EP1818539A2 - Radial piston pump for a fuel injection system having improved high-pressure resistance - Google Patents

Radial piston pump for a fuel injection system having improved high-pressure resistance Download PDF

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Publication number
EP1818539A2
EP1818539A2 EP20070109457 EP07109457A EP1818539A2 EP 1818539 A2 EP1818539 A2 EP 1818539A2 EP 20070109457 EP20070109457 EP 20070109457 EP 07109457 A EP07109457 A EP 07109457A EP 1818539 A2 EP1818539 A2 EP 1818539A2
Authority
EP
European Patent Office
Prior art keywords
radial piston
piston pump
pump according
high pressure
check valve
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.)
Granted
Application number
EP20070109457
Other languages
German (de)
French (fr)
Other versions
EP1818539A3 (en
EP1818539B1 (en
Inventor
Josef Guentert
Karl-Heinz Linek
Florian Kleer
Peter Grabert
Gerd Loesch
Paul Wuetherich
Nicola Cimaglia
Antonio Diaferia
Rosanna Iorizzo
Sandra Ranaldo
Giuseppe Palma
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1818539A2 publication Critical patent/EP1818539A2/en
Publication of EP1818539A3 publication Critical patent/EP1818539A3/en
Application granted granted Critical
Publication of EP1818539B1 publication Critical patent/EP1818539B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M59/485—Means for fixing delivery valve casing and barrel to each other or to pump casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/22—Reinforcements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7927—Ball valves

Definitions

  • the invention relates to a radial piston pump for high-pressure fuel supply in fuel systems of internal combustion engines, in particular in a common rail injection system, preferably with a plurality of respect to a mounted in a pump housing drive shaft radially arranged pump elements, wherein the pump elements are actuated by the drive shaft and one suction side and one high pressure side and with high pressure passages in the pump housing, each connecting the high pressure side of a pump element to a high pressure port in the pump housing.
  • Such a radial piston pump is for example from the DE 197 29 788.9 A1 known. This series-produced radial piston pump reaches operating pressures of up to 1300 bar on the high pressure side. This results in considerable mechanical stresses in the pump housing.
  • the invention has for its object to develop a radial piston pump so that it can be used for pressures up to 2000 bar.
  • a radial piston pump for high-pressure fuel supply in fuel injection systems of internal combustion engines with preferably several with respect to a stored in a pump housing drive shaft radially arranged pump elements, the pump elements are actuated by the drive shaft and each have a suction side and a high pressure side and with high pressure channels in the pump housing, which each connect the high pressure side of a pump element with a high pressure port in the pump housing, achieved in that each high pressure channel connects the high pressure side of a pump element directly to the high pressure port.
  • the radial piston pump according to the invention can be operated at higher pressures, at the same time reducing the material stress.
  • the surfaces of the high-pressure channels are compressed and provided with compressive residual stresses, in particular by the fact that a ball is pulled or pressed through the high-pressure channels, the diameter of which is slightly larger than the diameter of the high pressure channels is. This measure further increases the pressure resistance of the pump housing in the area of the high-pressure channels.
  • the high-pressure channels are hardened, in particular induction-hardened.
  • the high-pressure channels are rounded in the region of cross-sectional changes and / or junctions of other high-pressure channels, in particular rounded in a hydroerosive manner.
  • a particularly advantageous embodiment of the radial piston pump according to the invention provides that the high-pressure channels are each reinforced by a tubular insert, in particular an insert made of a high-strength material, with high-strength steel being found to be particularly suitable.
  • the tubular inserts according to the invention are inserted into the casting mold like a core before casting. When casting pump housing and tubular inserts combine very well with each other. The fact that because of the tubular inserts, the high-pressure channels of a different, more preferably a firmer material than the rest of the pump housing, there is an adaptation of the component strength to the local stresses and strains.
  • the rest of the pump housing can be made of a relatively inexpensive material, in addition to good machinability and has good sliding properties.
  • the tubular inserts according to the invention is that, in contrast to conventional bores, the high-pressure ducts can be curved or partially curved. It is also possible that the high pressure side of a pump element is connected directly to the high pressure port in the pump housing by one use, so that no Branching of the high-pressure channels are required. This has a favorable effect on the maximum stresses occurring in the pump housing, on the manufacturing costs and in particular the manufacturing reliability.
  • each pump element has a cylinder bore and a cylinder head, that the piston oscillates in the cylinder bore and delimits a delivery space, that a first check valve is arranged on the intake side, and that a second check valve is arranged on the high pressure side is arranged. It has proven to be advantageous if the cylinder bore is formed as a blind hole and the first check valve is arranged at the bottom of the blind hole. By forming the cylinder bore as a blind hole a sealing point is saved.
  • the second check valve has a sleeve with a stepped central bore, that the stepped central bore has a sealing seat for a valve member, in particular a ball particularly preferably a ceramic ball, and that the sleeve of a closure screw sealing against the cylinder head pressed.
  • This second check valve has the advantage that it is very simple and can be tested outside the radial piston pump. In the radial piston pump or the pump element, only a sealing surface is provided, which seals the screwed second check valve on the front side. Such a sealing surface is easy to control in terms of production, so that the sealing of the high-pressure side of the pump element to the environment at this point is simplified by the use of the second check valve according to the invention.
  • the sealing of the high pressure side relative to the environment is particularly effective when the sleeve has a biting edge on its end face applied to the screw plug, so that the surface pressure increases and Also, a plastic deformation of the sealing surfaces is possible, which further improves the sealing function.
  • the assembly of the check valve facilitates further, since the cohesion of a mounted and tested check valve is always guaranteed.
  • the sleeve has a transverse bore and an annular groove and that produce the transverse bore and groove a hydraulic connection of the central bore to the delivery chamber.
  • a sealing seat on the pump housing facing side of the cylinder head is incorporated in this, wherein the check valve has a cage in which a on the valve member, in particular a ball, acting closing spring is arranged.
  • the closing spring By the closing spring, the return flow of fuel is reduced, which has an advantageous effect on the pump efficiency.
  • the assembly of the check valve according to the invention in the pump element is simplified if the cage is pressed into a stepped bore comprising the sealing seat.
  • a manufacturing technology advantageous embodiment provides that the cylinder bore is formed as a blind hole, that the first check valve according to one of claims 17 and 18 is arranged at the bottom of the blind hole, so that the sealing seat of first and second check valve can be made in one setting and the assembly of the first and second check valve in the same direction.
  • FIG. 1 shows an exemplary embodiment of a radial piston pump according to the invention in a front view (FIG. 1A), in a longitudinal section (FIG. 1B) and in a cross section along the section line A-A.
  • the radial piston pump consists of a pump housing 1, in which a drive shaft 3 is rotatably mounted.
  • the pump housing 1 may advantageously be made of cast iron with globular graphite (GGG).
  • the drive shaft 3 has an eccentric portion 5.
  • the eccentric portion 5 drives via a polygon ring 7 three circumferentially distributed pump elements 9 at.
  • Each pump element 9 has a piston 11 which is guided in a cylinder bore 13 and limits a delivery chamber 15.
  • the individual components are not provided with reference numerals on all pump elements 9 in order not to worsen the clarity unnecessarily. However, the three pump elements 9 are all constructed the same.
  • a suction side 19 and a high pressure side 21 there is a suction side 19 and a high pressure side 21.
  • the suction side 19 of the cylinder head 17 is supplied with fuel via a low-pressure bore 23 in the pump housing.
  • a first check valve 25 is arranged, which prevents the return flow of fuel (not shown) from the delivery chamber 15 into the low-pressure bore 23.
  • the high pressure side 21 of the pump element 9 opens into a high pressure passage 27 in the pump housing 1.
  • a second check valve 29 is provided, which prevents the backflow of fuel under high pressure from the high pressure passage 27 into the delivery chamber 15.
  • the pump elements 9 are screwed by means not shown screws to the pump housing 1 and pressed by the screwing on a Zylinderfuß constitutional 31 of the pump housing 1.
  • a high pressure passage 27 in the pump housing 1 goes off and flows into a high pressure port which is not visible in FIGS. 1a to 1c.
  • the course of the high pressure channels is explained below with reference to FIG 2.
  • a second high-pressure channel 27 is shown in the lower half. Since this high-pressure channel is substantially perpendicular to the plane of the drawing, it is shown in Figure 1b as a circular surface.
  • a pump housing 1 is shown dreidmeinsional. From this representation, the course of the high-pressure channels 27 according to a first embodiment of the invention can be clearly seen.
  • the voltages occurring in the pump housing could be drastically reduced at the same pressures, so that the permissible operating pressures at the same Component strength could be raised to over 1800 bar.
  • the mechanical stress of the pump housing is lower than in the radial piston pumps according to the prior art.
  • the number of high-pressure channels is minimized.
  • three high-pressure channels 27a, 27b, 27c suffice to establish a hydraulic connection from the three cylinder base surfaces 31 to a high-pressure connection 33.
  • the high pressure channels 27a, 27b, and 27c are curved, and are formed directly, i. without branches, lead from a Zylinderfuß constitutional 31 to the high pressure port 33.
  • the resulting from the operating pressures of the pump housing 1 are further reduced because there are no branches.
  • this embodiment can be realized by curved tubular inserts 39a, 39b and 39c. Through these tubular inserts 39a to 39c, the strength of the pump housing 1 can be further increased.
  • tubular inserts 39a to 39c are inserted into the mold prior to casting of the pump housing 1. During the subsequent casting of the pump housing 1, the tubular inserts 39 intimately connect to the pump housing 1, so that the power transmission between tubular insert 31 and pump housing 1 is optimal.
  • FIG. 3 shows an embodiment of a radial piston pump according to the invention is shown, in which the cylinder bore 13 is listed in the pump element 9 as a blind hole. At the bottom of the blind hole a sealing seat 41 for the first check valve 25 is provided.
  • the first check valve 25 may be identical in construction to the second check valve 29 described with reference to FIGS. 5 and 6.
  • the piston 11 also driven by a polygon ring and a Kolbenfußplatte 43.
  • the invention is not limited to radial piston pumps with such drives of the pump elements 9. Rather, alternative drives, for example by cams or the like can be used.
  • the piston feet may also include bucket tappets which are guided in the pump housing 1 (not shown).
  • FIG. 4 a shows a cylinder head 17 of a further exemplary embodiment of a radial piston pump according to the invention in cross section.
  • the first check valve 25 corresponds to the first check valve 25 shown in FIG. 1.
  • the second check valve 29 shown in FIG. 1b is illustrated and explained below with reference to FIG. 4a and FIG. 4b, which shows an enlarged section of FIG. 4a.
  • the second check valve 29 consists of a sleeve 45.
  • a sealing seat 49 for a ball 51 in particular a ceramic ball, worked out.
  • the ball 51 is pressed by a closing spring 53, which is supported against a locking screw 55, on the sealing seat 49.
  • a closing spring 53 By using a closing spring 53, the efficiency of the radial piston pump according to the invention can be increased by several percentage points, since the return flow of fuel from the high-pressure passage 27, not shown in FIG. 4b, into the delivery space 15, which is likewise not shown, is suppressed.
  • the sleeve 45 is pressed onto a shoulder 57 of the closure screw 55, so that the second check valve 29 according to the invention can be preassembled and tested together with the closure screw 55.
  • the sleeve 45 On its side facing away from the screw plug 55 face 59, the sleeve 45 has a circumferential biting edge 61, which serves to seal the second check valve 29 against the cylinder head 17.
  • a transverse bore 63 and an annular groove 64 in the sleeve 45 allow the outflow of fuel when the second check valve is open in a bore 65 in the cylinder head 17th
  • FIG. 5 shows a further exemplary embodiment of a radial piston pump according to the invention.
  • the second check valve 29 is arranged on the side 67 of the cylinder head 17 which faces in the housing 1.
  • the sealing seat 49 is incorporated in the cylinder head 17.
  • a cage 69 is pressed, which receives a closing spring 53 which presses the ball 51 against the sealing seat 49.
  • This second check valve 29 according to the invention is very easy to manufacture and assemble. It can also be used as the first check valve 25, for example in an embodiment according to FIG. In this case, it is particularly advantageous in the production that the sealing seat 41 of the first check valve 25 and the sealing seat 49 of the second check valve are arranged parallel to one another, which facilitates their machining in one clamping of the cylinder head.
  • the cage 69 is shown with inserted closing spring 53 in a longitudinal section and a view from above without closing spring 53.

Abstract

Radial piston pump comprises preferably several pump elements arranged radially to a drive shaft positioned in a pump housing (1). The pump elements are operated by the drive shaft and each pump element has an intake side and a high pressure side. The pump housing has high pressure channels (27a-c) which connect the high pressure side of a pump element to a high pressure connection (33). The high pressure channels have very few branches (35, 37). The angle (alpha , beta ) between a high pressure channel and another high pressure channel is approximately 90[deg]. Preferred Features: The high pressure channels are reinforced by tubular inserts (39a-c) made of a strong material, especially high strength steel.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Einspritzsystem, mit vorzugsweise mehreren bezüglich einer in einem Pumpengehäuse gelagerten Antriebswelle radial angeordneten Pumpenelementen, wobei die Pumpenelemente von der Antriebswelle betätigt werden und je eine Saugseite und eine Hochdruckseite aufweisen, und mit Hochdruckkanälen im Pumpengehäuse, welche jeweils die Hochdruckseite eines Pumpenelements mit einem Hochdruckanschluss im Pumpengehäuse verbinden.The invention relates to a radial piston pump for high-pressure fuel supply in fuel systems of internal combustion engines, in particular in a common rail injection system, preferably with a plurality of respect to a mounted in a pump housing drive shaft radially arranged pump elements, wherein the pump elements are actuated by the drive shaft and one suction side and one high pressure side and with high pressure passages in the pump housing, each connecting the high pressure side of a pump element to a high pressure port in the pump housing.

Ein solche Radialkolbenpumpe ist beispielsweise aus der DE 197 29 788.9 A1 bekannt. Diese in Serie gefertigte Radialkolbenpumpe erreicht hochdruckseitig Betriebsdrücke von bis zu 1300 bar. Daraus resultieren erhebliche mechanische Spannungen im Pumpengehäuse.Such a radial piston pump is for example from the DE 197 29 788.9 A1 known. This series-produced radial piston pump reaches operating pressures of up to 1300 bar on the high pressure side. This results in considerable mechanical stresses in the pump housing.

Um das Emissionsverhalten von Brennkraftmaschinen weiter zu verbessern und den Wirkungsgrad weiter zu erhöhen, ist es notwendig, höhere Einspritzdrücke als die genannten 1300 bar vorzusehen.In order to further improve the emission behavior of internal combustion engines and to further increase the efficiency, it is necessary to provide injection pressures higher than the aforementioned 1300 bar.

Der Erfindung liegt die Aufgabe zugrunde eine Radialkolbenpumpe so weiter zu entwickeln, dass sie für Drücke bis zu 2000 bar einsetzbar ist.The invention has for its object to develop a radial piston pump so that it can be used for pressures up to 2000 bar.

Diese Aufgabe wird erfindungsgemäß bei einer Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen mit vorzugsweise mehreren bezüglich einer in einem Pumpengehäuse gelagerten Antriebswelle radial angeordneten Pumpenelementen, wobei die Pumpenelemente von der Antriebswelle betätigt werden und je eine Saugseite und eine Hochdruckseite aufweisen und mit Hochdruckkanälen im Pumpengehäuse, welche jeweils die Hochdruckseite eines Pumpenelements mit einem Hochdruckanschluss im Pumpengehäuse verbinden, dadurch gelöst, dass jeder Hochdruckkanal die Hochdruckseite eines Pumpenelements direkt mit dem Hochdruckanschluß verbindet.This object is achieved according to the invention in a radial piston pump for high-pressure fuel supply in fuel injection systems of internal combustion engines with preferably several with respect to a stored in a pump housing drive shaft radially arranged pump elements, the pump elements are actuated by the drive shaft and each have a suction side and a high pressure side and with high pressure channels in the pump housing, which each connect the high pressure side of a pump element with a high pressure port in the pump housing, achieved in that each high pressure channel connects the high pressure side of a pump element directly to the high pressure port.

Vorteile der ErfindungAdvantages of the invention

Durch die erfindungsgemäße Führung der Hochdruckkanäle im Pumpengehäuse ist es möglich, trotz gesteigerter Pumpendrücke eine Reduktion der an den kritischen Stellen des Pumpengehäuses auftretenden Maximalspannungen zu erzielen. Dadurch kann die erfindungsgemäße Radialkolbenpumpe bei höheren Drücken betrieben werden, wobei gleichzeitig die Materialbeanspruchung zurückgeht.Due to the inventive guidance of the high-pressure channels in the pump housing, it is possible to achieve a reduction of the maximum stresses occurring at the critical points of the pump housing despite increased pump pressures. As a result, the radial piston pump according to the invention can be operated at higher pressures, at the same time reducing the material stress.

Die auftretenden Maximalspannungen wurden durch FEM-Berechnungen ermittelt. Bei Versuchen mit Prototypen hat sich die verbesserte Druckfestigkeit des Pumpengehäuses aufgrund der erfindungsgemäßen Verlegung der Hochdruckkanäle nachweisen lassen.The occurring maximum stresses were determined by FEM calculations. In experiments with prototypes, the improved pressure resistance of the pump housing has been demonstrated due to the installation of the high-pressure channels according to the invention.

In Ergänzung der Erfindung ist vorgesehen, dass die Oberflächen der Hochdruckkanäle verdichtet und mit Druckeigenspannungen versehen werden, insbesondere dadurch, dass durch die Hochdruckkanäle eine Kugel hindurchgezogen oder gepresst wird, deren Durchmesser geringfügig größer als der Durchmesser der Hochdruckkanäle ist. Diese Maßnahme erhöht die Druckfestigkeit des Pumpengehäuses im Bereich der Hochdruckkanäle weiter.In addition to the invention it is provided that the surfaces of the high-pressure channels are compressed and provided with compressive residual stresses, in particular by the fact that a ball is pulled or pressed through the high-pressure channels, the diameter of which is slightly larger than the diameter of the high pressure channels is. This measure further increases the pressure resistance of the pump housing in the area of the high-pressure channels.

Es kann erfindungsgemäß auch vorgesehen sein, dass die Hochdruckkanäle gehärtet, insbesondere induktionsgehärtet, sind. Zur weiteren Minimierung der unter Druckbeanspruchung auftretenden Maximalspannungen des Pumpengehäuses ist vorgesehen, dass die Hochdruckkanäle im Bereich von Querschnittsänderungen und/oder Einmündungen von anderen Hochdruckkanälen verrundet, insbesondere hydroerosiv verrundet, sind.It can also be provided according to the invention that the high-pressure channels are hardened, in particular induction-hardened. In order to further minimize the maximum stresses of the pump housing occurring under compressive stress, it is provided that the high-pressure channels are rounded in the region of cross-sectional changes and / or junctions of other high-pressure channels, in particular rounded in a hydroerosive manner.

Eine besonders vorteilhafte Ausgestaltung der erfindungsgemäßen Radialkolbenpumpe sieht vor, dass die Hochdruckkanäle durch je einen rohrförmigen Einsatz, insbesondere einem Einsatz aus einem hochfesten Werkstoff, wobei sich hochfester Stahl als besonders geeignet erwiesen hat, verstärkt sind. Die erfindungsgemäßen rohrförmigen Einsätze werden vor dem Gießen wie ein Kern in die Gussform eingelegt. Beim Gießen verbinden sich Pumpengehäuse und rohrförmige Einsätze sehr gut miteinander. Dadurch dass wegen der rohrförmigen Einsätze die Hochdruckkanäle aus einem anderen, besonders bevorzugt einem festeren Werkstoff bestehen, als das übrige Pumpengehäuse, findet eine Anpassung der Bauteilfestigkeit an die lokalen Beanspruchungen und Spannungen statt. Somit ist einerseits gewährleistet, dass im Bereich der Hochdruckkanäle, wo die höchsten Spannungen des Betriebs auftreten, ein hochfester Werkstoff zum Einsatz kommt, der die auftretenden Spannungen sicher aufnehmen kann und andererseits das übrige Pumpengehäuse aus einem vergleichsweise kostengünstigen Werkstoff hergestellt werden kann, der noch dazu gut bearbeitbar ist und gute Gleiteigenschaften aufweist.A particularly advantageous embodiment of the radial piston pump according to the invention provides that the high-pressure channels are each reinforced by a tubular insert, in particular an insert made of a high-strength material, with high-strength steel being found to be particularly suitable. The tubular inserts according to the invention are inserted into the casting mold like a core before casting. When casting pump housing and tubular inserts combine very well with each other. The fact that because of the tubular inserts, the high-pressure channels of a different, more preferably a firmer material than the rest of the pump housing, there is an adaptation of the component strength to the local stresses and strains. Thus, on the one hand ensures that in the field of high-pressure channels, where the highest voltages of operation occur, a high-strength material is used, which can safely absorb the stresses occurring and on the other hand, the rest of the pump housing can be made of a relatively inexpensive material, in addition to good machinability and has good sliding properties.

Ein weiterer Vorteil der rohrförmigen erfindungsgemäßen Einsätze ist, dass, im Gegensatz zu konventionellen Bohrungen, die Hochdruckkanäle gekrümmt oder teilweise gekrümmt ausgeführt werden können. Auch ist es möglich, dass durch jeweils einen Einsatz die Hochdruckseite eines Pumpenelements direkt mit dem Hochdruckanschluss im Pumpengehäuse verbunden wird, so dass keine Verzweigungen der Hochdruckkanäle erforderlich sind. Dies wirkt sich günstig auf die im Pumpengehäuse auftretenden Maximalspannungen, auf die Herstellungskosten und insbesondere die Fertigungssicherheit aus.Another advantage of the tubular inserts according to the invention is that, in contrast to conventional bores, the high-pressure ducts can be curved or partially curved. It is also possible that the high pressure side of a pump element is connected directly to the high pressure port in the pump housing by one use, so that no Branching of the high-pressure channels are required. This has a favorable effect on the maximum stresses occurring in the pump housing, on the manufacturing costs and in particular the manufacturing reliability.

Bei einer weiteren erfindungsgemäßen Variante einer Radialkolbenpumpe ist vorgesehen, dass jedes Pumpenelement eine Zylinderbohrung und einen Zylinderkopf aufweist, dass der Kolben in der Zylinderbohrung oszilliert und einen Förderraum begrenzt, dass auf der Saugseite ein erstes Rückschlagventil angeordnet ist, und dass auf der Hochdruckseite ein zweites Rückschlagventil angeordnet ist. Es hat sich als vorteilhaft erwiesen, wenn die Zylinderbohrung als Sackloch ausgebildet ist und das erste Rückschlagventil am Grund des Sacklochs angeordnet ist. Durch die Ausbildung der Zylinderbohrung als Sackloch wird eine Dichtstelle eingespart.In a further variant of a radial piston pump according to the invention, it is provided that each pump element has a cylinder bore and a cylinder head, that the piston oscillates in the cylinder bore and delimits a delivery space, that a first check valve is arranged on the intake side, and that a second check valve is arranged on the high pressure side is arranged. It has proven to be advantageous if the cylinder bore is formed as a blind hole and the first check valve is arranged at the bottom of the blind hole. By forming the cylinder bore as a blind hole a sealing point is saved.

In weiterer Ergänzung der Erfindung ist vorgesehen, dass das zweite Rückschlagventil eine Hülse mit einer gestuften Mittenbohrung aufweist, dass die gestufte Mittenbohrung einen Dichtsitz für ein Ventilglied, insbesondere eine Kugel besonders bevorzugt eine Keramikkugel, aufweist, und dass die Hülse einer Verschlussschraube dichtend gegen den Zylinderkopf gepresst ist. Dieses zweite Rückschlagventil hat den Vorteil, dass es sehr einfach aufgebaut ist und außerhalb der Radialkolbenpumpe geprüft werden kann. In der Radialkolbenpumpe bzw. dem Pumpenelement ist lediglich eine Dichtfläche vorzusehen, die das eingeschraubte zweite Rückschlagventil stirnseitig abdichtet. Eine solche Dichtfläche ist fertigungstechnisch einfach zu beherrschen, so dass die Abdichtung der Hochdruckseite des Pumpenelements zur Umgebung an dieser Stelle durch die Verwendung des erfindungsgemäßen zweiten Rückschlagventils vereinfacht wird.In a further feature of the invention, it is provided that the second check valve has a sleeve with a stepped central bore, that the stepped central bore has a sealing seat for a valve member, in particular a ball particularly preferably a ceramic ball, and that the sleeve of a closure screw sealing against the cylinder head pressed. This second check valve has the advantage that it is very simple and can be tested outside the radial piston pump. In the radial piston pump or the pump element, only a sealing surface is provided, which seals the screwed second check valve on the front side. Such a sealing surface is easy to control in terms of production, so that the sealing of the high-pressure side of the pump element to the environment at this point is simplified by the use of the second check valve according to the invention.

Die Abdichtung der Hochdruckseite gegenüber der Umgebung ist besonders wirkungsvoll, wenn die Hülse an ihrer der Verschlussschraube angewandten Stirnfläche eine Beißkante aufweist, so dass die Flächenpressung erhöht und auch eine plastische Verformung der Dichtflächen möglich wird, was die Dichtfunktion weiter verbessert.The sealing of the high pressure side relative to the environment is particularly effective when the sleeve has a biting edge on its end face applied to the screw plug, so that the surface pressure increases and Also, a plastic deformation of the sealing surfaces is possible, which further improves the sealing function.

Wenn die Hülse mit der Verschlussschraube, insbesondere im Bereich der Mittenbohrung, verpresst wird, erleichtert sich die Montage des Rückschlagventils weiter, da der Zusammenhalt eines montierten und geprüften Rückschlagsventils stets gewährleistet ist.If the sleeve with the screw plug, in particular in the region of the center hole, is compressed, the assembly of the check valve facilitates further, since the cohesion of a mounted and tested check valve is always guaranteed.

Um die hydraulische Verbindung zwischen dem Förderraum einerseits und dem Hochdruckanschluss im Pumpengehäuse andererseits bei geöffnetem zweitenTo the hydraulic connection between the pumping chamber on the one hand and the high pressure port in the pump housing on the other hand with the second open

Rückschlagventil stets zu gewährleisten, ist vorgesehen, dass die Hülse eine Querbohrung und eine Ringnut aufweist und das die Querbohrung und Ringnut eine hydraulische Verbindung der Mittenbohrung zum Förderraum herstellen.Always ensure check valve, it is provided that the sleeve has a transverse bore and an annular groove and that produce the transverse bore and groove a hydraulic connection of the central bore to the delivery chamber.

Bei einer weiteren Variante eines ersten oder zweiten Rückschlagventils ist ein Dichtsitz an der dem Pumpengehäuse zugewandten Seite des Zylinderkopfs in diesen eingearbeitet, wobei das Rückschlagventil einen Käfig aufweist in dem eine auf das Ventilglied, insbesondere eine Kugel, wirkende Schließfeder angeordnet ist. Durch die Schließfeder wird das Rückströmen von Kraftstoff verringert, was sich vorteilhaft auf den Pumpenwirkungsgrad auswirkt.In a further variant of a first or second check valve, a sealing seat on the pump housing facing side of the cylinder head is incorporated in this, wherein the check valve has a cage in which a on the valve member, in particular a ball, acting closing spring is arranged. By the closing spring, the return flow of fuel is reduced, which has an advantageous effect on the pump efficiency.

Die Montage des erfindungsgemäßen Rückschlagventils in dem Pumpenelement wird vereinfacht, wenn der Käfig in eine den Dichtsitz umfassende Stufenbohrung eingepresst wird.The assembly of the check valve according to the invention in the pump element is simplified if the cage is pressed into a stepped bore comprising the sealing seat.

Eine fertigungstechnisch vorteilhafte Ausführungsform sieht vor, dass die Zylinderbohrung als Sackloch ausgebildet ist, dass das erste Rückschlagventil nach einem der Ansprüche 17 und 18 am Grund des Sacklochs angeordnet ist, so dass der Dichtsitz von
erstem und zweitem Rückschlagventil in einer Aufspannung hergestellt werden kann und die Montage des ersten und zweiten Rückschlagventils in der gleichen Richtung erfolgt.A manufacturing technology advantageous embodiment provides that the cylinder bore is formed as a blind hole, that the first check valve according to one of claims 17 and 18 is arranged at the bottom of the blind hole, so that the sealing seat of
first and second check valve can be made in one setting and the assembly of the first and second check valve in the same direction.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen zu entnehmen.Further advantages and advantageous embodiments of the invention are given in the following drawings, their description and the claims.

Es zeigen:

  • Figur 1a eine Ansicht von vorne eines ersten Ausführungsbeispiels einer erfindungsgemäßen Radialkolbenpumpe
  • Figur 1b einen Längsschnitt durch das Ausführungsbeispiel gemäß Figur 1a, und
  • Figur 1c einen Querschnitt durch das Ausführungsbeispiel entlang der Linie A-A,
  • Figur 2 eine 3D-Darstellung eines Ausführungsbeispiels eines erfindungsgemäßen Pumpengehäuses,
  • Figur 3 ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Zylinderkopfs,
  • Figur 4 und 5 weitere Ausführungsbeispiele von erfindungsgemäßen Zylinderköpfen im Längsschnitt,
  • Figur 6a und B Details des Rückschlagventils gemäß dem Ausführungsbeispiel von Fig. 5.
Show it:
  • Figure 1a is a front view of a first embodiment of a radial piston pump according to the invention
  • Figure 1b shows a longitudinal section through the embodiment of Figure 1a, and
  • 1c shows a cross section through the embodiment along the line AA,
  • FIG. 2 shows a 3D representation of an exemplary embodiment of a pump housing according to the invention,
  • FIG. 3 shows a further exemplary embodiment of a cylinder head according to the invention,
  • 4 and 5 further embodiments of cylinder heads according to the invention in longitudinal section,
  • FIGS. 6 a and b show details of the check valve according to the exemplary embodiment of FIG. 5.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Figur 1 ist ein Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe in einer Ansicht von vorne (Figur 1A), im Längsschnitt (Figur 1B) und einem Querschnitt entlang der Schnittlinie A-A dargestellt. Die Radialkolbenpumpe besteht aus einem Pumpengehäuse 1, in der eine Antriebswelle 3 drehbar gelagert ist. Das Pumpengehäuse 1 kann vorteilhafterweise aus Grauguß mit globularem Graphit (GGG) hergestellt werden. Die Antriebswelle 3 weist einen exzentrischen Abschnitt 5 auf. Der exzentrische Abschnitt 5 treibt über einen Polygonring 7 drei über den Umfang verteilte Pumpenelemente 9 an. Jedes Pumpenelement 9 weist einen Kolben 11 auf, der in einer Zylinderbohrung 13 geführt ist und einen Förderraum 15 begrenzt. In der Figur 1c sind nicht an allen Pumpenelementen 9 die einzelnen Bauteile mit Bezugszeichen versehen, um die Übersichtlichkeit nicht unnötig zu verschlechtern. Die drei Pumpenelemente 9 sind jedoch alle gleich aufgebaut.FIG. 1 shows an exemplary embodiment of a radial piston pump according to the invention in a front view (FIG. 1A), in a longitudinal section (FIG. 1B) and in a cross section along the section line A-A. The radial piston pump consists of a pump housing 1, in which a drive shaft 3 is rotatably mounted. The pump housing 1 may advantageously be made of cast iron with globular graphite (GGG). The drive shaft 3 has an eccentric portion 5. The eccentric portion 5 drives via a polygon ring 7 three circumferentially distributed pump elements 9 at. Each pump element 9 has a piston 11 which is guided in a cylinder bore 13 and limits a delivery chamber 15. In FIG. 1c, the individual components are not provided with reference numerals on all pump elements 9 in order not to worsen the clarity unnecessarily. However, the three pump elements 9 are all constructed the same.

In einem Zylinderkopf 17 der Pumpenelemente 9 ist eine Saugseite 19 und eine Hochdruckseite 21 vorhanden. Die Saugseite 19 des Zylinderkopfs 17 wird über eine Niederdruckbohrung 23 im Pumpengehäuse mit Kraftstoff versorgt. Auf der Saugseite 19 ist ein erstes Rückschlagventil 25 angeordnet, welches das Rückströmen von Kraftstoff (nicht dargestellt) aus dem Förderraum 15 in die Niederdruckbohrung 23 verhindert.In a cylinder head 17 of the pump elements 9, there is a suction side 19 and a high pressure side 21. The suction side 19 of the cylinder head 17 is supplied with fuel via a low-pressure bore 23 in the pump housing. On the suction side 19, a first check valve 25 is arranged, which prevents the return flow of fuel (not shown) from the delivery chamber 15 into the low-pressure bore 23.

Die Hochdruckseite 21 des Pumpenelements 9 mündet in einen Hochdruckkanal 27 im Pumpengehäuse 1. Auf der Hochdruckseite 21 des Pumpenelements ist ein zweites Rückschlagventil 29 vorgesehen, welches das Rückströmen von unter hohem Druck stehendem Kraftstoff aus dem Hochdruckkanal 27 in den Förderraum 15 verhindert. Die Pumpenelemente 9 sind mittels nicht dargestellter Schrauben mit dem Pumpengehäuse 1 verschraubt und durch die Verschraubung auf eine Zylinderfußfläche 31 des Pumpengehäuses 1 gepresst.The high pressure side 21 of the pump element 9 opens into a high pressure passage 27 in the pump housing 1. On the high pressure side 21 of the pump element, a second check valve 29 is provided, which prevents the backflow of fuel under high pressure from the high pressure passage 27 into the delivery chamber 15. The pump elements 9 are screwed by means not shown screws to the pump housing 1 and pressed by the screwing on a Zylinderfußfläche 31 of the pump housing 1.

Von jedem Pumpenelement 9 geht ein Hochdruckkanal 27 im Pumpengehäuse 1 ab und mündet in einem Hochdruckanschluss der in den Figuren 1a bis 1c nicht sichtbar ist. Der Verlauf der Hochdruckkanäle wird nachfolgend anhand der Figur 2 erläutert. In der Figur 1b ist in der unteren Hälfte ein zweiter Hochdruckanal 27 dargestellt. Da dieser Hochdruckkanal im wesentlichen senkrecht zur Zeichnungsebene verläuft, ist er in Figur 1b als kreisförmige Fläche dargestellt.From each pump element 9, a high pressure passage 27 in the pump housing 1 goes off and flows into a high pressure port which is not visible in FIGS. 1a to 1c. The course of the high pressure channels is explained below with reference to FIG 2. In the figure 1b, a second high-pressure channel 27 is shown in the lower half. Since this high-pressure channel is substantially perpendicular to the plane of the drawing, it is shown in Figure 1b as a circular surface.

Der bislang beschriebene Aufbau und die Funktionsweise einer solchen Radialkolbenpumpe sind aus dem Stand der Technik, beispielsweise aus der DE 197 29 788.9 A1 auf die hiermit ausrücklich Bezug genommen wird, bekannt, so dass auf eine detaillierte Erläuterung der Funktionsweise im Zusammenhang mit der vorliegenden Erfindung verzichtet wird.The structure described so far and the operation of such a radial piston pump are known from the prior art, for example from the DE 197 29 788.9 A1 to which reference is hereby expressly made, so that a detailed explanation of the operation in connection with the present invention will be omitted.

In der Figur 2 ist ein Pumpengehäuse 1 dreidmeinsional dargestellt. Aus dieser Darstellung ist der Verlauf der Hochdruckkanäle 27 gemäß einem ersten Ausführungsbeispiel der Erfindung deutlich zu erkennen.In the figure 2, a pump housing 1 is shown dreidmeinsional. From this representation, the course of the high-pressure channels 27 according to a first embodiment of the invention can be clearly seen.

In Figur 2 ist lediglich das Pumpengehäuse 1 dargestellt. Die Pumpenelemente 9 sind in Figur 2 nicht dargestellt. Da die Hochdruckkanäle 27 im Pumpengehäuse 1 mit dem vollen Förderdruck der Pumpenelemente beaufschlagt werden, entstehen während des Betriebs der Radialkolbenpumpe erhebliche Spannungen im Pumpengehäuse 1, die im wesentlichen aus den in den Hochdruckkanälen 27a bis 27c herrschenden Drücken resultieren. In der Serienfertigung werden bislang Radialkolbenpumpen mit eingesetzten Pumpenelementen 9 bei Betriebsdrücken von bis zu 1300 bar eingesetzt. Wenn nun die Betriebsdrücke weiter erhöht werden sollen, muss die Dauerfestigkeit des Pumpengehäuses vor allem im Bereich der Hochdruckkanäle 27a erhalten bleiben oder sogar verbessert werden. Durch die erfindungsgemäße Anordnung der Hochdruckkanäle 27a, 27b und 27c konnten die im Pumpengehäuse auftretenden Spannungen bei gleichen Drücken drastisch reduziert werden, so dass die zulässigen Betriebsdrücke bei gleicher Bauteilfestigkeit auf über 1800 bar angehoben werden konnten. Auch bei diesen im Vergleich zu den eingangs genannten Betriebsdrücke nach dem Stand der Technik (maximal 1300 bar) erhöhten Betriebsdrücken ist die mechanische Beanspruchung des Pumpengehäuses geringer als bei den Radialkolbenpumpen nach dem Stand der Technik.In Figure 2, only the pump housing 1 is shown. The pump elements 9 are not shown in FIG. Since the high-pressure channels 27 are acted upon in the pump housing 1 with the full delivery pressure of the pump elements, considerable stresses occur in the pump housing 1 during operation of the radial piston pump, which essentially result from the pressures prevailing in the high-pressure channels 27a to 27c. In series production so far radial piston pumps are used with pump elements 9 used at operating pressures of up to 1300 bar. Now, if the operating pressures are to be further increased, the fatigue strength of the pump housing, especially in the area of the high-pressure channels 27a must be maintained or even improved. The inventive arrangement of the high-pressure channels 27a, 27b and 27c, the voltages occurring in the pump housing could be drastically reduced at the same pressures, so that the permissible operating pressures at the same Component strength could be raised to over 1800 bar. Even with these compared to the above-mentioned operating pressures of the prior art (maximum 1300 bar) increased operating pressures, the mechanical stress of the pump housing is lower than in the radial piston pumps according to the prior art.

Dies wird erfindungsgemäß dadurch erreicht, dass die Zahl der Hochdruckkanäle minimiert wird. Im vorliegenden Fall genügen drei Hochdruckkanäle 27a, 27b, 27c um eine hydraulische Verbindung von den drei Zylinderfußflächen 31 zu einem Hochdruckanschluss 33 herzustellen. Es wird deutlich, dass bei diesem Ausführungsbeispiel die Hochdruckkanäle 27a, 27b und 27c gekrümmt ausgeführt sind und direkt, d.h. ohne Abzweigungen, von einer Zylinderfußfläche 31 zu dem Hochdruckanschluss 33 führen. Bei dieser Ausführungsform werden die aus den Betriebsdrücken resultierenden Belastungen des Pumpengehäuses 1 weiter reduziert, da keine Abzweigungen vorhanden sind. Fertigungstechnisch kann diese Ausführungsvariante durch gekrümmte rohrförmige Einsätze 39a, 39b und 39c realisiert werden. Durch diese rohrförmigen Einsätze 39a bis 39c kann die Festigkeit des Pumpengehäuses 1 weiter gesteigert werden. Die rohrförmigen Einsätze 39a bis 39c werden vor dem Gießen des Pumpengehäuses 1 in die Gussform eingelegt. Beim anschließenden Gießen des Pumpengehäuses 1 verbinden sich die rohrförmigen Einsätze 39 innig mit dem Pumpengehäuse 1, so dass die Kraftübertragung zwischen rohrförmigen Einsatz 31 und Pumpengehäuse 1 optimal ist.This is inventively achieved in that the number of high-pressure channels is minimized. In the present case, three high-pressure channels 27a, 27b, 27c suffice to establish a hydraulic connection from the three cylinder base surfaces 31 to a high-pressure connection 33. It will be appreciated that in this embodiment, the high pressure channels 27a, 27b, and 27c are curved, and are formed directly, i. without branches, lead from a Zylinderfußfläche 31 to the high pressure port 33. In this embodiment, the resulting from the operating pressures of the pump housing 1 are further reduced because there are no branches. Manufacturing technology, this embodiment can be realized by curved tubular inserts 39a, 39b and 39c. Through these tubular inserts 39a to 39c, the strength of the pump housing 1 can be further increased. The tubular inserts 39a to 39c are inserted into the mold prior to casting of the pump housing 1. During the subsequent casting of the pump housing 1, the tubular inserts 39 intimately connect to the pump housing 1, so that the power transmission between tubular insert 31 and pump housing 1 is optimal.

In Figur 3 ist ein Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe dargestellt, bei dem die Zylinderbohrung 13 im Pumpenelement 9 als Sacklochbohrung aufgeführt ist. Am Grund der Sacklochbohrung ist ein Dichtsitz 41 für das erste Rückschlagventil 25 vorgesehen. Das erste Rückschlagventil 25 kann baugleich wie das anhand der Figuren 5 und 6 beschriebene zweite Rückschlagventil 29 ausgeführt sein. Bei dem Ausführungsbeispiel gemäß Figur 3 wird der Kolben 11 ebenfalls über einen Polygonring sowie eine Kolbenfußplatte 43 angetrieben. Die Erfindung ist jedoch nicht auf Radialkolbenpumpen mit solchen Antrieben der Pumpenelemente 9 beschränkt. Es können vielmehr auch alternative Antriebe, beispielsweise durch Nockenscheiben oder ähnliches zum Einsatz kommen. Die Kolbenfüße können auch Tassenstößel umfassen, die im Pumpengehäuse 1 geführt werden (nicht dargestellt). In Figur 4a ist ein Zylinderkopf 17 eines weiteren erfindungsgemäßen Ausführungsbeispiels einer Radialkolbenpumpe im Querschnitt dargestellt. Das erste Rückschlagventil 25 entspricht dem in Figur 1 dargestellten ersten Rückschlagventil 25. Das in Figur 1b andeutungsweise dargestellte zweite Rückschlagventil 29 wird nachfolgend anhand der Figur 4a und der Figur 4b, die einen vergrößerten Ausschnitt aus der Figur 4a zeigt, dargestellt und erläutert.3 shows an embodiment of a radial piston pump according to the invention is shown, in which the cylinder bore 13 is listed in the pump element 9 as a blind hole. At the bottom of the blind hole a sealing seat 41 for the first check valve 25 is provided. The first check valve 25 may be identical in construction to the second check valve 29 described with reference to FIGS. 5 and 6. In the embodiment according to FIG. 3, the piston 11 also driven by a polygon ring and a Kolbenfußplatte 43. However, the invention is not limited to radial piston pumps with such drives of the pump elements 9. Rather, alternative drives, for example by cams or the like can be used. The piston feet may also include bucket tappets which are guided in the pump housing 1 (not shown). FIG. 4 a shows a cylinder head 17 of a further exemplary embodiment of a radial piston pump according to the invention in cross section. The first check valve 25 corresponds to the first check valve 25 shown in FIG. 1. The second check valve 29 shown in FIG. 1b is illustrated and explained below with reference to FIG. 4a and FIG. 4b, which shows an enlarged section of FIG. 4a.

Das zweite Rückschlagventil 29 besteht aus einer Hülse 45. In der gestuften Mittenbohrung 47 ist ein Dichtsitz 49 für eine Kugel 51, insbesondere eine Keramikkugel, ausgearbeitet. Die Kugel 51 wird von einer Schließfeder 53, welche sich gegen eine Verschlussschraube 55 abstützt, auf den Dichtsitz 49 gepresst. Durch den Einsatz einer Schließfeder 53 kann der Wirkungsgrad der erfindungsgemäßen Radialkolbenpumpe um mehrere Prozentpunkte gesteigert werden, da das Rückströmen von Kraftstoff aus dem in Figur 4b nicht dargestellten Hochdruckkanal 27 in den ebenfalls nicht dargestellten Förderraum 15 unterdrückt wird. Die Hülse 45 ist auf einen Absatz 57 der Verschlussschraube 55 aufgepresst, so dass das erfindungsgemäße zweite Rückschlagventil 29 zusammen mit der Verschlussschraube 55 vormontiert und geprüft werden kann. Auf ihrer der Verschlussschraube 55 abgewandten Stirnfläche 59 weist die Hülse 45 eine umlaufende Beißkante 61 auf, welche der Abdichtung des zweiten Rückschlagventils 29 gegen den Zylinderkopf 17 dient. Eine Querbohrung 63 sowie eine Ringnut 64 in der Hülse 45 erlauben das Abströmen von Kraftstoff bei geöffnetem zweiten Rückschlagventil in eine Bohrung 65 im Zylinderkopf 17.The second check valve 29 consists of a sleeve 45. In the stepped center bore 47, a sealing seat 49 for a ball 51, in particular a ceramic ball, worked out. The ball 51 is pressed by a closing spring 53, which is supported against a locking screw 55, on the sealing seat 49. By using a closing spring 53, the efficiency of the radial piston pump according to the invention can be increased by several percentage points, since the return flow of fuel from the high-pressure passage 27, not shown in FIG. 4b, into the delivery space 15, which is likewise not shown, is suppressed. The sleeve 45 is pressed onto a shoulder 57 of the closure screw 55, so that the second check valve 29 according to the invention can be preassembled and tested together with the closure screw 55. On its side facing away from the screw plug 55 face 59, the sleeve 45 has a circumferential biting edge 61, which serves to seal the second check valve 29 against the cylinder head 17. A transverse bore 63 and an annular groove 64 in the sleeve 45 allow the outflow of fuel when the second check valve is open in a bore 65 in the cylinder head 17th

In der Figur 5 ist ein weiteres erfindungsgemäßes Ausführungsbeispiel einer Radialkolbenpumpen dargestellt. Bei diesem Ausführungsbeispiel ist das zweite Rückschlagventil 29 an der im Gehäuse 1 zugewandten Seite 67 des Zylinderkopfs 17 angeordnet.FIG. 5 shows a further exemplary embodiment of a radial piston pump according to the invention. In this exemplary embodiment, the second check valve 29 is arranged on the side 67 of the cylinder head 17 which faces in the housing 1.

Der Dichtsitz 49 ist in den Zylinderkopf 17 eingearbeitet. An dem Dichtsitz 49 schließt eine zylindrische Bohrung 68 an. In die Bohrung 68 ist ein Käfig 69 eingepresst, der eine Schließfeder 53 aufnimmt, welche die Kugel 51 gegen den Dichtsitz 49 presst. Dieses erfindungsgemäße zweite Rückschlagventil 29 ist sehr einfach in der Herstellung und Montage. Es kann auch als erstes Rückschlagventil 25, beispielsweise bei einer Ausführungsform gemäß Figur 3, eingesetzt werden. Besonders vorteilhaft bei der Herstellung ist in diesem Fall, dass der Dichtsitz 41 des ersten Rückschlagventils 25 und der Dichtsitz 49 des zweiten Rückschlagventils parallel zueinander angeordnet sind, was deren Bearbeitung in einer Aufspannung des Zylinderkopfs erleichtert.The sealing seat 49 is incorporated in the cylinder head 17. At the sealing seat 49 includes a cylindrical bore 68 at. In the bore 68, a cage 69 is pressed, which receives a closing spring 53 which presses the ball 51 against the sealing seat 49. This second check valve 29 according to the invention is very easy to manufacture and assemble. It can also be used as the first check valve 25, for example in an embodiment according to FIG. In this case, it is particularly advantageous in the production that the sealing seat 41 of the first check valve 25 and the sealing seat 49 of the second check valve are arranged parallel to one another, which facilitates their machining in one clamping of the cylinder head.

In den Figuren 6a und 6b ist der Käfig 69 mit eingesetzter Schließfeder 53 in einem Längsschnitt und einer Ansicht von oben ohne Schließfeder 53 dargestellt.In the figures 6a and 6b, the cage 69 is shown with inserted closing spring 53 in a longitudinal section and a view from above without closing spring 53.

Alle in der Zeichnung, deren Beschreibung und den Patentansprüchen genannten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein.All in the drawing, the description and the claims mentioned features may be essential to the invention both individually and in any combination.

Claims (17)

Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Einspritzsystem, mit vorzugsweise mehreren bezüglich einer in einem Pumpengehäuse (1) gelagerten Antriebswelle (3) radial angeordneten Pumpenelementen (9), wobei die Pumpenelemente (9) von der Antriebswelle (3) betätigt werden und je eine Saugseite (19) und eine Hochdruckseite (21) aufweisen und mit Hochdruckkanälen (27) im Pumpengehäuse (1), welche jeweils die Hochdruckseite (21) eines Pumpenelements (9) mit einem Hochdruckanschluß (33) im Pumpengehäuse (1) verbinden, dadurch gekennzeichnet, dass jeder Hochdruckkanal (27 a, b, c) die Hochdruckseite (21) eines Pumpenelements (9) direkt mit dem Hochdruckanschluß (33) verbindet.Radial piston pump for high-pressure fuel supply in fuel injection systems of internal combustion engines, in particular in a common rail injection system, preferably with a plurality of in a pump housing (1) mounted drive shaft (3) radially arranged pump elements (9), wherein the pump elements (9) from the drive shaft ( 3) and each having a suction side (19) and a high pressure side (21) and with high pressure channels (27) in the pump housing (1), each having the high pressure side (21) of a pump element (9) with a high pressure port (33) in the pump housing (1), characterized in that each high pressure passage (27 a, b, c) connects the high pressure side (21) of a pump element (9) directly to the high pressure port (33). Radialkolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Oberflächen der Hochdruckkanäle (27a, 27b, 27c) verdichtet werden.Radial piston pump according to claim 1, characterized in that the surfaces of the high-pressure channels (27a, 27b, 27c) are compressed. Radialkolbenpumpe nach Anspruch 2, dadurch gekennzeichnet, dass durch die Hochdruckkanäle (27a, 27b, 27c) je eine Kugel hindurchgezogen oder gepresst wird, deren Durchmesser geringfügig größer als der Durchmesser des Hochdruckkanals (27a, 27b, 27c) ist.Radial piston pump according to claim 2, characterized in that a respective ball is pulled or pressed through the high-pressure channels (27a, 27b, 27c), whose diameter is slightly larger than the diameter of the high-pressure channel (27a, 27b, 27c). Radialkolbenpumpe nach einem der Ansprüche 2 und 3, dadurch gekennzeichnet, dass die Hochdruckkanäle (27a, 27b, 27c) gehärtet, insbesondere induktionsgehärtet, sind.Radial piston pump according to one of claims 2 and 3, characterized in that the high-pressure channels (27a, 27b, 27c) hardened, in particular induction hardened, are. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass die Hochdruckkanäle (27a, 27b, 27c) im Bereich von Querschnittsänderungen und/oder Abzweigungen (35, 37) von anderen Hochdruckkanälen (27a, 27b, 27c) verrundet, insbesondere hydroerosiv verrundet sind.Radial piston pump according to one of the preceding claims,
characterized in that the high-pressure channels (27a, 27b, 27c) in the region of cross-sectional changes and / or branches (35, 37) of other high-pressure channels (27a, 27b, 27c) rounded, in particular are rounded hydroerosive. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass die Hochdruckkanäle (27a, b, c) durch je einen rohrförmigen Einsatz (39 a, b, c) verstärkt sind.Radial piston pump according to one of the preceding claims,
characterized in that the high-pressure channels (27a, b, c) are reinforced by a respective tubular insert (39 a, b, c). Radialkolbenpumpe nach Anspruch 6, dadurch gekennzeichnet, dass die Einsätze (39 a, b, c) aus einem hochfesten Werkstoff, insbesondere aus hochfestem Stahl, bestehen.Radial piston pump according to claim 6, characterized in that the inserts (39 a, b, c) made of a high-strength material, in particular high-strength steel exist. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass mindestens ein Hochdruckkanal (27 a, b, c) teilweise gekrümmt ausgeführt ist.Radial piston pump according to one of the preceding claims,
characterized in that at least one high-pressure channel (27 a, b, c) is executed partially curved. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass jedes Pumpenelement (9) einen Kolben (11), eine Zylinderbohrung (13) und einen Zylinderkopf (17) aufweist, dass der Kolben (11) in der Zylinderbohrung (13) oszilliert und einen Förderraum (15) begrenzt, dass auf der Saugseite (19) ein erstes Rückschlagventil (25) angeordnet ist, und dass auf der Hochdruckseite (21) ein zweites Rückschlagventil (29) angeordnet ist.Radial piston pump according to one of the preceding claims,
characterized in that each pump element (9) comprises a piston (11), a cylinder bore (13) and a cylinder head (17), that the piston (11) in the cylinder bore (13) oscillates and limits a delivery space (15) on the suction side (19), a first check valve (25) is arranged, and that on the high pressure side (21), a second check valve (29) is arranged. Radialkolbenpumpe nach Anspruch 9, dadurch gekennzeichnet, dass das zweite Rückschlagventil (29) eine Hülse (45) mit einer gestuften Mittenbohrung (47) aufweist, dass die gestufte Mittenbohrung (47) einen Dichtsitz (49) für ein Ventilglied, insbesondere eine Kugel (51), aufweist, und dass die Hülse (45) von einer Verschlussschraube (55) dichtend gegen den Zylinderkopf (17) gepresst wird.Radial piston pump according to claim 9, characterized in that the second check valve (29) has a sleeve (45) with a stepped central bore (47) that the stepped central bore (47) has a sealing seat (49) for a valve member, in particular a ball (51 ), and that the sleeve (45) by a plug (55) sealingly against the cylinder head (17) is pressed. Radialkolbenpumpe nach Anspruch 10, dadurch gekennzeichnet, dass die Hülse (45) an ihrer der Verschlussschraube (55) abgewandten Stirnfläche (59) als Dichtfläche, insbesondere mit einer Beißkante (61), ausgeführt wird.Radial piston pump according to claim 10, characterized in that the sleeve (45) on its the screw plug (55) facing away from the end face (59) as a sealing surface, in particular with a biting edge (61) is executed. Radialkolbenpumpe nach Anspruch 10 oder 11, dadurch gekennzeichnet, dass die Hülse (45) mit der Verschlussschraube (55), insbesondere im Bereich der Mittenbohrung (47), verpresst ist.Radial piston pump according to claim 10 or 11, characterized in that the sleeve (45) with the closure screw (55), in particular in the region of the central bore (47), is pressed. Radialkolbenpumpe nach einem der Ansprüche 10 bis 12, dadurch gekennzeichnet, dass die Hülse (45) eine Querbohrung (61) und eine Ringnut (63) aufweist, und dass die Querbohrung (61) und die Ringnut (63) eine hydraulische Verbindung der Mittenbohrung (47) zum Förderraum (15) herstellen.Radial piston pump according to one of claims 10 to 12, characterized in that the sleeve (45) has a transverse bore (61) and an annular groove (63), and that the transverse bore (61) and the annular groove (63) has a establish hydraulic connection of the central bore (47) to the delivery chamber (15). Radialkolbenpumpe nach Anspruch 9 bis 13, dadurch gekennzeichnet, dass ein Dichtsitz (49) des zweiten Rückschlagventils (29) an der dem Pumpengehäuse (1) zugewandten Seite (67) des Zylinderkopfes (17) angeordnet ist.Radial piston pump according to claim 9 to 13, characterized in that a sealing seat (49) of the second check valve (29) on the pump housing (1) facing side (67) of the cylinder head (17) is arranged. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das erste und/oder zweite Rückschlagventil (25, 29) einen Käfig (69) aufweist, und dass in dem Käfig (69) eine auf das Ventilglied (51) wirkende Schließfeder (53) angeordnet ist.Radial piston pump according to one of the preceding claims, characterized in that the first and / or second check valve (25, 29) has a cage (69), and in that in the cage (69) acting on the valve member (51) closing spring (53) is arranged. Radialkolbenpumpe nach Anspruch 15 dadurch gekennzeichnet, dass der Käfig (69) in eine den Dichtsitz (49) umfassende Stufenbohrung (65) im Zylinderkopf (17) einpressbar ist.Radial piston pump according to claim 15, characterized in that the cage (69) in a sealing seat (49) comprehensive stepped bore (65) in the cylinder head (17) can be pressed. Radialkolbenpumpe nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass die Zylinderbohrung (13) als Sackloch ausgebildet ist, und dass das erste Rückschlagventil (25) am Grund des Sacklochs angeordnet ist.Radial piston pump according to one of the preceding claims,
characterized in that the cylinder bore (13) is formed as a blind hole, and that the first check valve (25) is arranged at the bottom of the blind hole.
EP20070109457 2002-05-14 2003-05-13 Radial piston pump for a fuel injection system having improved high-pressure resistance Expired - Lifetime EP1818539B1 (en)

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DE2002121305 DE10221305A1 (en) 2002-05-14 2002-05-14 Radial piston pump for fuel injection system with improved high pressure resistance
EP03749849A EP1506349B1 (en) 2002-05-14 2003-05-13 Radial piston pump for a fuel injection system having improved high-pressure resistance

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EP03749849A Division EP1506349B1 (en) 2002-05-14 2003-05-13 Radial piston pump for a fuel injection system having improved high-pressure resistance

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EP1506349B1 (en) 2009-08-05
JP2005525502A (en) 2005-08-25
JP4589104B2 (en) 2010-12-01
DE50312918D1 (en) 2010-09-02
CN100476209C (en) 2009-04-08
DE50311781D1 (en) 2009-09-17
EP1818539A3 (en) 2008-03-19
WO2003095839A1 (en) 2003-11-20
US7775192B2 (en) 2010-08-17
DE10221305A1 (en) 2003-11-27
EP1818539B1 (en) 2010-07-21
EP1506349A1 (en) 2005-02-16
US20050207908A1 (en) 2005-09-22
CN1653268A (en) 2005-08-10

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