EP1068448B1 - Pompe a pistons radiaux pour l'alimentation haute pression en carburant - Google Patents

Pompe a pistons radiaux pour l'alimentation haute pression en carburant Download PDF

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Publication number
EP1068448B1
EP1068448B1 EP99907314A EP99907314A EP1068448B1 EP 1068448 B1 EP1068448 B1 EP 1068448B1 EP 99907314 A EP99907314 A EP 99907314A EP 99907314 A EP99907314 A EP 99907314A EP 1068448 B1 EP1068448 B1 EP 1068448B1
Authority
EP
European Patent Office
Prior art keywords
plate
drive shaft
piston pump
radial piston
pump according
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
EP99907314A
Other languages
German (de)
English (en)
Other versions
EP1068448A1 (fr
Inventor
Kasim-Melih Hamutcu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1068448A1 publication Critical patent/EP1068448A1/fr
Application granted granted Critical
Publication of EP1068448B1 publication Critical patent/EP1068448B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam

Definitions

  • the invention relates to a radial piston pump for High-pressure fuel supply in fuel injection systems of internal combustion engines, especially in a common rail injection system, with one stored in a pump housing Drive shaft which is eccentric or in Has circumferential cam-like elevations, and with preferably several radially in relation to the drive shaft a piston arranged in each cylinder space, at the ends facing the drive shaft each have a plate is attached, the piston by rotating the Radial drive shaft in the respective cylinder space Direction can be moved back and forth.
  • the invention is therefore based on the problem of a Radial piston pump to provide the above overcomes the disadvantages mentioned.
  • the plate is supposed to work wear-free in operation, even at high ones To press. In doing so, the proper operation of the Radial piston pump even with partial filling of the cylinder chambers to be guaranteed.
  • the radial piston pump according to the invention should withstand a pump pressure of up to 2000 bar.
  • the problem is with a radial piston pump High-pressure fuel supply in fuel injection systems of internal combustion engines, especially in a common rail injection system, with one stored in a pump housing Drive shaft which is eccentric or in Has circumferential cam-like elevations, and with preferably several radially in one with respect to the drive shaft Pistons arranged in each cylinder chamber, at the for Drive shaft facing ends each have a plate is attached, the piston by rotating the Radial drive shaft in the respective cylinder space Direction can be moved back and forth, solved in that the Plate in the middle is designed so that in operation occurring voltages can be reduced at this point.
  • the Plate in the middle is designed so that in operation occurring voltages can be reduced at this point.
  • the plate in the middle is less Thickness than in the outer areas. This will the stresses in the middle of the plate are reduced. The Power flow is redirected to the outer areas. Thereby there is a force redirection to those places be less burdened. So the critical area in relieved the middle of the plate.
  • a special meaning comes to the concrete shape of the plate.
  • the plate can be one central recess for receiving one end of one of the Have pistons. In such a case it is Training the plate center according to the invention within Well arranged.
  • Another special embodiment of the invention is characterized in that the plate in the middle on the side facing away from the drive shaft has a recess in the form of a cone, the tip of which is directed towards the inside of the plate.
  • This conical shape of the plate in the middle can be produced, for example, by turning. This has the advantage that conventional plates can be easily formed in accordance with the present invention.
  • the cone shape is particularly well suited to optimize the stress distribution in the plate.
  • Another special embodiment of the invention is characterized in that the plate in the middle on the a recess in the form facing the drive shaft has a cone, the tip of which is towards the inside of the plate is directed.
  • the plate can either be on its top or be conical on its underside. The Deciding on the top or bottom depends on the forces acting on the plate. It has in the Within the scope of the present invention it has been proven that is advantageous, the cone in particular on the side to train on which the greatest forces occur. This will usually be the side on which the drive shaft is arranged.
  • Another special embodiment of the invention is characterized in that the plate in the middle on the away from the drive shaft and on the Drive shaft facing side each have a recess in Has the shape of a cone, with the tips of the two cones are directed towards each other. According to the best results if both the top and also the bottom of the plate is conical in the middle be formed. This results in an optimal one Voltage curve during operation.
  • the wear resistance of a plate designed in this way is advantageously increased.
  • Another special embodiment of the invention is characterized in that the height of the cone at that of the side facing away from the drive shaft is about 1/10 of the height of the Cone on the side facing the drive shaft. This is an advantage because on the drive shaft facing the greatest forces occur. This is especially the case when the cylinder rooms are not be completely filled.
  • the exact dimensions of the Plate depend among other things on the pump pressure and the Number of load changes per unit of time.
  • Another special embodiment of the invention is characterized in that the plate is round.
  • the In principle, rectangular plates are also used possible, but the round shape is because of the cheaper introduction of force in cooperation with the Prefer drive shaft.
  • Another special embodiment of the invention is characterized in that the plate in the middle has a round recess.
  • the round depression in the The middle of the plate is used to hold the drive shaft directed end of one of the pistons. If the end of the Piston is received in the recess, the Plate essentially no longer relative to the drive shaft move.
  • Another special embodiment of the invention is characterized in that the plate has a collar.
  • the federal government forms a stop for a cage, which on the Is attached to the piston and serves to attach the plate to the To keep pistons.
  • Another special embodiment of the invention is characterized in that between the drive shaft and a ring is arranged on the plate.
  • the ring is used for Transfer of forces from the eccentrically trained Drive shaft to the plate.
  • the ring is advantageous slidably mounted on the drive shaft.
  • the Ring either cylindrical or polygonal his.
  • the present invention generally has the advantage that the basic idea of the present invention in simpler Way applied to existing radial piston pumps can be.
  • component strength especially in the event of zero delivery in the suction stroke.
  • Figure 1 shows a radial piston pump High pressure fuel supply at Fuel injection systems for internal combustion engines.
  • the Radial piston pump is with an integrated Required quantity control.
  • the fuel supply and dimensioning takes place via a not shown Metering unit.
  • the radial piston pump according to the invention is particularly in Common rail fuel injection systems for Diesel engines used.
  • “Common rail” means as much as “common management” or “common rail”.
  • Injectors in common rail injection systems from one fed common line Injectors in common rail injection systems from one fed common line.
  • the radial piston pump shown in FIG. 1 comprises a drive shaft 4 mounted in a pump housing 2 with an eccentrically designed shaft section 6.
  • a polygonal ring 8 is provided on the eccentric shaft section 6, with respect to which the shaft section 6 can be rotated.
  • the ring 8 comprises three flats 10, each offset by 120 ° to each other, against which a piston 12 is supported.
  • a cylindrical ring can also be used.
  • the pistons 12 are each received in a cylinder chamber 18 so that they can move back and forth in the radial direction relative to the drive shaft 4.
  • a plate 14 is fastened to the end of the pistons 12 facing the drive shaft 4.
  • the plates 14 are each held by a cage 15 on the associated piston 12.
  • the plates 14 are each biased by a spring 16 against the ring 8. As can be seen in FIG. 1, the plates 14 are in contact with the flats 10 of the ring 8.
  • the plate 14 according to the invention is alone shown.
  • the plate shown in cross section in FIG. 2 has the shape of a circular cylinder with a diameter of about 15 millimeters and a height of about 5 millimeters.
  • On the top of the plate 14 is also in the middle circular cylindrical recess 20 with a rounded Edge 21 recessed.
  • the recess 20 is used for receiving One end of one of the pistons 12 is on the plate 14 a collar 22 is also provided, the upper edge 23 is chamfered and into the top of the plate 14 transforms. There is a chamfer on the underside of the plate 14 24 provided.
  • Figure 3 shows the detail X from Figure 1 on a scale of 20: 1.
  • the plate 14 on the underside opposite the depression 20 has a conical recess 25 in the center.
  • the height H of the conical recess 25 is approximately 0.2 Millimeter.
  • the diameter of the conical recess 25 is about 2.8 millimeters.
  • Figure 4 shows the detail Y from Figure 1 on a scale of 20: 1.
  • the plate 14 in a conical recess in the middle of the recess 20 26 has.
  • the height h of the conical recess 26 is approximately 0.02 millimeters.

Landscapes

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

Claims (8)

  1. Pompe à pistons radiaux pour l'alimentation en carburant à haute pression d'un système d'injection de carburant d'un moteur à combustion interne, notamment d'un système d'injection à rampe commune, comportant monté dans le corps (2) de la pompe, un arbre d'entraínement (4) excentré ou ayant dans sa direction périphérique des bossages en forme de cames, ainsi que de préférence plusieurs pistons logés chacun dans une chambre cylindrique (18) dans une direction radiale par rapport à l'arbre d'entraínement (4), les pistons (12) ayant leur extrémité tournée vers l'arbre d'entrainement (4) une plaque (14), et étant commandés en mouvement de va-et-vient dans la direction radiale dans chaque chambre de cylindre (18) par la rotation de l'arbre d'entraínement (4),
    caractérisée en ce que
    la plaque (14) comporte au milieu du côté opposé à l'arbre d'entraínement (4) une cavité en forme de cône (26) dont la pointe est tournée vers l'intérieur de la plaque (14) pour diminuer les contraintes produites au milieu de la plaque pendant le fonctionnement.
  2. Pompe à pistons radiaux selon préambule de la revendication 1,
    caractérisée en ce que
    la plaque (14) comporte au milieu du côté tourné vers l'arbre d'entraínement (4), une cavité en forme de cône (25) dont la pointe est dirigée vers l'Intérieur de la plaque (14).
  3. Pompe à pistons radiaux selon le préambule de la revendication 1,
    caractérisée en ce que
    la plaque (14) comporte au milieu du côté à l'opposé de l'arbre d'entraínement (4) et sur le côté tourné vers l'arbre d'entraínement (4), chaque fois une cavité sous la forme d'un cône (25, 26) et les pointes des deux cônes (25, 26) sont tournées l'une vers l'autre.
  4. Pompe à pistons radiaux selon la revendication 3,
    caractérisée en ce que
    la hauteur du cône (26) du côté à l'opposé de l'arbre d'entraínement (4) correspond sensiblement à 1/10 de la hauteur du cône (25) du côté tourné vers l'arbre d'entrainement (4).
  5. Pompe à pistons radiaux selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    la plaque (14) est circulaire.
  6. Pompe à pistons radiaux selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    la plaque (14) comporte en son milieu une cavité circulaire (20).
  7. Pompe à pistons radiaux selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    la plaque (14) comporte une collerette (22).
  8. Pompe à pistons radiaux selon l'une quelconque des revendications précédentes,
    caractérisée par
    un anneau (8) prévu entre l'arbre d'entraínement (4) et la plaque (14).
EP99907314A 1998-04-01 1999-02-09 Pompe a pistons radiaux pour l'alimentation haute pression en carburant Expired - Lifetime EP1068448B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19814506 1998-04-01
DE19814506A DE19814506A1 (de) 1998-04-01 1998-04-01 Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
PCT/DE1999/000344 WO1999050555A1 (fr) 1998-04-01 1999-02-09 Pompe a pistons radiaux pour l'alimentation haute pression en carburant

Publications (2)

Publication Number Publication Date
EP1068448A1 EP1068448A1 (fr) 2001-01-17
EP1068448B1 true EP1068448B1 (fr) 2003-07-30

Family

ID=7863182

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99907314A Expired - Lifetime EP1068448B1 (fr) 1998-04-01 1999-02-09 Pompe a pistons radiaux pour l'alimentation haute pression en carburant

Country Status (5)

Country Link
US (1) US6350107B1 (fr)
EP (1) EP1068448B1 (fr)
JP (1) JP4288000B2 (fr)
DE (2) DE19814506A1 (fr)
WO (1) WO1999050555A1 (fr)

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DE10147981A1 (de) * 2001-09-28 2003-04-24 Siemens Ag Verbindungselement zur Verbindung eines Kolbens mit einem Rückstellelement
DE10150351A1 (de) * 2001-10-15 2003-05-08 Bosch Gmbh Robert Pumpenelement und Kolbenpumpe zur Kraftstoffhochdruckerzeugung
JP3733928B2 (ja) * 2002-05-28 2006-01-11 三菱電機株式会社 高圧燃料供給装置
DE10247645A1 (de) * 2002-10-11 2004-04-22 Robert Bosch Gmbh Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE10249818B4 (de) * 2002-10-24 2005-10-20 Daimler Chrysler Ag Oberfläche eines Körpers, auf dem ein anderer Körper in einer bevorzugten Gleitrichtung gegeneinander gleitend anordenbar ist
GB0311814D0 (en) * 2003-05-22 2003-06-25 Delphi Tech Inc Pump assembly
DE10326863A1 (de) * 2003-06-14 2004-12-30 Daimlerchrysler Ag Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen
ATE343060T1 (de) * 2003-06-18 2006-11-15 Delphi Tech Inc Antriebsanordnung für eine pumpe
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DE102008041449A1 (de) 2008-08-22 2010-02-25 Robert Bosch Gmbh Hochdruckpumpe zur Versorgung einer Verbrennungskraftmaschine mit Kraftstoff
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DE102008043993B3 (de) * 2008-11-21 2010-04-29 Thielert Aircraft Engines Gmbh Common-Rail-Hochdruckpumpe
DE102009002529A1 (de) 2009-04-21 2010-10-28 Robert Bosch Gmbh Einspritzpumpe für eine Verbrennungskraftmaschine
DE102018211654A1 (de) * 2018-07-12 2020-01-16 Robert Bosch Gmbh Kolbenpumpe, insbesondere Hochdruck-Kraftstoffpumpe für ein Einspritzsystem einer Brennkraftmaschine
RU191730U1 (ru) * 2019-06-06 2019-08-19 Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" Топливный насос высокого давления
RU202059U1 (ru) * 2020-09-18 2021-01-28 Общество с ограниченной ответственностью Управляющая компания "Алтайский завод прецизионных изделий" Топливный насос высокого давления
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Also Published As

Publication number Publication date
DE19814506A1 (de) 1999-10-14
US6350107B1 (en) 2002-02-26
WO1999050555A1 (fr) 1999-10-07
EP1068448A1 (fr) 2001-01-17
JP4288000B2 (ja) 2009-07-01
DE59906437D1 (de) 2003-09-04
JP2002510015A (ja) 2002-04-02

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