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EP1676031B1 - Radial piston pump for common rail injection systems - Google Patents

Radial piston pump for common rail injection systems Download PDF

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Publication number
EP1676031B1
EP1676031B1 EP04787234.6A EP04787234A EP1676031B1 EP 1676031 B1 EP1676031 B1 EP 1676031B1 EP 04787234 A EP04787234 A EP 04787234A EP 1676031 B1 EP1676031 B1 EP 1676031B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
radial piston
type high
pressure accumulator
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
EP04787234.6A
Other languages
German (de)
French (fr)
Other versions
EP1676031A1 (en
Inventor
Stefan Portner
Ngoc-Tam Vu
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP1676031A1 publication Critical patent/EP1676031A1/en
Application granted granted Critical
Publication of EP1676031B1 publication Critical patent/EP1676031B1/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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • 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
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention relates to a radial piston high-pressure pump for common rail injection systems with a high-pressure accumulator integrated into the radial piston high-pressure pump.
  • the radial piston high-pressure pump has a housing in which a drive shaft is guided.
  • the drive shaft has an eccentric portion on which a cam ring is mounted.
  • On the cam preferably based several, with respect to the drive shaft radially in pump size longitudinally movably guided pump piston.
  • Each pump piston is assigned a suction valve and a pressure valve. Via the suction valve, fuel is supplied from the low-pressure region to the pump piston.
  • the compressed fuel is discharged via the pressure valve and fed via a high-pressure line to the common high-pressure accumulator (common rail).
  • the high pressure accumulator is integrated in a peripheral region of the radial piston high pressure pump.
  • the WO 02/084105 A also discloses a radial piston high pressure pump with an integrated high pressure accumulator.
  • the object of the invention is therefore to provide a radial piston high-pressure pump for common rail injection systems with a high-pressure accumulator integrated in the radial piston high pressure pump, which is simple and inexpensive to manufacture.
  • the invention is characterized in that the high-pressure accumulator is annular.
  • the annular configuration of the high-pressure accumulator allows a particularly cost-effective and simple production.
  • the annular design of the high pressure accumulator has the advantage that the high pressure lines can open at any point in the high pressure accumulator. This results in very short and easy to train high pressure lines.
  • a preferred embodiment of the invention provides to arrange the high pressure accumulator concentric to the drive shaft. This results in a symmetrical and particularly compact arrangement of the high-pressure fuel lines within the pump.
  • a further preferred embodiment of the invention provides to form the high-pressure accumulator by a frontally introduced into the pump housing annular groove and to close this with a lid.
  • the annular groove can be particularly easily introduced, for example by turning, in the pump housing.
  • the production of the annular groove can be done in one step with the production of the housing bore, which is required for the drive shaft, without the pump housing must be re-clamped during manufacture. This results in a particularly cost-effective production.
  • the lid can also be manufactured as a low-cost turned part.
  • a further advantageous embodiment of the invention provides to form at least one metallic sealing surface for sealing the high-pressure accumulator on the pump housing and / or on the cover.
  • the metallic sealing surface is reduced Thus, the number of required components and also facilitates the installation of the pump. An incorrect insertion of the seal is excluded.
  • the metallic sealing surface can preferably be formed by raised areas in the pump housing and / or in the lid.
  • a further advantageous embodiment of the invention provides to connect the lid by means of a concentric with the annular groove arranged central screw with the pump housing.
  • the central screw offers the advantage that the force is distributed evenly over the entire circumference of the annular groove, whereby a secure sealing of the high-pressure accumulator is achieved.
  • a through hole is introduced in the central screw, through which a leakage flow can be removed from the radial piston high-pressure pump.
  • a further advantageous embodiment of the invention provides to form the high-pressure accumulator as an annular groove, wherein the annular groove is introduced into the outer periphery of a rotationally symmetrical pump insert.
  • the annular groove can be very simple and inexpensive, for example, by turning, bring in the outer periphery of the rotationally symmetrical pump insert.
  • the pump insert is inserted into a corresponding opening of the pump housing and the outer peripheral surface of the rotationally symmetrical pump insert acts together with the inner peripheral surface of the pump housing.
  • the pump insert is cylindrical.
  • the cylindrical configuration allows a particularly simple and inexpensive production of the pump insert and the corresponding pump opening.
  • a further advantageous embodiment of the invention provides that the high-pressure accumulator at least one high-pressure port for supplying at least one injector Internal combustion engine is formed.
  • the high pressure port may be formed in the pump housing or in the pump cover.
  • a further advantageous embodiment of the invention provides that the high-pressure accumulator is in operative connection with a built-in the radial piston high pressure pump or arranged on the radial piston high-pressure pump pressure relief valve.
  • the integration of the pressure relief valve or the arrangement in the immediate vicinity of the radial piston high pressure pump allows a particularly compact design.
  • FIG. 1 shows a first embodiment of the radial piston high-pressure pump.
  • the radial piston high-pressure pump has a pump housing 1, in which a drive shaft 2 is rotatably mounted.
  • the drive shaft 2 is designed as an eccentric shaft.
  • On the outer circumference of the eccentric 15 three preferably at an angle of 120 ° to each other arranged pump piston 3 are arranged.
  • each pump piston 3 performs a complete suction and Compression stroke through.
  • the cylinder piston 3 moves in the direction of the drive shaft 2 and a in FIG. 1 not shown suction valve is supplied to the cylinder chamber fuel.
  • suction valve is supplied to the cylinder chamber fuel.
  • the suction valve closes and the fuel is subsequently compressed during the upward movement of the pump piston 3 to a pressure of up to 1800 bar.
  • Upon reaching the upper end position of the pump piston 3 opens the pressure valve 13 and the compressed fuel flows from the cylinder chamber, via a high-pressure line 16 to the common high-pressure accumulator 4.
  • the high-pressure accumulator 4 is annular in an end face of the pump housing 1 is formed.
  • the introduction of the annular groove can be done in a simple manner by Spannabriolde method, for example by turning. It makes sense to make the introduction of the annular groove in one step with the introduction of the bearing bores for the drive shaft 2.
  • the pump housing 1 can be processed without re-clamping in one step, resulting in a particularly simple production process.
  • the open side of the high-pressure accumulator 4 is closed by a cover 5.
  • the cover 5 is screwed via a central screw 8 with the pump housing 1.
  • the central screw 8 has the advantage that the force is distributed uniformly over the entire circumference of the annular groove by the central arrangement.
  • a through hole 14 is formed, via which a leakage current is discharged from the pump housing 1.
  • additional screws which are arranged distributed on the circumference of the lid 5 can be used.
  • a plurality of high pressure ports 12 are formed in the cover 5.
  • the high pressure ports 12 of the high-pressure accumulator 4 can be connected to the individual injectors of the internal combustion engine.
  • a secure sealing of the lid is ensured by metallic sealing surface 6, 7.
  • the metallic Sealing surfaces 6, 7 a raised area. This creates a very high surface pressure, which ensures a secure seal.
  • the raised area can be formed in the cover 5 and / or in the pump housing 1.
  • each high-pressure line 16 discharges individually into the high-pressure accumulator. This eliminates the usual Bohrungsverschneidung when meeting the individual high-pressure lines. The bore intersection are so far very problematic, especially with regard to component strength.
  • the high pressure line 16 may be formed as short as possible.
  • the short high pressure lines 16 can be made with a larger tolerance, since deviations on the short length do not make so much noticeable. In the prior art, however, very low tolerances must be observed, since otherwise it can happen that the individual high-pressure lines do not coincide exactly.
  • the lines lead preferably at an angle of 120 ° to each other in the high-pressure accumulator.
  • FIG. 2 shows a second embodiment of the radial piston high-pressure pump.
  • the basic mode of operation of the radial piston high-pressure pump is identical to the first exemplary embodiment, to which reference is hereby made. The difference is only in the design of the high-pressure accumulator 4.
  • the high-pressure accumulator 4 is not formed in the pump housing 1 but in a pump insert 10.
  • the high pressure accumulator 4 is formed as an annular groove in the lateral surface of a rotationally symmetrical pump insert 10. The introduction of the annular groove can be done again in a simple manner, in particular by a machining process, such as turning.
  • a cylindrical pump insert is chosen as a rotationally symmetrical pump insert, since this is easy to manufacture with the lowest tolerances.
  • Conceivable are other rotationally symmetric inserts, such as a conical pump insert.
  • the pump insert 10 is inserted into a correspondingly formed opening of the pump housing 1 and is, in FIG. 2 not shown, fixed by additional fasteners.
  • the outer peripheral surface 9 of the pump insert 10 corresponds to the inner peripheral surface 11 of the pump housing 1.
  • the play-free fit already results in a good seal between the pump housing 1 and the pump insert 10.
  • additional sealing lips in the region of the high-pressure accumulator 4 are provided.
  • pump insert 10 instead of a cylindrical pump insert 10, it is also possible to form the pump insert conical. In the pump housing 1, a corresponding conical surface is then formed.
  • the conical design of pump insert 10 and pump housing 1 has the advantage that when screwing the two components, the contact surfaces wedge together and thereby already results in a good seal between the pump housing 1 and the pump insert 10 in the high-pressure accumulator 4.
  • the high-pressure lines 16 can again be made very short, in turn, at any point in the High-pressure accumulator 4 can open. Preferably, they open at an angle of 120 ° to each other in the high-pressure accumulator. 4
  • a particularly compact design of the injection system is obtained when a pressure-limiting valve required for control is integrated directly into the high-pressure accumulator 4 or is fastened directly to the pump housing 1.
  • high-pressure connections 12 are formed, via which the high-pressure accumulator 4 can be connected to the injectors of an internal combustion engine.
  • the high-pressure connections 12 can alternatively also be introduced into the pump insert 10.
  • the invention is thus characterized by the fact that the annular design of the high-pressure accumulator 4 a particularly favorable and simple production is possible. Due to the fact that the high-pressure ducts 16 can open into the high-pressure accumulator 4 at any point, particularly short high-pressure ducts 16 can be realized. Overall, the radial piston high pressure pump according to the invention allows a particularly compact design of radial piston pump and high-pressure accumulator.

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

Description

Die Erfindung betrifft eine Radialkolbenhochdruckpumpe für Common Rail Einspritzsysteme mit einem in die Radialkolbenhochdruckpumpe integrierten Hochdruckspeicher.The invention relates to a radial piston high-pressure pump for common rail injection systems with a high-pressure accumulator integrated into the radial piston high-pressure pump.

Aus der älteren, nachveröffentlichten Patentanmeldung DE 10228551.9 der Anmelderin ist bereits eine Radialkolbenhochdruckpumpe für Common Rail Einspritzsysteme mit einem in die Radialkolbenhochdruckpumpe integrierten Hochdruckspeicher bekannt. Die Radialkolbenhochdruckpumpe weist ein Gehäuse auf, in dem eine Antriebswelle geführt ist. Die Antriebswelle besitzt einen Exzenterabschnitt, auf dem ein Hubring gelagert ist. An dem Hubring stützen sich vorzugsweise mehrere, bezüglich der Antriebswelle radial in Pumpengröße längs bewegbar geführte Pumpenkolben ab. Jedem Pumpenkolben ist ein Saugventil sowie ein Druckventil zugeordnet. Über das Saugventil wird dem Pumpenkolben Kraftstoff aus dem Niederdruckbereich zugeführt. Nach dem Druckaufbau wird der komprimierte Kraftstoff über das Druckventil abgeleitet und über eine Hochdruckleitung dem gemeinsamen Hochdruckspeicher (Common Rail) zugeführt. Um eine kompakte Bauweise zu ermöglichen, ist der Hochdruckspeicher in einem Umfangsbereich der Radialkolbenhochdruckpumpe integriert.From the older, postpublished patent application DE 10228551.9 the applicant is already known a radial piston high-pressure pump for common rail injection systems with a high-pressure accumulator integrated in the radial piston high-pressure pump. The radial piston high pressure pump has a housing in which a drive shaft is guided. The drive shaft has an eccentric portion on which a cam ring is mounted. On the cam preferably based several, with respect to the drive shaft radially in pump size longitudinally movably guided pump piston. Each pump piston is assigned a suction valve and a pressure valve. Via the suction valve, fuel is supplied from the low-pressure region to the pump piston. After the pressure has built up, the compressed fuel is discharged via the pressure valve and fed via a high-pressure line to the common high-pressure accumulator (common rail). In order to allow a compact design, the high pressure accumulator is integrated in a peripheral region of the radial piston high pressure pump.

Die WO 02/084105 A offenbart ebenfalls eine Radialkolbenhochdruckpumpe mit einem integrierten Hochdruckspeicher.The WO 02/084105 A also discloses a radial piston high pressure pump with an integrated high pressure accumulator.

Nachteilig an diesen Lösungen ist die zum Teil sehr komplizierte Führung der Hochdruckleitungen zum Hochdruckspeicher innerhalb des Pumpengehäuses.A disadvantage of these solutions is the sometimes very complicated leadership of the high pressure lines to the high-pressure accumulator within the pump housing.

Aufgabe der Erfindung ist es daher, eine Radialkolbenhochdruckpumpe für Common Rail Einspritzsysteme mit einem in die Radialkolbenhochdruckpumpe integrierten Hochdruckspeicher bereitzustellen, die einfach und kostengünstig herzustellen ist.The object of the invention is therefore to provide a radial piston high-pressure pump for common rail injection systems with a high-pressure accumulator integrated in the radial piston high pressure pump, which is simple and inexpensive to manufacture.

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

Die Erfindung zeichnet sich dadurch aus, dass der Hochdruckspeicher ringförmig ausgebildet ist. Die ringförmige Ausgestaltung des Hochdruckspeichers ermöglicht eine besonders kostengünstige und einfache Herstellung. Darüber hinaus hat die ringförmige Ausbildung des Hochdruckspeichers den Vorteil, dass die Hochdruckleitungen an einer beliebigen Stelle in dem Hochdruckspeicher münden können. Hierdurch ergeben sich sehr kurze und einfach auszubildende Hochdruckleitungen.The invention is characterized in that the high-pressure accumulator is annular. The annular configuration of the high-pressure accumulator allows a particularly cost-effective and simple production. In addition, the annular design of the high pressure accumulator has the advantage that the high pressure lines can open at any point in the high pressure accumulator. This results in very short and easy to train high pressure lines.

Eine bevorzugte Ausgestaltung der Erfindung sieht vor, den Hochdruckspeicher konzentrisch zur Antriebswelle anzuordnen. Hierdurch ergibt sich eine symmetrische und besonders kompakte Anordnung der Kraftstoffhochdruckleitungen innerhalb der Pumpe.A preferred embodiment of the invention provides to arrange the high pressure accumulator concentric to the drive shaft. This results in a symmetrical and particularly compact arrangement of the high-pressure fuel lines within the pump.

Eine weitere bevorzugte Ausgestaltung der Erfindung sieht vor, den Hochdruckspeicher durch eine stirnseitig in das Pumpengehäuse eingebrachte Ringnut auszubilden und dies mit einem Deckel zu verschließen. Die Ringnut kann dabei besonders einfach, beispielsweise durch Drehen, in das Pumpengehäuse eingebracht werden. Das Herstellen der Ringnut kann dabei in einem Arbeitsschritt mit dem Herstellen der Gehäusebohrung, welche für die Antriebswelle erforderlich ist, erfolgen, ohne dass das Pumpengehäuse bei der Fertigung umgespannt werden muss. Hierdurch ergibt sich eine besonders kostengünstige Herstellung. Der Deckel kann ebenfalls als preiswertes Drehteil hergestellt werden.A further preferred embodiment of the invention provides to form the high-pressure accumulator by a frontally introduced into the pump housing annular groove and to close this with a lid. The annular groove can be particularly easily introduced, for example by turning, in the pump housing. The production of the annular groove can be done in one step with the production of the housing bore, which is required for the drive shaft, without the pump housing must be re-clamped during manufacture. This results in a particularly cost-effective production. The lid can also be manufactured as a low-cost turned part.

Eine weitere vorteilhafte Ausgestaltung der Erfindung sieht vor, zur Abdichtung des Hochdruckspeichers am Pumpengehäuse und/oder am Deckel wenigstens eine metallische Dichtfläche auszubilden. Dadurch kann auf ein zusätzliches Dichtungselement verzichtet werden Die metallische Dichtfläche verringert somit die Anzahl der erforderlichen Bauteile und erleichtert zusätzlich die Montage der Pumpe. Ein fehlerhaftes Einlegen der Dichtung ist ausgeschlossen. Die metallische Dichtfläche kann dabei vorzugsweise durch erhabene Bereiche im Pumpengehäuses und/oder im Deckel ausgebildet sein.A further advantageous embodiment of the invention provides to form at least one metallic sealing surface for sealing the high-pressure accumulator on the pump housing and / or on the cover. As a result, it is possible to dispense with an additional sealing element. The metallic sealing surface is reduced Thus, the number of required components and also facilitates the installation of the pump. An incorrect insertion of the seal is excluded. The metallic sealing surface can preferably be formed by raised areas in the pump housing and / or in the lid.

Eine weitere vorteilhafte Ausgestaltung der Erfindung sieht vor, den Deckel mittels einer konzentrisch zur Ringnut angeordneten Zentralschraube mit dem Pumpengehäuse zu verbinden. Die Zentralschraube bietet dabei den Vorteil, dass die Kraft gleichmäßig über den gesamten Umfang der Ringnut verteilt wird, wodurch eine sichere Abdichtung des Hochdruckspeichers erzielt wird. In einer bevorzugten Ausgestaltung ist in der Zentralschraube eine Durchgangsbohrung eingebracht, durch die ein Leckagestrom aus der Radialkolbenhochdruckpumpe abgeführt werden kann.A further advantageous embodiment of the invention provides to connect the lid by means of a concentric with the annular groove arranged central screw with the pump housing. The central screw offers the advantage that the force is distributed evenly over the entire circumference of the annular groove, whereby a secure sealing of the high-pressure accumulator is achieved. In a preferred embodiment, a through hole is introduced in the central screw, through which a leakage flow can be removed from the radial piston high-pressure pump.

Eine weitere vorteilhafte Ausgestaltung der Erfindung sieht vor, den Hochdruckspeicher als Ringnut auszubilden, wobei die Ringnut in den Außenumfang eines rotationssymmetrischen Pumpeneinsatzes eingebracht ist. Die Ringnut lässt sich dabei sehr einfach und kostengünstig, beispielsweise durch Drehen, in den Außenumfang des rotationssymmetrischen Pumpeneinsatzes einbringen. Der Pumpeneinsatz wird in eine korrespondierende Öffnung des Pumpengehäuse eingeschoben und die Außenumfangsfläche des rotationssymmetrischen Pumpeneinsatzes wirkt dabei mit der Innenumfangsfläche des Pumpengehäuses zusammen.A further advantageous embodiment of the invention provides to form the high-pressure accumulator as an annular groove, wherein the annular groove is introduced into the outer periphery of a rotationally symmetrical pump insert. The annular groove can be very simple and inexpensive, for example, by turning, bring in the outer periphery of the rotationally symmetrical pump insert. The pump insert is inserted into a corresponding opening of the pump housing and the outer peripheral surface of the rotationally symmetrical pump insert acts together with the inner peripheral surface of the pump housing.

In einer besonders vorteilhaften Ausgestaltung der Erfindung ist der Pumpeneinsatz zylindrisch ausgebildet. Die zylindrische Ausgestaltung ermöglicht eine besonders einfache und preiswerte Herstellung des Pumpeneinsatzes sowie der korrespondierenden Pumpenöffnung.In a particularly advantageous embodiment of the invention, the pump insert is cylindrical. The cylindrical configuration allows a particularly simple and inexpensive production of the pump insert and the corresponding pump opening.

Eine weitere vorteilhafte Ausgestaltung der Erfindung sieht vor, dass am Hochdruckspeicher wenigstens ein Hochdruckanschluss zur Versorgung von wenigstens einem Injektor einer Brennkraftmaschine ausgebildet ist. Der Hochdruckanschluss kann dabei im Pumpengehäuse oder im Pumpendeckel ausgebildet sein.A further advantageous embodiment of the invention provides that the high-pressure accumulator at least one high-pressure port for supplying at least one injector Internal combustion engine is formed. The high pressure port may be formed in the pump housing or in the pump cover.

Eine weitere vorteilhafte Ausgestaltung der Erfindung sieht vor, dass der Hochdruckspeicher mit einem in die Radialkolbenhochdruckpumpe integrierten oder an der Radialkolbenhochdruckpumpe angeordneten Druckbegrenzungsventil in Wirkverbindung steht. Die Integration des Druckbegrenzungsventils bzw. die Anordnung in unmittelbare Nähe der Radialkolbenhochdruckpumpe ermöglicht eine besonders kompakte Bauform.A further advantageous embodiment of the invention provides that the high-pressure accumulator is in operative connection with a built-in the radial piston high pressure pump or arranged on the radial piston high-pressure pump pressure relief valve. The integration of the pressure relief valve or the arrangement in the immediate vicinity of the radial piston high pressure pump allows a particularly compact design.

Ausführungsbeispiele der Erfindung werden im folgenden anhand der schematischen Zeichnungen erläutert. Es zeigt:

Figur 1
eine erste Ausführungsform der Radialkolbenhochdruckpumpe, bei der der Hochdruckspeicher durch eine stirnseitig in das Pumpengehäuse eingebrachte Ringnut ausgebildet und mit einem Deckel verschlossen ist,
Figur 2
eine zweite Ausführungsform der Radialkolbenhochdruckpumpe, bei der der Hochdruckspeicher als Ringnut ausgebildet ist, welche in dem Außenumfang eines rotationssymmetrischen Pumpeneinsatzes eingebracht ist.
Embodiments of the invention are explained below with reference to the schematic drawings. It shows:
FIG. 1
a first embodiment of the radial piston high-pressure pump, in which the high-pressure accumulator is formed by a frontally introduced into the pump housing annular groove and closed with a lid,
FIG. 2
a second embodiment of the radial piston high pressure pump, wherein the high-pressure accumulator is designed as an annular groove, which is introduced in the outer periphery of a rotationally symmetrical pump insert.

Elemente gleicher Konstruktion und Funktion sind figurübergreifend mit den gleichen Bezugszeichen versehen.Elements of the same construction and function are cross-figurative provided with the same reference numerals.

Figur 1 zeigt ein erstes Ausführungsbeispiel der Radialkolbenhochdruckpumpe. Die Radialkolbenhochdruckpumpe weist ein Pumpengehäuse 1 auf, in dem eine Antriebswelle 2 drehbar gelagert ist. Die Antriebswelle 2 ist als Exzenterwelle ausgebildet. Am Außenumfang des Exzenters 15 sind vorzugsweise drei in einem Winkel von 120° zueinander angeordnet Pumpenkolben 3 angeordnet. Während einer Umdrehung der Antriebswelle 2 führt jeder Pumpenkolben 3 einen vollständiaen Saug- und Kompressionshub durch. Während des Saughubs bewegt sich der Zylinderkolben 3 in Richtung der Antriebswelle 2 und über ein in Figur 1 nicht dargestelltes Saugventil wird dem Zylinderraum Kraftstoff zugeführt. Nach dem der Zylinderkolben 3 seine untere Endstellung erreicht hat, erfolgt eine Umkehrung der Bewegungsrichtung und es beginnt der Kompressionshub. Dabei schließt das Saugventil und der Kraftstoff wird nachfolgend während der Aufwärtsbewegung des Pumpenkolbens 3 auf einen Druck von bis zu 1800 bar komprimiert. Beim Erreichen der oberen Endstellung des Pumpenkolbens 3 öffnet das Druckventil 13 und der komprimierte Kraftstoff strömt aus dem Zylinderraum, über eine Hochdruckleitung 16, zu dem gemeinsamen Hochdruckspeicher 4. Der Hochdruckspeicher 4 ist dabei ringförmig in einer Stirnseite des Pumpengehäuses 1 ausgebildet. Das Einbringen der Ringnut kann auf einfache Weise durch spannabhebende Verfahren, beispielsweise durch Drehen, erfolgen. Dabei bietet es sich an, das Einbringen der Ringnut in einem Arbeitsschritt mit dem Einbringen der Lagerbohrungen für die Antriebswelle 2 vorzunehmen. Dadurch kann das Pumpengehäuse 1 ohne Umspannen in einem Schritt bearbeitet werden, wodurch sich ein besonders einfacher Herstellungsprozess ergibt. Die offene Seite des Hochdruckspeichers 4 wird durch einen Deckel 5 verschlossen. Der Deckel 5 ist dabei über eine Zentralschraube 8 mit dem Pumpengehäuse 1 verschraubt. Die Zentralschraube 8 bietet den Vorteil, dass durch die zentrale Anordnung die Kraft gleichmäßig über den gesamten Umfang der Ringnut verteilt wird. Zusätzlich ist in der Zentralschraube 8 eine Durchgangsbohrung 14 ausgebildet, über die ein Leckagestrom aus dem Pumpengehäuse 1 abgeführt wird. Für eine besonders sichere Abdichtung des Hochdrucksspeicher 4 können zusätzliche Schrauben, welche am Umfang des Deckels 5 verteilt angeordnet sind verwendet werden. In den Deckel 5 sind mehrere Hochdruckanschlüsse 12 ausgebildet. Über die Hochdruckanschlüsse 12 ist der Hochdruckspeicher 4 mit den einzelnen Injektoren der Brennkraftmaschine verbindbar. Eine sichere Abdichtung des Deckels ist durch metallische Dichtfläche 6, 7 gewährleistet. Vorzugsweise weisen die metallische Dichtflächen 6, 7 einen erhabenen Bereich auf. Hierdurch entsteht eine sehr hohe Flächenpressung, wodurch eine sichere Abdichtung gewährleistet ist. Der erhabene Bereich kann dabei im Deckel 5 und/oder im Pumpengehäuse 1 ausgebildet sein. FIG. 1 shows a first embodiment of the radial piston high-pressure pump. The radial piston high-pressure pump has a pump housing 1, in which a drive shaft 2 is rotatably mounted. The drive shaft 2 is designed as an eccentric shaft. On the outer circumference of the eccentric 15 three preferably at an angle of 120 ° to each other arranged pump piston 3 are arranged. During one revolution of the drive shaft 2, each pump piston 3 performs a complete suction and Compression stroke through. During the intake stroke, the cylinder piston 3 moves in the direction of the drive shaft 2 and a in FIG. 1 not shown suction valve is supplied to the cylinder chamber fuel. After the cylinder piston 3 has reached its lower end position, there is a reversal of the direction of movement and it begins the compression stroke. In this case, the suction valve closes and the fuel is subsequently compressed during the upward movement of the pump piston 3 to a pressure of up to 1800 bar. Upon reaching the upper end position of the pump piston 3 opens the pressure valve 13 and the compressed fuel flows from the cylinder chamber, via a high-pressure line 16 to the common high-pressure accumulator 4. The high-pressure accumulator 4 is annular in an end face of the pump housing 1 is formed. The introduction of the annular groove can be done in a simple manner by Spannabhebende method, for example by turning. It makes sense to make the introduction of the annular groove in one step with the introduction of the bearing bores for the drive shaft 2. As a result, the pump housing 1 can be processed without re-clamping in one step, resulting in a particularly simple production process. The open side of the high-pressure accumulator 4 is closed by a cover 5. The cover 5 is screwed via a central screw 8 with the pump housing 1. The central screw 8 has the advantage that the force is distributed uniformly over the entire circumference of the annular groove by the central arrangement. In addition, in the central screw 8, a through hole 14 is formed, via which a leakage current is discharged from the pump housing 1. For a particularly secure sealing of the high pressure accumulator 4 additional screws, which are arranged distributed on the circumference of the lid 5 can be used. In the cover 5, a plurality of high pressure ports 12 are formed. About the high pressure ports 12 of the high-pressure accumulator 4 can be connected to the individual injectors of the internal combustion engine. A secure sealing of the lid is ensured by metallic sealing surface 6, 7. Preferably, the metallic Sealing surfaces 6, 7 a raised area. This creates a very high surface pressure, which ensures a secure seal. The raised area can be formed in the cover 5 and / or in the pump housing 1.

Der ringförmig ausgebildete und in das Pumpengehäuse 1 integrierte Hochdruckspeicher 4 ermöglicht eine besonders kompakte Bauweise. Im Gegensatz zum Stand der Technik, bei dem die einzelnen Hochdruckleitungen zunächst im Pumpengehäuse zusammengeführt werden und dann als gemeinsame Leitung aus dem Pumpengehäuse zum Hochdruckspeicher geführt werden, mündet bei der erfindungsgemäßen Ausführung, jede Hochdruckleitung 16 einzeln in den Hochdruckspeicher. Hierdurch entfällt die sonst übliche Bohrungsverschneidung beim zusammentreffen der einzelnen Hochdruckleitungen. Die Bohrungsverschneidung sind insbesondere im Hinblick auf die Bauteilfestigkeit bislang sehr problematisch.The ring-shaped and integrated into the pump housing 1 high-pressure accumulator 4 allows a particularly compact design. In contrast to the prior art, in which the individual high-pressure lines are first brought together in the pump housing and then passed as a common line from the pump housing to the high-pressure accumulator, in the embodiment according to the invention, each high-pressure line 16 discharges individually into the high-pressure accumulator. This eliminates the usual Bohrungsverschneidung when meeting the individual high-pressure lines. The bore intersection are so far very problematic, especially with regard to component strength.

Dadurch, dass die Hochdruckleitung einzeln und an beliebiger Stelle in den Hochdruckspeicher münden, können die Hochdruckleitung 16 so kurz wie möglich ausgebildet sein. Die kurzen Hochdruckleitungen 16 können dabei mit einer größeren Toleranz gefertigt werden, da sich Abweichungen auf der kurzen Länge nicht so stark bemerkbar machen. Beim Stand der Technik sind dagegen sehr geringe Toleranzen einzuhalten, da es sonst passieren kann, dass die einzelnen Hochdruckleitungen nicht exakt zusammentreffen.Characterized in that the high pressure line open individually and at any point in the high pressure accumulator, the high pressure line 16 may be formed as short as possible. The short high pressure lines 16 can be made with a larger tolerance, since deviations on the short length do not make so much noticeable. In the prior art, however, very low tolerances must be observed, since otherwise it can happen that the individual high-pressure lines do not coincide exactly.

Um möglicht kurze Hochdruckleitungen 16 zu realisieren, münden die Leitungen vorzugsweise in einem Winkel von 120° zueinander in den Hochdruckspeicher.In order to make possible short high-pressure lines 16, the lines lead preferably at an angle of 120 ° to each other in the high-pressure accumulator.

Figur 2 zeigt ein zweites Ausführungsbeispiel der Radialkolbenhochdruckpumpe. Die prinzipielle Funktionsweise der Radialkolbenhochdruckpumpe ist identisch mit dem ersten Ausführungsbeispiel, auf das hier mit verwiesen wird. Der Unterschied besteht lediglich in der Ausbildung des Hochdruckspeichers 4. Im Gegensatz zum ersten Ausführungsbeispiel ist der Hochdruckspeicher 4 nicht im Pumpengehäuse 1 sondern in einem Pumpeneinsatz 10 ausgebildet. Der Hochdruckspeicher 4 ist dabei als Ringnut in die Mantelfläche eines rotationssymmetrischen Pumpeneinsatzes 10 ausgebildet. Das Einbringen der Ringnut kann dabei wieder auf einfache Weise, insbesondere durch ein spanabhebendes Verfahren, beispielsweise Drehen erfolgen. Vorzugsweise wird als rotationssymmetrischer Pumpeneinsatz ein zylindrischer Pumpeneinsatz gewählt, da dieser leicht und mit geringsten Toleranzen herzustellen ist. Denkbar sind aber auch andere rotationssymmetrische Einsätze, beispielsweise ein konisch ausgebildeter Pumpeneinsatz. Der Pumpeneinsatz 10 ist in eine entsprechend ausgebildete Öffnung des Pumpengehäuse 1 eingeschoben und wird, in Figur 2 nicht dargestellt, durch zusätzliche Befestigungselemente fixiert. Die Außenumfangsfläche 9 des Pumpeneinsatzes 10 korrespondiert dabei mit der Innenumfangsfläche 11 des Pumpengehäuses 1. Somit ist ein spielfreier Sitz des Pumpeneinsatzes 10 gewährleistet. Durch den spielfreien Sitz ergibt sich bereits eine gute Abdichtung zwischen dem Pumpengehäuse 1 und dem Pumpeneinsatz 10. Zusätzlich sind im Pumpeneinsatz 10 und/oder im Pumpgehäuse 1 zusätzliche Dichtlippen im Bereich des Hochdruckspeichers 4 vorgesehen. FIG. 2 shows a second embodiment of the radial piston high-pressure pump. The basic mode of operation of the radial piston high-pressure pump is identical to the first exemplary embodiment, to which reference is hereby made. The difference is only in the design of the high-pressure accumulator 4. In contrast to the first embodiment, the high-pressure accumulator 4 is not formed in the pump housing 1 but in a pump insert 10. The high pressure accumulator 4 is formed as an annular groove in the lateral surface of a rotationally symmetrical pump insert 10. The introduction of the annular groove can be done again in a simple manner, in particular by a machining process, such as turning. Preferably, a cylindrical pump insert is chosen as a rotationally symmetrical pump insert, since this is easy to manufacture with the lowest tolerances. Conceivable, however, are other rotationally symmetric inserts, such as a conical pump insert. The pump insert 10 is inserted into a correspondingly formed opening of the pump housing 1 and is, in FIG. 2 not shown, fixed by additional fasteners. The outer peripheral surface 9 of the pump insert 10 corresponds to the inner peripheral surface 11 of the pump housing 1. Thus, a play-free fit of the pump insert 10 is ensured. The play-free fit already results in a good seal between the pump housing 1 and the pump insert 10. In addition, in the pump insert 10 and / or in the pump housing 1 additional sealing lips in the region of the high-pressure accumulator 4 are provided.

Anstelle eines zylinderförmigen Pumpeneinsatzes 10 ist es auch möglich, den Pumpeneinsatz konisch auszubilden. Im Pumpengehäuse 1 ist dann eine korrespondierende konische Fläche ausgebildet. Die konische Ausbildung von Pumpeneinsatz 10 und Pumpengehäuse 1 bietet den Vorteil, dass sich beim Verschrauben der beiden Bauteile die Kontaktflächen miteinander verkeilen und sich dadurch bereits eine gute Abdichtung zwischen dem Pumpengehäuse 1 und dem Pumpeneinsatz 10 im Bereich des Hochdruckspeichers 4 ergibt.Instead of a cylindrical pump insert 10, it is also possible to form the pump insert conical. In the pump housing 1, a corresponding conical surface is then formed. The conical design of pump insert 10 and pump housing 1 has the advantage that when screwing the two components, the contact surfaces wedge together and thereby already results in a good seal between the pump housing 1 and the pump insert 10 in the high-pressure accumulator 4.

Durch die ringförmige Ausgestaltung des Hochdruckspeichers 4 können die Hochdruckleitungen 16 wieder sehr kurz ausgeführt sein, wobei sie wiederum an einer beliebigen Stelle in den Hochdruckspeicher 4 münden können. Vorzugsweise münden sie in einem Winkel von 120° zueinander in den Hochdruckspeicher 4.Due to the annular configuration of the high-pressure accumulator 4, the high-pressure lines 16 can again be made very short, in turn, at any point in the High-pressure accumulator 4 can open. Preferably, they open at an angle of 120 ° to each other in the high-pressure accumulator. 4

Eine besonders kompakte Bauform des Einspritzsystems ergibt sich, wenn ein zur Regelung notweniges Druckbegrenzungsventil direkt in den Hochdruckspeicher 4 integriert wird oder unmittelbar am Pumpengehäuse 1 befestigt wird.A particularly compact design of the injection system is obtained when a pressure-limiting valve required for control is integrated directly into the high-pressure accumulator 4 or is fastened directly to the pump housing 1.

Im Pumpengehäuse 1, sind Hochdruckanschlüsse 12 ausgebildet, über die der Hochdruckspeicher 4 mit den Injektoren einer Brennkraftmaschine verbindbar ist. Die Hochdruckanschlüsse 12 können alternativ auch in den Pumpeneinsatz 10 eingebracht werden.In the pump housing 1, high-pressure connections 12 are formed, via which the high-pressure accumulator 4 can be connected to the injectors of an internal combustion engine. The high-pressure connections 12 can alternatively also be introduced into the pump insert 10.

Die Erfindung zeichnet sich somit dadurch aus, dass durch die ringförmige Ausbildung des Hochdruckspeichers 4 eine besonders günstige und einfache Herstellung ermöglicht wird. Dadurch, dass die Hochdruckkanäle 16 an einer beliebigen Stelle in den Hochdruckspeicher 4 münden können, lassen sich besonders kurze Hochdruckkanäle 16 realisieren. Ingesamt ermöglicht die erfindungsgemäße Radialkolbenhochdruckpumpe eine besonders kompakte Bauform von Radialkolbenpumpe und Hochdruckspeicher. The invention is thus characterized by the fact that the annular design of the high-pressure accumulator 4 a particularly favorable and simple production is possible. Due to the fact that the high-pressure ducts 16 can open into the high-pressure accumulator 4 at any point, particularly short high-pressure ducts 16 can be realized. Overall, the radial piston high pressure pump according to the invention allows a particularly compact design of radial piston pump and high-pressure accumulator.

Claims (10)

  1. Radial piston-type high-pressure pump for common-rail injection systems, having
    - a pump housing (1),
    - a drive shaft (2),
    - at least one pump piston (3) which is movable in a radial direction with respect to the drive shaft (2) and
    - a high-pressure accumulator (4) integrated into the radial piston-type high-pressure pump,
    characterized in that
    the high-pressure accumulator (4) is of annular form.
  2. Radial piston-type high-pressure pump according to Claim 1,
    characterized in that
    the high-pressure accumulator (4) is arranged concentrically with respect to the drive shaft (2).
  3. Radial piston-type high-pressure pump according to Claim 1 or 2,
    characterized in that
    the high-pressure accumulator (4) is formed by an annular groove formed into the face side of the pump housing (1), and is closed off by means of a cover (5).
  4. Radial piston-type high-pressure pump according to Claim 3,
    characterized in that
    at least one metallic sealing surface (6, 7) is formed on the pump housing (1) and/or on the cover (5) for the purposes of sealing off the high-pressure accumulator (4).
  5. Radial piston-type high-pressure pump according to Claim 3 or 4,
    characterized in that
    the cover (5) is connected to the pump housing (1) at least by means of a central screw (8) arranged concentrically with respect to the annular groove.
  6. Radial piston-type high-pressure pump according to Claim 1 or 2,
    characterized in that
    the high-pressure accumulator (4) is in the form of an annular groove which is formed into the outer circumference (9) of a rotationally symmetrical pump insert (10).
  7. Radial piston-type high-pressure pump according to Claim 6,
    characterized in that
    the outer circumference (9) of the pump insert (10) interacts with a corresponding inner circumferential surface (11) of the pump housing (1).
  8. Radial piston-type high-pressure pump according to Claim 6 or 7,
    characterized in that
    the pump insert (10) is of cylindrical form.
  9. Radial piston-type high-pressure pump according to one of the preceding claims,
    characterized in that,
    on the high-pressure accumulator (4), there is formed at least one high-pressure port (12) for providing a supply to at least one injector of an internal combustion engine.
  10. Radial piston-type high-pressure pump according to one of the preceding claims,
    characterized in that
    the high-pressure accumulator (4) is operatively connected to a pressure-limiting valve which is integrated into the radial piston-type high-pressure pump or which is arranged on the radial piston-type high-pressure pump.
EP04787234.6A 2003-10-23 2004-09-28 Radial piston pump for common rail injection systems Expired - Lifetime EP1676031B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10349310A DE10349310B3 (en) 2003-10-23 2003-10-23 Radial piston pump for Common Rail injection systems
PCT/EP2004/052338 WO2005040609A1 (en) 2003-10-23 2004-09-28 Radial piston pump for common rail injection systems

Publications (2)

Publication Number Publication Date
EP1676031A1 EP1676031A1 (en) 2006-07-05
EP1676031B1 true EP1676031B1 (en) 2015-07-29

Family

ID=34442219

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04787234.6A Expired - Lifetime EP1676031B1 (en) 2003-10-23 2004-09-28 Radial piston pump for common rail injection systems

Country Status (5)

Country Link
US (1) US7647918B2 (en)
EP (1) EP1676031B1 (en)
CN (1) CN100422550C (en)
DE (1) DE10349310B3 (en)
WO (1) WO2005040609A1 (en)

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DE102009000964A1 (en) * 2009-02-18 2010-08-19 Robert Bosch Gmbh High pressure fuel pump for an internal combustion engine
DE102009000965A1 (en) * 2009-02-18 2010-08-19 Robert Bosch Gmbh High pressure fuel pump with integrated high pressure accumulator
DE102010001252A1 (en) * 2010-01-27 2011-07-28 Robert Bosch GmbH, 70469 Fuel injection system with integrated high-pressure accumulator on a cylinder head
DE102010002291A1 (en) * 2010-02-24 2011-08-25 Robert Bosch GmbH, 70469 High pressure pump and high pressure accumulator
DE102014220937B4 (en) * 2014-10-15 2016-06-30 Continental Automotive Gmbh Drive device for driving a high-pressure fuel pump and high-pressure fuel pump
US9593653B2 (en) 2015-01-21 2017-03-14 Ford Global Technologies, Llc Direct injection fuel pump system
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DE102018215132A1 (en) * 2018-09-06 2020-03-12 Ford Global Technologies, Llc High pressure pump for a fuel supply to an internal combustion engine
WO2022055807A1 (en) 2020-09-10 2022-03-17 Cummins Inc. Fuel pump devices, systems, and methods

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CN2202803Y (en) * 1994-09-19 1995-07-05 霍启顺 Radial plunger pump
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DE10228551A1 (en) * 2002-06-26 2004-01-22 Siemens Ag Radial piston pump

Also Published As

Publication number Publication date
CN1871434A (en) 2006-11-29
WO2005040609A1 (en) 2005-05-06
US7647918B2 (en) 2010-01-19
CN100422550C (en) 2008-10-01
DE10349310B3 (en) 2005-05-19
US20070277785A1 (en) 2007-12-06
EP1676031A1 (en) 2006-07-05

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