EP1604112B1 - Radial piston pump - Google Patents

Radial piston pump Download PDF

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Publication number
EP1604112B1
EP1604112B1 EP04713078A EP04713078A EP1604112B1 EP 1604112 B1 EP1604112 B1 EP 1604112B1 EP 04713078 A EP04713078 A EP 04713078A EP 04713078 A EP04713078 A EP 04713078A EP 1604112 B1 EP1604112 B1 EP 1604112B1
Authority
EP
European Patent Office
Prior art keywords
pump housing
channel
sealing area
pressure
radial piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04713078A
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German (de)
French (fr)
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EP1604112A1 (en
Inventor
Werner Knauth
Uwe Nigrin
Ngoc-Tam Vu
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VDO Automotive AG
Original Assignee
Siemens AG
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Publication of EP1604112A1 publication Critical patent/EP1604112A1/en
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Classifications

    • 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
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • F04B1/0443—Draining of the housing; Arrangements for handling leaked fluids
    • 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
    • F04B53/22—Arrangements for enabling ready assembly or disassembly

Definitions

  • the invention relates to a radial piston pump for fuel high pressure generation in fuel injection systems.
  • a high-pressure fuel pump which has a pump housing and a plurality of cylinder inserts designed as cylinder heads. Each cylinder insert is fixed in the pump housing via a centering lug. From the pump housing, a suction line leads into the cylinder head. The fuel passes from the intake via an intake valve to the cylinder chamber. There, the fuel is compressed and then passes through a high-pressure valve and a high-pressure line back into the pump housing, from where the fuel to a common high-pressure accumulator, the so-called common rail arrives. Between the cylinder insert and the pump housing, an O-ring seal is arranged. To accommodate the O-ring seal, the cylinder insert has a groove.
  • the object of the invention is therefore to ensure a secure sealing of the high-pressure fuel pump with a simple assembly of the cylinder insert.
  • the invention is characterized in that the cylinder insert with an end face on a flattening of the pump housing rests and that the end face of the cylinder insert or the flattening of the pump housing has specifically designed raised sealing areas, which are small in relation to the entire face of the cylinder insert and the entire flattening of the pump housing, whereby a high surface pressure in the sealing area can be achieved.
  • the cylinder insert with an end face on a flattening of the pump housing rests and that the end face of the cylinder insert or the flattening of the pump housing has specifically designed raised sealing areas, which are small in relation to the entire face of the cylinder insert and the entire flattening of the pump housing, whereby a high surface pressure in the sealing area can be achieved.
  • an additional O-ring which significantly simplifies the installation of the cylinder insert. Damage to the sealing surface during assembly is largely excluded.
  • a preferred embodiment of the invention provides that a first raised sealing area is formed around the intake passage and a second raised sealing area around the high pressure passage.
  • the raised sealing areas can be made as small as possible, whereby a high surface pressure is made possible.
  • a further preferred embodiment of the invention provides that an additional third raised sealing area is formed around the first and the second sealing area, which completely surrounds the two sealing area. This ensures that in the event of a leak of the first and / or the second sealing area no fuel can pass through the sealing surfaces to the outside, but by the third enclosing sealing area, the tightness remains ensured.
  • FIG. 1 shows a detailed view of the high-pressure fuel pump.
  • the drawing shows a part of the pump housing 1 and a cylinder insert 2.
  • a plurality of preferably three at an angle of 120 ° staggered cylinder inserts are provided.
  • the cylinder insert 2 is fixed via a spigot in the pump housing 1 and rests with an end face 5 on a flattening 6 of the pump housing.
  • the cylinder insert 2 is clamped to the pump housing 1 via clamping means, not shown, preferably screws.
  • an intake passage 8 and a high-pressure passage 9 is introduced, each opening in the end face 5.
  • the pump housing 1 has a first, with the intake passage 8 corresponding channel 10, and a second, corresponding to the high-pressure passage 9 channel 11, which open into the flattening 6 of the pump housing 1.
  • the first channel 10 is arranged to the intake passage 8 and the second passage 11 is arranged substantially in alignment with the high-pressure passage 9.
  • the fuel passes from the pump housing 1, via the first, channel 10 to the intake passage 8 and an intake valve in the cylinder chamber 3. There, the fuel is compressed and then flows, via a high pressure valve, the high pressure passage 9 and the second channel 11 to a common high-pressure accumulator (not shown).
  • the end face 5 of the cylinder insert 2, which bears against the flattening 6 of the bottom housing 1, has a plurality of raised areas 12, 13, 14.
  • the raised areas 12, 13, 14 of the sealing area ie the bearing surface is reduced to the flattening 6 such that at the same tightening force a significantly higher surface pressure is achieved, as in the case of a flat end face.
  • a secure sealing of the cylinder insert 2 with respect to the pump housing 1 is achieved.
  • the first raised sealing area 12 is formed around the intake channel 8 and the second raised sealing area 13 around the high-pressure channel 9.
  • the sealing force is selectively introduced in the vicinity of the sealed areas.
  • the sealing surface can be minimized thereby, which leads to a high surface pressure in the sealing area.
  • an additional third raised sealing area 14 is formed, which completely encloses the two sealing areas 12, 13. This ensures that, in the event of a leak in the first and / or second sealing region, no fuel can escape to the outside via the sealing surfaces, but the tightness continues to be ensured by the third enclosing sealing region.
  • a cavity 15 is formed, in which the liquid can flow off in the event of a leakage of the first or second sealing area 12, 13.
  • a drain passage 16 is preferably provided. About the drain passage 16, the fuel can flow back to the fuel tank.
  • the cavity 15 can be used for monitoring purposes.
  • a corresponding sensor can be arranged within the cavity which, in the event of a leak in the first and / or second sealing region 12, 13, outputs a signal to a corresponding evaluation unit.
  • FIG. 2 shows an exploded view of the cylinder insert 2 used in FIG. 1, with a first raised sealing region 12 and a second raised sealing region 13.
  • the first and second raised sealing regions 12, 13 are substantially annular around the center of the intake passage 8 and the high pressure passage, respectively 9 trained.
  • the two raised sealing areas 12, 13 are completely enclosed by a third raised sealing area 14.
  • the fuel can flow into the cavity 15 and via the drainage channel 16 back to the fuel tank.
  • the targeted elaborate raised sealing portions 12, 13 and 14 are small in relation to the entire end face 5 of the cylinder insert 2. This results in a high surface pressure in the sealing area and thus a secure seal.
  • an elastomeric seal can additionally be provided in the region of the high-pressure passage 9.
  • the elastomer seal is preferably arranged together with a support ring 18 centrally in a, not shown, recess around the high-pressure channel 9.
  • four support surfaces 18 are preferably provided at the outer corners of the end face 5.
  • the sealing contour can advantageously be produced by electrochemical removal methods, by a screen printing method, by etching, eroding or surface embossing.
  • the raised areas are preferably 0.1 to 0.3 mm. This ensures that when clamping the cylinder insert with the pump housing only the raised areas have contact and the rest of the surface do not touch. At the same time, the necessary material removal remains low, resulting in a low processing time.
  • the proposed invention thus ensures a secure sealing of the cylinder insert relative to the pump housing.
  • the raised sealing areas and the high surface pressures that can be achieved thereby result in a high sealing force.
  • Additional sealing elements such as e.g. O-rings are not required. This simplifies the assembly effort considerably. In addition, incorrect assembly is largely excluded.
  • an additional third raised sealing area which surrounds the first and second sealing area, it is ensured that even in the event of a leak, the fuel can not escape from the pump housing.
  • the invention is not limited to the embodiments.
  • different embodiments of the raised sealing areas are possible.
  • the raised sealing areas may have different heights, whereby one can bring in the high pressure area, for example, a higher surface pressure than in the low pressure area.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen.The invention relates to a radial piston pump for fuel high pressure generation in fuel injection systems.

Aus der DE 198 41 642 C2 ist eine Kraftstoffhochdruckpumpe bekannt, die ein Pumpengehäuse und mehrere als Zylindereinsätze ausgebildete Zylinderköpfe aufweist. Jeder Zylindereinsatz ist über einen Zentrieransatz im Pumpengehäuse fixiert. Vom Pumpengehäuse führt eine Ansaugleitung in den Zylinderkopf. Der Kraftstoff gelangt von der Ansaugleitung über ein Ansaugventil zum Zylinderraum. Dort wird der Kraftstoff verdichtet und gelangt anschließend über ein Hochdruckventil und eine Hochdruckleitung zurück in das Pumpengehäuse, von wo der Kraftstoff zu einem gemeinsamen Hochdruckspeicher, dem so genannten Common-Rail, gelangt. Zwischen dem Zylindereinsatz und dem Pumpengehäuse ist eine O-Ring-Dichtung angeordnet. Zur Aufnahme der O-Ring-Dichtung weist der Zylindereinsatz eine Nut auf. Das Einlegen des O-Rings erfordert einen hohen Montageaufwand und es kann leicht passieren, dass der O-Ring nicht richtig in der Nut liegt. Beim Verschrauben des Zylindereinsatzes wird der O-Ring dann zwischen den Dichtflächen der beiden Bauteile eingequetscht und beschädigt. Dadurch kann Kraftstoff aus der Kraftstoffhochdruckpumpe austreten.From the DE 198 41 642 C2 a high-pressure fuel pump is known, which has a pump housing and a plurality of cylinder inserts designed as cylinder heads. Each cylinder insert is fixed in the pump housing via a centering lug. From the pump housing, a suction line leads into the cylinder head. The fuel passes from the intake via an intake valve to the cylinder chamber. There, the fuel is compressed and then passes through a high-pressure valve and a high-pressure line back into the pump housing, from where the fuel to a common high-pressure accumulator, the so-called common rail arrives. Between the cylinder insert and the pump housing, an O-ring seal is arranged. To accommodate the O-ring seal, the cylinder insert has a groove. Inserting the O-ring requires a great deal of installation effort and it can easily happen that the O-ring is not properly in the groove. When screwing the cylinder insert, the O-ring is then crushed between the sealing surfaces of the two components and damaged. As a result, fuel can escape from the high-pressure fuel pump.

Die Aufgabe der Erfindung ist es daher, bei einfacher Montage des Zylindereinsatzes, eine sichere Abdichtung der Kraftstoffhochdruckpumpe zu gewährleisten.The object of the invention is therefore to ensure a secure sealing of the high-pressure fuel pump with a simple assembly of the cylinder insert.

Die Aufgabe wird gelöst durch die Merkmale des Patentanspruchs 1. Vorteilhafte Ausgestaltung der Erfindung sind in den Unteransprüchen gekennzeichnet.The object is solved by the features of claim 1. Advantageous embodiment of the invention are characterized in the subclaims.

Die Erfindung zeichnet sich dadurch aus, dass der Zylindereinsatz mit einer Stirnfläche an einer Abflachung des Pumpengehäuses anliegt und dass die Stirnfläche des Zylindereinsatzes oder die Abflachung des Pumpengehäuses gezielt ausgearbeitete erhabene Dichtbereiche aufweist, die klein sind im Verhältnis zur gesamten Stirnfläche des Zylindereinsatzes sowie zur gesamten Abflachung des Pumpengehäuses, wodurch eine hohe Flächenpressung im Dichtbereich erzielbar ist. Hierdurch kann auf einem zusätzlichen O-Ring verzichtet werden, wodurch sich die Montage des Zylindereinsatzes deutlich vereinfacht. Eine Beschädigung der Dichtfläche bei der Montage ist weitgehend ausgeschlossen.The invention is characterized in that the cylinder insert with an end face on a flattening of the pump housing rests and that the end face of the cylinder insert or the flattening of the pump housing has specifically designed raised sealing areas, which are small in relation to the entire face of the cylinder insert and the entire flattening of the pump housing, whereby a high surface pressure in the sealing area can be achieved. As a result, can be dispensed with an additional O-ring, which significantly simplifies the installation of the cylinder insert. Damage to the sealing surface during assembly is largely excluded.

Eine bevorzugte Ausgestaltung der Erfindung sieht vor, dass ein erster erhabener Dichtbereich um den Ansaugkanal und ein zweiter erhabener Dichtbereich um den Hochdruckkanal ausgebildet ist. Hierdurch können die erhabenen Dichtbereiche möglichst klein gestaltet werden, wodurch eine hohe Flächenpressung ermöglicht wird.A preferred embodiment of the invention provides that a first raised sealing area is formed around the intake passage and a second raised sealing area around the high pressure passage. As a result, the raised sealing areas can be made as small as possible, whereby a high surface pressure is made possible.

Eine weitere bevorzugte Ausgestaltung der Erfindung sieht vor, dass ein zusätzlicher dritter erhabener Dichtbereich um den ersten und den zweiten Dichtbereich ausgebildet ist, der die beiden Dichtbereich vollständig umschließt. Hierdurch ist gewährleistet, dass im Falle einer Undichtigkeit des ersten und/oder des zweiten Dichtbereichs kein Kraftstoff über die Dichtflächen nach außen gelangen kann, sondern durch den dritten umschließenden Dichtbereich die Dichtigkeit weiterhin gewährleistet bleibt.A further preferred embodiment of the invention provides that an additional third raised sealing area is formed around the first and the second sealing area, which completely surrounds the two sealing area. This ensures that in the event of a leak of the first and / or the second sealing area no fuel can pass through the sealing surfaces to the outside, but by the third enclosing sealing area, the tightness remains ensured.

Ausführungsbeispiele der Erfindung werden im Folgenden anhand der schematischen Zeichnungen erläutert. Es zeigen:

Figur 1
eine Detailansicht der erfindungsgemäßen Kraftstoffhochdruckpumpe,
Figur 2
eine Explosionsdarstellung eines erfindungsgemäße Zylindereinsatzes.
Embodiments of the invention are explained below with reference to the schematic drawings. Show it:
FIG. 1
a detailed view of the high-pressure fuel pump according to the invention,
FIG. 2
an exploded view of a cylinder insert according to the invention.

Figur 1 zeigt eine Detailansicht der Kraftstoffhochdruckpumpe. Die Zeichnung zeigt einen Teil des Pumpengehäuses 1 sowie einen Zylindereinsatz 2. Üblicherweise sind mehrere vorzugsweise drei in einem Winkel von 120° zueinander versetzte Zylindereinsätze vorgesehen. Der Zylindereinsatz 2 ist über einen Zentrieransatz im Pumpengehäuse 1 fixiert und liegt mit einer Stirnfläche 5 an einer Abflachung 6 des Pumpengehäuses an. Der Zylindereinsatz 2 wird mit dem Pumpengehäuse 1 über nicht dargestellte Spannmittel, vorzugsweise Schrauben, verspannt. In den Zylindereinsatz 2 ist ein Ansaugkanal 8 sowie ein Hochdruckkanal 9 eingebracht, die jeweils in der Stirnfläche 5 münden. Das Pumpengehäuse 1 weist einen ersten, mit dem Ansaugkanal 8 korrespondierenden Kanal 10, sowie einen zweiten, mit dem Hochdruckkanal 9 korrespondierenden Kanal 11 auf, die in der Abflachung 6 des Pumpengehäuses 1 münden. Der erste Kanal 10 ist zu dem Ansaugkanal 8 und der zweite Kanal 11 ist zu dem Hochdruckkanal 9 im wesentlichen fluchtend angeordnet.
Der Kraftstoff gelangt vom Pumpengehäuse 1, über den ersten, Kanal 10 zum Ansaugkanal 8 und über ein Ansaugventil in den Zylinderraum 3. Dort wird der Kraftstoff verdichtet und strömt anschließend, über ein Hochdruckventil, den Hochdruckkanal 9 und den zweiten Kanal 11 zu einem gemeinsamen Hochdruckspeicher (nicht dargestellt).FIG. 1 shows a detailed view of the high-pressure fuel pump. The drawing shows a part of the pump housing 1 and a cylinder insert 2. Usually, a plurality of preferably three at an angle of 120 ° staggered cylinder inserts are provided. The cylinder insert 2 is fixed via a spigot in the pump housing 1 and rests with an end face 5 on a flattening 6 of the pump housing. The cylinder insert 2 is clamped to the pump housing 1 via clamping means, not shown, preferably screws. In the cylinder insert 2, an intake passage 8 and a high-pressure passage 9 is introduced, each opening in the end face 5. The pump housing 1 has a first, with the intake passage 8 corresponding channel 10, and a second, corresponding to the high-pressure passage 9 channel 11, which open into the flattening 6 of the pump housing 1. The first channel 10 is arranged to the intake passage 8 and the second passage 11 is arranged substantially in alignment with the high-pressure passage 9.
The fuel passes from the pump housing 1, via the first, channel 10 to the intake passage 8 and an intake valve in the cylinder chamber 3. There, the fuel is compressed and then flows, via a high pressure valve, the high pressure passage 9 and the second channel 11 to a common high-pressure accumulator (not shown).

Die Stirnfläche 5 des Zylindereinsatzes 2, welcher an der Abflachung 6 des Bodengehäuses 1 anliegt, weist mehrere erhabene Bereiche 12, 13, 14 auf. Durch die erhabenen Bereiche 12, 13, 14 wird der Dichtbereich d. h. die Auflagefläche an der Abflachung 6 derart verkleinert, dass bei gleicher Anzugskraft eine deutlich höhere Flächenpressung erreicht wird, als im Falle einer ebenen Stirnfläche. Hierdurch wird eine sichere Abdichtung des Zylindereinsatzes 2 gegenüber dem Pumpengehäuse 1 erreicht. Selbstverständlich ist es auch möglich die erhabenen Bereiche in der Abflachung 6 des Pumpengehäuses 1 auszubilden. Auch ist es möglich die erhabenen Bereiche sowohl im Zylindereinsatz 2, als auch im Pumpengehäuse 1 auszubilden. Aus Kostengründen ist es allerdings vorteilhaft die erhabenen Dichtbereiche nur in einem Bauteil vorzusehen und die korrespondierende Fläche als plane Fläche auszubilden. Auf eine hohe Güte der planen Dichtfläche kann dabei verzichtet werden, da die hohen Flächenpressungen einen Ausgleich der Unebenheiten, durch das elastische Verformen des Materials im Bereich der Dichtflächen, ermöglicht.The end face 5 of the cylinder insert 2, which bears against the flattening 6 of the bottom housing 1, has a plurality of raised areas 12, 13, 14. By the raised areas 12, 13, 14 of the sealing area ie the bearing surface is reduced to the flattening 6 such that at the same tightening force a significantly higher surface pressure is achieved, as in the case of a flat end face. As a result, a secure sealing of the cylinder insert 2 with respect to the pump housing 1 is achieved. Of course, it is also possible to form the raised areas in the flattening 6 of the pump housing 1. It is also possible to form the raised areas both in the cylinder insert 2 and in the pump housing 1. For cost reasons, however, it is advantageous to provide the raised sealing areas only in one component and to form the corresponding surface as a flat surface. In this case, a high quality of the planar sealing surface can be dispensed with, since the high surface pressures make it possible to compensate for the unevenness caused by the elastic deformation of the material in the region of the sealing surfaces.

Bei dem in Figur 1 gezeigten Ausführungsbeispiel ist der erste erhabene Dichtbereich 12 um den Ansaugkanal 8 und der zweite erhabene Dichtbereich 13 um den Hochdruckkanal 9 ausgebildet. Hierdurch wird die Dichtkraft gezielt in die Nähe der abzudichtenden Bereiche eingebracht. Die Dichtfläche kann dadurch minimiert werden, was zu einer hohen Flächenpressung im Dichtbereich führt.In the exemplary embodiment shown in FIG. 1, the first raised sealing area 12 is formed around the intake channel 8 and the second raised sealing area 13 around the high-pressure channel 9. As a result, the sealing force is selectively introduced in the vicinity of the sealed areas. The sealing surface can be minimized thereby, which leads to a high surface pressure in the sealing area.

Zusätzlich zu dem ersten und zweiten erhabenen Dichtbereich 12, 13 ist ein zusätzlicher dritter erhabener Dichtbereich 14 ausgebildet, der die beiden Dichtbereiche 12, 13 vollständig umschließt. Hierdurch ist gewährleistet, dass im Falle einer Undichtigkeit des ersten und/oder zweiten Dichtbereiches kein Kraftstoff über die Dichtflächen nach außen gelangen kann sondern durch den dritten umschließenden Dichtbereich die Dichtigkeit weiterhin gewährleistet bleibt. Durch den dritten erhabenen Dichtbereich 14, der den ersten und zweiten Dichtbereich 12, 13 vollständig umschließt, wird ein Hohlraum 15 gebildet, in dem die Flüssigkeit im Falle einer Undichtigkeit des ersten bzw. zweiten Dichtbereiches 12, 13 abfließen kann. Damit sich innerhalb des Hohlraums 15 kein Flüssigkeitsdruck aufbauen kann, ist vorzugsweise ein Ablaufkanal 16 vorgesehen. Über die Ablaufkanal 16 kann der Kraftstoff zurück zum Kraftstofftank fließen. Gleichzeitig kann der Hohlraum 15 zu Überwachungszwecken genutzt werden. Hierzu kann ein entsprechender Sensor innerhalb des Hohlraums angeordnet werden, der im Falle einer Undichtigkeit des ersten und/oder zweiten Dichtbereiches 12, 13 ein Signal an eine entsprechende Auswerteeinheit ausgibt.In addition to the first and second raised sealing area 12, 13, an additional third raised sealing area 14 is formed, which completely encloses the two sealing areas 12, 13. This ensures that, in the event of a leak in the first and / or second sealing region, no fuel can escape to the outside via the sealing surfaces, but the tightness continues to be ensured by the third enclosing sealing region. By the third raised sealing area 14, which completely encloses the first and second sealing area 12, 13, a cavity 15 is formed, in which the liquid can flow off in the event of a leakage of the first or second sealing area 12, 13. Thus, no fluid pressure can build up within the cavity 15, a drain passage 16 is preferably provided. About the drain passage 16, the fuel can flow back to the fuel tank. At the same time, the cavity 15 can be used for monitoring purposes. For this purpose, a corresponding sensor can be arranged within the cavity which, in the event of a leak in the first and / or second sealing region 12, 13, outputs a signal to a corresponding evaluation unit.

Figur 2 zeigt eine Explosionsdarstellung des in Fig. 1 verwendeten Zylindereinsatzes 2, mit einem ersten erhabenen Dichtbereiches 12 sowie einem zweiten erhabenen Dichtbereich 13. Der erste und zweite erhabene Dichtbereich 12, 13 ist im Wesentlichen ringförmig um das Zentrum des Ansaugkanals 8 bzw. des Hochdruckkanals 9 ausgebildet. Die beiden erhabenen Dichtbereiche 12, 13 werden von einem dritten erhabenen Dichtbereich 14 vollständig umschlossen. Bei einer evtl. Undichtigkeit einer der beiden Dichtflächen kann der Kraftstoff in den Hohlraum 15 und über den Ablaufkanal 16 zurück zum Kraftstofftank abfließen. Wie aus der Abbildung deutlich wird, sind die gezielt ausgearbeiteten erhabenen Dichtbereiche 12, 13 und 14 klein im Verhältnis zur gesamten Stirnfläche 5 des Zylindereinsatzes 2. Hierdurch ergibt sich eine hohe Flächenpressung im Dichtbereich und somit eine sichere Abdichtung.FIG. 2 shows an exploded view of the cylinder insert 2 used in FIG. 1, with a first raised sealing region 12 and a second raised sealing region 13. The first and second raised sealing regions 12, 13 are substantially annular around the center of the intake passage 8 and the high pressure passage, respectively 9 trained. The two raised sealing areas 12, 13 are completely enclosed by a third raised sealing area 14. In case of a possible leakage of one of the two sealing surfaces, the fuel can flow into the cavity 15 and via the drainage channel 16 back to the fuel tank. As is clear from the figure, the targeted elaborate raised sealing portions 12, 13 and 14 are small in relation to the entire end face 5 of the cylinder insert 2. This results in a high surface pressure in the sealing area and thus a secure seal.

Bei sehr hohen Kraftstoffdrücken kann zusätzlich im Bereich des Hochdruckkanals 9 eine Elastomerdichtung vorgesehen werden. Die Elastomerdichtung wird vorzugsweise zusammen mit einem Stützring 18 zentrisch in eine, nicht näher dargestellte, Ausnehmung um den Hochdruckkanal 9 angeordnet.At very high fuel pressures, an elastomeric seal can additionally be provided in the region of the high-pressure passage 9. The elastomer seal is preferably arranged together with a support ring 18 centrally in a, not shown, recess around the high-pressure channel 9.

Um ein Verkanten des Zylindereinsatzes 2 beim Verspannen am Pumpengehäuse 1 zu verhindern sind, vorzugsweise an den äußeren Ecken der Stirnfläche 5, vier Stützflächen 18 vorgesehen.In order to prevent tilting of the cylinder insert 2 during clamping on the pump housing 1, four support surfaces 18 are preferably provided at the outer corners of the end face 5.

Die Dichtkontur kann vorteilhaft durch elektrochemische Abtragungsverfahren, durch ein Siebdruckverfahren, durch Ätzen, Erodieren oder Flächenprägung hergestellt werden. Die erhabenen Bereiche stehen vorzugsweise 0,1 bis 0,3 mm hervor. Dies gewährleistet, dass beim Verspannen des Zylindereinsatzes mit dem Pumpengehäuse nur die erhabenen Bereiche Kontakt haben und die übrige Fläche sich nicht berühren. Gleichzeitig bleibt der notwendige Materialabtrag gering, wodurch sich eine geringe Bearbeitungszeit ergibt.The sealing contour can advantageously be produced by electrochemical removal methods, by a screen printing method, by etching, eroding or surface embossing. The raised areas are preferably 0.1 to 0.3 mm. This ensures that when clamping the cylinder insert with the pump housing only the raised areas have contact and the rest of the surface do not touch. At the same time, the necessary material removal remains low, resulting in a low processing time.

Durch die vorgeschlagene Erfindung ist somit eine sichere Abdichtung des Zylindereinsatzes gegenüber dem Pumpengehäuse gewährleistet. Durch die erhabenen Dichtbereiche und die hierdurch erzielbare hohen Flächenpressungen ergibt sich eine hohe Dichtkraft. Zusätzliche Dichtelemente wie z.B. O-Ringe sind nicht erforderlich. Hierdurch vereinfacht sich der Montageaufwand erheblich. Zudem wird eine Fehlmontage weitgehend ausgeschlossen. Durch einen zusätzlichen dritten erhabenen Dichtbereich, der den ersten und zweiten Dichtbereich umschließt, wird sichergestellt, dass auch im Falle einer Undichtigkeit der Kraftstoff nicht am Pumpengehäuse austreten kann.The proposed invention thus ensures a secure sealing of the cylinder insert relative to the pump housing. The raised sealing areas and the high surface pressures that can be achieved thereby result in a high sealing force. Additional sealing elements such as e.g. O-rings are not required. This simplifies the assembly effort considerably. In addition, incorrect assembly is largely excluded. By an additional third raised sealing area, which surrounds the first and second sealing area, it is ensured that even in the event of a leak, the fuel can not escape from the pump housing.

Die Erfindung ist selbstverständlich nicht auf die Ausführungsbeispiele beschränkt. Insbesondere sind unterschiedliche Ausbildungen der erhabenen Dichtbereiche möglich. So können beispielsweise die erhabenen Dichtbereiche unterschiedliche Höhen aufweisen, wodurch man im Hochdruckbereich beispielsweise eine höhere Flächenpressung einbringen kann als im Niederdruckbereich. Of course, the invention is not limited to the embodiments. In particular, different embodiments of the raised sealing areas are possible. Thus, for example, the raised sealing areas may have different heights, whereby one can bring in the high pressure area, for example, a higher surface pressure than in the low pressure area.

Claims (7)

  1. A radial piston pump for generating high-pressure fuel injection in a fuel injection system, with
    - a pump housing (1)
    - a pump shaft and
    - at least one cylinder insert (2) arranged radially to the pump shaft in which a cylinder space (3) is embodied within which a piston (4) is guided so that it is able to be moved to and fro, with
    - one face (5) of the cylinder insert (2) lying against a flat section (6) of the pump housing and being braced against the latter by bracing means,
    - the cylinder insert featuring at least one inlet channel (8) through which the fuel can be supplied to the cylinder space,
    - the cylinder insert featuring at least one high-pressure channel (9) via which the fuel can flow out of the cylinder space,
    - the inlet channel as well as the high-pressure channel ending in the end face of the cylinder insert, and
    - a first corresponding channel (10) and a second corresponding channel (11) being arranged in the pump housing, which end in the flat section of the pump housing and essentially mate with the inlet channel or the high-pressure channel respectively.
    characterised in that the end face (5) of the cylinder insert (2) and/or the flat section (6) of the pump housing (1) feature explicitly formed, raised sealing areas (12) (13) (14) which are small in relation to the overall end face (5) of the cylinder insert (2) as well to the overall flat section (6) of the pump housing (1), which allows a high surface pressure in the seal area (12) (13) (14) to be achieved.
  2. The radial piston pump according to claim 1,
    characterised in that a first raised sealing area (12) is embodied around the inlet channel (8) and a second raised sealing area (13) around the high-pressure channel (9) .
  3. The radial piston pump according to claim 2,
    characterised in that the first and second raised sealing area (12) (13) are essentially embodied in the form of a ring around the center of the inlet channel (8) or the high-pressure channel (9) respectively.
  4. The radial piston pump according to claim 2,
    characterised in that an additional third raised sealing area (14) is embodied around the first and second sealing area (12) (13), entirely enclosing the two sealing areas.
  5. The radial piston pump according to claim 4,
    characterised in that, in the flat section (6) of the pump housing, within the surface enclosed by the third sealing area (14), an outlet channel (16) is embodied, to take away any possible leakage flow from the first and/or second sealing area as well to monitor the sealing system.
  6. The radial piston pump according to one of the previous claims,
    characterised in that an additional elastomer seal is arranged around the high pressure channel (9).
  7. The radial piston pump according to claim 6,
    characterised in that the elastomer seal is embodied as an annular seal and is supported at its outer circumference by a support ring (18).
EP04713078A 2003-03-07 2004-02-20 Radial piston pump Expired - Lifetime EP1604112B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10310123A DE10310123A1 (en) 2003-03-07 2003-03-07 Radial piston pump
DE10310123 2003-03-07
PCT/EP2004/001702 WO2004079190A1 (en) 2003-03-07 2004-02-20 Radial piston pump

Publications (2)

Publication Number Publication Date
EP1604112A1 EP1604112A1 (en) 2005-12-14
EP1604112B1 true EP1604112B1 (en) 2007-07-04

Family

ID=32891954

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04713078A Expired - Lifetime EP1604112B1 (en) 2003-03-07 2004-02-20 Radial piston pump

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Country Link
US (1) US7415920B2 (en)
EP (1) EP1604112B1 (en)
JP (1) JP4372782B2 (en)
CN (1) CN1756905B (en)
DE (2) DE10310123A1 (en)
WO (1) WO2004079190A1 (en)

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Publication number Priority date Publication date Assignee Title
DE10310124B4 (en) * 2003-03-07 2009-09-10 Continental Automotive Gmbh gasket
DE102006017036A1 (en) 2006-04-11 2007-10-18 Siemens Ag Radial piston pump for fuel high pressure supply in an internal combustion engine
US7240668B1 (en) * 2006-07-18 2007-07-10 Delphi Technologies, Inc. Fuel leak detection apparatus and method
JP4862077B2 (en) 2006-09-18 2012-01-25 ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング Valve devices for hydraulic machines
JP5295802B2 (en) * 2009-01-30 2013-09-18 ヤンマー株式会社 Fuel injection pump
JP6366539B2 (en) * 2015-05-29 2018-08-01 三菱重工業株式会社 Radial piston hydraulic machine, wind power generator, and seal construction method
DE102017222171A1 (en) * 2017-12-07 2019-06-13 Robert Bosch Gmbh Fuel delivery device for cryogenic fuels

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AT338049B (en) 1975-06-27 1977-07-25 Friedmann & Maier Ag FUEL INJECTION PUMP FOR INJECTION COMBUSTION MACHINES
JP3849067B2 (en) * 1995-03-30 2006-11-22 ボッシュ株式会社 Fuel injection pump
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DE19729789A1 (en) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Radial piston pump for high-pressure fuel supply
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DE19801398A1 (en) * 1998-01-16 1999-07-22 Bosch Gmbh Robert Radial piston pump for the fuel delivery to a motor fuel injection system
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IT1308782B1 (en) * 1999-07-02 2002-01-10 Elasis Sistema Ricerca Fiat IMPROVEMENTS TO A HIGH PRESSURE PUMP FOR THE FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE.
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DE10102233A1 (en) 2001-01-19 2002-07-25 Bosch Gmbh Robert High-pressure fuel system for internal combustion engines

Also Published As

Publication number Publication date
CN1756905A (en) 2006-04-05
US7415920B2 (en) 2008-08-26
EP1604112A1 (en) 2005-12-14
WO2004079190A1 (en) 2004-09-16
JP4372782B2 (en) 2009-11-25
DE10310123A1 (en) 2004-09-23
US20050287016A1 (en) 2005-12-29
JP2006519950A (en) 2006-08-31
CN1756905B (en) 2011-06-08
DE502004004234D1 (en) 2007-08-16

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