EP1676031B1 - Pompe a pistons radiaux pour systemes d'injection a rampe commune - Google Patents

Pompe a pistons radiaux pour systemes d'injection a rampe commune 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)
English (en)
Other versions
EP1676031A1 (fr
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/fr
Application granted granted Critical
Publication of EP1676031B1 publication Critical patent/EP1676031B1/fr
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)

Claims (10)

  1. Pompe haute pression à pistons radiaux pour systèmes d'injection Common Rail, avec
    - un carter de pompe (1),
    - un arbre d'entraînement (2),
    - au moins un piston de pompe (3) qui est mobile dans la direction radiale par rapport à l'arbre d'entraînement (2) et
    - un accumulateur haute pression (4) intégré dans la pompe haute pression à pistons radiaux,
    caractérisée en ce que l'accumulateur haute pression (4) présente une forme annulaire.
  2. Pompe haute pression à pistons radiaux selon la revendication 1, caractérisée en ce que l'accumulateur haute pression (4) est disposé de manière concentrique par rapport à l'arbre d'entraînement (2).
  3. Pompe haute pression à pistons radiaux selon la revendication 1 ou 2, caractérisée en ce que l'accumulateur haute pression (4) est formé par une rainure annulaire réalisée du côté frontal dans le carter de pompe (1) et est fermé par un couvercle (5).
  4. Pompe haute pression à pistons radiaux selon la revendication 3, caractérisée en ce que, pour l'étanchéification de l'accumulateur haute pression (4), au moins une surface d'étanchéité (6, 7) métallique est prévue sur le carter de pompe (1) et/ou sur le couvercle (5).
  5. Pompe haute pression à pistons radiaux selon la revendication 3 ou 4, caractérisée en ce que le couvercle (5) est relié au carter de pompe (1) au moins à l'aide d'une vis centrale (8) disposée de manière concentrique par rapport à la rainure annulaire.
  6. Pompe haute pression à pistons radiaux selon la revendication 1 ou 2, caractérisée en ce que l'accumulateur haute pression (4) présente la forme d'une rainure annulaire qui est réalisée dans la circonférence externe (9) d'un insert de pompe (10) à symétrie de rotation.
  7. Pompe haute pression à pistons radiaux selon la revendication 6, caractérisée en ce que la circonférence externe (9) de l'insert de pompe (10) interagit avec une surface circonférentielle interne (11) du carter de pompe (1).
  8. Pompe haute pression à pistons radiaux selon la revendication 6 ou 7, caractérisée en ce que l'insert de pompe (10) présente une forme cylindrique.
  9. Pompe haute pression à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce que, sur l'accumulateur haute pression (4), est prévu un raccord haute pression (12) pour l'alimentation d'au moins un injecteur d'un moteur à combustion interne.
  10. Pompe haute pression à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce que l'accumulateur haute pression (4) est en interaction fonctionnelle avec une soupape de limitation de pression intégrée dans la pompe haute pression à pistons radiaux ou disposée sur la pompe haute pression à pistons radiaux.
EP04787234.6A 2003-10-23 2004-09-28 Pompe a pistons radiaux pour systemes d'injection a rampe commune Expired - Lifetime EP1676031B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10349310A DE10349310B3 (de) 2003-10-23 2003-10-23 Radialkolbenpumpe für Common Rail Einspritzsysteme
PCT/EP2004/052338 WO2005040609A1 (fr) 2003-10-23 2004-09-28 Pompe a pistons radiaux pour systemes d'injection a rampe commune

Publications (2)

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

Family

ID=34442219

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04787234.6A Expired - Lifetime EP1676031B1 (fr) 2003-10-23 2004-09-28 Pompe a pistons radiaux pour systemes d'injection a rampe commune

Country Status (5)

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

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009000965A1 (de) * 2009-02-18 2010-08-19 Robert Bosch Gmbh Hochdruckkraftstoffpumpe mit intergriertem Hochdruckspeicher
DE102009000964A1 (de) * 2009-02-18 2010-08-19 Robert Bosch Gmbh Hochdruckkraftstoffpumpe für eine Brennkraftmaschine
DE102010001252A1 (de) * 2010-01-27 2011-07-28 Robert Bosch GmbH, 70469 Kraftstoffeinspritzsystem mit integriertem Hochdruckspeicher an einem Zylinderkopf
DE102010002291A1 (de) * 2010-02-24 2011-08-25 Robert Bosch GmbH, 70469 Hochdruckpumpe und Hochdruckspeicher
DE102014220937B4 (de) * 2014-10-15 2016-06-30 Continental Automotive Gmbh Antriebsvorrichtung zum Antreiben einer Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe
US9593653B2 (en) 2015-01-21 2017-03-14 Ford Global Technologies, Llc Direct injection fuel pump system
DE102016106232B3 (de) * 2016-04-06 2017-08-31 L'orange Gmbh Radialkolbenpumpe, insbesondere für Kraftstoff, mit mehreren Speicherbohrungen im Gehäuse der Radialkolbenpumpe
DE102018215132A1 (de) * 2018-09-06 2020-03-12 Ford Global Technologies, Llc Hochdruckpumpe für eine Treibstoffzufuhr eines Verbrennungsmotors

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2679808A (en) * 1949-04-22 1954-06-01 Bernard M Thun Fluid pressure generator
US5634777A (en) * 1990-06-29 1997-06-03 Albertin; Marc S. Radial piston fluid machine and/or adjustable rotor
CN2202803Y (zh) * 1994-09-19 1995-07-05 霍启顺 径向柱塞泵
DE19801398A1 (de) * 1998-01-16 1999-07-22 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
EP0979353B1 (fr) * 1998-02-27 2004-09-29 Stanadyne Corporation Pompe d'alimentation pour rampe d'alimentation en essence
DE19920998B4 (de) * 1999-05-06 2004-11-04 Siemens Ag Radialkolbenpumpe
US6669166B2 (en) * 2000-07-28 2003-12-30 Nippon Soken, Inc. Electromagnetic valve
DE10118884A1 (de) * 2001-04-18 2002-11-07 Bosch Gmbh Robert Hochdruck-Kraftstoffpumpe für ein Kraftstoffsystem einer direkteinspritzenden Brennkraftmaschine, Kraftstoffsystem sowie Brennkraftmaschine
DE10139519A1 (de) * 2001-08-10 2003-02-27 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung, sowie Verfahren zum Betreiben einer Brennkraftmaschine, Computerprogramm und Steuer- und/oder Regelgerät
JP2005502816A (ja) * 2001-09-10 2005-01-27 スタナダイン コーポレイション 液圧式ポンプのための複合型要求制御
DE10228552B9 (de) * 2002-06-26 2007-08-23 Siemens Ag Radialkolbenpumpeneinheit
DE10228551A1 (de) * 2002-06-26 2004-01-22 Siemens Ag Radialkolbenpumpe

Also Published As

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

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