EP1047875A1 - Pompe a pistons radiaux pour alimentation haute pression en carburant - Google Patents
Pompe a pistons radiaux pour alimentation haute pression en carburantInfo
- Publication number
- EP1047875A1 EP1047875A1 EP98965060A EP98965060A EP1047875A1 EP 1047875 A1 EP1047875 A1 EP 1047875A1 EP 98965060 A EP98965060 A EP 98965060A EP 98965060 A EP98965060 A EP 98965060A EP 1047875 A1 EP1047875 A1 EP 1047875A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- radial piston
- piston pump
- ring
- recess
- 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.)
- Withdrawn
Links
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
- 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
- F02M59/10—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 the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- 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
- 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
- F02M59/08—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 two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
-
- 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
- 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
- Fuel injection systems of internal combustion engines in particular in the case of a common rail injection system, with one which is mounted eccentrically in a pump housing
- Drive shaft on which a ring is slidably mounted which cooperates with preferably a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, which pistons can be moved back and forth in the respective cylinder space by rotating the drive shaft.
- the base of the piston has contact with the ring mounted on the drive shaft.
- the pistons are successively reciprocated due to the eccentricity of the drive shaft.
- the stroke of the pistons is constant and corresponds to twice the eccentricity of the drive shaft.
- the invention is based on the problem of enabling partial filling of the cylinder spaces of the radial piston pump.
- the aim is to minimize wear on the individual components and avoid damage during operation.
- the radial piston pump according to the invention is intended to withstand a pump pressure of up to 2000 bar in the conveying direction.
- Fuel injection systems of internal combustion engines in particular in the case of a common rail injection system, with one which is mounted eccentrically in a pump housing
- Drive shaft on which a ring is slidably mounted which cooperates with preferably a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space, which can be moved back and forth in the respective cylinder space by rotating the drive shaft, in that a guide device prevents the ring from rotating about its own axis.
- a guide device prevents the ring from rotating about its own axis.
- a special embodiment of the invention is characterized in that the guide device comprises a projection which extends at least partially parallel to the axis of rotation of the drive shaft and projects into a recess whose dimensions are larger than that of the projection.
- the projection can either on the ring or on the
- Pump housing may be formed. In the first case it is associated recess in the pump housing and in the second case provided in the ring.
- the projection can only move in the transverse direction as far as the dimensions of the recess allow. This advantageously ensures that the movements of the ring are restricted in the circumferential direction.
- Another special embodiment of the invention is characterized in that the projection is formed on the ring and the recess in the pump housing.
- the reverse case is also possible, as described above, but in this case the size of the recess is limited to the dimensions of the ring. In contrast, there is sufficient space in the pump housing for the recess.
- the projection and the recess each have the shape of a cylinder, the longitudinal axis of which is parallel to the axis of the drive shaft.
- the ideal trajectory of the ring is a circle. Accordingly, it is advantageous if both the depression and the projection are cylindrical. This reduces the movement of the ring in the circumferential direction to the minimum necessary due to the eccentricity of the drive shaft.
- Another special embodiment of the invention is characterized in that the diameter of the recess is slightly greater than twice the sum of the eccentricity of the drive shaft and the radius of the projection. This ensures that the ring can move in its ideal path without the projection and the recess being in contact with one another. This has the advantage that wear due to friction is reduced. The projection only comes into contact with the depression when the ring no longer moves on its ideal path.
- a further special embodiment of the invention is characterized in that the projection is a pin which is fastened in a bore in the pump housing and in that the depression is a bore.
- Another special embodiment of the invention is characterized in that the recess is annular.
- the projection protrudes into the annular depression and can therefore only move in the circumferential direction of the depression.
- the ring can only perform such movements. In this way, a positive guidance of the ring along its ideal path of movement is advantageously ensured.
- the recess is a bore in which a pin is attached.
- the ring shape of the recess can be realized easily and inexpensively.
- the diameter of the pin is slightly less than twice the difference between the eccentricity and the radius of the Lead.
- a further special embodiment of the invention is characterized in that at least three pistons are arranged radially to the drive shaft, a plate being held at the end of each piston directed towards the drive shaft by a cage which is in contact with a flattened portion is formed on the ring.
- the guide device according to the invention has a particularly advantageous effect. Experiments carried out with such a pump have found that the ring can tilt about its axis if the cylinder spaces are not completely filled. This tilting is attributed to the fact that one
- Element part filling does not keep all plates firmly enough against the ring.
- the tilting causes shock forces on the plate, which are transferred to the cage and the piston.
- the resulting moments then lead to damage to the affected components.
- the guide device according to the invention can consist of at least one guide piston which, in addition to the already existing pistons, is arranged radially to the drive shaft and bears against the ring.
- Figure 1 shows a sectional view of a radial piston pump according to the invention, the section running along the line DE in Figure 2;
- FIG. 2 shows a section along line B-C through the radial piston pump from FIG. 1.
- Figure 3 shows a partial view of a section along the line A-A in Figure 2;
- Figure 4 shows the ideal trajectory of a ring and a guide device according to the present invention.
- Figures 1 and 2 show a radial piston pump
- Radial piston pump is equipped with an integrated demand control.
- the fuel supply and dimensioning takes place via a not shown
- the radial piston pump according to the invention is used in particular in common rail injection systems for supplying fuel
- Common rail means “common line” or “common rail”.
- the radial piston pump shown in FIGS. 1 and 2 comprises a one mounted in a pump housing 2
- a shaft 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.
- 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.
- the foot of each piston 12 is designed as a plate 14, which lies against the flat 10 of the ring 8.
- the plate 14 is fastened to the piston 12 by a cage 16 and is pressed against the ring 8 by a spring 20.
- a twisting of the ring is reduced to a minimum by a guide device 24.
- the guide device 24 shown by way of example in FIGS. 1 and 2 comprises, as can be seen most clearly in the partial view of FIG. 3, a bore 25 provided in the ring, in which a pin 26 is fastened.
- the pin 26 protrudes into a further bore 28 which is provided in the housing 2 and whose diameter is larger than that of the pin 26.
- Another pin 30 is fastened centrally in the bore 28 in the housing 2.
- the .Dimensions of the holes and the pins are chosen so that the difference between the diameter of the bore 28 in the housing 2 and the diameter of the pin 30 in the housing 2 is slightly larger than the diameter of the pin 26 in the ring 8. Therefore the pin 26 can move in the annular space around the pin 30 in the bore 28 in the housing 2 on a circular path.
- FIG. 4 shows the ideal movement path 46 of a polygonal ring 48.
- the polygonal ring 48 is, as previously described, on an eccentrically designed drive shaft, not shown in FIG slidably mounted.
- the eccentricity is designated E in FIG. 4.
- a pin 44 with a diameter 45 is fastened in the ring 48.
- the pin 44 projects with its free end into a bore 50 which is provided in a housing (not shown) and has a diameter 51.
- a pin 47 is arranged, which is fixed in the housing and the diameter of which is designated 55.
- the circle 46 has a diameter which corresponds to twice the eccentricity E, that is to say the piston stroke.
- the diameter 51 of the bore 50 ideally corresponds to the sum of the piston stroke and the diameter of the pin 44 in the ring 48. In practice, the ideal dimensions are still the usual ones
- the invention now has not only the advantage that the torque of the ring 8 is absorbed by the pin 26, but also the advantage that the center offset M can be eliminated. This has the consequence that the same thing for left and right-hand rotation of the radial piston pump according to the invention
- the present invention also provides the advantage that the spring 20, which presses the plate 14 against the ring 8, is relieved. This increases the durability of the spring 20. In addition, breaks in the cage 16, which holds the plate 14 on the piston 12, are prevented. This simplifies quality assurance with regard to zero errors. Finally, it is pointed out that no one else for partial filling Center offset M of the piston 12 is necessary.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Reciprocating Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
L'invention concerne une pompe à pistons radiaux pour l'alimentation haute pression en carburant dans des systèmes d'injection de carburant de moteurs à combustion interne, notamment dans un système d'injection pour rampe d'alimentation, comportant un arbre d'entraînement (4) monté excentrique dans un carter de pompe (2). Sur cet arbre d'entraînement (4) est montée coulissante une bague (8) qui coopère avec de préférence plusieurs pistons (12) disposés dans une chambre de cylindre respective (18), radialement par rapport audit arbre (4), ces pistons étant animés d'un mouvement alternatif par la rotation de l'arbre d'entraînement (4) dans la chambre de cylindre respective (18). Dans le but d'accroître le rendement du moteur à combustion interne, les chambres de cylindre sont remplies avec moins de carburant en cas de diminution de la demande. Lors de ce remplissage dit partiel de l'élément, il se produit une usure et une détérioration accrues notamment dans le cas d'une pompe à pistons radiaux, du type précité, avec trois pistons au niveau desquels respectivement un disque est maintenu en appui sur une bague polygonale. Dans le but d'éliminer ce problème, un système de guidage (24) empêche une rotation de la bague (18, 48) autour de son propre axe.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19801398A DE19801398A1 (de) | 1998-01-16 | 1998-01-16 | Radialkolbenpumpe zur Kraftstoffhochdruckversorgung |
DE19801398 | 1998-01-16 | ||
PCT/DE1998/003222 WO1999036697A1 (fr) | 1998-01-16 | 1998-11-05 | Pompe a pistons radiaux pour alimentation haute pression en carburant |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1047875A1 true EP1047875A1 (fr) | 2000-11-02 |
Family
ID=7854762
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98965060A Withdrawn EP1047875A1 (fr) | 1998-01-16 | 1998-11-05 | Pompe a pistons radiaux pour alimentation haute pression en carburant |
Country Status (5)
Country | Link |
---|---|
US (1) | US6446604B1 (fr) |
EP (1) | EP1047875A1 (fr) |
JP (1) | JP2002509223A (fr) |
DE (1) | DE19801398A1 (fr) |
WO (1) | WO1999036697A1 (fr) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE29915179U1 (de) | 1999-08-30 | 2000-01-05 | TRW Fahrwerksysteme GmbH & Co KG, 40547 Düsseldorf | Lenksystem für ein Fahrzeug |
DE19949166A1 (de) * | 1999-10-12 | 2001-04-26 | Siemens Ag | Vorrichtung zur Stabilisierung des Exzenterrings einer Radialkolbenpumpe |
US6460510B1 (en) * | 2000-05-30 | 2002-10-08 | Robert H. Breeden | Pump assembly and method |
DE10058050C1 (de) * | 2000-11-23 | 2002-03-21 | Ats Spartec Inc | Radialkolbenpumpe |
DE10147981A1 (de) * | 2001-09-28 | 2003-04-24 | Siemens Ag | Verbindungselement zur Verbindung eines Kolbens mit einem Rückstellelement |
DE10310123A1 (de) * | 2003-03-07 | 2004-09-23 | Siemens Ag | Radialkolbenpumpe |
DE10349310B3 (de) * | 2003-10-23 | 2005-05-19 | Siemens Ag | Radialkolbenpumpe für Common Rail Einspritzsysteme |
US7134846B2 (en) * | 2004-05-28 | 2006-11-14 | Stanadyne Corporation | Radial piston pump with eccentrically driven rolling actuation ring |
ATE439517T1 (de) * | 2005-03-24 | 2009-08-15 | Delphi Tech Inc | Kraftstoffpumpe |
JP2007120492A (ja) * | 2005-09-29 | 2007-05-17 | Denso Corp | 高圧燃料ポンプ |
DE102006017036A1 (de) * | 2006-04-11 | 2007-10-18 | Siemens Ag | Radialkolbenpumpe zur Kraftstoff-Hochdruckversorgung bei einer Brennkraftmaschine |
DE102008017535B3 (de) * | 2008-04-03 | 2009-08-27 | Hofer Mechatronik Gmbh | Radialkolbenpumpe |
DE102009000964A1 (de) * | 2009-02-18 | 2010-08-19 | Robert Bosch Gmbh | Hochdruckkraftstoffpumpe für eine Brennkraftmaschine |
EP2299114B1 (fr) | 2009-09-10 | 2012-05-02 | Delphi Technologies Holding S.à.r.l. | Ensemble de pompe |
DE102011003104A1 (de) * | 2011-01-25 | 2012-07-26 | Continental Automotive Gmbh | Hochdruckpumpe |
JP6293994B2 (ja) * | 2012-10-31 | 2018-03-14 | 日立オートモティブシステムズ株式会社 | 高圧燃料供給ポンプ |
CN103498741A (zh) * | 2013-10-18 | 2014-01-08 | 中国重汽集团重庆燃油喷射系统有限公司 | Y形高压供油泵总成 |
JP6432886B2 (ja) * | 2015-06-25 | 2018-12-05 | 日立オートモティブシステムズ株式会社 | ポンプ装置 |
CN108869231B (zh) * | 2018-08-03 | 2024-02-13 | 东莞力嘉塑料制品有限公司 | 一种旋转式导轨驱动活塞泵 |
CN110578684B (zh) * | 2019-08-23 | 2020-07-24 | 浙江大学 | 一种径向柱塞泵/马达及其配流结构 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1027031B (de) * | 1952-11-20 | 1958-03-27 | Spladis Soc Pour L Applic D In | Exzenterantrieb fuer radial zur Antriebswellenachse gelagerte und belastete Kolben |
GB2160596B (en) * | 1984-06-23 | 1987-04-29 | Pitcraft Summit Ltd | Pump |
DE3612942A1 (de) * | 1986-04-17 | 1987-10-22 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
GB8718857D0 (en) * | 1987-08-08 | 1987-09-16 | Glasdon Ltd | Post & rail assembly |
US5035221A (en) * | 1989-01-11 | 1991-07-30 | Martin Tiby M | High pressure electronic common-rail fuel injection system for diesel engines |
US4957419A (en) * | 1989-04-14 | 1990-09-18 | Rascov Anthony J | Compressor |
US5634777A (en) * | 1990-06-29 | 1997-06-03 | Albertin; Marc S. | Radial piston fluid machine and/or adjustable rotor |
DE4237851A1 (en) * | 1991-11-12 | 1993-05-13 | Barmag Luk Automobiltech | Radial piston pump with actuating eccentric |
US5364234A (en) * | 1992-05-20 | 1994-11-15 | Karl Eickmann | High pressure devices |
MX9403372A (es) * | 1993-05-06 | 1995-01-31 | Cummins Engine Co Inc | Bomba de alta presion de desplazamiento variable para sistemas deinyeccion de combustible a deposito comun. |
EP0816675B1 (fr) * | 1996-07-01 | 2002-04-10 | Mannesmann Rexroth AG | Dispositif pour la stabilisation de l'anneau excentrique d'une pompe à pistons radiaux |
-
1998
- 1998-01-16 DE DE19801398A patent/DE19801398A1/de not_active Withdrawn
- 1998-11-05 EP EP98965060A patent/EP1047875A1/fr not_active Withdrawn
- 1998-11-05 WO PCT/DE1998/003222 patent/WO1999036697A1/fr not_active Application Discontinuation
- 1998-11-05 JP JP2000540372A patent/JP2002509223A/ja active Pending
- 1998-11-05 US US09/600,397 patent/US6446604B1/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO9936697A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO1999036697A1 (fr) | 1999-07-22 |
US6446604B1 (en) | 2002-09-10 |
DE19801398A1 (de) | 1999-07-22 |
JP2002509223A (ja) | 2002-03-26 |
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Legal Events
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PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
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17P | Request for examination filed |
Effective date: 20000816 |
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AK | Designated contracting states |
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17Q | First examination report despatched |
Effective date: 20031217 |
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STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
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18D | Application deemed to be withdrawn |
Effective date: 20040428 |