EP2137402B1 - High-pressure pump for delivering fuel comprising a torsion-decoupled compression spring element in the plunger unit - Google Patents
High-pressure pump for delivering fuel comprising a torsion-decoupled compression spring element in the plunger unit Download PDFInfo
- Publication number
- EP2137402B1 EP2137402B1 EP08708238A EP08708238A EP2137402B1 EP 2137402 B1 EP2137402 B1 EP 2137402B1 EP 08708238 A EP08708238 A EP 08708238A EP 08708238 A EP08708238 A EP 08708238A EP 2137402 B1 EP2137402 B1 EP 2137402B1
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- EP
- European Patent Office
- Prior art keywords
- spring element
- pressure pump
- compression spring
- contact face
- surface coating
- 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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Classifications
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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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/445—Selection of particular materials
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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
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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
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
- F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
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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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
Definitions
- the present invention relates to a high-pressure pump, in particular for conveying fuel for a common-rail fuel injection system according to the type defined in more detail in the preamble of claim 1 (US Pat. DE-A-4 227 853 ).
- High pressure pumps for the promotion of fuel which are used for common rail fuel injection systems, are generally known.
- the high-pressure pumps are used to provide a high-pressure fuel within the common rail, which are acted upon by service bridges up to 2 Kbar and more. Therefore, special requirements are placed on the high-pressure pumps in order to promote the fuel in an efficient manner to the said pressures.
- the high-pressure pumps are usually driven via a coupling with the crankshaft of the internal combustion engine, wherein the high-pressure pump can be designed according to the principle of a cam drive. These include a camshaft having a cam geometry which displaces a picking element into a lifting movement in the direction of a lifting axis, and thus a pump piston connected to the picking element is set in a lifting movement.
- the pump piston can cooperate with this to promote the fuel.
- the pump piston is guided in a liftable manner in the pump body or in the cylinder head, and communicates with the tapping element at least via a roller shoe.
- the tapping element is usually designed as a roller, which rolls over the cam geometry.
- the arrangement of the roller in operative connection with the cam geometry is advantageous, since forms a line contact between the roller and the cam geometry, which has a high load capacity. In addition, only rolling movements take place, which are wear-minimized compared to sliding movements.
- the tapping element in the form of the roller is pressed to guide it on the cam geometry by means of a compression spring element against this, whereby at the same time the return stroke of the pump piston is ensured.
- Such compression spring elements are designed as coil springs and extend between a collar within the cylinder head and the so-called roller shoe in which the roller is received.
- linear guides have minimal play, which is comparatively large, and the line contact between the pick-off element and the cam geometry also remains unaffected. This circumstance leads to premature wear of the high pressure pump, which is undesirable in view of the required operating time and reliability of the high pressure pump.
- the invention provides the technical teaching that the at least one contact surface between the compression spring element and the plunger device and / or the adjoining surface of the compression spring element comprises a frictional force minimized surface coating to create a Torsionsentkopplung the compression spring element.
- the advantage of the solution according to the invention lies in a decoupling of the torsional movement of the compression spring element from the plunger device.
- the rotation accompanying the compression of the compression spring element can not be transferred further to the plunger device in the case of a contact surface with a friction-minimized surface coating, so that rotation of the plunger device, and thus rotation of the pick-off element on the cam geometry, are no longer caused by the torsion of the compression spring element can.
- the compression spring element is received between the cylinder head and the plunger guide, so that one end of the compression spring element is supported against a receiving contour in the plunger guide.
- This AufwcDesign within the ram guide forms the contact surface, which includes the frictional force minimized surface coating.
- this may also be formed on the part of the compression spring element, so that the surface of the compression spring element, which is adjacent to the tappet guide, having the friction-minimized surface coating.
- the plunger device comprises a Andruekusionnelement, against which the compression spring element is brought into abutment, wherein at least one flat surface of the An réelleusionn institutes forms the contact surface with the frictional force minimized surface coating.
- the An réelleusionnelement is annular and has two opposing planar surfaces, so that a planar surface of the contact surface in the tappet guide and the other planar surface to the end of the compression spring elements, adjacent.
- the opposite plane surface or both planar surfaces of Andruekusionn be provided with a frictional force minimized surface coating.
- the Anhuiludenelement can also be connected on one side rotationally fixed to the compression spring element, so that a defined sliding movement of the opposite plane surface of the Antikinnides can take place relative to the plunger guide. If the compression spring element is compressed, then a torsion in the compression spring element can be caused, which is compensated between the Antikinnelement and the tappet guide.
- the tapping element is designed as a roller element and the tappet device further comprises a tappet guide with a roller shoe inserted into it, on which the contact surface is formed with the friction-minimized surface coating itself.
- the contact surface with the friction-minimized surface coating can be formed both on the pressure disk element and on the tappet guide itself, whereby a combination of the respective contact surfaces with a respective friction-minimized surface coating is possible.
- the advantage can be used to select different surface coatings, which slide on each other, so that a tribologically optimized friction pairing is formed.
- a spring disk element is arranged rotationally fixed thereto, which is flush with the contact surface of the tappet guide.
- the spring disk element can be cohesively, positively or by means of connecting elements attached to the compression spring element, so that the spring disk element is likewise designed as a planar ring contour, and forms an annular contact surface.
- the adjacent to the contact surface of the tappet guide contact surface of the spring disk element comprises the frictional force minimized surface coating.
- An even more advantageous embodiment of the present invention comprises both a spring disk element arranged on the end side of the compression spring element and a pressure disk element, so that the pressure disk element is arranged between the spring disk element and the tappet guide, and the contact surface of the compression spring element adjoins the contact surface of the spring disk element.
- four contact surfaces with a respective friction-minimized surface coating in a stack arrangement can adjoin one another, wherein the pressure-disk element is located between the spring-disk element and the tappet guide.
- the friction-minimized surface coating is applied to the at least one contact surface by means of a PVD process, a CVD process, a galvanic process or a chemical process. Furthermore, there is the possibility that the friction-minimized surface coating comprises a bonded coating and / or a dry lubricant applied to the contact surface.
- the friction-minimized Surface coating may also be a hard coating, such as a titanium oxide coating, a zirconium oxide coating, a silicon oxide coating, a titanium carbide coating or a titanium nitride coating. Furthermore, it is possible to provide innovative PVD hard coatings such as TiMgN coatings.
- a combination of friction-minimized surface coatings and a surface-layer treatment of the respective contact surface should also be provided as an advantageous possibility within the scope of the present invention.
- Particularly advantageous are titanium carbide coatings, which are characterized by a very high hardness, coupled with a low coefficient of friction and highest adhesion.
- Titanium nitrite coatings are characterized by high hardness, high toughness and a very low tendency to weld on, so that seizing and deposit formation can be avoided. Furthermore, good corrosion and oxidation properties are advantageous.
- the plunger device which comprises the compression spring element, is located inside the pump body, which is filled with fuel. Therefore, the fuel may act as a lubricant, so that the surface coating cooperates with the lubricating effect of the fuel. Therefore, the surface coating should have a corresponding resistance to the fuel, which is particularly a diesel fuel.
- a further surface coating may be mentioned a titanium-aluminum nitride coating, wherein a chromium nitride coating is also a possible hard material coating.
- These coatings are characterized in particular by a very high chemical and thermal stability, in which case the chromium nitrite coating has a low tendency to adhesion, since the arrangement of the compression spring element can have locally high surface pressures in operative connection with the pressure disk element or the spring disk element Adhesion tendency is advantageous.
- a frictional force-minimized surface coating in the form of a monolayer, wherein also binary layers (Ti (C, N)), multilayer coatings (TiC / TiN) or graded coatings (TiC / Ti (C, N) / TiN) represent a possible variant.
- the friction-minimized surface coating according to the invention is not limited to a specific layer system, but comprises several different layer systems.
- the sliding movement comprises an oscillating rotational movement in small angular ranges, since at each stroke of the roller shoe 15 there is a torsion of the compression spring element 7 relative to the tipping guide 10.
- This rotation of the compression spring element 7 is thus compensated between the contact surfaces 8a, 8b, 8c and 8d, since the contact surfaces are minimized friction and allow a sliding movement to each other, the sliding causes minimal or even in connection with the lubricating effect of the fuel no significant frictional force.
- the Verwarne Trent of the compression spring element 7 is not transmitted to the tappet guide 10 so that it does not transmit the rotational movement further to the tapping element 2, and the line contact between the tapping element 2 and the cam geometry 4 is maintained on the camshaft 3.
- the invention is not limited in its execution to the above-mentioned preferred Au Unitsbeispiel. Rather, a number of variants is conceivable, which makes use of the solution shown in the scope of claim 1.
Abstract
Description
Die vorliegende Erfindung betrifft eine Hochdruckpumpe, insbesondere zur Förderung von Kraftstoff für ein Common- Rail- Kraftstoffeinspritzsystem gemäß der im Oberbegriff des Anspruchs 1 näher definierten Art (
Allgemein bekannt sind Hochdruckpumpen zur Förderung von Kraftstoff, welche für Common-Rail- Kraftstoffeinspritzsysteme Anwendung finden. Die Hochdruckpumpen dienen zur Bereitstellung eines unter Hochdruck stehenden Kraftstoffs innerhalb des Common- Rail, welche mit Betriebsbrücken bis zu 2 Kbar und mehr beaufschlagt sind. Daher sind an die Hochdruckpumpen besondere Anforderungen gestellt, um auf effiziente Weise den Kraftstoff auf die genannten Drücke zu fördern. Angetrieben werden die Hochdruckpumpen üblicherweise über eine Kopplung mit der Kurbelwelle der Brennkraftmaschine, wobei die Hochdruckpumpe nach dem Prinzip eines Nockentriebs ausgelegt sein kann. Diese umfassen eine Nockenwelle mit einer Nockengeometrie, die ein Abgriffselement in eine Hubbewegung in Richtung einer Hubachse versetzt, und somit ein mit dem Abgriffselement verbundener Pumpenkolben in Hubbewegung versetzt wird. Über ein in einem Zylinderkopf eingebrachten Ventiltrieb kann der Pumpenkolben mit diesem zusammenwirken, um den Kraftstoff zu fördern. Der Pumpenkolben ist im Pumpenkörper oder im Zylinderkopf hubbeweglich geführt, und steht wenigstens über einen Rollenschuh mit dem Abgriffselement in Verbindung. Das Abgriffselement ist meist als eine Rolle ausgeführt, welche über der Nockengeometrie abwälzt. Die Anordnung der Rolle in Wirkverbindung mit der Nockengeometrie ist von Vorteil, da sich zwischen der Rolle und der Nockengeometrie eine Linienberührung bildet, welche eine hohe Tragfähigkeit aufweist. Zudem finden nur Wälzbewegungen statt, welche gegenüber Gleitbewegungen verschleißminimiert sind. Das Abgriffselement in Gestalt der Rolle wird zur Führung desselben auf der Nockengeometrie mittels eines Druckfederelementes gegen diese gedrückt, womit zugleich der Rückhub des Pumpenkolbens sichergestellt wird. Derartige Druckfederelemente sind als Spiralfedern ausgeführt und erstrecken sich zwischen einem Bund innerhalb des Zylinderkopfes und dem so genannten Rollenschuh, in dem die Rolle aufgenommen ist.High pressure pumps for the promotion of fuel, which are used for common rail fuel injection systems, are generally known. The high-pressure pumps are used to provide a high-pressure fuel within the common rail, which are acted upon by service bridges up to 2 Kbar and more. Therefore, special requirements are placed on the high-pressure pumps in order to promote the fuel in an efficient manner to the said pressures. The high-pressure pumps are usually driven via a coupling with the crankshaft of the internal combustion engine, wherein the high-pressure pump can be designed according to the principle of a cam drive. These include a camshaft having a cam geometry which displaces a picking element into a lifting movement in the direction of a lifting axis, and thus a pump piston connected to the picking element is set in a lifting movement. Via a valve train introduced in a cylinder head, the pump piston can cooperate with this to promote the fuel. The pump piston is guided in a liftable manner in the pump body or in the cylinder head, and communicates with the tapping element at least via a roller shoe. The tapping element is usually designed as a roller, which rolls over the cam geometry. The arrangement of the roller in operative connection with the cam geometry is advantageous, since forms a line contact between the roller and the cam geometry, which has a high load capacity. In addition, only rolling movements take place, which are wear-minimized compared to sliding movements. The tapping element in the form of the roller is pressed to guide it on the cam geometry by means of a compression spring element against this, whereby at the same time the return stroke of the pump piston is ensured. Such compression spring elements are designed as coil springs and extend between a collar within the cylinder head and the so-called roller shoe in which the roller is received.
Bei einer derartigen Anordnung einer Hochdruckpumpe zur Förderung von Kraftstoff nach dem Prinzip des Nockentriebs ergibt sich jedoch das Problem, dass bei Anwendung eines Druckfederelementes in Gestalt einer Spiralfeder durch die Kompression des Druckfederelementes eine Torsion auf den Verbund des Rollenschuhs, der Stößelführung, den Pumpenkolben und damit auch auf das Abgriffselement, d.h. die Rolle ausgeübt wird. Daher ergibt sich eine Verdrehneigung des Rollenschuhs sowie des Abgriffselementes, so dass die Linienberührung zwischen dem Abgriffselement und der Nockengeometrie nicht näher sichergestellt ist. Hierfür sind zwar Verdrehsicherungen zwischen der Stößeleinrichtung und dem Pumpenkörper in Form von Linearführungen bekannt, jedoch ist eine hinreichende Genauigkeit häufig nicht erreichbar. Auch Linearführungen weisen ein minimales Spiel auf, welches vergleichsweise groß ist, und der Linienkontakt zwischen dem Abgriffselement und der Nockengeometrie auch damit nicht gewährleistet bleibt. Dieser Umstand führt zu einem verfrühten Verschleiß der Hochdruckpumpe, was in Anbetracht der erforderlichen Betriebsdauer und der Zuverlässigkeit der Hochdruckpumpe nicht wünschenswert ist.In such an arrangement, a high-pressure pump for the promotion of fuel according to the principle of cam drive, however, the problem arises that when using a compression spring element in the form of a coil spring by the compression of the compression spring element torsion on the composite of the roller shoe, the plunger guide, the pump piston and thus also on the tapping element, ie the role is exercised. Therefore, there is a Verdrehneigung the roller shoe and the Abgriffselementes, so that the line contact between the Abgriffselement and the cam geometry is not ensured closer. Although this against rotation between the plunger device and the pump body in the form of linear guides are known, however, a sufficient accuracy is often not achievable. Also, linear guides have minimal play, which is comparatively large, and the line contact between the pick-off element and the cam geometry also remains unaffected. This circumstance leads to premature wear of the high pressure pump, which is undesirable in view of the required operating time and reliability of the high pressure pump.
Ferner ist es erforderlich, derartige Hubeinrichtungen aus wenigen Bauteilen aufzubauen und eine einfache Konstruktion zu gewährleisten. Anordnungen von torsionsminimierten Druckfederelementen, welche von der Bauart einer einfachen Spiralfeder abweichen, sind häufig sehr aufwendig ausgestaltet und bewirken dennoch nicht die torsionsfreie Kompression des Federbereiches.Furthermore, it is necessary to build such lifting devices from a few components and to ensure a simple construction. Arrangements of torsion-minimized compression spring elements, which differ from the design of a simple coil spring, are often designed very expensive and yet do not cause the torsion-free compression of the spring portion.
Es ist daher die Aufgabe der vorliegenden Erfindung, eine Hochdruckpumpe zur Förderung von Kraftstoff für eine Brennkraftmaschine zu schaffen, welche zum Erhalt der Linienberührung zwischen dem Abgriffselement und der Nockengeometrie eine verdrehfreie Führung der Stößeleinrichtung ermöglicht.It is therefore the object of the present invention to provide a high pressure pump for delivering fuel for an internal combustion engine, which allows for obtaining the line contact between the Abgriffselement and the cam geometry rotational guidance of the plunger device.
Diese Aufgabe wird ausgehend von einer Hochdruckpumpe zur Förderung von Kraftstoff für eine Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den abhängigen Ansprüchen angegeben.This object is achieved on the basis of a high-pressure pump for conveying fuel for an internal combustion engine according to the preamble of claim 1 in conjunction with its characterizing features. Advantageous developments of the invention are specified in the dependent claims.
Die Erfindung schießt die technische Lehre ein, dass die wenigstens eine Kontaktfläche zwischen dem Druckfederelement und der Stößeleinrichtung und/oder die an diese angrenzende Oberfläche des Druckfederelementes eine reibkraftminimierte Oberflächenbeschichtung umfasst, um eine Torsionsentkopplung des Druckfederelements zu schaffen.The invention provides the technical teaching that the at least one contact surface between the compression spring element and the plunger device and / or the adjoining surface of the compression spring element comprises a frictional force minimized surface coating to create a Torsionsentkopplung the compression spring element.
Der Vorteil der erfindungsgemäßen Lösung liegt in einer Entkopplung der Torsionsbewegung des Druckfederelementes von der Stößeleinrichtung. Die bei der Kompression des Druckfederelementes einhergehende Verdrehung derselben kann sich bei einer Kontaktfläche mit einer reibkraftminimierten Oberflächenbeschichtung nicht weiter auf die Stößeleinrichtung übertragen, so dass eine Verdrehung der Stößeleinrichtung, und damit eine Verdrehung des Abgriffselementes auf der Nockengeometrie nicht mehr durch die Torsion des Druckfederelementes hervorgerufen werden kann. Das Druckfederelement ist zwischen dem Zylinderkopf und der Stößelführung aufgenommen, so dass sich ein Ende des Druckfederelementes gegen eine Aufnahmekontur in der Stößelführung abstützt. Diese Aufnahmcstruktur innerhalb der Stößelführung bildet die Kontaktfläche, welche die reibkraftminimierte Oberflächenbeschichtung umfasst. Diese kann jedoch auch seitens des Druckfederetementes ausgebildet sein, so dass die Oberfläche des Druckfederelementes, die gegen die Stößelführung, angrenzt, die reibkraftminimierte Oberflächenbeschichtung aufweist.The advantage of the solution according to the invention lies in a decoupling of the torsional movement of the compression spring element from the plunger device. The rotation accompanying the compression of the compression spring element can not be transferred further to the plunger device in the case of a contact surface with a friction-minimized surface coating, so that rotation of the plunger device, and thus rotation of the pick-off element on the cam geometry, are no longer caused by the torsion of the compression spring element can. The compression spring element is received between the cylinder head and the plunger guide, so that one end of the compression spring element is supported against a receiving contour in the plunger guide. This Aufnahmcstruktur within the ram guide forms the contact surface, which includes the frictional force minimized surface coating. However, this may also be formed on the part of the compression spring element, so that the surface of the compression spring element, which is adjacent to the tappet guide, having the friction-minimized surface coating.
Gemäß einer vorteilhaften Weiterbildung der Anordnung der Stößeleinrichtung umfasst ein Andruekscheibenelement, gegen dass das Druckfederelement zur Anlage gebracht ist, wobei wenigstens eine Planfläche des Andruckscheibenelementes die Kontaktfläche mit der reibkraftminimierten Oberflächenbeschichtung bildet. Das Andruckscheibenelement ist ringförmig ausgebildet und weist zwei sich gegenüberliegende Planflächen auf, so dass eine Planfläche an die Kontaktfläche in der Stößelführung und die andere Planfläche an das Ende des Druckfederelemente, angrenzt. Zur Minimierung der Reibkraft und damit zur Entkopplung der Torsion zwischen dem Druekfederelement und der Stößelführung kann entweder die erste Planfläche, die gegenüberliegende Planfläche oder beide Planflächen des Andruekscheibenelementes mit einer reibkraftminimierten Oberflächenbeschichtung versehen sein. Jedoch kann das Andruckscheibenelement auch mit dem Druckfederelement einseitig verdrehfest verbunden sein, so dass eine definierte Gleitbewegung der gegenüberliegenden Planfläche des Andruckscheibenelementes relativ zur Stößelführung stattfinden kann. Wird das Druckfederelement komprimiert, so kann eine Torsion im Druckfederelement hervorgerufen werden, die zwischen dem Andruckscheibenelement und der Stößelführung ausgeglichen wird.According to an advantageous development of the arrangement of the plunger device comprises a Andruekscheibenelement, against which the compression spring element is brought into abutment, wherein at least one flat surface of the Andruckscheibenelementes forms the contact surface with the frictional force minimized surface coating. The Andruckscheibenelement is annular and has two opposing planar surfaces, so that a planar surface of the contact surface in the tappet guide and the other planar surface to the end of the compression spring elements, adjacent. To minimize the frictional force and thus to decouple the torsion between the Druekfederelement and the tappet guide either the first planar surface, the opposite plane surface or both planar surfaces of Andruekscheibenelementes be provided with a frictional force minimized surface coating. However, the Andruckscheibenelement can also be connected on one side rotationally fixed to the compression spring element, so that a defined sliding movement of the opposite plane surface of the Andruckscheibenelementes can take place relative to the plunger guide. If the compression spring element is compressed, then a torsion in the compression spring element can be caused, which is compensated between the Andruckscheibenelement and the tappet guide.
Es ist von Vorteil, dass das Abgriffselement als Rollenelement ausgebildet ist und die Stößeleinrichtung ferner eine Stößelführung mit einem in diese eingesetzten Rollenschuh umfasst, an welchem die Kontaktfläche mit der reibkraftminimierten Oberflächenbeschichtung selbst ausgebildet ist. Damit wird eine weitere Möglichkeit aufgezeigt, dass die Kontaktfläche mit der reibkraftminimierten Oberflächenbeschichtung sowohl am Andruckscheibenelement als auch an der Stößelführung selbst ausgebildet sein kann, wobei auch eine Kombination der jeweiligen Kontaktflächen mit einer jeweiligen reibkraftminimierten Oberflächenbeschichtung möglich ist. Hier kann insbesondere der Vorteil genutzt werden, verschiedene Oberflächenbeschichtungen zu wählen, welche aufeinander abgleiten, so dass eine tribologisch optimierte Reibpaarung gebildet wird.It is advantageous that the tapping element is designed as a roller element and the tappet device further comprises a tappet guide with a roller shoe inserted into it, on which the contact surface is formed with the friction-minimized surface coating itself. This shows a further possibility that the contact surface with the friction-minimized surface coating can be formed both on the pressure disk element and on the tappet guide itself, whereby a combination of the respective contact surfaces with a respective friction-minimized surface coating is possible. Here in particular the advantage can be used to select different surface coatings, which slide on each other, so that a tribologically optimized friction pairing is formed.
Es ist ferner von Vorteil, dass endseitig am Druckfederelement ein Federscheibenelement verdrehfest an diesem angeordnet ist, welches plan an die Kontaktfläche der Stößelführung angrenzt. Das Federscheibenelement kann stoffschlüssig, formschlüssig oder mittels Verbindungselementen am Druckfederelement angebracht sein, so dass das Federscheibenelement ebenfalls als plane Ringkontur ausgebildet ist, und eine ringförmige Kontaktfläche bildet. Vorteilhafterweise umfasst die an die Kontaktfläche der Stößelführung angrenzende Kontaktfläche des Federscheibenelementes die reibkraftminimierte Oberflächenbeschichtung. Eine noch vorteilhaftere Ausführungsform der vorliegenden Erfindung umfasst sowohl ein endseitig an das Druckfederelement angeordnetes Federscheibenelement und ein Andruckscheibenelement, so dass das Andruckscheibenelement zwischen dem Federscheibenelement und der Stößelführung angeordnet ist, und die Kontaktfläche des Druckfederelementes an die Kontaktfläche des Federscheibenelementes angrenzt. Gemäß der letztgenannten Anordnung können vier Kontaktflächen mit einer jeweiligen reibkraftminimierten Oberflächenbeschichtung in einer Stapelanordnung aneinander angrenzen, wobei sich das Andruckscheibenelement zwischen dem Federscheibenelement und der Stößelführung befindet.It is also advantageous that at the end of the compression spring element, a spring disk element is arranged rotationally fixed thereto, which is flush with the contact surface of the tappet guide. The spring disk element can be cohesively, positively or by means of connecting elements attached to the compression spring element, so that the spring disk element is likewise designed as a planar ring contour, and forms an annular contact surface. Advantageously, the adjacent to the contact surface of the tappet guide contact surface of the spring disk element comprises the frictional force minimized surface coating. An even more advantageous embodiment of the present invention comprises both a spring disk element arranged on the end side of the compression spring element and a pressure disk element, so that the pressure disk element is arranged between the spring disk element and the tappet guide, and the contact surface of the compression spring element adjoins the contact surface of the spring disk element. According to the last-mentioned arrangement, four contact surfaces with a respective friction-minimized surface coating in a stack arrangement can adjoin one another, wherein the pressure-disk element is located between the spring-disk element and the tappet guide.
Vorteilhafterweise ist die reibkraftminimierte Oberflächenbeschichtung mittels eines PVD-Verfahrens, eines CVD-Verfahrens, eines galvanischen Verfahrens oder eines chemischen Verfahrens auf die wenigstens eine Kontaktfläche aufgebracht. Ferner besteht die Möglichkeit, dass die reibkraftminimierte Oberflächenbeschichtung einen Gleitlack und/oder einen auf die Kontaktfläche aufgebrachten Trockenschmierstoff umfasst. Die reibkraftminimierte Oberflächenbeschichtung kann auch eine Hartstoffbeschichtung sein, wie beispielsweise eine Titan-Oxid-Beschichtung, eine Zirkon-Oxid-Beschichtung, eine Silizium-Oxid-Beschichtung, eine Titankarbid-Beschichtung oder eine Titannitrit-Beschichtung. Weiterhin besteht die Möglichkeit, innovative PVD- Hartstoff- Beschichtungen wie TiMgN- Beschichtungen vorzuschen. Auch eine Kombination von reibkraftminimierten Oberflächenbeschichtungen und einer Randschichtbehandlung der jeweiligen Kontaktoberfläche ist als vorteilhafte Möglichkeit im Rahmen der vorliegenden Erfindung vorzusehen. Besonders vorteilhaft sind Titankarbid-Beschichtungen, welche sich durch eine sehr hohe Härte, gepaart mit einem niedrigen Reibkoeffizient und höchster Haftfestigkeit, auszeichnen. Titannitrit-Beschichtungen zeichnen sich hingegen durch eine hohe Härte, eine hohe Zähigkeit und eine sehr geringe Neigung zu Aufschweißungen aus, so dass ein Fressen und eine Belagbildung vermieden werden kann. Ferner sind gute Korrosions- und Oxidationseigenschaften vorteilhaft.Advantageously, the friction-minimized surface coating is applied to the at least one contact surface by means of a PVD process, a CVD process, a galvanic process or a chemical process. Furthermore, there is the possibility that the friction-minimized surface coating comprises a bonded coating and / or a dry lubricant applied to the contact surface. The friction-minimized Surface coating may also be a hard coating, such as a titanium oxide coating, a zirconium oxide coating, a silicon oxide coating, a titanium carbide coating or a titanium nitride coating. Furthermore, it is possible to provide innovative PVD hard coatings such as TiMgN coatings. A combination of friction-minimized surface coatings and a surface-layer treatment of the respective contact surface should also be provided as an advantageous possibility within the scope of the present invention. Particularly advantageous are titanium carbide coatings, which are characterized by a very high hardness, coupled with a low coefficient of friction and highest adhesion. Titanium nitrite coatings, on the other hand, are characterized by high hardness, high toughness and a very low tendency to weld on, so that seizing and deposit formation can be avoided. Furthermore, good corrosion and oxidation properties are advantageous.
Die Stößeleinrichtung, welche das Druckfederelement umfasst, befindet sich innerhalb des Pumpenkörpers, welcher mit Kraftstoff gefüllt ist. Daher kann der Kraftstoff als Schmiermittel zur Wirkung kommen, so dass die Oberflächenbeschichtung mit der Schmierwirkung des Kraftstoffs zusammenwirkt. Daher sollte die Oberflächenbeschichtung eine entsprechende Beständigkeit gegenüber dem Kraftstoff, welcher insbesondere ein Dieselkraftstoff ist, aufweisen. Als eine weitere Oberflächenbeschichtung kann eine Titan-Aluminiumnitrit-Beschichtung genannt werden, wobei ferner eine Chromnitrit-Beschichtung eine mögliche Hartstoff-Beschichtung darstellt. Diese Beschichtungen zeichnen sich insbesondere durch eine sehr hohe chemische und thermische Stabilität aus, wobei gerade die Chromnitrit-Beschichtung eine geringe Adhäsionstendenz aufweist, da die Anordnung des Druckfederelementes in Wirkverbindung mit dem Andruckscheibenelement bzw. dem Federscheibenelement lokal hohe Flächenpressungen aufweisen kann, so dass eine geringe Adhäsionstendenz vorteilhaft ist.The plunger device, which comprises the compression spring element, is located inside the pump body, which is filled with fuel. Therefore, the fuel may act as a lubricant, so that the surface coating cooperates with the lubricating effect of the fuel. Therefore, the surface coating should have a corresponding resistance to the fuel, which is particularly a diesel fuel. As a further surface coating may be mentioned a titanium-aluminum nitride coating, wherein a chromium nitride coating is also a possible hard material coating. These coatings are characterized in particular by a very high chemical and thermal stability, in which case the chromium nitrite coating has a low tendency to adhesion, since the arrangement of the compression spring element can have locally high surface pressures in operative connection with the pressure disk element or the spring disk element Adhesion tendency is advantageous.
Es kann auch eine reibkraftminimierte Oberflächenbeschichtung in Gestalt einer Mono-Schicht zur Anwendung kommen, wobei auch binäre Schichten (Ti(C,N)), Mehrlagenschichten (TiC/TiN) oder gradierte Schichten (TiC/Ti(C,N)/TiN) eine mögliche Variante darstellen. Damit ist die erfindungsgemäße reibkraftminimierte Oberflächenbeschichtung nicht auf ein bestimmtes Schichtsystem begrenzt, sondern umfasst mehrere verschiedene Schichtsysteme.It is also possible to use a frictional force-minimized surface coating in the form of a monolayer, wherein also binary layers (Ti (C, N)), multilayer coatings (TiC / TiN) or graded coatings (TiC / Ti (C, N) / TiN) represent a possible variant. Thus, the friction-minimized surface coating according to the invention is not limited to a specific layer system, but comprises several different layer systems.
Um die Vorteile der erfindungsgemäßen Lösung der reibkraftminimierten Oberflächenbeschichtung auch für andere beanspruchte Oberflächen zu nutzen, kann im Rahmen der vorliegenden Erfindung vorgesehen sein, das gesamte Druckfederelement sowie die gesamte Stößelführung und auch das gesamte Andruckscheibenelement sowie das Federscheibenelement vollständig mit einer Oberflächenbeschichtung zu versehen. Gerade die Stößelführung gleitet innerhalb des Pumpenkörpers oder des Zylinderkopfes in einer Führungsbohrung, so dass eine ganzheitliche Beschichtung der Bauteile ebenfalls von Vorteil ist.In order to use the advantages of the inventive solution of friction-minimized surface coating for other claimed surfaces, can in Be provided within the scope of the present invention, to provide the entire compression spring element and the entire plunger guide and also the entire Andruckscheibenelement and the spring washer element completely with a surface coating. Especially the plunger guide slides within the pump body or the cylinder head in a guide bore, so that a holistic coating of the components is also beneficial.
Weitere, die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt.Further, measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to FIGS.
Es zeigt:
-
Fig. 1 eine quergeschnittene Ansicht einer Hochdruckpumpe mit einer Stößeleinrichtung sowie einem Druckfederelement, einer Stößelführung mit einem eingesetzten Rollenschuh und einem zwischen dem Druckfederelement und der Stößelführung angeordneten Andruckscheibenelement; -
Fig. 2 eine quergeschnittene Ansicht des erfindungsgemäßen Andruckscheibenelementes mit einer ersten sowie einer zweiten Kontaktfläche; und -
Fig. 3 eine quergeschnittene Ansicht der Anordnung der Stößeleinrichtung mit jeweiligen erfindungsgemäßen Kontaktflächen, wobei das Druckfederelement, das Andruckscheibenelement sowie ein Federscheibenelement jeweils in einer voneinander gelösten Anordnung dargestellt ist. -
Fig. 1 zeigt eine quergeschnittene Seitenansicht einer Hochdruckpumpe 1, wie sie bei Common-Rail- Kraftstoffeinspritzsystemen für Dieselmotoren zum Einsatz kommt. Die Hochdruckpumpe 1 dient zur Förderung von Dieselkraftstoff, um diesen mit einem hohen Druck einem Common-Rail zur Verfügung zu stellen. Die Hochdruckpumpe 1umfasst ein Abgriffselement 2, welches über einer auf einer Nockenwelle 3 angeordneten Nockengeometrie 4 abwälzt.Die Nockenwelle 3 wird motorseitig angetrieben, und umfasst wenigstens eine Nockengeometrie 4, wobei diese eine oder mehrere auf den Umfang gleichverteilt angeordnete Nocken umfasst. Dadurchübt das Abgriffselement 2 eine Hubbewegung inRichtung einer Hubachse 5 aus, wobei die Hubbewegung des Abgriffselementes 2 auf eine Stößeleinrichtung 6 übertragen wird.Die Stößeleinrichtung 6 umfasst ein Druckfederelement 7 sowie einen Pumpenkolben 12,wobei das Abgriffselement 2 innerhalb einer Stößelführung 10 aufgenommen ist, welche gemeinsammit dem Rollenschuh 15 ebenfalls Bestandteil der Stößeleinrichtung 6 ist. Zwischen dem Druckfederelement 7 und der Stößelführung 10 ist ein Andruckscheibenelement 9 angeordnet, welches quergeschnitten dargestellt und in Gestalt einer Planscheibe ausgeführt ist. Mittigaus dem Rollenschuh 10 erstreckt sich der Pumpenkolben 12, welcher innerhalb eines Zylinderkopfes 13 geführt ist, und mit einerVentileinrichtung im Zylinderkopf 13 zur Förderung des Kraftstoffes zusammenwirkt. Die Hochdruckpumpe 1 umfasst imWesentlichen einen Pumpenkörper 14, wobei der Zylinderkopf 13 aufden Pumpenkörper 14 dichtend aufgesetzt ist. Daher bildet sowohl der Pumpenkörper 14 als auch der Zylinderkopf 13 die Führungseinrichtung der Hubbewegung der Stößeleinrichtung 6 inRichtung der Hubachse 5, wobei eine Verdrehsicherung der Stößeleinrichtung 6 zur Vermeidung einer Verdrehung um dieHubachse 5 nicht näher dargestellt ist. -
Fig. 2 zeigt eine vergrößerte Darstellung der Andruckscheibenelementes 9, welche sich - mit Blick aufFig. 1 - zwischen dem Druckfederelement und der Stößelführung befindet. Das Andruckscheibenelement 9 umfasst eine erfindungsgemäße Kontaktfläche 8a sowie eine gegenüberliegende weitere Kontaktfläche 8b, welche eine reibkraftminimierte Oberflächenbeschichtung aufweist. Das Andruckscheibenelement 9 erstreckt sich ringförmig um dieHubachse 5, so dass sich durch das Andruckscheibenelement 9 der Pumpenkolben erstrecken kann.Die reibkraftminimierten Kontaktflächen 8a und 8b grenzen jeweils an das Druckfederelement sowie an die Stößelführung an, so dass entweder die erste Kontaktfläche 8a oder diezweite Kontaktfläche 8b oder beide Kontaktflächen die erfindungsgemäße reibkraftminimierte Oberflächenbeschichtung aufweisen. -
Fig. 3 zeigt eine mögliche Anordnung einer erfindungsgemäßen Stößeleinrichtung 6 mit einem Andruckscheibenelement 9, welches zwischen der Stößelführung 10 sowie einem Federscheibenelement 11 angeordnet ist, wobei inder Stößelführung 10der Rollenschuh 15 zur Aufnahme des Abgriffselementes 2 eingesetzt ist.Das Federscheibenelement 11 ist mit dem Druckfederelement 7 in Verbindung gebracht, wobei die Verbindung entweder stoffschlüssig (Schweißen, Löten, Kleben) oder formschlüssig (Verpressen, Verkeilen oder Verstemmen) mit dem Druckfederelement verbunden ist.Das Federscheibenelement 11 kann eine weitere erfindungsgemäße Kontaktfläche 8d umfassen, welche ebenfalls eine reibkraftminimierte Oberflächenbeschichtung aufweist. Ferner befindet sich auf der Stößelführung 10eine Kontaktfläche 8c, welche ebenfalls eine reibkraftminimierte Oberflächenbeschichtung aufweisen kann. GemäßFig. 3 ist ein Andruckscheibenelement 9zwischen dem Federscheibenelement 11 und der Stößelführung 10 eingebracht, wobei das Andruckscheibenelement 9 auch entfallen kann, so dass dieKontaktfläche 8d des Federscheibenetementes 11 direkt auf derKontaktfläche 8c der Stößelführung 10 angrenzt, und auf dieser abgleiten kann.
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Fig. 1 a cross-sectional view of a high-pressure pump with a plunger device and a compression spring element, a plunger guide with a roller shoe inserted and arranged between the compression spring element and the plunger guide Andruckscheibenelement; -
Fig. 2 a cross-sectional view of the Andruckscheibenelementes invention having a first and a second contact surface; and -
Fig. 3 a cross-sectional view of the arrangement of the plunger device with respective contact surfaces according to the invention, wherein the compression spring element, the Andruckscheibenelement and a spring washer element is shown in each case in a disassembled arrangement. -
Fig. 1 shows a cross-sectional side view of a high pressure pump 1, as used in common rail fuel injection systems for diesel engines. The high-pressure pump 1 serves to deliver diesel fuel in order to provide it with a common rail at high pressure. The high-pressure pump 1 comprises atapping element 2, which rolls over acam geometry 3 arranged on acamshaft 3. Thecamshaft 3 is driven on the engine side, and comprises at least one cam geometry 4, wherein these includes one or more evenly distributed on the circumference arranged cams. As a result, the tappingelement 2 exerts a lifting movement in the direction of a liftingaxis 5, wherein the lifting movement of the tappingelement 2 is transmitted to atappet device 6. Thetappet device 6 comprises a compression spring element 7 and apump piston 12, wherein the tappingelement 2 is received within atappet guide 10, which together with theroller shoe 15 is also part of thetappet device 6. Between the compression spring element 7 and thetappet guide 10, a Andruckscheibenelement 9 is arranged, which is shown cross-cut and executed in the form of a face plate. Centrally from theroller shoe 10, thepump piston 12 extends, which is guided within acylinder head 13, and cooperates with a valve device in thecylinder head 13 for conveying the fuel. The high-pressure pump 1 essentially comprises apump body 14, wherein thecylinder head 13 is placed sealingly on thepump body 14. Therefore, both thepump body 14 and thecylinder head 13, the guide device of the lifting movement of theplunger device 6 in the direction of the liftingaxis 5, wherein a rotation of theplunger device 6 to prevent rotation about the liftingaxis 5 is not shown in detail. -
Fig. 2 shows an enlarged view of the Andruckscheibenelementes 9, which - with respect toFig. 1 - Located between the compression spring element and the tappet guide. The Andruckscheibenelement 9 comprises acontact surface 8a according to the invention and an oppositefurther contact surface 8b, which has a frictional force-minimized surface coating. The Andruckscheibenelement 9 extends annularly around the liftingaxis 5, so that can extend through the Andruckscheibenelement 9 of the pump piston. The friction-minimized 8a and 8b respectively adjoin the compression spring element and the tappet guide, so that either thecontact surfaces first contact surface 8a or thesecond contact surface 8b or both contact surfaces have the friction-minimized surface coating according to the invention. -
Fig. 3 shows a possible arrangement of aplunger device 6 according to the invention with a Andruckscheibenelement 9, which is disposed between theplunger guide 10 and aspring washer element 11, wherein in theplunger guide 10 of theroller shoe 15 is used to receive the pick-offelement 2. Thespring disk element 11 is brought into contact with the compression spring element 7, wherein the connection either cohesively (welding, soldering, gluing) or form-fitting (pressing, wedging or caulking) with is connected to the compression spring element. Thespring disk element 11 may comprise afurther contact surface 8d according to the invention, which likewise has a friction-minimized surface coating. Further, located on thetappet guide 10, acontact surface 8c, which may also have a frictional force minimized surface coating. According toFig. 3 a Andruckscheibenelement 9 is inserted between thespring disk element 11 and thetappet guide 10, wherein the Andruckscheibenelement 9 can also be omitted, so that thecontact surface 8d of theFederscheibenetementes 11 directly adjacent to thecontact surface 8c of thetappet guide 10, and can slide on this.
Die Gleitbewegung umfasst dabei eine oszillierende Rotationsbewegung in kleinen Winkelbereichen, da bei jedem Hub des Rollenschuhs 15 eine Torsion des Druckfederelementes 7 gegenüber der Stußelführung 10 erfolgt. Diese Verdrehung des Druckfederelementes 7 wird damit zwischen den Kontaktflächen 8a, 8b, 8c sowie 8d ausgeglichen, da die Kontaktflächen reibkraftminimiert sind und eine Gleitbewegung zueinander zulassen, wobei die Gleitbewegung minimale oder sogar in Verbindung mit der Schmierwirkung des Kraftstoffes keine nennenswerte Reibkraft hervorruft. Damit wird die Verdrehneigung des Druckfederelementes 7 nicht auf die Stößelführung 10 übertragen, so dass dieser die Drehbewegung ferner nicht auf das Abgriffselement 2 überträgt, und die Linienberührung zwischen dem Abgriffselement 2 und der Nockengeometrie 4 auf der Nockenwelle 3 beibehalten wird.The sliding movement comprises an oscillating rotational movement in small angular ranges, since at each stroke of the
Die Erfindung beschränkt sich in ihrer Ausführung nicht auf das vorstehend angegebene bevorzugte Auführungsbeispiel. Vielmehr ist eine Anzahl von Varianten denkbar, welche von der dargestellten Lösung im Rahmen des Anspruchs 1 Gebrauch macht.The invention is not limited in its execution to the above-mentioned preferred Auführungsbeispiel. Rather, a number of variants is conceivable, which makes use of the solution shown in the scope of claim 1.
Claims (8)
- High-pressure pump (1), in particular for the conveyance of fuel for a common-rail fuel injection system, comprising at least one cam drive with a pick-off element (2) which can be set in a lifting movement in the direction of a lifting axis (5) by a cam geometry (4) introduced into a camshaft (3), the lifting movement being transmittable to a plunger device (6), the plunger device (6) and the pick-off element (2) being acted upon with force in the direction of the cam geometry (4) by means of a compression-spring element (7), and the plunger device (6) having at least one contact face (8a, 8b, 8c, 8d) to which the compression-spring element (7) is contiguous, characterized in that the at least one contact face (8a, 8b, 8c, 8d) and/or that surface of the compression-spring element (7) which is contiguous to this comprise/comprises a surface coating having minimized frictional force, in order to provide a torsional decoupling of the compression-spring element (7).
- High-pressure pump (1) according to Claim 1, characterized in that the plunger device (6) comprises a pressure-washer element (9), against which the compression-spring element (7) is brought to bear, and at least one plane face of the pressure-washer element (9) forms the contact face (8a, 8b) with the surface coating having minimized frictional force.
- High-pressure pump (1) according to Claim 1 or 2, characterized in that the pick-off element (2) is designed as a roller element, and the plunger device (6) comprises, furthermore, a plunger guide (10), on which is formed the contact face (8c) with the surface coating having minimized frictional force.
- High-pressure pump (1) according to Claim 3, characterized in that a spring-washer element (11) is arranged on the end face of the compression-spring element (7) fixedly in terms of rotation on the latter and is continuous in a planar manner to the contact face (8c) of the plunger guide (10).
- High-pressure pump (1) according to Claim 3 or 4, characterized in that that contact face (8d) of the spring-washer element (11) which is contiguous to the contact face (8c) of the plunger guide (10) comprises a surface coating having minimized frictional force.
- High-pressure pump (1) according to Claim 4 or 5, characterized in that the pressure-washer element (9) is arranged between the spring-washer element (11) and the plunger guide (10), so that the contact face (8a, 8b) of the compression-spring element (7) is contiguous to the contact face (8d).
- High-pressure pump (1) according to one of the abovementioned claims, characterized in that the surface coating having minimized frictional force is applied by means of a PVD method, a CVD method, an electroplating method or a chemical method to the at least one contact face (8a, 8b, 8c, 8d).
- High-pressure pump (1) according to one of the abovementioned claims, characterized in that the surface coating having minimized frictional force comprises a slip lacquer and/or a dry lubricant applied to the contact face (8a, 8b, 8c, 8d).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102007012705A DE102007012705A1 (en) | 2007-03-16 | 2007-03-16 | High-pressure pump for conveying fuel with a torsion-decoupled compression spring element in the plunger device |
PCT/EP2008/050915 WO2008113626A1 (en) | 2007-03-16 | 2008-01-28 | High-pressure pump for delivering fuel comprising a torsion-decoupled compression spring element in the plunger unit |
Publications (2)
Publication Number | Publication Date |
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EP2137402A1 EP2137402A1 (en) | 2009-12-30 |
EP2137402B1 true EP2137402B1 (en) | 2010-11-24 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP08708238A Not-in-force EP2137402B1 (en) | 2007-03-16 | 2008-01-28 | High-pressure pump for delivering fuel comprising a torsion-decoupled compression spring element in the plunger unit |
Country Status (8)
Country | Link |
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US (1) | US20100101539A1 (en) |
EP (1) | EP2137402B1 (en) |
JP (1) | JP2010521620A (en) |
KR (1) | KR20090119977A (en) |
CN (1) | CN101636579B (en) |
AT (1) | ATE489554T1 (en) |
DE (2) | DE102007012705A1 (en) |
WO (1) | WO2008113626A1 (en) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102010001882A1 (en) * | 2010-02-12 | 2011-08-18 | Robert Bosch GmbH, 70469 | High-pressure fuel pump |
DE102010003886A1 (en) * | 2010-04-13 | 2011-10-13 | Robert Bosch Gmbh | high pressure pump |
DE102010020578A1 (en) * | 2010-05-14 | 2011-11-17 | Bayerische Motoren Werke Aktiengesellschaft | Device for driving an auxiliary unit |
DE102010038468A1 (en) * | 2010-07-27 | 2012-02-02 | Robert Bosch Gmbh | high pressure pump |
DE102011077766A1 (en) * | 2011-06-17 | 2012-12-20 | Elringklinger Ag | Actuating device for an exhaust gas flow control of an exhaust gas turbocharger |
DE102011086703A1 (en) * | 2011-11-21 | 2013-05-23 | Robert Bosch Gmbh | high pressure pump |
CN102539056A (en) * | 2011-12-31 | 2012-07-04 | 北京理工大学 | Sliding bearing oil film pressure measuring device |
NL2010455C2 (en) * | 2013-03-14 | 2014-09-16 | Glind Metrology B V | Hydraulic pressure calibrator and calibration method. |
JP2018031333A (en) * | 2016-08-26 | 2018-03-01 | 日立オートモティブシステムズ株式会社 | High-pressure fuel pump |
JP7058505B2 (en) * | 2018-01-09 | 2022-04-22 | ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング | Fuel supply pump |
KR102228818B1 (en) | 2019-09-17 | 2021-03-18 | (주)모토닉 | High pressure fuel pump and lpdi system with the same |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3143073A1 (en) * | 1981-10-30 | 1983-05-11 | Robert Bosch Gmbh, 7000 Stuttgart | INJECTION PUMP WITH ADJUSTABLE SPRAYING POINT |
DE3624134A1 (en) * | 1986-07-17 | 1988-01-21 | Bosch Gmbh Robert | INJECTION PUMP |
DE4227853C2 (en) * | 1992-08-22 | 1996-05-30 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines |
DE4227854B4 (en) * | 1992-08-22 | 2005-12-15 | Robert Bosch Gmbh | Fuel injection pump for internal combustion engines |
US5239951A (en) * | 1992-11-12 | 1993-08-31 | Ford Motor Company | Valve lifter |
DE19829547C2 (en) * | 1998-07-02 | 2002-03-28 | Bosch Gmbh Robert | Radial piston pump |
DE10106983A1 (en) * | 2001-02-15 | 2002-08-29 | Ina Schaeffler Kg | tappet |
CN2627233Y (en) * | 2003-05-21 | 2004-07-21 | 上海东维燃油喷射有限公司 | Tappet unit with locating slot and without ferrule |
DE10345089A1 (en) * | 2003-09-26 | 2005-04-21 | Bosch Gmbh Robert | Plunger for a high pressure pump and high pressure pump with at least one plunger |
DE102004048711B4 (en) * | 2004-10-06 | 2006-09-14 | Siemens Ag | Radial piston pump with roller tappet |
US7311087B2 (en) * | 2004-11-23 | 2007-12-25 | Cummins Inc. | Fuel pump with a guided tappet assembly and methods for guiding and assembly |
-
2007
- 2007-03-16 DE DE102007012705A patent/DE102007012705A1/en not_active Withdrawn
-
2008
- 2008-01-28 CN CN2008800085036A patent/CN101636579B/en not_active Expired - Fee Related
- 2008-01-28 KR KR1020097019255A patent/KR20090119977A/en not_active Application Discontinuation
- 2008-01-28 EP EP08708238A patent/EP2137402B1/en not_active Not-in-force
- 2008-01-28 DE DE502008001897T patent/DE502008001897D1/en active Active
- 2008-01-28 WO PCT/EP2008/050915 patent/WO2008113626A1/en active Application Filing
- 2008-01-28 AT AT08708238T patent/ATE489554T1/en active
- 2008-01-28 US US12/531,642 patent/US20100101539A1/en not_active Abandoned
- 2008-01-28 JP JP2009553984A patent/JP2010521620A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
DE102007012705A1 (en) | 2008-09-18 |
WO2008113626A1 (en) | 2008-09-25 |
US20100101539A1 (en) | 2010-04-29 |
CN101636579A (en) | 2010-01-27 |
JP2010521620A (en) | 2010-06-24 |
EP2137402A1 (en) | 2009-12-30 |
CN101636579B (en) | 2011-10-05 |
KR20090119977A (en) | 2009-11-23 |
ATE489554T1 (en) | 2010-12-15 |
DE502008001897D1 (en) | 2011-01-05 |
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