WO2018060158A1 - Tappet assembly for a radial piston pump, and radial piston pump - Google Patents

Tappet assembly for a radial piston pump, and radial piston pump Download PDF

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Publication number
WO2018060158A1
WO2018060158A1 PCT/EP2017/074287 EP2017074287W WO2018060158A1 WO 2018060158 A1 WO2018060158 A1 WO 2018060158A1 EP 2017074287 W EP2017074287 W EP 2017074287W WO 2018060158 A1 WO2018060158 A1 WO 2018060158A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller shoe
pump
plunger
plunger assembly
pressing
Prior art date
Application number
PCT/EP2017/074287
Other languages
German (de)
French (fr)
Inventor
Gerhard Meier
Marcel MEIXNER
Frank Maurer
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to CN201780060552.3A priority Critical patent/CN109790763A/en
Publication of WO2018060158A1 publication Critical patent/WO2018060158A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B4/00—Shrinkage connections, e.g. assembled with the parts at different temperature; Force fits; Non-releasable friction-grip fastenings
    • F16B4/004—Press fits, force fits, interference fits, i.e. fits without heat or chemical treatment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit

Definitions

  • the invention relates to a plunger assembly for a radial piston pump, in particular a high-pressure fuel pump, with the features of the preamble of claim 1.
  • the plunger assembly specified serves to support a pump piston of Ra ⁇ dialkolbenpumpe on a cam of a drive shaft.
  • the invention relates ei ⁇ ne radial piston pump, in particular a high-pressure fuel pump for supplying an internal combustion engine with fuel, with such a plunger assembly.
  • a plunger assembly for a high-pressure pump which has a plunger body with a receptacle and a in the
  • the roller shoe Including receiving the plunger body pressed roller shoe for rotatably supporting ei ⁇ ner role.
  • the roller shoe has a press excess with respect to the receptacle of the tappet body.
  • the plunger body forms a centering. By centering an automatic centering is achieved when pressing the roller shoe, which prevents a Schräginpressung.
  • the robustness of the press fit increases, since the press-in forces are not distorted, as is the case regularly with an oblique press.
  • the task is to provide a plunger assembly for a radial piston pump, in particular for a high-pressure fuel pump, indicate their robustness is further increased.
  • the plunger assembly is specified with the features of claim 1.
  • Advantageous developments of the invention can be found in the dependent claims.
  • a radial piston pump is proposed with such a plunger assembly.
  • the proposed plunger assembly is suitable for supporting a liftable pump piston of a radial piston pump, in particular a high-pressure fuel pump, on a cam of a drive shaft.
  • the plunger assembly comprises a hollow cylindrical plunger body and a roller shoe press-fitted into the plunger body for rotatably supporting a roller.
  • the roller shoe has a pressing oversize which varies in the pressing-in direction. This means that the roller shoe does not have a cylindrical excess pressure.
  • the varying excess pressure serves to optimize the surface pressure in the press fit. Because with a cylindrical excess pressure of the roller shoe, the surface pressure over the pressing surface is distributed unevenly. For example, creates an increased surface pressure at the edges of the roller shoe. This leads to voltage peaks in the tappet body, which have a negative effect on the robustness of the tappet assembly. Due to the varying excess pressure, voltage peaks in the tappet body can be avoided so that the robustness of the tappet assembly increases.
  • the roller shoe has a pressing excess, which decreases in the pressing-in direction. In this way, the pressing of the roller shoe is simplified in the plunger body. In addition, the edge region of the roller shoe is relieved, via which the roller shoe is pressed into the plunger body. Accordingly, no increased surface pressure is to be expected at least in this edge region.
  • the roller shoe is at least partially conical and / or bulbous in the pressing direction.
  • the roller shoe can also have a plurality of conical and / or bulbous shaped sections. For example, a plurality of conically shaped sections with different cone angle can follow each other. Furthermore, conical and / or bulbous shaped sections can be formed by a cylindrical interrupted section. The section in which the roller shoe has its greatest pressing interference is preferably arranged at a distance from at least one edge of the roller shoe.
  • the roller shoe has at least one section without excess press. This means that in this area no press-in forces act on the plunger body, so that it is at least partially relieved.
  • the portion extends without Pressbergerargued to an end face of the roller shoe, which faces the cam. An increased surface pressure in the region of the end face bounding edge of the roller shoe can thus be effectively prevented.
  • the section without press excess has a height HA which is less than half, preferably less than one third, of the total height H G of the roller shoe.
  • a radially inwardly projecting annular collar is formed in the plunger body, against which the roller shoe rests.
  • the annular collar thus provides the Einpresstiefe, so that the pressing of the roller shoe is simplified.
  • the annular collar can serve to support a spring plate and a spring, by means of which a pump piston can be connected to the plunger assembly.
  • the plunger assembly according to the invention is preferably used in a radial piston pump, a radial piston pump, in particular a high-pressure fuel pump, with a pump housing and a plunger assembly according to the invention is also proposed.
  • the plunger assembly is accommodated in a plunger space of the pump housing to move back and forth.
  • FIG. 1 shows a schematic longitudinal section through a radial piston pump according to the invention with a plunger assembly according to the invention
  • 2 shows a schematic longitudinal section through the plunger assembly of the radial piston pump of FIG. 1
  • FIG. 3 shows a schematic side view of the roller shoe of the plunger assembly of FIG.
  • Fig. 4 is a schematic side view of a roller shoe of a plunger assembly according to a second preferred embodiment of the invention.
  • Fig. 5 is a schematic side view of a roller shoe of a plunger assembly according to a third preferred embodiment of the invention.
  • the pump piston 2 defines a pump working chamber 15, which is formed within a cylinder bore 16 of the pump housing 11 and can be filled with fuel via a suction valve 17.
  • the plunger assembly 1 In order to drive the pump piston 2 in a lifting movement, it is supported on the cam 3 via a tappet assembly 1.
  • the plunger assembly 1 has a hollow-cylindrical plunger body 5, which is received in a plunger space 12 of the pump housing 11 so as to be movable back and forth.
  • a roller shoe 6 In the plunger body 5 is a roller shoe 6 for rotatably supporting a roller 7 is pressed.
  • the plunger assembly 1 is directly on the cam 3 of Drive shaft 4 supported.
  • the roller 7 runs on the outer peripheral surface 21 of the cam 3 from.
  • a spring 22 is provided, which is indirectly supported by a spring plate 23 on an annular collar 10 of the plunger body 5 and biases the plunger assembly 1 against the cam 3.
  • the spring plate 23 engages behind a piston 24 of the pump piston 2, so that it follows the movement of the plunger assembly 1.
  • the roller shoe 6 of the plunger assembly 1 of Fig. 2 in an individual view, in a side view, refer.
  • the roller shoe 6 has a pressing surface 13, which is formed by a conical portion of the roller shoe 6.
  • a section 8 connects, in which the roller shoe 6 has no excess pressure.
  • the section 8 extends to an end face 9, in which a serving as a pivot bearing for the roller 7 recess 25 is formed. That is, the end face 9 faces the cam 3, when the roller shoe 6 is used as part of the plunger assembly 1 in the high-pressure fuel pump of FIG. Accordingly, no surface pressure occurs in the area of an edge 26 of the roller shoe 6 delimiting the end face 9 (see the curve represented above FIG. 3, which reproduces the surface pressure).
  • the curve can also be seen that the surface pressure on the pressing surface 13 is approximately uniformly distributed. Only at the two edge regions of the pressing surface 13 occur slight pressure peaks, which, however, are significantly less extreme than with a cylindrical pressing surface according to the prior art.
  • the tappet body 5 is less burdened by voltage peaks and the robustness of the tappet assembly 1 increases. Accordingly, the excess pressure can be increased.
  • the plunger assembly 1 according to the invention is thus able to transmit higher torques under dynamic load. Furthermore, the risk that the plunger body 5 plastically deforms under load decreases.
  • the conical shape of the pressing surface 13 of the roller shoe 6 of Fig. 3 also has the advantage that the pressing of the roller shoe 6 in the plunger body 5 simplified is, since initially - due to the lower excess pressure in the region of an edge 27 - a reduced press-in force is required.
  • FIG. 4 shows a roller shoe 6 for a plunger assembly 1 according to the invention, which has a bulbous pressing surface 13 instead of a conically shaped pressing surface 13.
  • the pressing surface 13 follows a radius Ri. As can be seen from the curve shown above FIG. 4, this leads to a largely uniform distribution of the surface pressure over the pressing surface 13, so that substantially the same advantages as previously described in connection with FIG 3 described.
  • FIG. 5 A further advantageous modification of the pressing surface 13 is shown in FIG. 5.
  • the pressing surface 13 has in its edge regions in each case a radius R2 following pressing surface sections which are interrupted by a central cylindrical pressing surface section. Also in this embodiment, the advantages already described above arise.

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

Abstract

The invention relates to a tappet assembly (1) for supporting a reciprocating pump piston (2) of a radial piston pump, in particular a high-pressure fuel pump, on a cam (3) of a drive shaft (4), comprising a hollow-cylindrical tappet body (5) and a roller shoe (6) pressed into the tappet body (5) for the rotatable mounting of a roller (7). According to the invention, the roller shoe (6) has a pressing oversize that varies in the press-in direction. The invention further relates to a radial piston pump having a tappet assembly (1) of said type.

Description

Beschreibung  description
Titel title
Stößelbaugruppe für eine Radialkolbenpumpe, Radialkolbenpumpe Die Erfindung betrifft eine Stößelbaugruppe für eine Radialkolbenpumpe, insbesondere eine Kraftstoffhochdruckpumpe, mit den Merkmalen des Oberbegriffs des Anspruchs 1. Die angegebene Stößelbaugruppe dient der Abstützung eines Pumpenkolbens der Ra¬ dialkolbenpumpe an einem Nocken einer Antriebswelle. Ferner betrifft die Erfindung ei¬ ne Radialkolbenpumpe, insbesondere eine Kraftstoffhochdruckpumpe zur Versorgung eines Verbrennungsmotors mit Kraftstoff, mit einer solchen Stößelbaugruppe. The invention relates to a plunger assembly for a radial piston pump, in particular a high-pressure fuel pump, with the features of the preamble of claim 1. The plunger assembly specified serves to support a pump piston of Ra ¬ dialkolbenpumpe on a cam of a drive shaft. Furthermore, the invention relates ei ¬ ne radial piston pump, in particular a high-pressure fuel pump for supplying an internal combustion engine with fuel, with such a plunger assembly.
Stand der Technik State of the art
Aus der Offenlegungsschrift DE 10 2009 001 631 AI ist eine Stößelbaugruppe für eine Hochdruckpumpe bekannt, die einen Stößelkörper mit einer Aufnahme und einen in dieFrom the published patent application DE 10 2009 001 631 AI a plunger assembly for a high-pressure pump is known, which has a plunger body with a receptacle and a in the
Aufnahme des Stößelkörpers eingepressten Rollenschuh zur drehbaren Lagerung ei¬ ner Rolle umfasst. Zur Herstellung des Pressverbandes weist der Rollenschuh ein Pressübermaß gegenüber der Aufnahme des Stößelkörpers auf. Um eine Schrägstel¬ lung des Rollenschuhs beim Einpressen in den Stößelkörper zu verhindern, bildet der Stößelkörper eine Zentrierführung aus. Durch die Zentrierführung wird beim Einpressen des Rollenschuhs eine automatische Zentrierung erreicht, die eine Schrägeinpressung verhindert. Zugleich steigt die Robustheit des Pressverbandes, da die Einpresskräfte nicht verfälscht werden, wie dies bei einer Schrägeinpressung regelmäßig der Fall ist. Ausgehend von dem vorstehend genannten Stand der Technik liegt der vorliegendenIncluding receiving the plunger body pressed roller shoe for rotatably supporting ei ¬ ner role. For the production of the interference fit, the roller shoe has a press excess with respect to the receptacle of the tappet body. In order to prevent an inclined Stel ¬ ment of the roller shoe when pressed into the plunger body, the plunger body forms a centering. By centering an automatic centering is achieved when pressing the roller shoe, which prevents a Schräginpressung. At the same time, the robustness of the press fit increases, since the press-in forces are not distorted, as is the case regularly with an oblique press. Based on the above-mentioned prior art is the present
Erfindung die Aufgabe zugrunde, eine Stößelbaugruppe für eine Radialkolbenpumpe, insbesondere für eine Kraftstoffhochdruckpumpe, anzugeben, deren Robustheit weiter gesteigert ist. Zur Lösung der Aufgabe wird die Stößelbaugruppe mit den Merkmalen des Anspruchs 1 angegeben. Vorteilhafte Weiterbildungen der Erfindung sind den Unteransprüchen zu entnehmen. Ferner wird eine Radialkolbenpumpe mit einer solchen Stößelbaugruppe vorgeschlagen. Invention the task is to provide a plunger assembly for a radial piston pump, in particular for a high-pressure fuel pump, indicate their robustness is further increased. To solve the problem, the plunger assembly is specified with the features of claim 1. Advantageous developments of the invention can be found in the dependent claims. Furthermore, a radial piston pump is proposed with such a plunger assembly.
Offenbarung der Erfindung Disclosure of the invention
Die vorgeschlagene Stößelbaugruppe ist zur Abstützung eines hubbeweglichen Pumpenkolbens einer Radialkolbenpumpe, insbesondere einer Kraftstoffhochdruckpumpe, an einem Nocken einer Antriebswelle geeignet. Die Stößelbaugruppe umfasst hierzu einen hohlzylinderförmigen Stößelkörper und einen in den Stößelkörper eingepressten Rollenschuh zur drehbaren Lagerung einer Rolle. Erfindungsgemäß weist der Rollenschuh ein in Einpressrichtung variierendes Pressübermaß auf. Das heißt, dass der Rollenschuh kein zylindrisches Pressübermaß besitzt. The proposed plunger assembly is suitable for supporting a liftable pump piston of a radial piston pump, in particular a high-pressure fuel pump, on a cam of a drive shaft. For this purpose, the plunger assembly comprises a hollow cylindrical plunger body and a roller shoe press-fitted into the plunger body for rotatably supporting a roller. According to the invention, the roller shoe has a pressing oversize which varies in the pressing-in direction. This means that the roller shoe does not have a cylindrical excess pressure.
Das variierende Pressübermaß dient der Optimierung der Flächenpressung im Pressverband. Denn bei einem zylindrischen Pressübermaß des Rollenschuhs ist die Flächenpressung über die Pressfläche ungleichmäßig verteilt. Beispielsweise entsteht an den Kanten des Rollenschuhs eine erhöhte Flächenpressung. Dies führt zu Span- nungsspitzen im Stößelkörper, die sich negativ auf die Robustheit der Stößelbaugruppe auswirken. Durch das variierende Pressübermaß können Spannungsspitzen im Stößelkörper vermieden werden, so dass die Robustheit der Stößelbaugruppe steigt. The varying excess pressure serves to optimize the surface pressure in the press fit. Because with a cylindrical excess pressure of the roller shoe, the surface pressure over the pressing surface is distributed unevenly. For example, creates an increased surface pressure at the edges of the roller shoe. This leads to voltage peaks in the tappet body, which have a negative effect on the robustness of the tappet assembly. Due to the varying excess pressure, voltage peaks in the tappet body can be avoided so that the robustness of the tappet assembly increases.
Bevorzugt weist der Rollenschuh ein Pressübermaß auf, das in Einpressrichtung ab- nimmt. Auf diese Weise wird das Einpressen des Rollenschuhs in den Stößelkörper vereinfacht. Zudem wird der Kantenbereich des Rollenschuhs entlastet, über den der Rollenschuh in den Stößelkörper eingepresst wird. Zumindest in diesem Kantenbereich ist demnach keine erhöhte Flächenpressung mehr zu erwarten. Ferner bevorzugt ist der Rollenschuh in Einpressrichtung zumindest abschnittsweise konisch und/oder bauchig geformt. Der Rollenschuh kann dabei auch mehrere konisch und/oder bauchig geformte Abschnitte aufweisen. Beispielsweise können mehrere konisch geformte Abschnitte mit unterschiedlichem Konuswinkel aufeinanderfolgen. Ferner können konisch und/oder bauchig geformte Abschnitte durch einen zylinderförmi- gen Abschnitt unterbrochen sein. Der Abschnitt, in dem der Rollenschuh sein größtes Pressübermaß besitzt, ist vorzugsweise in einem Abstand zu mindestens einer Kante des Rollenschuhs angeordnet. Preferably, the roller shoe has a pressing excess, which decreases in the pressing-in direction. In this way, the pressing of the roller shoe is simplified in the plunger body. In addition, the edge region of the roller shoe is relieved, via which the roller shoe is pressed into the plunger body. Accordingly, no increased surface pressure is to be expected at least in this edge region. Further preferably, the roller shoe is at least partially conical and / or bulbous in the pressing direction. The roller shoe can also have a plurality of conical and / or bulbous shaped sections. For example, a plurality of conically shaped sections with different cone angle can follow each other. Furthermore, conical and / or bulbous shaped sections can be formed by a cylindrical interrupted section. The section in which the roller shoe has its greatest pressing interference is preferably arranged at a distance from at least one edge of the roller shoe.
Darüber hinaus wird vorgeschlagen, dass der Rollenschuh zumindest einen Abschnitt ohne Pressübermaß aufweist. Das heißt, dass in diesem Bereich keine Einpresskräfte auf den Stößelkörper wirken, so dass dieser zumindest bereichsweise entlastet wird. Vorzugsweise erstreckt sich der Abschnitt ohne Pressübermaß bis zu einer Stirnfläche des Rollenschuhs, die dem Nocken zugewandt ist. Eine erhöhte Flächenpressung im Bereich der die Stirnfläche begrenzenden Kante des Rollenschuhs kann somit wirksam verhindert werden. In addition, it is proposed that the roller shoe has at least one section without excess press. This means that in this area no press-in forces act on the plunger body, so that it is at least partially relieved. Preferably, the portion extends without Pressübermaß to an end face of the roller shoe, which faces the cam. An increased surface pressure in the region of the end face bounding edge of the roller shoe can thus be effectively prevented.
In Weiterbildung der Erfindung wird vorgeschlagen, dass der Abschnitt ohne Pressübermaß eine Höhe HA aufweist, die weniger als die Hälfte, vorzugsweise weniger als ein Drittel, der Gesamthöhe HG des Rollenschuhs beträgt. Dadurch ist weiterhin eine ausreichend große Pressfläche sichergestellt. In a further development of the invention, it is proposed that the section without press excess has a height HA which is less than half, preferably less than one third, of the total height H G of the roller shoe. As a result, a sufficiently large pressing surface is still ensured.
Vorteilhafterweise ist im Stößelkörper ein nach radial innen vorspringender Ringbund ausgebildet, an dem der Rollenschuh anliegt. Der Ringbund gibt somit die Einpresstiefe vor, so dass das Einpressen des Rollenschuhs vereinfacht wird. Ferner kann der Ringbund zur Abstützung eines Federtellers und einer Feder dienen, mittels welcher ein Pumpenkolben mit der Stößelbaugruppe verbindbar ist. Advantageously, a radially inwardly projecting annular collar is formed in the plunger body, against which the roller shoe rests. The annular collar thus provides the Einpresstiefe, so that the pressing of the roller shoe is simplified. Furthermore, the annular collar can serve to support a spring plate and a spring, by means of which a pump piston can be connected to the plunger assembly.
Da die erfindungsgemäße Stößelbaugruppe bevorzugt in einer Radialkolbenpumpe zum Einsatz gelangt, wird ferner eine Radialkolbenpumpe, insbesondere eine Kraftstoffhochdruckpumpe, mit einem Pumpengehäuse und einer erfindungsgemäßen Stößelbaugruppe vorgeschlagen. Die Stößelbaugruppe ist dabei in einem Stößelraum des Pumpengehäuses hin und her beweglich aufgenommen. Since the plunger assembly according to the invention is preferably used in a radial piston pump, a radial piston pump, in particular a high-pressure fuel pump, with a pump housing and a plunger assembly according to the invention is also proposed. The plunger assembly is accommodated in a plunger space of the pump housing to move back and forth.
Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der beigefügten Zeichnungen näher erläutert. Diese zeigen: Preferred embodiments of the invention are explained below with reference to the accompanying drawings. These show:
Fig. 1 einen schematischen Längsschnitt durch eine erfindungsgemäße Radialkolbenpumpe mit einer erfindungsgemäßen Stößelbaugruppe, Fig. 2 einen schematischen Längsschnitt durch die Stößelbaugruppe der Radialkol- benpumpe der Fig. 1, Fig. 3 eine schematische Seitenansicht des Rollenschuhs der Stößelbaugruppe der1 shows a schematic longitudinal section through a radial piston pump according to the invention with a plunger assembly according to the invention, 2 shows a schematic longitudinal section through the plunger assembly of the radial piston pump of FIG. 1, FIG. 3 shows a schematic side view of the roller shoe of the plunger assembly of FIG
Fig. 2, 2,
Fig. 4 eine schematische Seitenansicht eines Rollenschuhs einer Stößelbaugruppe gemäße einer zweiten bevorzugten Ausführungsform der Erfindung und Fig. 4 is a schematic side view of a roller shoe of a plunger assembly according to a second preferred embodiment of the invention and
Fig. 5 eine schematische Seitenansicht eines Rollenschuhs einer Stößelbaugruppe gemäße einer dritten bevorzugten Ausführungsform der Erfindung. Fig. 5 is a schematic side view of a roller shoe of a plunger assembly according to a third preferred embodiment of the invention.
Ausführliche Beschreibung der Zeichnungen Detailed description of the drawings
Der Fig. 1 ist eine als Radialkolbenpumpe ausgeführte Kraftstoffhochdruckpumpe mit einem Pumpengehäuse 11 zu entnehmen, in dem in einem Trieb werksraum 14 eine Antriebswelle 4 aufgenommen ist. Die Antriebswelle 4 weist einen Nocken 3 auf, über den ein Pumpenkolben 2 der Kraftstoffhochdruckpumpe in einer Hubbewegung an¬ treibbar ist. Der Pumpenkolben 2 begrenzt einen Pumpenarbeitsraum 15, der innerhalb einer Zylinderbohrung 16 des Pumpengehäuses 11 ausgebildet und über ein Saugventil 17 mit Kraftstoff befüllbar ist. Im Förderbetrieb der Kraftstoffhochdruckpumpe wird der im Pumpenarbeitsraum vorhandene Kraftstoff durch die Hubbewegung des Pum¬ penkolbens 2 komprimiert und anschließend über ein Hochdruckventil 18 einem Hoch¬ druckspeicher 19 zugeführt. Über mindestens einen an den Hochdruckspeicher 19 an¬ geschlossenen Kraftstoffinjektor 20 ist dann der komprimierte Kraftstoff in einen Brenn¬ raum (nicht dargestellt) eines Verbrennungsmotors einspritzbar. 1 is a run as a radial piston pump high-pressure fuel pump with a pump housing 11 can be seen in which a drive shaft 4 in a power plant housing 14 is added. The drive shaft 4 has a cam 3, via which a pump piston 2 of the high-pressure fuel pump is drivable in a lifting movement ¬ . The pump piston 2 defines a pump working chamber 15, which is formed within a cylinder bore 16 of the pump housing 11 and can be filled with fuel via a suction valve 17. In the conveying operation of the high-pressure fuel pump of the present in the pump working space fuel is compressed by the reciprocating motion of the Pum ¬ penkolbens 2 and then via a high pressure valve 18 accumulator fed to a high ¬ 19th At least one closed at the high-pressure accumulator 19 at ¬ fuel injector 20 of the fuel compressed in a combustion space ¬ (not shown) of an internal combustion engine is then injected.
Um den Pumpenkolben 2 in eine Hubbewegung anzutreiben, ist dieser über eine Stö- ßelbaugruppe 1 am Nocken 3 abgestützt. Wie insbesondere der Fig. 2 zu entnehmen ist, weist die Stößelbaugruppe 1 einen hohlzylinderförmigen Stößelkörper 5 auf, der in einem Stößelraum 12 des Pumpengehäuses 11 hin und her beweglich aufgenommen ist. In den Stößelkörper 5 ist ein Rollenschuh 6 zur drehbaren Lagerung einer Rolle 7 eingepresst. Über die Rolle 7 ist die Stößelbaugruppe 1 unmittelbar am Nocken 3 der Antriebswelle 4 abgestützt. Bei einer Rotation der Antriebswelle 4 läuft die Rolle 7 auf der Außenumfangsfläche 21 des Nockens 3 ab. In order to drive the pump piston 2 in a lifting movement, it is supported on the cam 3 via a tappet assembly 1. As can be seen in particular from FIG. 2, the plunger assembly 1 has a hollow-cylindrical plunger body 5, which is received in a plunger space 12 of the pump housing 11 so as to be movable back and forth. In the plunger body 5 is a roller shoe 6 for rotatably supporting a roller 7 is pressed. About the roller 7, the plunger assembly 1 is directly on the cam 3 of Drive shaft 4 supported. Upon rotation of the drive shaft 4, the roller 7 runs on the outer peripheral surface 21 of the cam 3 from.
Zur Verbindung des Pumpenkolbens 2 mit der Stößelbaugruppe 1 ist eine Feder 22 vorgesehen, die mittelbar über einen Federteller 23 an einem Ringbund 10 des Stößelkörpers 5 abgestützt ist und die Stößelbaugruppe 1 gegen den Nocken 3 vorspannt. Der Federteller 23 hintergreift dabei einen Kolbenfuß 24 des Pumpenkolbens 2, so dass dieser der Bewegung der Stößelbaugruppe 1 folgt. To connect the pump piston 2 with the plunger assembly 1, a spring 22 is provided, which is indirectly supported by a spring plate 23 on an annular collar 10 of the plunger body 5 and biases the plunger assembly 1 against the cam 3. The spring plate 23 engages behind a piston 24 of the pump piston 2, so that it follows the movement of the plunger assembly 1.
Der Fig. 3 ist der Rollenschuh 6 der Stößelbaugruppe 1 der Fig. 2 in einer Einzeldarstellung, und zwar in einer Seitenansicht, zu entnehmen. Der Rollenschuh 6 weist eine Pressfläche 13 auf, die durch einen konischen Abschnitt des Rollenschuhs 6 gebildet wird. An die Pressfläche 13 schließt sich ein Abschnitt 8 an, in dem der Rollenschuh 6 kein Pressübermaß aufweist. Der Abschnitt 8 erstreckt sich bis zu einer Stirnfläche 9, in der eine als Drehlager für die Rolle 7 dienende Ausnehmung 25 ausgebildet ist. Das heißt, dass die Stirnfläche 9 dem Nocken 3 zugewandt ist, wenn der Rollenschuh 6 als Bestandteil der Stößelbaugruppe 1 in die Kraftstoffhochdruckpumpe der Fig. 1 eingesetzt wird. Im Bereich einer die Stirnfläche 9 begrenzenden Kante 26 des Rollenschuhs 6 tritt demnach keine Flächenpressung auf (siehe die oberhalb der Fig. 3 dargestellte Kurve, welche die Flächenpressung wiedergibt). Der Kurve ist ferner zu entnehmen, dass die Flächenpressung über die Pressfläche 13 annähernd gleichmäßig verteilt ist. Lediglich an den beiden Randbereichen der Pressfläche 13 treten leichte Druckspitzen auf, die jedoch deutlich weniger extrem als bei einer zylindrischen Pressfläche gemäß dem Stand der Technik ausfallen. 3, the roller shoe 6 of the plunger assembly 1 of Fig. 2 in an individual view, in a side view, refer. The roller shoe 6 has a pressing surface 13, which is formed by a conical portion of the roller shoe 6. At the pressing surface 13, a section 8 connects, in which the roller shoe 6 has no excess pressure. The section 8 extends to an end face 9, in which a serving as a pivot bearing for the roller 7 recess 25 is formed. That is, the end face 9 faces the cam 3, when the roller shoe 6 is used as part of the plunger assembly 1 in the high-pressure fuel pump of FIG. Accordingly, no surface pressure occurs in the area of an edge 26 of the roller shoe 6 delimiting the end face 9 (see the curve represented above FIG. 3, which reproduces the surface pressure). The curve can also be seen that the surface pressure on the pressing surface 13 is approximately uniformly distributed. Only at the two edge regions of the pressing surface 13 occur slight pressure peaks, which, however, are significantly less extreme than with a cylindrical pressing surface according to the prior art.
Dadurch, dass die Flächenpressung über die Pressfläche 13 annähernd gleichmäßig verteilt ist, wird der Stößelkörper 5 weniger durch Spannungsspitzen belastet und die Robustheit der Stößelbaugruppe 1 steigt. Entsprechend kann das Pressübermaß erhöht werden. Die erfindungsgemäße Stößelbaugruppe 1 ist demnach in der Lage, unter dynamischer Belastung höhere Drehmomente zu übertragen. Ferner sinkt die Gefahr, dass sich der Stößelkörper 5 unter Belastung plastisch verformt. Because the surface pressure is approximately evenly distributed over the pressing surface 13, the tappet body 5 is less burdened by voltage peaks and the robustness of the tappet assembly 1 increases. Accordingly, the excess pressure can be increased. The plunger assembly 1 according to the invention is thus able to transmit higher torques under dynamic load. Furthermore, the risk that the plunger body 5 plastically deforms under load decreases.
Die konische Form der Pressfläche 13 des Rollenschuhs 6 der Fig. 3 weist ferner den Vorteil auf, dass das Einpressen des Rollenschuhs 6 in den Stößelkörper 5 vereinfacht wird, da anfänglich - aufgrund des geringeren Pressübermaßes im Bereich einer Kante 27 - eine verminderte Einpresskraft erforderlich ist. The conical shape of the pressing surface 13 of the roller shoe 6 of Fig. 3 also has the advantage that the pressing of the roller shoe 6 in the plunger body 5 simplified is, since initially - due to the lower excess pressure in the region of an edge 27 - a reduced press-in force is required.
Der Fig. 4 ist ein Rollenschuh 6 für eine erfindungsgemäße Stößelbaugruppe 1 zu entnehmen, der anstelle einer konisch geformten Pressfläche 13 eine bauchige Pressfläche 13 aufweist. Die Pressfläche 13 folgt einem Radius Ri. Wie der oberhalb der Fig. 4 dargestellten Kurve zu entnehmen ist, führt dies zu einer weitegehend gleichmäßigen Verteilung der Flächenpressung über die Pressfläche 13, so dass sich im Wesentlichen die gleichen Vorteile wie zuvor in Zusammenhang mit der Fig. 3 beschrieben ergeben. FIG. 4 shows a roller shoe 6 for a plunger assembly 1 according to the invention, which has a bulbous pressing surface 13 instead of a conically shaped pressing surface 13. The pressing surface 13 follows a radius Ri. As can be seen from the curve shown above FIG. 4, this leads to a largely uniform distribution of the surface pressure over the pressing surface 13, so that substantially the same advantages as previously described in connection with FIG 3 described.
Eine weitere vorteilhafte Modifikation der Pressfläche 13 ist der Fig. 5 zu entnehmen. Hier weist die Pressfläche 13 in ihren Randbereichen jeweils einem Radius R2 folgende Pressflächenabschnitte auf, die durch einen zentralen zylinderförmigen Pressflächenabschnitt unterbrochen werden. Auch in dieser Ausgestaltung ergeben sich die bereits vorstehend beschriebenen Vorteile. A further advantageous modification of the pressing surface 13 is shown in FIG. 5. Here, the pressing surface 13 has in its edge regions in each case a radius R2 following pressing surface sections which are interrupted by a central cylindrical pressing surface section. Also in this embodiment, the advantages already described above arise.

Claims

Ansprüche claims
1. Stößelbaugruppe (1) zur Abstützung eines hubbeweglichen Pumpenkolbens (2) einer Radialkolbenpumpe, insbesondere einer Kraftstoffhochdruckpumpe, an einem Nocken (3) einer Antriebswelle (4), umfassend einen hohlzylinderförmigen Stößelkörper (5) und einen in den Stößelkörper (5) eingepressten Rollenschuh (6) zur drehbaren Lagerung einer Rolle (7), A plunger assembly (1) for supporting a liftable pump piston (2) of a radial piston pump, in particular a high-pressure fuel pump, on a cam (3) of a drive shaft (4) comprising a hollow cylindrical plunger body (5) and a roller shoe pressed into the plunger body (5) (6) for rotatably supporting a roller (7),
dadurch gekennzeichnet, dass der Rollenschuh (6) ein in Einpressrichtung variierendes Pressübermaß aufweist. characterized in that the roller shoe (6) has a press-overs varying in the pressing-in direction.
2. Stößelbaugruppe (1) nach Anspruch 1, 2. plunger assembly (1) according to claim 1,
dadurch gekennzeichnet, dass der Rollenschuh (6) ein Pressübermaß aufweist, das in Einpressrichtung abnimmt. characterized in that the roller shoe (6) has a pressing excess, which decreases in the pressing-in direction.
3. Stößelbaugruppe (1) nach Anspruch 1 oder 2, 3. ram assembly (1) according to claim 1 or 2,
dadurch gekennzeichnet, dass der Rollenschuh (6) in Einpressrichtung zumindest abschnittsweise konisch und/oder bauchig geformt ist. characterized in that the roller shoe (6) is at least partially conical and / or bulbous in the press-fitting.
4. Stößelbaugruppe (1) nach einem der vorhergehenden Ansprüche, 4. plunger assembly (1) according to any one of the preceding claims,
dadurch gekennzeichnet, dass der Rollenschuh (6) zumindest einen Abschnitt (8) ohne Pressübermaß aufweist, wobei sich vorzugsweise der Abschnitt (8) bis zu einer Stirnfläche (9) des Rollenschuhs (6) erstreckt, die dem Nocken (3) zugewandt ist. characterized in that the roller shoe (6) has at least one section (8) without excess pressing, wherein preferably the section (8) extends to an end face (9) of the roller shoe (6) which faces the cam (3).
5. Stößelbaugruppe (1) nach Anspruch 4, 5. ram assembly (1) according to claim 4,
dadurch gekennzeichnet, dass der Abschnitt (8) ohne Pressübermaß eine Höhe (HA) aufweist, die weniger als die Hälfte, vorzugsweise weniger als ein Drittel, der Gesamthöhe (HG) des Rollenschuhs (6) beträgt. characterized in that the portion (8) without press interference has a height (HA) which is less than half, preferably less than one third, of the total height (HG) of the roller shoe (6).
6. Stößelbaugruppe (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass im Stößelkörper (5) ein nach radial innen vorspringender Ringbund (10) ausgebildet ist, an dem der Rollenschuh (6) anliegt. 6. plunger assembly (1) according to any one of the preceding claims, characterized in that in the plunger body (5) a radially inwardly projecting annular collar (10) is formed, against which the roller shoe (6).
7. Radialkolbenpumpe, insbesondere Kraftstoffhochdruckpumpe, mit einem Pum- pengehäuse (11) und einer Stößelbaugruppe (1) nach einem der vorhergehenden Ansprüche, wobei die Stößelbaugruppe (1) in einem Stößelraum (12) des Pumpengehäuses (11) hin und her beweglich aufgenommen ist. 7. Radial piston pump, in particular high-pressure fuel pump, with a pump housing (11) and a plunger assembly (1) according to one of the preceding claims, wherein the plunger assembly (1) in a plunger space (12) of the pump housing (11) is reciprocally accommodated ,
PCT/EP2017/074287 2016-09-30 2017-09-26 Tappet assembly for a radial piston pump, and radial piston pump WO2018060158A1 (en)

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DE102016219046.6A DE102016219046A1 (en) 2016-09-30 2016-09-30 Plunger assembly for a radial piston pump, radial piston pump

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