
EP14720621.3A
Other languages
German (de)
French (fr)
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EP3014107A1 (en
Inventor
Andreas Dutt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP3014107A1 publication Critical patent/EP3014107A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails

Definitions

  • the invention relates to a pump device, in particular high-pressure fuel pump device for a fuel injection device, according to the preamble of claim 1.
  • Such a pump device in the form of a high-pressure fuel pump device is characterized by the DE 10 2006 028 851 A1 known.
  • This pumping device has at least one pump element, which is driven via a plunger by a drive shaft in a lifting movement.
  • the at least one pump element in this case has at least one pump piston.
  • the drive shaft has at least one cam or eccentric on which the plunger is at least indirectly supported.
  • the drive shaft is rotatably mounted via at least one bearing, wherein the at least one bearing point is supplied lubricating medium.
  • Lubricating oil for example, is provided as lubricating medium, which is supplied under pressure to the at least one bearing point.
  • the drive shaft has an outer contour which increases in diameter from the at least one bearing point to the at least one cam or eccentric, which ends in the region of the plunger in the direction of a rotation axis of the drive shaft .
  • a roller is rotatably mounted in the plunger, via which the plunger is supported on the cam or eccentric. The outer contour of the drive shaft ends in the direction of the axis of rotation of the drive shaft in the region of a bearing of the roller in the plunger.
  • the pumping device according to the invention with the features according to claim 1 has the advantage that directed by the outer contour of the drive shaft from the bearing outlet lubricant is directed to the plunger and thus its lubrication and the lubrication of its support is ensured. For this purpose, no additional components are required. Furthermore, the inventive design of the pumping device according to claim 1 has the advantage that lubrication of the bearing of the roller in the plunger is ensured in a simple manner, since the outer contour of the drive shaft in the direction of the axis of rotation of the drive shaft ends in the region of a bearing of the roller in the plunger. Furthermore, the embodiment according to claim 1 allows a directed introduction of lubricating medium between the roller and the plunger.
  • the embodiment according to claim 3 allows a directed outflow of the lubricating medium from the drive shaft to the plunger. Due to the design according to claim 7, a lubrication of the storage of the roller and the bolt is ensured in the plunger in a simple manner.
  • FIGS. 1 to 3 is a simplified representation of a fragmentary pumping device shown, which is preferably a high-pressure fuel pumping device for a fuel injector of an internal combustion engine.
  • the pumping device has at least one pump element 10, which in turn has a pump piston 12 which is driven at least indirectly by a drive shaft 14 in a lifting movement.
  • the drive shaft 14 has one or more cams 16 or eccentric, via which the rotational movement of the drive shaft 14 is converted into the lifting movement of the pump piston 12.
  • the pump piston 12 is supported via a plunger 18 on the cam 16 or eccentric of the drive shaft 14.
  • the pump element 10 has a housing 20, in which in a cylinder bore 22 of the pump piston 12 is tightly guided, wherein the housing part 20 is hereinafter referred to as the cylinder head. With its end facing away from the drive shaft 14, the pump piston 12 in the cylinder bore 22 defines a pump working space 24.
  • the pump working space 24 has an inlet valve 26, which is an inlet check valve opening into the pump working space 24, with an inlet 28 via which the Pump work chamber 24 is filled with the radially inward to the drive means 14 directed suction stroke of the pump piston 12 with fuel.
  • the pump working chamber 24 also has an outlet valve 30, which is for example an outlet check valve opening out of the pump working chamber 24, a connection to a drain 32, which can lead to a high-pressure accumulator 34 and over the radially outwardly from the drive means 14 directed away Delivery stroke of the pump piston 12 fuel is displaced from the pump working chamber 24.
  • an outlet valve 30 is for example an outlet check valve opening out of the pump working chamber 24, a connection to a drain 32, which can lead to a high-pressure accumulator 34 and over the radially outwardly from the drive means 14 directed away Delivery stroke of the pump piston 12 fuel is displaced from the pump working chamber 24.
  • the plunger 18 is designed as a roller tappet and has a plunger body 40, which is formed as a hollow cylinder. Within the plunger body 40, a bottom 42 is provided, on whose side facing away from the drive shaft 14, the pump piston 12 is supported at least indirectly with the piston foot. Surrounding the pump piston 12, a spring 44 is arranged in the plunger body 40, which is, for example, a helical compression spring, and on the one hand at the bottom 42 and on the other hand supported on the cylinder head 20. By the spring 44 of the pump piston 12 and the plunger body 40 to the drive shaft 14 are acted upon.
  • a roller 46 is rotatably mounted, wherein the axis of rotation 47 of the roller 46 extends at least approximately parallel to the axis of rotation 15 of the drive shaft 14.
  • the roller 46 is arranged in the tappet body 40 on the side facing away from the pump piston 12 side of the bottom 42.
  • the roller 46 is mounted on a pin 48 inserted into the plunger body 40, wherein between the roller 46 and the pin 48, a plain bearing bushing 50 may be arranged.
  • the bolt 48 is received in its end in two coaxial with each other in respect to the axis of rotation 47 of the roller 46 opposite walls 52 of the plunger body 40 provided holes 54.
  • the roller 46 may also be as in FIG FIG. 2 shown in a concave recess 56 of the plunger body 40 or a support member 57 inserted into the plunger body 40 may be rotatably supported via its outer jacket, in which case the bolt 48 is omitted.
  • the column 58 starting from the bores 54 to the drive shaft 14 toward increase. This can be achieved by increasing the distance between the mutually facing inner sides 53 of the walls 52 of the tappet body 40, starting from the bores 54 to the drive shaft 14.
  • the inner sides 53 of the walls 52 of the plunger body 40 may be, for example, beveled at least approximately conically. Alternatively, the inner sides 53 of the walls 52 of the plunger body 40 may also be curved.
  • the inner sides 53 of the walls 52 of the plunger body 40 extend approximately radially to the axis of rotation 47 of the roller 46 and the inner sides 53 facing end faces of the roller 46 are chamfered such that the column 58 to the drive shaft 14 increase ,
  • the drive shaft 14 is rotatably supported by at least one bearing point 60 in a housing 62, wherein the housing 62 may be a housing of the pump device or a housing of the internal combustion engine.
  • the drive shaft 14 is rotatably supported by two in the direction of its axis of rotation 15 to each other spaced bearings 60, wherein the bearing points 60 are arranged on opposite sides of the cam 16 or eccentric.
  • the bearings 60 are preferably designed as plain bearings and these may each comprise a bearing bush 64.
  • the bearings 60 is each as in the FIGS. 1 and 2 indicated by arrows liquid lubricant supplied, for example, lubricating oil from the lubricating oil circuit of the internal combustion engine.
  • the lubricating medium is preferably supplied to the bearings 60 under elevated pressure so that it is pressed through the bearings 60. From the bearings 60 lubricant enters the direction of the axis of rotation 15 of the drive shaft 14 to the cam 16 or eccentric out.
  • the drive shaft 14 between at least one bearing point 60 and the cam 16 or eccentric has a shaped outer contour 66, that from the bearing 60 leaking lubricating medium is directed to the plunger 18 to ensure the lubrication of the plunger 18 or improve ,
  • the outer contour 66 is designed in such a way that the diameter of the outer contour 66 increases away from the bearing point 60 and towards the cam 16 or eccentric.
  • an outer contour 66 may be provided between the cam 16 or eccentric and each bearing 60, wherein both outer contours 66 are arranged and formed in mirror image to each other.
  • the drive shaft 14 is shown with the outer contour 66 according to a first embodiment.
  • the outer contour 66 is at least approximately conical, so that its diameter increases linearly from the bearing 60 to the cam 16 or eccentric.
  • the outer contour 66 closes in the direction of the axis of rotation 15 of the drive shaft 14 seen directly or at a small distance to the bearing point 60 at.
  • the drive shaft 14, viewed in the direction of its axis of rotation 15 starting from the bearing point 60 is initially formed with a constant diameter starting from the cam 16 or eccentric and the outer contour 66 adjoins it.
  • the transition to the drive shaft 14 to the outer contour 66 may be formed in a kink or rounded.
  • a portion 68 of the drive shaft 14 is provided with a reduced diameter between the end facing the bearing 60 of the cam 16 or eccentric and the bearing 60 remote from the outer contour 66, so that the outer contour 66 to the cam 16 or eccentric out in an edge 70th ends.
  • the section 68 forms a puncture on the drive shaft 14 between the cam 16 or eccentric and the edge 70 of the outer contour 66.
  • the edge 70 is arranged in the region of the gap 58 between the roller 46 and the wall 52 of the tappet body 40.
  • the edge 70 is arranged in the region of the gap 58 between the roller 46 and the wall 52 of the tappet body 40.
  • the lubrication in the plunger 18 is improved or ensured, ie the bearing of the roller 46 on the pin 48 or in the recess 56 of the plunger body 40 or the support member 57 and / or the axial bearing of the roller 46 in the direction of its axis of rotation 47 in the plunger body 40th and / or the mounting of the bolt 48 in the bores 54 of the plunger body 40th
  • the drive shaft 14 is shown with the outer contour 66 according to a second embodiment, in which the outer contour 66 is concave, so that the diameter of the cam 16 or eccentric towards non-linearly increases but increases closer to the cam 16 or eccentric.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Pumpvorrichtung, insbesondere Kraftstoffhochdruckpumpvorrichtung für eine Kraftstoffeinspritzeinrichtung, nach der Gattung des Anspruchs 1.The invention relates to a pump device, in particular high-pressure fuel pump device for a fuel injection device, according to the preamble of claim 1.

Eine solche Pumpvorrichtung in Form einer Kraftstoffhochdruckpumpvorrichtung ist durch die DE 10 2006 028 851 A1 bekannt. Diese Pumpvorrichtung weist wenigstens ein Pumpenelement auf, das über einen Stößel durch eine Antriebswelle in einer Hubbewegung angetrieben wird. Das wenigstens eine Pumpenelement weist hierbei wenigstens einen Pumpenkolben auf. Die Antriebswelle weist dabei wenigstens einen Nocken oder Exzenter auf, an dem sich der Stößel zumindest mittelbar abstützt. Die Antriebswelle ist über wenigstens eine Lagerstelle drehbar gelagert, wobei der wenigstens einen Lagerstelle Schmiermedium zugeführt wird. Als Schmiermedium ist beispielsweise Schmieröl vorgesehen, das unter Druck der wenigstens einen Lagerstelle zugeführt wird. Es ist auch anzunehmen, dass das Schmiermedium aus der einen oder anderen Lagerstelle zum Nocken hin austritt und entlang der Antriebswelle zum Nocken hin fließt. Des Weiteren weist die Antriebswelle zwischen der wenigstens einen Lagerstelle und dem wenigstens einen Nocken oder Exzenter eine sich im Durchmesser von der wenigstens einen Lagerstelle zum wenigstens einen Nocken oder Exzenter hin vergrößernde Außenkontur auf, die in Richtung einer Drehachse der Antriebswelle gesehen im Bereich des Stößels endet. Zudem ist im Stößel eine Rolle drehbar gelagert, über die sich der Stößel an dem Nocken oder Exzenter abstützt. Die Außenkontur der Antriebswelle endet in Richtung der Drehachse der Antriebswelle gesehen im Bereich einer Lagerung der Rolle im Stößel.Such a pump device in the form of a high-pressure fuel pump device is characterized by the DE 10 2006 028 851 A1 known. This pumping device has at least one pump element, which is driven via a plunger by a drive shaft in a lifting movement. The at least one pump element in this case has at least one pump piston. The drive shaft has at least one cam or eccentric on which the plunger is at least indirectly supported. The drive shaft is rotatably mounted via at least one bearing, wherein the at least one bearing point is supplied lubricating medium. Lubricating oil, for example, is provided as lubricating medium, which is supplied under pressure to the at least one bearing point. It is also to be assumed that the lubricant escapes from one or the other bearing point towards the cam and flows along the drive shaft towards the cam. Furthermore, between the at least one bearing point and the at least one cam or eccentric, the drive shaft has an outer contour which increases in diameter from the at least one bearing point to the at least one cam or eccentric, which ends in the region of the plunger in the direction of a rotation axis of the drive shaft , In addition, a roller is rotatably mounted in the plunger, via which the plunger is supported on the cam or eccentric. The outer contour of the drive shaft ends in the direction of the axis of rotation of the drive shaft in the region of a bearing of the roller in the plunger.

Für den Stößel sowie dessen Abstützung an der Antriebswelle ist ebenfalls eine Schmierung erforderlich, die bei der bekannten Pumpvorrichtung durch infolge der Drehbewegung der Antriebswelle aufgewirbeltes Schmiermedium oder Schmierölnebel erfolgt. Hierbei ist es schwierig eine ausreichende Schmierung des Stößels und dessen Abstützung sicherzustellen, so dass es zu Verschleiß kommen kann.For the plunger and its support on the drive shaft lubrication is also required, which takes place in the known pumping device by fluidized by the rotational movement of the drive shaft lubricant or lubricating oil mist. Here it is difficult to ensure adequate lubrication of the plunger and its support, so that it can cause wear.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Pumpvorrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch die Außenkontur der Antriebswelle aus der Lagerstelle austretendes Schmiermedium gezielt zum Stößel geleitet wird und somit dessen Schmierung sowie die Schmierung von dessen Abstützung sichergestellt ist. Hierzu sind keine zusätzlichen Bauteile erforderlich. Weiterhin bietet die erfindungsgemäße Ausgestaltung der Pumpvorrichtung nach Anspruch 1 den Vorteil, dass auf einfache Weise eine Schmierung der Lagerung der Rolle im Stößel sichergestellt ist, da die Außenkontur der Antriebswelle in Richtung der Drehachse der Antriebswelle gesehen im Bereich einer Lagerung der Rolle im Stößel endet. Des Weiteren ermöglicht die Ausbildung gemäß Anspruch 1 eine gerichtete Einbringung von Schmiermedium zwischen die Rolle und den Stößel.The pumping device according to the invention with the features according to claim 1 has the advantage that directed by the outer contour of the drive shaft from the bearing outlet lubricant is directed to the plunger and thus its lubrication and the lubrication of its support is ensured. For this purpose, no additional components are required. Furthermore, the inventive design of the pumping device according to claim 1 has the advantage that lubrication of the bearing of the roller in the plunger is ensured in a simple manner, since the outer contour of the drive shaft in the direction of the axis of rotation of the drive shaft ends in the region of a bearing of the roller in the plunger. Furthermore, the embodiment according to claim 1 allows a directed introduction of lubricating medium between the roller and the plunger.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Pumpvorrichtung angegeben. Die Ausbildung gemäß Anspruch 3 ermöglicht einen gerichteten Abfluss des Schmiermediums von der Antriebswelle zum Stößel hin. Durch die Ausbildung gemäß Anspruch 7 ist auf einfache Weise eine Schmierung der Lagerung der Rolle sowie des Bolzens im Stößel sichergestellt. Durch die Ausbildung gemäß Anspruch 8 oder 9 wird die Einbringung von Schmiermedium zwischen die Rolle und den Stößel weiter verbessert.In the dependent claims advantageous refinements and developments of the pump device according to the invention are given. The embodiment according to claim 3 allows a directed outflow of the lubricating medium from the drive shaft to the plunger. Due to the design according to claim 7, a lubrication of the storage of the roller and the bolt is ensured in the plunger in a simple manner. The embodiment according to claim 8 or 9, the introduction of lubricating medium between the roller and the plunger is further improved.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In den Figuren 1 bis 3 ist in vereinfachter Darstellung ausschnittsweise eine Pumpvorrichtung gezeigt, die vorzugsweise eine Kraftstoffhochdruckpumpvorrichtung für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine ist. Die Pumpvorrichtung weist wenigstens ein Pumpenelement 10 auf, das wiederum einen Pumpenkolben 12 aufweist, der zumindest mittelbar durch eine Antriebswelle 14 in einer Hubbewegung angetrieben wird. Die Antriebswelle 14 weist einen oder mehrere Nocken 16 oder Exzenter auf, über den die Drehbewegung der Antriebswelle 14 in die Hubbewegung des Pumpenkolbens 12 umgesetzt wird. Der Pumpenkolben 12 stützt sich über einen Stößel 18 am Nocken 16 oder Exzenter der Antriebswelle 14 ab.In the FIGS. 1 to 3 is a simplified representation of a fragmentary pumping device shown, which is preferably a high-pressure fuel pumping device for a fuel injector of an internal combustion engine. The pumping device has at least one pump element 10, which in turn has a pump piston 12 which is driven at least indirectly by a drive shaft 14 in a lifting movement. The drive shaft 14 has one or more cams 16 or eccentric, via which the rotational movement of the drive shaft 14 is converted into the lifting movement of the pump piston 12. The pump piston 12 is supported via a plunger 18 on the cam 16 or eccentric of the drive shaft 14.

Das Pumpenelement 10 weist ein Gehäuse 20 auf, in dem in einer Zylinderbohrung 22 der Pumpenkolben 12 dicht geführt ist, wobei das Gehäuseteil 20 nachfolgend als Zylinderkopf bezeichnet wird. Mit seinem der Antriebswelle 14 abgewandten Ende begrenzt der Pumpenkolben 12 in der Zylinderbohrung 22 einen Pumpenarbeitsraum 24. Der Pumpenarbeitsraum 24 weist über ein Einlassventil 26, das ein in den Pumpenarbeitsraum 24 hinein öffnendes Einlassrückschlagventil ist, eine Verbindung mit einem Zulauf 28 auf, über den der Pumpenarbeitsraum 24 beim radial nach innen zur Antriebseinrichtung 14 gerichteten Saughub des Pumpenkolbens 12 mit Kraftstoff befüllt wird. Der Pumpenarbeitsraum 24 weist außerdem über ein Auslassventil 30, das beispielsweise ein aus dem Pumpenarbeitsraum 24 heraus öffnendes Auslassrückschlagventil ist, eine Verbindung mit einem Ablauf 32 auf, der zu einem Hochdruckspeicher 34 führen kann und über den beim radial nach außen von der Antriebseinrichtung 14 weg gerichteten Förderhub des Pumpenkolbens 12 Kraftstoff aus dem Pumpenarbeitsraum 24 verdrängt wird.The pump element 10 has a housing 20, in which in a cylinder bore 22 of the pump piston 12 is tightly guided, wherein the housing part 20 is hereinafter referred to as the cylinder head. With its end facing away from the drive shaft 14, the pump piston 12 in the cylinder bore 22 defines a pump working space 24. The pump working space 24 has an inlet valve 26, which is an inlet check valve opening into the pump working space 24, with an inlet 28 via which the Pump work chamber 24 is filled with the radially inward to the drive means 14 directed suction stroke of the pump piston 12 with fuel. The pump working chamber 24 also has an outlet valve 30, which is for example an outlet check valve opening out of the pump working chamber 24, a connection to a drain 32, which can lead to a high-pressure accumulator 34 and over the radially outwardly from the drive means 14 directed away Delivery stroke of the pump piston 12 fuel is displaced from the pump working chamber 24.

Der Stößel 18 ist als Rollenstößel ausgebildet und weist einen Stößelkörper 40 auf, der hohlzylinderförmig ausgebildet ist. Innerhalb des Stößelkörpers 40 ist ein Boden 42 vorgesehen, an dessen der Antriebswelle 14 abgewandter Seite sich der Pumpenkolben 12 zumindest mittelbar mit dem Kolbenfuß abstützt. Den Pumpenkolben 12 umgebend ist im Stößelkörper 40 außerdem eine Feder 44 angeordnet, die beispielsweise eine Schraubendruckfeder ist, und die sich einerseits am Boden 42 und andererseits am Zylinderkopf 20 abstützt. Durch die Feder 44 werden der Pumpenkolben 12 und der Stößelkörper 40 zur Antriebswelle 14 hin beaufschlagt.The plunger 18 is designed as a roller tappet and has a plunger body 40, which is formed as a hollow cylinder. Within the plunger body 40, a bottom 42 is provided, on whose side facing away from the drive shaft 14, the pump piston 12 is supported at least indirectly with the piston foot. Surrounding the pump piston 12, a spring 44 is arranged in the plunger body 40, which is, for example, a helical compression spring, and on the one hand at the bottom 42 and on the other hand supported on the cylinder head 20. By the spring 44 of the pump piston 12 and the plunger body 40 to the drive shaft 14 are acted upon.

Im Stößelkörper 40 ist eine Rolle 46 drehbar gelagert, wobei die Drehachse 47 der Rolle 46 zumindest annähernd parallel zur Drehachse 15 der Antriebswelle 14 verläuft. Die Rolle 46 ist im Stößelkörper 40 auf der dem Pumpenkolben 12 abgewandten Seite des Bodens 42 angeordnet. Die Rolle 46 ist auf einem in den Stößelkörper 40 eingesetzten Bolzen 48 gelagert, wobei zwischen der Rolle 46 und dem Bolzen 48 eine Gleitlagerbuchse 50 angeordnet sein kann. Der Bolzen 48 ist in seinen Endbereichen in zwei koaxial zueinander in bezüglich der Drehachse 47 der Rolle 46 einander gegenüberliegenden Wandungen 52 des Stößelkörpers 40 vorgesehenen Bohrungen 54 aufgenommen. Alternativ kann die Rolle 46 auch wie in Figur 2 dargestellt in einer konkav gewölbten Vertiefung 56 des Stößelkörpers 40 oder eines in den Stößelkörper 40 eingesetzten Stützelements 57 über ihren Außenmantel drehbar gelagert sein, wobei dann der Bolzen 48 entfällt.In the plunger body 40, a roller 46 is rotatably mounted, wherein the axis of rotation 47 of the roller 46 extends at least approximately parallel to the axis of rotation 15 of the drive shaft 14. The roller 46 is arranged in the tappet body 40 on the side facing away from the pump piston 12 side of the bottom 42. The roller 46 is mounted on a pin 48 inserted into the plunger body 40, wherein between the roller 46 and the pin 48, a plain bearing bushing 50 may be arranged. The bolt 48 is received in its end in two coaxial with each other in respect to the axis of rotation 47 of the roller 46 opposite walls 52 of the plunger body 40 provided holes 54. Alternatively, the roller 46 may also be as in FIG FIG. 2 shown in a concave recess 56 of the plunger body 40 or a support member 57 inserted into the plunger body 40 may be rotatably supported via its outer jacket, in which case the bolt 48 is omitted.

Aus Toleranzgründen und um die Drehbewegung der Rolle 46 nicht zu behindern sind zwischen der Rolle 46 und den in Richtung ihrer Drehachse 47 an diese angrenzenden Wandungen 52 des Stößelkörpers 40 Spalte 58 vorhanden. Es kann vorgesehen sein, dass sich die Spalte 58 ausgehend von den Bohrungen 54 zur Antriebswelle 14 hin vergrößern. Dies kann erreicht werden indem sich der Abstand zwischen den einander zugewandten Innenseiten 53 der Wandungen 52 des Stößelkörpers 40 ausgehend von den Bohrungen 54 zur Antriebswelle 14 hin vergrößert. Die Innenseiten 53 der Wandungen 52 des Stößelkörpers 40 können dabei beispielsweise zumindest annähernd konisch angeschrägt sein. Alternativ können die Innenseiten 53 der Wandungen 52 des Stößelkörpers 40 auch gekrümmt ausgebildet sein. Weiterhin alternativ kann auch vorgesehen sein, dass die Innenseiten 53 der Wandungen 52 des Stößelkörpers 40 etwa radial zur Drehachse 47 der Rolle 46 verlaufen und die den Innenseiten 53 zugewandten Stirnseiten der Rolle 46 derart angeschrägt sind, dass sich die Spalte 58 zur Antriebswelle 14 hin vergrößern.For reasons of tolerance and not to hinder the rotational movement of the roller 46 are between the roller 46 and in the direction of its axis of rotation 47 adjacent to these walls 52 of the plunger body 40 column 58 available. It can be provided that the column 58, starting from the bores 54 to the drive shaft 14 toward increase. This can be achieved by increasing the distance between the mutually facing inner sides 53 of the walls 52 of the tappet body 40, starting from the bores 54 to the drive shaft 14. The inner sides 53 of the walls 52 of the plunger body 40 may be, for example, beveled at least approximately conically. Alternatively, the inner sides 53 of the walls 52 of the plunger body 40 may also be curved. Further alternatively, it may also be provided that the inner sides 53 of the walls 52 of the plunger body 40 extend approximately radially to the axis of rotation 47 of the roller 46 and the inner sides 53 facing end faces of the roller 46 are chamfered such that the column 58 to the drive shaft 14 increase ,

Die Antriebswelle 14 ist über wenigstens eine Lagerstelle 60 in einem Gehäuse 62 drehbar gelagert, wobei das Gehäuse 62 ein Gehäuse der Pumpvorrichtung oder ein Gehäuse der Brennkraftmaschine sein kann. Vorzugsweise ist die Antriebswelle 14 über zwei in Richtung ihrer Drehachse 15 zueinander beanstandete Lagerstellen 60 drehbar gelagert, wobei die Lagerstellen 60 auf gegenüberliegenden Seiten des Nockens 16 oder Exzenters angeordnet sind. Die Lagerstellen 60 sind vorzugsweise als Gleitlagerstellen ausgebildet und diese können jeweils eine Lagerbuchse 64 umfassen. Den Lagerstellen 60 wird jeweils wie in den Figuren 1 und 2 durch Pfeile verdeutlicht flüssiges Schmiermedium zugeführt, beispielsweise Schmieröl aus dem Schmierölkreislauf der Brennkraftmaschine. Das Schmiermedium wird den Lagerstellen 60 vorzugsweise unter erhöhtem Druck zugeführt, so dass dieses durch die Lagerstellen 60 hindurchgepresst wird. Aus den Lagerstellen 60 tritt Schmiermedium in Richtung der Drehachse 15 der Antriebswelle 14 zum Nocken 16 oder Exzenter hin aus. Erfindungsgemäß ist vorgesehen, dass die Antriebswelle 14 zwischen wenigstens einer Lagerstelle 60 und dem Nocken 16 oder Exzenter eine derart geformte Außenkontur 66 aufweist, dass aus der Lagerstelle 60 austretendes Schmiermedium gezielt zum Stößel 18 geleitet wird, um die Schmierung des Stößels 18 sicherzustellen oder zu verbessern. Die Außenkontur 66 ist dabei derart ausgebildet, dass sich der Durchmesser der Außenkontur 66 von der Lagerstelle 60 weg und zum Nocken 16 oder Exzenter hin vergrößert. Es kann vorgesehen sein, dass nur zwischen einer Lagerstelle 60 und dem Nocken 16 oder Exzenter eine Außenkontur 66 vorgesehen sein. Vorzugsweise ist zwischen dem Nocken 16 oder Exzenter und jeder Lagerstelle 60 jeweils eine Außenkontur 66 vorgesehen, wobei beide Außenkonturen 66 spiegelbildlich zueinander angeordnet und ausgebildet sind.The drive shaft 14 is rotatably supported by at least one bearing point 60 in a housing 62, wherein the housing 62 may be a housing of the pump device or a housing of the internal combustion engine. Preferably, the drive shaft 14 is rotatably supported by two in the direction of its axis of rotation 15 to each other spaced bearings 60, wherein the bearing points 60 are arranged on opposite sides of the cam 16 or eccentric. The bearings 60 are preferably designed as plain bearings and these may each comprise a bearing bush 64. The bearings 60 is each as in the FIGS. 1 and 2 indicated by arrows liquid lubricant supplied, for example, lubricating oil from the lubricating oil circuit of the internal combustion engine. The lubricating medium is preferably supplied to the bearings 60 under elevated pressure so that it is pressed through the bearings 60. From the bearings 60 lubricant enters the direction of the axis of rotation 15 of the drive shaft 14 to the cam 16 or eccentric out. According to the invention, the drive shaft 14 between at least one bearing point 60 and the cam 16 or eccentric has a shaped outer contour 66, that from the bearing 60 leaking lubricating medium is directed to the plunger 18 to ensure the lubrication of the plunger 18 or improve , The outer contour 66 is designed in such a way that the diameter of the outer contour 66 increases away from the bearing point 60 and towards the cam 16 or eccentric. It can be provided that only between a bearing 60 and the cam 16 or eccentric an outer contour 66 may be provided. Preferably, an outer contour 66 is provided between the cam 16 or eccentric and each bearing 60, wherein both outer contours 66 are arranged and formed in mirror image to each other.

In Figur 1 ist die Antriebswelle 14 mit der Außenkontur 66 gemäß einem ersten Ausführungsbeispiel dargestellt. Die Außenkontur 66 ist dabei zumindest annähernd konisch ausgebildet, so dass sich deren Durchmesser linear von der Lagerstelle 60 zum Nocken 16 oder Exzenter vergrößert. Die Außenkontur 66 schließt sich in Richtung der Drehachse 15 der Antriebswelle 14 gesehen direkt oder mit geringem Abstand an die Lagerstelle 60 an. Alternativ kann auch vorgesehen sein, dass die Antriebswelle 14 in Richtung ihrer Drehachse 15 gesehen von der Lagerstelle 60 ausgehend zum Nocken 16 oder Exzenter hin zunächst mit konstantem Durchmesser ausgebildet ist und sich daran die Außenkontur 66 anschließt. Der Übergang an der Antriebswelle 14 zur Außenkontur 66 kann dabei in einem Knick oder gerundet ausgebildet sein. Vorzugsweise ist zwischen der der Lagerstelle 60 zugewandten Stirnseite des Nockens 16 oder Exzenters und dem der Lagerstelle 60 abgewandten Ende der Außenkontur 66 ein Abschnitt 68 der Antriebswelle 14 mit verringertem Durchmesser vorgesehen, so dass die Außenkontur 66 zum Nocken 16 oder Exzenter hin in einer Kante 70 endet. Der Abschnitt 68 bildet einen Einstich an der Antriebswelle 14 zwischen dem Nocken 16 oder Exzenter und der Kante 70 der Außenkontur 66.In FIG. 1 the drive shaft 14 is shown with the outer contour 66 according to a first embodiment. The outer contour 66 is at least approximately conical, so that its diameter increases linearly from the bearing 60 to the cam 16 or eccentric. The outer contour 66 closes in the direction of the axis of rotation 15 of the drive shaft 14 seen directly or at a small distance to the bearing point 60 at. Alternatively, it can also be provided that the drive shaft 14, viewed in the direction of its axis of rotation 15 starting from the bearing point 60, is initially formed with a constant diameter starting from the cam 16 or eccentric and the outer contour 66 adjoins it. The transition to the drive shaft 14 to the outer contour 66 may be formed in a kink or rounded. Preferably, a portion 68 of the drive shaft 14 is provided with a reduced diameter between the end facing the bearing 60 of the cam 16 or eccentric and the bearing 60 remote from the outer contour 66, so that the outer contour 66 to the cam 16 or eccentric out in an edge 70th ends. The section 68 forms a puncture on the drive shaft 14 between the cam 16 or eccentric and the edge 70 of the outer contour 66.

In Richtung der Drehachse 15 der Antriebswelle 14 gesehen ist die Kante 70 im Bereich des Spalts 58 zwischen der Rolle 46 und der Wandung 52 des Stößelkörpers 40 angeordnet. Bei der Drehbewegung der Antriebswelle 14 wird aus der Lagerstelle 60 austretendes Schmiermedium von der Kante 70 infolge der Zentrifugalkraft wie in den Figuren 1 und 2 durch Pfeile verdeutlicht radial nach außen weggeschleudert und tritt in den Spalt 58 ein. Hierdurch wird die Schmierung im Stößel 18 verbessert oder sichergestellt, also der Lagerung der Rolle 46 auf dem Bolzen 48 oder in der Vertiefung 56 des Stößelkörpers 40 oder des Stützelements 57 und/oder die axiale Lagerung der Rolle 46 in Richtung ihrer Drehachse 47 im Stößelkörper 40 und/oder die Lagerung des Bolzens 48 in den Bohrungen 54 des Stößelkörpers 40.Viewed in the direction of the axis of rotation 15 of the drive shaft 14, the edge 70 is arranged in the region of the gap 58 between the roller 46 and the wall 52 of the tappet body 40. During the rotational movement of the drive shaft 14 from the bearing 60 leaking lubricant from the edge 70 due to the centrifugal force as in FIGS. 1 and 2 indicated by arrows thrown radially outward and enters the gap 58 a. As a result, the lubrication in the plunger 18 is improved or ensured, ie the bearing of the roller 46 on the pin 48 or in the recess 56 of the plunger body 40 or the support member 57 and / or the axial bearing of the roller 46 in the direction of its axis of rotation 47 in the plunger body 40th and / or the mounting of the bolt 48 in the bores 54 of the plunger body 40th

In Figur 2 ist die Antriebswelle 14 mit der Außenkontur 66 gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem die Außenkontur 66 konkav gekrümmt ausgebildet ist, so dass deren Durchmesser zum Nocken 16 oder Exzenter hin nicht linear zunimmt sondern bei Annäherung zum Nocken 16 oder Exzenter stärker zunimmt.In FIG. 2 the drive shaft 14 is shown with the outer contour 66 according to a second embodiment, in which the outer contour 66 is concave, so that the diameter of the cam 16 or eccentric towards non-linearly increases but increases closer to the cam 16 or eccentric.

Claims (9)

  1. Pump device, in particular high-pressure fuel pump device, having at least one pump element (10) which has a pump piston (12) which is driven in a reciprocating movement by a drive shaft (14) via a tappet (18), wherein the drive shaft (14) has at least one cam (16) or eccentric on which the tappet (18) is at least indirectly supported, wherein the drive shaft (14) is rotatably mounted by means of at least one bearing point (60), wherein the at least one bearing point (60) is supplied with lubricating medium which emerges from the at least one bearing point (60) toward the at least one cam (16) or eccentric, wherein the drive shaft (14) has, between the at least one bearing point (60) and the at least one cam (16) or eccentric, an outer contour (66) which increases in diameter from the at least one bearing point (60) towards the at least one cam (16) or eccentric, which outer contour ends, as viewed in the direction of an axis of rotation (15) of the drive shaft (14), in the region of the tappet (18), and wherein, in the tappet (18), there is rotatably mounted a roller (46) by means of which the tappet (18) is supported on the cam (16) or eccentric, and in that the outer contour (66) of the drive shaft (14) ends, as viewed in the direction of the axis of rotation (15) of the drive shaft (14), in the region of a mounting of the roller (46) in the tappet (18), wherein the tappet (18) has a tappet body (40) which has a receptacle which is open toward the drive shaft (14), in which receptacle the roller (46) is arranged in the direction of the drive shaft (14), and a gap (58) is present between the face side of the roller (46) and the tappet body (40) as viewed in the direction of an axis of rotation (47) of the roller (46), characterized in that the outer contour (66) of the drive shaft (14) ends, as viewed in the direction of the axis of rotation (15) of the drive shaft (14), in the region of the gap (58).
  2. Pump device according to Claim 1, characterized in that the drive shaft (14) is mounted, to both sides of the at least one cam (16) or eccentric, by means of in each case one bearing point (60), and in that the outer contour (66) is provided to both sides of the at least one cam (16) or eccentric, and in that the drive shaft (14) has, between the at least one bearing point (60) and the at least one cam (16) or eccentric, the outer contour (66) which increases in diameter from the at least one bearing point (60) toward the at least one cam (16) or eccentric, which outer contour ends, as viewed in the direction of the axis of rotation (15) of the drive shaft (14), in the region of the tappet (18).
  3. Pump device according to Claim 1, characterized in that the outer contour (66) of the drive shaft (14) ends, in the direction of the at least one cam (16) or eccentric, at an edge (70) which is directed away from the axis of rotation (15) of the drive shaft (14) at least approximately radially with respect to said axis of rotation.
  4. Pump device according to one of Claims 1 to 3, characterized in that the outer contour (66) of the drive shaft (14) is of at least approximately conical form.
  5. Pump device according to one of Claims 1 to 3, characterized in that the outer contour (66) is of curved, in particular concavely curved form.
  6. Pump device according to one of the preceding claims, characterized in that the drive shaft (14) has, between the at least one cam (16) or eccentric and that end of the outer contour (66) which faces toward said at least one cam or eccentric, a section (68) with a diameter smaller than the end of the outer contour (66).
  7. Pump device according to Claim 1, characterized in that the roller (46) is mounted in the tappet body (40) by way of a bolt (48), and in that the bolt (48) extends through the gap (58) that exists between the roller (46) and the tappet body (40).
  8. Pump device according to one of Claims 1 to 7, characterized in that the width, as viewed in the direction of the axis of rotation (47) of the roller (46), within the tappet body (40) increases toward the drive shaft (14) such that the gap (58) becomes larger toward the drive shaft (14).
  9. Pump device according to Claim 8, characterized in that the inner sides (53), which face toward one another, of the tappet body (40) are of bevelled or curved form for the enlargement of the gap (58).
EP14720621.3A 2013-06-25 2014-04-30 Pumping device, in particular high pressure fuel pumping device for a fuel injection device Active EP3014107B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013212047.8A DE102013212047A1 (en) 2013-06-25 2013-06-25 Pump device, in particular high-pressure fuel pump device for a fuel injection device
PCT/EP2014/058926 WO2014206609A1 (en) 2013-06-25 2014-04-30 Pumping device, in particular high pressure fuel pumping device for a fuel injection device

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EP3014107A1 EP3014107A1 (en) 2016-05-04
EP3014107B1 true EP3014107B1 (en) 2017-04-12

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EP (1) EP3014107B1 (en)
CN (1) CN105358819B (en)
DE (1) DE102013212047A1 (en)
WO (1) WO2014206609A1 (en)

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GB2543354A (en) * 2015-10-16 2017-04-19 Gm Global Tech Operations Llc Roller tappet for a fuel unit pump of an internal combustion engine
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DE102016208581A1 (en) * 2016-05-19 2017-11-23 Robert Bosch Gmbh High-pressure fuel pump
WO2022036230A1 (en) * 2020-08-14 2022-02-17 Cummins Inc. Sliding cam follower

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JP3633314B2 (en) * 1998-10-14 2005-03-30 三菱電機株式会社 High pressure fuel pump device
US6722864B2 (en) * 2001-12-12 2004-04-20 Denso Corporation Fuel injection pump
DE10256528A1 (en) 2002-12-04 2004-06-24 Robert Bosch Gmbh High pressure pump for a fuel injector of an internal combustion engine
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KR101091402B1 (en) * 2008-11-17 2011-12-07 현대자동차주식회사 Automobile High-Pressure Fuel Pump
JP5320079B2 (en) * 2009-01-06 2013-10-23 ヤンマー株式会社 Fuel injection pump
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DE102013212047A1 (en) 2015-01-08
EP3014107A1 (en) 2016-05-04
CN105358819A (en) 2016-02-24
CN105358819B (en) 2019-01-01
WO2014206609A1 (en) 2014-12-31

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