EP2702270B1 - Spring washer for a plunger assembly of a high pressure pump and high pressure pump - Google Patents
Spring washer for a plunger assembly of a high pressure pump and high pressure pump Download PDFInfo
- Publication number
- EP2702270B1 EP2702270B1 EP12707348.4A EP12707348A EP2702270B1 EP 2702270 B1 EP2702270 B1 EP 2702270B1 EP 12707348 A EP12707348 A EP 12707348A EP 2702270 B1 EP2702270 B1 EP 2702270B1
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- EP
- European Patent Office
- Prior art keywords
- spring plate
- support ring
- inner support
- radially inner
- pump piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0439—Supporting or guiding means for the pistons
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0435—Arrangements for disconnecting the pistons from the actuated cam
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- 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
Description
Die vorliegende Erfindung betrifft einen Federteller für eine Stößelbaugruppe einer Hochdruckpumpe mit den Merkmalen des Oberbegriffs des Anspruchs 1. Ferner betrifft die Erfindung eine Hochdruckpumpe mit einem solchen Federteller.The present invention relates to a spring plate for a plunger assembly of a high pressure pump having the features of the preamble of
Ein Federteller der vorstehend genannten Art bzw. eine Hochdruckpumpe mit einem solchen Federteller ist durch die
Der Stößel weist einen sich nach radial innen erstreckenden Ringbund auf, an welchem einerseits der Federteller und andererseits ein Stützelement zur drehbaren Lagerung einer Rolle anliegen. Zwischen dem Stützelement und dem Federteller kommt der Kolbenfuß des Pumpenkolbens zu liegen. Der bekannte Federteller weist eine zentrale Ausnehmung zur Aufnahme des Pumpenkolbens und mehrere um die zentrale Aushemung herum angeordnete bogenförmig verlaufende Ausnehmungen zur Ausbildung eines radial innen liegenden Stützrings und eines radial außen liegenden Stützrings besitzt, die über im Wesentlichen radial verlaufende Stege miteinander verbunden sind. Der radial innen liegende Stützring liegt am Pumpenkolben an.The plunger has a radially inwardly extending annular collar on which on the one hand the spring plate and on the other hand abut a support member for rotatably supporting a roller. Between the support element and the spring plate, the piston foot of the pump piston comes to rest. The known spring plate has a central recess for receiving the pump piston and a plurality of arranged around the central Aushemung arcuate recesses for forming a radially inner support ring and a radially outer support ring has, which are interconnected via substantially radially extending webs. The radially inner support ring abuts against the pump piston.
Aufgrund von Fertigungstoleranzen ist zwischen den Bauteilen oftmals ein axiales Spiel vorhanden, das insbesondere in den Bereichen der Bewegungsumkehr des Pumpenkolbens, beispielsweise beim Übergang von der Förderphase in die Saugphase, vom Pumpenkolben dynamisch durchlaufen wird. Dies führt dazu, dass die Bauteile gegeneinander schlagen und demzufolge einem erhöhten Verschleiß unterliegen. Beim Durchlaufen eines axialen Spiels erfährt der Pumpenkolben hohe Beschleunigungen, die dazu führen, dass der Pumpenkolben mit hoher Geschwindigkeit auf den Federteller aufschlägt. Neben den unerwünschten Geräuschentwicklungen kann dies zu einer Überbelastung des Federtellers und diese wiederum zum Bruch des Federtellers führen. Ferner wirkt sich ein axiales Spiel im Bereich der Kolbenfußaufnahme auf die Fördertoleranzen der Hochdruckpumpe aus.Due to manufacturing tolerances, there is often axial play between the components, which is passed through dynamically by the pump piston, in particular in the areas of movement reversal of the pump piston, for example during the transition from the delivery phase to the suction phase. As a result, the components strike against each other and are therefore subject to increased wear. When passing through an axial clearance of the pump piston undergoes high accelerations, which cause the pump piston strikes the spring plate at high speed. In addition to the unwanted noise developments, this can lead to an overload of the spring plate and this in turn to break the spring plate. Furthermore, an axial clearance in the area of the piston foot receptacle has an effect on the delivery tolerances of the high-pressure pump.
Durch die
Ausgehend von dem vorstehend genannten Stand der Technik ist es Aufgabe der vorliegenden Erfindung, einen elastisch verformbaren Federteller für eine Stößelbaugruppe einer Hochdruckpumpe derart weiterzuentwickeln, dass der Ausgleich eines axialen Spiels im Bereich der Kolbenaufnahme vereinfacht wird.Based on the above-mentioned prior art, it is an object of the present invention to further develop an elastically deformable spring plate for a plunger assembly of a high-pressure pump such that the compensation of an axial clearance in the region of the piston receptacle is simplified.
Die Aufgabe wird gelöst durch einen Federteller mit den Merkmalen des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. Die Aufgabe wird ferner gelöst durch eine Hochdruckpumpe mit den Merkmalen des Anspruchs 9.The object is achieved by a spring plate with the features of
Vorgeschlagen wird ein Federteller für eine Stößelbaugruppe einer Hochdruckpumpe in einem Kraftstoffeinspritzsystem, wobei der Federteller insbesondere ein Biege-Stanzteil ist und eine zentrale Ausnehmung zur Aufnahme eines Pumpenkolbens aufweist. Erfindungsgemäß besitzt der radial innen liegende Stützring gegenüber einer Ebene E angehobene und abgesenkte Bereiche, die jeweils in einem Winkelabstand zu den im Wesentlichen radial verlaufenden Stegen angeordnet sind. Durch die Anhebungen und Absenkungen des radial innen liegenden Stützrings weist der Federteller eine zirkulare Welligkeit auf, welche den Ausgleich eines fertigungsbedingten axialen Spiels im Bereich der Aufnahme des Pumpenkolbens bzw. des Kolbenfußes des Pumpenkolbens ermöglicht. Denn die zirkulare Welligkeit bewirkt eine elastische Verformbarkeit des Federtellers, so dass dieser axial vorspannbar ist. Der Federteller ist demzufolge derart in eine Stößelbaugruppe einer Hochdruckpumpe einsetzbar, dass er unter axialer Vorspannung am Pumpenkolben anliegt. Der Kolbenfuß des Pumpenkolbens wird dabei bevorzugt zwischen dem Federteller und einem Stützelement der Stößelbaugruppe eingeklemmt. Die zur Vorspannung des Federtellers erforderliche axiale Kraft wird weiterhin bevorzugt von einer Rückstellfeder bewirkt, welche die Stößelbaugruppe in Anlage mit dem Nocken oder Exzenter einer Antriebswelle hält.Proposed is a spring plate for a plunger assembly of a high-pressure pump in a fuel injection system, wherein the spring plate is in particular a bending stamped part and has a central recess for receiving a pump piston. According to the invention has the radially inner support ring with respect to a plane E raised and lowered areas, which are each arranged at an angular distance to the substantially radially extending webs. Due to the increases and decreases of the radially inner support ring, the spring plate has a circular waviness, which allows the compensation of a production-related axial play in the region of the recording of the pump piston or the piston foot of the pump piston. Because the circular waviness causes elastic deformability of the spring plate, so that it is axially biased. The spring plate is therefore used in such a plunger assembly of a high pressure pump that it rests under axial bias on the pump piston. The piston foot of the pump piston is preferably clamped between the spring plate and a support member of the plunger assembly. The required for biasing the spring plate axial force is further preferably effected by a return spring, which holds the plunger assembly in abutment with the cam or eccentric drive shaft.
Die elastische Verformbarkeit des Federtellers durch die zirkulare Welligkeit führt ferner dazu, dass der Pumpenkolben in den Bereichen seiner Bewegungsumkehr "weich" abgefangen wird. Auf diese Weise werden zum Einen unerwünschte Geräuschentwicklungen vermieden und zum Anderen die Belastungen des Federtellers verringert. Die Gefahr eines Federtellerbruchs ist demzufolge nicht mehr gegeben. Zugleich wird die Fülleffizienz der Hochdruckpumpe erhöht.The elastic deformability of the spring plate by the circular ripple also leads to the pump piston is "soft" intercepted in the areas of its reversal of motion. In this way, on the one hand undesirable noise developments are avoided and on the other hand reduces the burden of the spring plate. The risk of a spring plate break is therefore no longer present. At the same time, the filling efficiency of the high-pressure pump is increased.
Durch die Anordnung der angehobenen bzw. abgesenkten Bereiche des radial innen liegenden Stützrings in einem Winkelabstand zu den im Wesentlichen radial verlaufenden Stegen wird die elastische Verformbarkeit des Federtellers erhöht. Denn als Biegebalken steht nicht nur der radial verlaufende Steg, sondern auch das jeweils im Bereich des Winkelabstandes liegende Teilstück des radial innen liegenden Stützringes zur Verfügung. Vorzugsweise ist daher der Winkelabstand einer Anhebung oder Absenkung zu einem Steg möglichst groß gewählt.By the arrangement of the raised or lowered portions of the radially inner support ring at an angular distance from the substantially radially extending webs, the elastic deformability of the spring plate is increased. Because as a bending beam is not only the radially extending web, but also each lying in the range of the angular distance portion of the radially inner support ring available. Preferably, therefore, the angular distance of an increase or decrease to a web is chosen as large as possible.
Weiterhin bevorzugt ist der Winkelabstand der angehobenen und abgesenkten Bereiche zu den im Wesentlichen radial verlaufenden Stegen jeweils gleich groß gewählt. Das heißt einerseits, dass der Winkelabstand einer Anhebung zum nächsten Steg dem Winkelabstand der weiteren Anhebungen zum jeweils nächsten Steg entspricht, andererseits, dass die Winkelabstände der Anhebungen denen der Absenkungen entsprechen. Die Länge eines Biegebalkens, der in einer Anhebung oder Absenkung endet, ist demnach immer gleich groß, so dass die über die angehobenen und abgesenkten Bereiche bewirkbare elastische Verformbarkeit des Federtellers unabhängig von der Einbaurichtung des Federtellers ebenfalls gleich groß ist.Further preferably, the angular distance of the raised and lowered regions is selected to be equal to the substantially radially extending webs. On the one hand, this means that the angular distance of an increase to the next bridge corresponds to the angular distance of the further elevations to the next bridge, on the other hand, that the angular distances of the elevations correspond to those of the reductions. The length of a bending beam that ends in an increase or decrease, therefore, is always the same size, so that the effect on the raised and lowered areas effected elastic deformability of the spring plate, regardless of the installation direction of the spring plate is also the same size.
Vorzugsweise entspricht die Anzahl der Anhebungen denen der Absenkungen, wobei ferner vorzugsweise die Anhebungen und Absenkungen jeweils im gleichen Winkelabstand zueinander angeordnet sind. Weisen die Anhebungen und Absenkungen zudem den gleichen Winkelabstand zu den im Wesentlichen radial verlaufenden Stegen auf, folgt hieraus, dass auch die Stege im gleichen Winkelabstand zueinander angeordnet sind. Durch den jeweils gleichen Winkelabstand der angehobenen und abgesenkten Bereiche sowie der Stege zueinander ist eine gleichmäßige elastische Verformung des Federtellers bei einer Beaufschlagung mit einer Axialkraft sichergestellt.Preferably, the number of elevations corresponds to those of the subsidence, wherein further preferably, the elevations and depressions are each arranged at the same angular distance from each other. If the elevations and depressions also have the same angular spacing from the essentially radially extending webs, it follows that the webs are also arranged at the same angular distance from one another. By the same angular distance of the raised and lowered areas and the webs to each other a uniform elastic deformation of the spring plate is ensured when subjected to an axial force.
Gemäß einem bevorzugten Ausführungsbeispiel der Erfindung sind die angehobenen Bereiche um ein Maß a gegenüber der Ebene E angehoben, wobei das Maß a 0,2 mm oder weniger beträgt. Das über die Anhebungen des radial innen liegenden Stützrings maximal ausgleichbare axiale Spiel beträgt demnach 0,2 mm.According to a preferred embodiment of the invention, the raised portions are raised by a dimension a from the plane E, the dimension a being 0.2 mm or less. The maximum over the increases of the radially inner support ring axial clearance is therefore 0.2 mm.
Alternativ oder ergänzend kann vorgesehen sein, dass die abgesenkten Bereiche um ein Maß b gegenüber der Ebene E abgesenkt sind, wobei das Maß b 0,2 mm oder weniger betragen kann. Das über die Absenkungen des radial innen liegenden Stützrings maximal ausgleichbare axiale Spiel beträgt demnach ebenfalls 0,2 mm.Alternatively or additionally, it may be provided that the lowered regions are lowered by a dimension b with respect to the plane E, wherein the dimension b may be 0.2 mm or less. The maximum compensation over the subsidence of the radially inner support ring axial play is therefore also 0.2 mm.
Um die elastische Verformbarkeit des Federtellers zu erhöhen, wird ferner vorgeschlagen, dass der radial innen liegende Stützring Durchbrechungen aufweist. Die Durchbrechungen teilen den radial innen liegenden Stützring in Teilstücke auf, welche gemeinsam mit den im Wesentlichen radial verlaufenden Stegen elastisch verformbare Federarme ausbilden. Vorzugsweise sind die Durchbrechungen im gleichen Winkelabstand zueinander angeordnet, so dass sich gleich große Teilstücke des radial innen liegenden Stützrings ergeben. Weiterhin vorzugsweise entspricht die Anzahl der Durchbrechungen der Anzahl der Stege. Um eine gleichmäßige elastische Verformung der Federarme bei einer Beaufschlagung des Federtellers mit einer Axialkraft zu bewirken, wird des Weiteren vorgeschlagen, dass der Winkelabstand der Durchbrechungen zu den Stegen jeweils gleich groß gewählt ist. Vorteilhafterweise ist jeweils eine Durchbrechung mit zwischen zwei Stegen angeordnet.In order to increase the elastic deformability of the spring plate, it is also proposed that the radially inner support ring has openings. The openings divide the radially inner support ring into sections, which together with the essentially radially extending webs form elastically deformable spring arms. Preferably, the openings are in arranged equal angular distance from each other so that equal parts of the radially inner support ring arise. Further preferably, the number of openings corresponds to the number of webs. In order to effect a uniform elastic deformation of the spring arms when the spring plate is acted upon with an axial force, it is further proposed that the angular spacing of the apertures from the webs be selected to be the same. Advantageously, an opening is arranged in each case between two webs.
Gemäß einer Weiterbildung der Erfindung sind die Durchbrechungen jeweils zwischen einem angehobenen und einem abgesenkten Bereich des radial innen liegenden Stützrings ausgebildet. Auf diese Weise kommen die angehobenen und abgesenkten Bereiche des radial innen liegenden Stützrings jeweils an den Enden der Federarme ausbildenden Teilstücke des radial innen liegenden Stützrings zu liegen. Dabei weist jedes Teilstück bevorzugt an einem Ende einen angehobenen und an dem anderen Ende einen abgesenkten Bereich auf, wobei sich an den gegenüberliegenden Enden zweier Teilstücke im Bereich einer Durchbrechung jeweils ein angehobener und ein abgesenkter Bereich gegenüberliegen. Jede Anhebung bzw. Absenkung bildet eine Stützfläche aus, mit welcher der Federteller als Bestandteil einer Stößelbaugruppe bevorzugt unter Vorspannung am Pumpenkolben anliegt. Die Vorspannung wird durch eine elastische Verformung des Federtellers im Bereich der Anhebungen und/oder Absenkungen des radial innen liegenden Stützrings bewirkt. Ein axiales Spiel kann somit vollständig ausgeglichen werden.According to one embodiment of the invention, the openings are each formed between a raised and a lowered portion of the radially inner support ring. In this way, the raised and lowered portions of the radially inner support ring come to lie at the ends of the spring arms forming portions of the radially inner support ring. In this case, each section preferably has a raised area at one end and a lowered area at the other end, with a raised area and a lowered area opposite one another at the opposite ends of two sections in the region of an opening. Each increase or decrease forms a support surface, with which the spring plate preferably rests as a component of a plunger assembly under bias on the pump piston. The bias is effected by an elastic deformation of the spring plate in the region of the elevations and / or lowering of the radially inner support ring. An axial clearance can thus be completely compensated.
Gemäß einem weiteren bevorzugten Ausführungsbeispiel weist der radial innen liegende Stützring eine Durchbrechung auf, welche die zentrale Ausnehmung zur Aufnahme des Pumpenkolbens mit einer exzentrisch angeordneten Ausnehmung verbindet. Die exzentrisch angeordnete Ausnehmung soll das Einsetzen eines Pumpenkolbens in den Federteller vereinfachen. Dies gilt insbesondere, wenn ein durchgangsgeschliffener Kolben eingesetzt werden soll. Der Kolben kann zunächst in die exzentrische Ausnehmung eingesetzt und dann seitlich in Richtung der zentralen Ausnehmung verschoben werden, so dass der radial innen liegende Stützring den Kolbenfuß hintergreift bzw. in eine Umfangsnut des Pumpenkolbens eingreift.According to a further preferred embodiment, the radially inner support ring has an opening which connects the central recess for receiving the pump piston with an eccentrically arranged recess. The eccentrically arranged recess is intended to simplify the insertion of a pump piston in the spring plate. This is especially true when a through-ground piston is to be used. The piston can first be inserted into the eccentric recess and then moved laterally in the direction of the central recess, so that the radially inner support ring engages behind the piston foot or engages in a circumferential groove of the pump piston.
Vorteilhafterweise besitzt die exzentrisch angeordnete Ausnehmung einen größeren Durchmesser als die zentrale Ausnehmung. Der durchgangsgeschliffene Kolben kann dann über die exzentrische Ausnehmung eingeführt und auf Höhe einer Umfangsnut in radialer Richtung in die zentrale Ausnehmung verschoben werden. Die beiden unterschiedlich großen Durchmesser der beiden Ausnehmungen führen zu einer schlüssellochähnlichen Form der Kolbenaufnahme. Der Durchmesser der zentralen Ausnehmung des Federtellers ist dabei bevorzugt kleiner als der Außendurchmesser des Pumpenkolbens gewählt, damit der radial innen liegende Stützring den Kolbenfuß hintergreift bzw. in Eingriff mit der Umfangsnut des Pumpenkolbens bringbar ist.Advantageously, the eccentrically arranged recess has a larger diameter than the central recess. The through-ground piston can then be inserted through the eccentric recess and at the level of a circumferential groove in radial direction are moved into the central recess. The two different diameters of the two recesses lead to a keyhole-like shape of the piston receiving. The diameter of the central recess of the spring plate is preferably chosen smaller than the outer diameter of the pump piston, so that the radially inner support ring engages behind the piston or is engageable with the circumferential groove of the pump piston.
Die Anhebungen und Absenkungen des radial innen liegenden Stützrings können bereits beim Schneiden des Federtellers mittels der Schneidmatrize ausgebildet werden. Auf diese Weise ist der erfindungsgemäße Federteller zudem einfach und kostengünstig herstellbar.The elevations and depressions of the radially inner support ring can already be formed when cutting the spring plate by means of the cutting die. In this way, the spring plate according to the invention is also easy and inexpensive to produce.
Die des Weiteren zur Lösung der eingangs genannten Aufgabe vorgeschlagene Hochdruckpumpe für ein Kraftstoffeinspritzsystem weist wenigstens ein Pumpenelement mit einem erfindungsgemäßen Federteller auf. Der Federteller ist dabei Bestandteil einer Stößelbaugruppe, über welche ein hubbeweglich geführter Pumpenkolben des Pumpenelementes mittelbar an einem Nocken oder Exzenter einer Antriebswelle abgestützt ist, über welche der Pumpenkolben entgegen der Federkraft einer Rückstellfeder zu einer Hubbewegung antreibbar ist. Über die Anhebungen und Absenkungen im Bereich des radial innen liegenden Stützrings vermag der Federteller ein axiales Spiel im Bereich der Kolbenaufnahme auszugleichen. Denn die Anhebungen und Absenkungen bewirken eine elastische Verformbarkeit des Federtellers, so dass dieser in axialer Richtung vorspannbar ist, um den Kolbenfuß zwischen dem Federteller und einem Stützelement einzuklemmen. Die Klemmwirkung verhindert, dass der Pumpenkolben bei einer Bewegungsumkehr an den angrenzenden Bauteilen anschlägt und es zu Schlaggeräuschen kommt. Die Bewegung des Pumpenkolbens wird zudem über den elastisch verformbaren Federteller "weich" abgefangen, so dass ferner die Gefahr von Federtellerbrüchen reduziert wird. Darüber hinaus wird die Fülleffizienz der Hochdruckpumpe erhöht, da der Pumpenkolben stets nachgeführt wird.The further proposed to achieve the object mentioned high-pressure pump for a fuel injection system has at least one pump element with a spring plate according to the invention. The spring plate is part of a plunger assembly, via which a hubbeweglich guided pump piston of the pump element is indirectly supported on a cam or eccentric drive shaft, via which the pump piston against the spring force of a return spring is driven to a lifting movement. About the increases and reductions in the region of the radially inner support ring of the spring plate can compensate for an axial play in the piston receiving area. Because the increases and decreases cause elastic deformability of the spring plate, so that it can be biased in the axial direction to clamp the piston foot between the spring plate and a support member. The clamping action prevents the pump piston from abutting the adjoining components when there is a reversal of motion and sounding banging occurs. The movement of the pump piston is also "soft" intercepted via the elastically deformable spring plate, so that further the risk of spring plate fractures is reduced. In addition, the filling efficiency of the high-pressure pump is increased because the pump piston is always tracked.
Vorteilhafterweise ist der Federteller einer erfindungsgemäßen Hochdruckpumpe über den radial innen liegenden Stützring am Pumpenkolben und über den radial außen liegenden Stützring an einem Stößelkörper der Stößelbaugruppe abgestützt. In dieser Anordnung ist eine Klemmverbindung des Pumpenkolbens mit der Stößelbaugruppe realisierbar. Beim Zusammensetzen der Stößelbaugruppe wird der radial innen liegende Stützring des Federtellers durch die Federkraft der Rückstellfeder, welche bis 600 N und darüber betragen kann, auf ein axiales Maß zusammengedrückt, so dass der Federteller unter axialer Vorspannung am Pumpenkolben anliegt. Ein axiales Spiel wird somit vollständig ausgeglichen. Bei spiegelsymmetrischer Ausbildung der angehobenen und abgesenkten Bereiche des radial innen liegenden Stützrings ist ferner gewährleistet, dass die Einbaurichtung des Federtellers unerheblich ist. Das heißt, dass der Federteller in beiden Einbaulagen das gleiche Verhalten zeigt, so dass Montagefehler wirksam verhindert werden.Advantageously, the spring plate of a high-pressure pump according to the invention is supported via the radially inner support ring on the pump piston and via the radially outer support ring on a plunger body of the plunger assembly. In this arrangement, a clamping connection of the pump piston with the plunger assembly can be realized. When assembling the plunger assembly is the radially inside lying support ring of the spring plate by the spring force of the return spring, which may be up to 600 N and above, compressed to an axial dimension, so that the spring plate rests under axial bias on the pump piston. An axial play is thus completely compensated. In mirror-symmetrical design of the raised and lowered portions of the radially inner support ring is further ensured that the installation direction of the spring plate is irrelevant. This means that the spring plate shows the same behavior in both installation positions, so that assembly errors are effectively prevented.
Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der beigefügten Zeichnungen näher erläutert. Diese zeigen:
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eine teilweise perspektivisch dargestellte Schnittansicht einer erfindungsgemäßen Hochdruckpumpe im Bereich der Stößelbaugruppe,Figur 1 -
Figur 2a eine Draufsicht auf eine erste bevorzugte Ausführungsform eines erfindungsgemäßen Federtellers, -
Figur 2b einen Teilschnitt durch den Federteller derFigur 2a , -
Figur 3a eine Draufsicht auf eine zweite bevorzugte Ausführungsform eines erfindungsgemäßen Federtellers, -
Figur 3b einen Teilschnitt durch den Federteller derFigur 3a und -
Figur 4 eine perspektivische Darstellung einer dritten bevorzugten Ausführungsform eines erfindungsgemäßen Federtellers.
-
FIG. 1 1 is a partially perspective view of a high-pressure pump according to the invention in the region of the plunger assembly, -
FIG. 2a a top view of a first preferred embodiment of a spring plate according to the invention, -
FIG. 2b a partial section through the spring plate ofFIG. 2a . -
FIG. 3a a plan view of a second preferred embodiment of a spring plate according to the invention, -
FIG. 3b a partial section through the spring plate ofFIG. 3a and -
FIG. 4 a perspective view of a third preferred embodiment of a spring plate according to the invention.
Die in der
Der hülsenförmige Stößelkörper 17 weist innenumfangseitig einen Ringbund 20 auf, an welchem einerseits das Stützelement 18, andererseits ein Federteller 1 abgestützt ist. Der Federteller 1 weist eine zentrale Ausnehmung 3 zur Aufnahme des Pumpenkolbens 4 auf. Dieser ist derart in den Federteller 1 eingesetzt, dass der radial innen liegende Stützring einen Kolbenfuß 21 des Pumpenkolbens hintergreift. Auf diese Weise wird ein Formschluss des Federtellers 1 mit dem Pumpenkolben 4 bewirkt. Der Federteller 1 ist aus Metall hergestellt, insbesondere aus Stahl, vorzugsweise aus Federstahl.The sleeve-shaped
Der Bereich der Kolbenfußaufnahme weist fertigungsbedingt ein axiales Spiel auf, das vom Pumpenkolben 4 bei einer Bewegungsumkehr dynamisch durchlaufen wird. Die in
Eine erste Ausführungsform eines elastisch verformbaren erfindungsgemäßen Federtellers 1 ist in den
Wie der Draufsicht der
Der radial innen liegende Stützring weist gegenüber einer Ebene E angehobene und abgesenkte Bereiche 9, 10 auf (siehe
Um ein Poka Yoke Einbauverhalten des Federtellers 1 zu erzielen, ist ferner vorgesehen, dass die Anhebung um ein Maß a und die Absenkung um ein Maß b erfolgt, welche gleich groß gewählt sind. Die angehobenen Bereiche 9 und die abgesenkten Bereiche 10 weisen demnach den gleichen axialen Abstand zur Ebene E auf (siehe
Ein zweites Ausführungsbeispiel eines erfindungsgemäßen Federtellers 1 ist den
Wie der
Ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Federtellers 1 ist der
Claims (10)
- Spring plate for a tappet assembly (2) of a high-pressure pump in a fuel injection system, wherein the spring plate (1) is in particular a bent and punched part, and wherein the spring plate (1) has a central recess (3) for receiving a pump piston (4), wherein the spring plate (1) furthermore has at least two arcuately running recesses (5) which are arranged around the central recess (3) and which serve for forming a radially inner support ring (6) and a radially outer support ring (7) which are connected to one another by means of substantially radially running webs (8),
characterized in that the radially inner support ring (6) has regions (9, 10) which are elevated and sunken relative to a plane (E) and which are arranged in each case with an angular spacing to the substantially radially running webs (8) and which give rise to a circular undulation of the inner support ring (6) and to elastic deformability of the spring plate (1). - Spring plate according to Claim 1,
characterized in that the angular spacing of the elevated and sunken regions (9, 10) to the substantially radially running webs (8) is selected to be equal in each case. - Spring plate according to 1 or 2,
characterized in that the elevated regions (9) are elevated relative to the plane (E) by a dimension (a), wherein the dimension (a) amounts to at most approximately 0.2 mm. - Spring plate according to one of the preceding claims,
characterized in that the sunken regions (10) are sunken relative to the plane (E) by a dimension (b), wherein the dimension (b) amounts to at most approximately 0.2 mm. - Spring plate according to one of the preceding claims,
characterized in that the radially inner support ring (6) has apertures (11) which are preferably arranged with uniform angular spacings to one another. - Spring plate according to Claim 5,
characterized in that the apertures (11) are formed in each case between an elevated and a sunken region (9, 10). - Spring plate according to one of the preceding claims,
characterized in that the radially inner support ring (6) has an aperture (12) which connects the central recess (3) to an eccentrically arranged recess (13). - Spring plate according to Claim 7,
characterized in that the eccentrically arranged recess (13) has a larger diameter than the central recess (3). - High-pressure pump for a fuel inj.ection system, having at least one pump element comprising a spring plate (1) according to one of the preceding claims, wherein the spring plate (1) is a constituent part of a tappet assembly (2) by means of which a pump piston (4), which is guided such that it can perform stroke movements, is supported indirectly on a cam (14) or eccentric of a drive shaft (15), by means of which the pump piston (4) can be driven in a reciprocating movement counter to the spring force of a restoring spring (16).
- High-pressure pump according to Claim 9,
characterized in that the spring plate (1) is supported by means of the radially inner support ring (6) on the pump piston (4) and by means of the radially outer support ring (7) on a tappet body (17) of the tappet assembly (2).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011017573A DE102011017573A1 (en) | 2011-04-27 | 2011-04-27 | Spring plate for a plunger assembly of a high pressure pump and high pressure pump |
PCT/EP2012/053972 WO2012146427A1 (en) | 2011-04-27 | 2012-03-08 | Spring washer for a plunger assembly of a high pressure pump and high pressure pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2702270A1 EP2702270A1 (en) | 2014-03-05 |
EP2702270B1 true EP2702270B1 (en) | 2017-07-05 |
Family
ID=45808987
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12707348.4A Active EP2702270B1 (en) | 2011-04-27 | 2012-03-08 | Spring washer for a plunger assembly of a high pressure pump and high pressure pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2702270B1 (en) |
CN (1) | CN103492714B (en) |
DE (1) | DE102011017573A1 (en) |
WO (1) | WO2012146427A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITMI20131903A1 (en) * | 2013-11-15 | 2015-05-16 | Bosch Gmbh Robert | HIGH PRESSURE PUMP FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE |
DE102019132343A1 (en) * | 2019-01-29 | 2020-07-30 | Rpc Bramlage Gmbh | Dispenser for dispensing flowable, for example liquid or pasty masses |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH10507982A (en) * | 1993-07-23 | 1998-08-04 | アイティーティー・オートモーティブ・ヨーロップ・ゲーエムベーハー | Hydraulic brake system with brake slip control and traction slip control |
IT239879Y1 (en) * | 1996-12-23 | 2001-03-13 | Elasis Sistema Ricerca Fiat | REFINEMENTS TO A PISTON PUMP, IN PARTICULAR TO A RADIAL APISTON PUMP FOR THE FUEL OF AN INTERNAL COMBUSTION ENGINE. |
DE19804275A1 (en) * | 1998-02-04 | 1999-08-12 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel supply |
DE10147981A1 (en) * | 2001-09-28 | 2003-04-24 | Siemens Ag | Connecting element for piston movable inside cylinder by means of re-adjusting element, consists of two parts with first part in piston cavity |
DE10355027A1 (en) * | 2003-11-25 | 2005-06-23 | Robert Bosch Gmbh | High-pressure pump, in particular for a fuel injection device of an internal combustion engine |
DE102009027689A1 (en) * | 2009-07-14 | 2011-01-20 | Robert Bosch Gmbh | Fuel high-pressure pump for fuel injection system of internal-combustion engine of motor vehicle, has slots extending from central through-hole of spring disk, which is supported at guided piston in axial direction |
DE102010038468A1 (en) * | 2010-07-27 | 2012-02-02 | Robert Bosch Gmbh | high pressure pump |
-
2011
- 2011-04-27 DE DE102011017573A patent/DE102011017573A1/en not_active Withdrawn
-
2012
- 2012-03-08 EP EP12707348.4A patent/EP2702270B1/en active Active
- 2012-03-08 WO PCT/EP2012/053972 patent/WO2012146427A1/en active Application Filing
- 2012-03-08 CN CN201280020065.1A patent/CN103492714B/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
DE102011017573A1 (en) | 2012-10-31 |
CN103492714B (en) | 2016-10-12 |
CN103492714A (en) | 2014-01-01 |
EP2702270A1 (en) | 2014-03-05 |
WO2012146427A1 (en) | 2012-11-01 |
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