EP1068448A1 - Radialkolbenpumpe zur kraftstoffhochdruckversorgung - Google Patents
Radialkolbenpumpe zur kraftstoffhochdruckversorgungInfo
- Publication number
- EP1068448A1 EP1068448A1 EP99907314A EP99907314A EP1068448A1 EP 1068448 A1 EP1068448 A1 EP 1068448A1 EP 99907314 A EP99907314 A EP 99907314A EP 99907314 A EP99907314 A EP 99907314A EP 1068448 A1 EP1068448 A1 EP 1068448A1
- 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.)
- Granted
Links
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
- Radial piston pump for supplying high-pressure fuel
- the invention relates to a radial piston pump for high-pressure fuel supply
- Fuel injection systems of internal combustion engines in particular in the case of a common rail injection system, with a drive shaft mounted in a pump housing, which is eccentrically formed or has cam-like elevations in the circumferential direction, and preferably with a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, on the other of which A shaft is attached to the ends facing the drive shaft, the pistons being movable back and forth in the respective cylinder space by rotating the drive shaft in the radial direction.
- the plate attached to the ends of the pistons is in contact with the drive shaft.
- the pistons are successively caused to reciprocate by the eccentricity of the drive shaft or by cam-like elevations on the drive shaft. Relatively large forces are applied to the pistons by the rotating drive shaft depending on the force sucked into the cylinder chambers in order to pressurize the fuel.
- sucking fuel the pistons with the plate are usually pressed against the drive shaft by a spring.
- the invention is therefore based on the problem of a
- Radial piston pump can be guaranteed even with partial filling of the cylinder chambers.
- the radial piston pump according to the invention is designed to withstand a pump pressure of up to 2000 bar.
- Fuel injection systems of internal combustion engines in particular in a common rail injection system, with a drive shaft mounted in a pump housing, which is eccentrically formed or has cam-like elevations in the circumferential direction, and preferably - 3 - a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, on each of whose ends facing the drive shaft a plate is attached, the pistons being turned radially in the respective cylinder space by rotating the drive shaft
- Peak pressures of up to 2000 bar ensure that the plate functions properly.
- a special embodiment of the invention is characterized in that the plate has a smaller thickness in the middle than in the outer areas. This reduces the tension in the middle of the plate. The power flow is redirected to the outer areas. As a result, the force is redirected to those points that are less stressed. This relieves the critical area in the middle of the plate.
- the concrete shape of the plate is particularly important. Various designs are possible, but all of them implement the common basic idea of the present invention. Depending on the type of plate, the plate may have a central recess for receiving one end of one of the pistons. In such a case, the design of the plate center according to the invention is arranged within the depression.
- Another special embodiment of the invention is - 4 - 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 achieved, for example, by a
- the plate has a recess in the center on the side facing the drive shaft in the form of a cone, the tip of which is directed towards the inside of the plate.
- the plate can either be conical on its upper side or on its lower side. The decision for the top or bottom depends on the forces acting on the plate. It has proven in the context of the present invention that it is advantageous to form the cone in particular on the side on which the greatest forces occur. As a rule, this will be the side on which the drive shaft is arranged.
- a further special embodiment of the invention is characterized in that the plate has a recess in the form of a cone in the middle on the side facing away from the drive shaft and on the side facing the drive shaft, the tips of the two cones being directed towards one another. According to the invention, the best results are achieved if both the top and the bottom of the plate are conical in the middle. This results in an optimal 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 on the side facing away from the drive shaft is approximately 1/10 of the height of the cone on the side facing the drive shaft. This is advantageous because the greatest forces occur on the side facing the drive shaft. This is particularly the case if the cylinder spaces are not 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.
- the plate is round.
- rectangular plates can also be used, but the round shape is preferable because of the more favorable force transmission in cooperation with the drive shaft.
- the plate has a round recess in the middle.
- the round recess in the middle of the plate serves to receive the end of one of the pistons facing the drive shaft. When the end of the piston is received in the recess, the plate is essentially unable to move relative to the drive shaft.
- the plate has a collar.
- the collar forms a stop for a cage, which is attached to the piston and serves to hold the plate on the piston.
- Another special embodiment of the invention is characterized in that a ring is arranged between the drive shaft and the plate.
- the ring is used for Transfer of forces from the eccentrically designed drive shaft to the plate.
- the ring is advantageously slidably mounted on the drive shaft.
- the ring can be either cylindrical or polygonal.
- the present invention has the general advantage that the basic idea of the present invention can be applied to existing radial piston pumps in a simple manner.
- the component strength is increased, especially with zero delivery in the suction stroke.
- Figure 1 shows a sectional view of a radial piston pump
- Figure 2 shows a plate according to the present invention
- FIG. 3 shows an enlarged view of the detail X from FIG. 1 on a scale of 20: 1;
- FIG. 4 shows an enlarged view of detail Y from FIG. 1 on a 20: 1 scale.
- FIG. 1 shows a radial piston pump for supplying high-pressure fuel Fuel injection systems of internal combustion engines.
- the radial piston pump is equipped with an integrated demand control.
- the fuel supply and dimensioning takes place via a metering unit, not shown.
- the radial piston pump according to the invention is used in particular in common rail injection systems for supplying fuel to diesel engines.
- Common rail means “common line” or “common rail”.
- the injection nozzles in common-rail injection systems are fed from a 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 space 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 against the ring 8 by a spring 16. As can be seen in FIG. 1, the plates 14 are in contact with the flats 10 of the ring 8. - 8th -
- the plate 14 according to the invention is shown alone.
- the plate shown in cross section in FIG. 2 has the shape of a circular cylinder with a diameter of approximately 15 millimeters and a height of approximately 5 millimeters.
- a likewise circular-cylindrical depression 20 with a rounded edge 21 is cut out in the center on the top of the plate 14.
- the recess 20 serves to receive one end of one of the pistons 12.
- a collar 22 is also provided on the plate 14, the upper edge 23 of which is chamfered and merges into the top of the plate 14.
- a chamfer 24 is provided on the underside of the plate 14.
- Figure 3 shows the detail X from Figure 1 on a scale of 20: 1.
- the plate 14 has a conical recess 25 in the center on the underside opposite the depression 20.
- the height H of the conical recess 25 is approximately 0.2 millimeters.
- the diameter of the conical recess 25 is approximately 2.8 millimeters.
- Figure 4 shows the detail Y from Figure 1 on a scale of 20: 1.
- the plate 14 has a conical recess 26 in the center of the recess 20.
- 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)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19814506A DE19814506A1 (de) | 1998-04-01 | 1998-04-01 | Radialkolbenpumpe zur Kraftstoffhochdruckversorgung |
DE19814506 | 1998-04-01 | ||
PCT/DE1999/000344 WO1999050555A1 (de) | 1998-04-01 | 1999-02-09 | Radialkolbenpumpe zur kraftstoffhochdruckversorgung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1068448A1 true EP1068448A1 (de) | 2001-01-17 |
EP1068448B1 EP1068448B1 (de) | 2003-07-30 |
Family
ID=7863182
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99907314A Expired - Lifetime EP1068448B1 (de) | 1998-04-01 | 1999-02-09 | Radialkolbenpumpe zur kraftstoffhochdruckversorgung |
Country Status (5)
Country | Link |
---|---|
US (1) | US6350107B1 (de) |
EP (1) | EP1068448B1 (de) |
JP (1) | JP4288000B2 (de) |
DE (2) | DE19814506A1 (de) |
WO (1) | WO1999050555A1 (de) |
Families Citing this family (35)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10044997A1 (de) * | 2000-09-11 | 2002-03-21 | Schaeffler Waelzlager Ohg | Druckplatte einer Radialkolbenpumpe |
DE10108703C1 (de) * | 2001-02-23 | 2002-11-21 | Ats Spartec Inc | Radialkolbenpumpe |
US6461117B2 (en) * | 2001-02-27 | 2002-10-08 | International Truck Intellectual Property Company, L.L.C. | Reversible volume oil pump |
DE10110658C1 (de) * | 2001-03-06 | 2002-07-11 | Lucas Automotive Gmbh | Pumpvorrichtung für ein Fahrzeugbremssystem |
JP2003074439A (ja) * | 2001-06-19 | 2003-03-12 | Denso Corp | 燃料噴射ポンプ |
KR20040035730A (ko) * | 2001-08-08 | 2004-04-29 | 씨알티 커먼 레일 테크놀로지스 아게 | 고압 급송 펌프 |
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 |
DE60309145T2 (de) * | 2003-06-18 | 2007-08-16 | Delphi Technologies, Inc., Troy | Antriebsanordnung für eine Pumpe |
DE10347715A1 (de) * | 2003-10-14 | 2005-05-12 | Zahnradfabrik Friedrichshafen | Radialkolbenpumpe |
DE102004018163A1 (de) * | 2004-04-14 | 2005-11-10 | Siemens Ag | Radialkolbenpumpe |
JP4467469B2 (ja) * | 2005-06-08 | 2010-05-26 | ボッシュ株式会社 | 燃料供給用ポンプ及びタペット構造体 |
DE102006045897B4 (de) * | 2006-09-28 | 2008-09-11 | Continental Automotive Gmbh | Radialkolbenpumpe zur Kraftstoffhochdruckversorgung |
DE102006048605B3 (de) * | 2006-10-13 | 2008-04-17 | Siemens Ag | Radialkolbenpumpe zur Kraftstoffhochdruckversorgung |
ES2542856T3 (es) * | 2007-10-12 | 2015-08-12 | Delphi International Operations Luxembourg S.À R.L. | Mejoras relacionadas con bombas de combustible |
DE102007060772A1 (de) * | 2007-12-17 | 2009-06-18 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
JP5479330B2 (ja) * | 2008-05-14 | 2014-04-23 | 株式会社小金井精機製作所 | ディーゼルポンプ |
DE102008001858A1 (de) | 2008-05-19 | 2009-11-26 | Robert Bosch Gmbh | Steckpumpe |
DE102008002101A1 (de) | 2008-05-30 | 2009-12-03 | Robert Bosch Gmbh | Radialkolbenpumpe |
DE102008040239A1 (de) | 2008-07-08 | 2010-01-14 | Robert Bosch Gmbh | Radialkolbenpumpe |
DE102008041449A1 (de) | 2008-08-22 | 2010-02-25 | Robert Bosch Gmbh | Hochdruckpumpe zur Versorgung einer Verbrennungskraftmaschine mit Kraftstoff |
DE102008042068A1 (de) | 2008-09-12 | 2010-03-18 | Robert Bosch Gmbh | Kolbenpumpe |
GB0818811D0 (en) * | 2008-10-14 | 2008-11-19 | Delphi Tech Inc | Fuel pump assembly |
DE102008057089A1 (de) | 2008-11-13 | 2010-05-20 | Continental Mechanical Components Germany Gmbh | Pumpeneinheit für eine Hochdruckpumpe |
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 |
JP2023013759A (ja) * | 2021-07-16 | 2023-01-26 | 株式会社Soken | サプライポンプ |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3628425A (en) * | 1968-12-13 | 1971-12-21 | Messrs Mitsubishi Jukogyo Kk | Fluid motor-pump construction |
DE2061960B2 (de) * | 1970-12-16 | 1974-01-17 | Fichtel & Sachs Ag, 8720 Schweinfurt | Radialkolbenpumpe mit Drosseleinrichtung zur Begrenzung des Fördervolumens |
US4075932A (en) * | 1972-01-07 | 1978-02-28 | Karl Eickmann | Rotor, pistons, piston shoes and associated means in fluid handling devices |
GB1436752A (en) * | 1973-05-09 | 1976-05-26 | Eickmann K | Fluid handling devices having pistons and piston shoes |
CH570541A5 (de) * | 1973-10-10 | 1975-12-15 | Sulzer Ag | |
DE2529473C3 (de) * | 1975-07-02 | 1980-11-20 | Danfoss A/S, Nordborg (Daenemark) | Gleitschuhanordnung, insbesondere für Axial- und Radialkolbenmaschinen |
DE3505176C1 (de) * | 1985-02-15 | 1986-04-24 | Hauhinco Maschinenfabrik G. Hausherr, Jochums Gmbh & Co Kg, 4300 Essen | Radialkolbenpumpe für hydraulische Medien |
DE4136624A1 (de) * | 1991-11-07 | 1993-05-27 | Daimler Benz Ag | Ventilgesteuertes verdraengeraggregat mit ventilausloesung |
US5382140A (en) * | 1993-02-11 | 1995-01-17 | Elasis Sistema Ricerca Fiat Nel Mezzogiorno | Radial-piston pump |
DE4401074B4 (de) * | 1994-01-15 | 2007-01-18 | Robert Bosch Gmbh | Pumpenanordnung, insbesondere zur Förderung von Kraftstoff aus einem Vorratsbehälter zu einer Brennkraftmaschine |
DE19635164A1 (de) * | 1996-08-30 | 1998-03-05 | Bosch Gmbh Robert | Kolbenpumpe |
DE19705205A1 (de) * | 1997-02-12 | 1998-08-13 | Bosch Gmbh Robert | Kolbenpumpe |
DE19725564C2 (de) * | 1997-05-27 | 2001-05-23 | Hydraulik Ring Gmbh | Radialkolbenpumpe |
-
1998
- 1998-04-01 DE DE19814506A patent/DE19814506A1/de not_active Ceased
-
1999
- 1999-02-09 DE DE59906437T patent/DE59906437D1/de not_active Expired - Lifetime
- 1999-02-09 WO PCT/DE1999/000344 patent/WO1999050555A1/de active IP Right Grant
- 1999-02-09 US US09/647,358 patent/US6350107B1/en not_active Expired - Fee Related
- 1999-02-09 JP JP2000541427A patent/JP4288000B2/ja not_active Expired - Fee Related
- 1999-02-09 EP EP99907314A patent/EP1068448B1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9950555A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE19814506A1 (de) | 1999-10-14 |
JP2002510015A (ja) | 2002-04-02 |
WO1999050555A1 (de) | 1999-10-07 |
US6350107B1 (en) | 2002-02-26 |
JP4288000B2 (ja) | 2009-07-01 |
DE59906437D1 (de) | 2003-09-04 |
EP1068448B1 (de) | 2003-07-30 |
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