WO2002002937A1 - Radialkolbenpumpe - Google Patents
Radialkolbenpumpe Download PDFInfo
- Publication number
- WO2002002937A1 WO2002002937A1 PCT/DE2001/002234 DE0102234W WO0202937A1 WO 2002002937 A1 WO2002002937 A1 WO 2002002937A1 DE 0102234 W DE0102234 W DE 0102234W WO 0202937 A1 WO0202937 A1 WO 0202937A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston pump
- radial piston
- fuel
- high pressure
- channels
- Prior art date
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
- F04B1/0408—Pistons
-
- 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
- F04B1/0421—Cylinders
-
- 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
- F04B53/02—Packing the free space between cylinders and pistons
Definitions
- the invention relates to a radial piston pump for generating high fuel pressure
- Fuel injection systems of internal combustion engines in particular in a common rail injection system, with a drive shaft mounted in a housing, which has an eccentrically formed shaft section which interacts with preferably a plurality of pistons which can be moved radially back and forth with respect to the drive shaft in a respective element bore in order to draw in fuel and to apply high pressure in a high pressure area.
- the raceways of the pistons and the element bores must be very smooth and have a uniform surface.
- a certain amount of the medium to be compressed should also act as a lubricant on the surfaces adhere, which requires a certain surface roughness.
- This roughness is to the disadvantage of the bearing portion of the surfaces, ie not the entire outer surface of the pistons and element bores can be effectively used as a raceway.
- the shape and dimension accuracy to be achieved is also limited by the surface roughness. This limitation means that certain minimum cycles cannot be undershot, which in turn reduces the efficiency of the radial piston pump. The higher the pressure in the radial piston pump, the greater the effect.
- the object of the invention is to increase the efficiency and the service life of the known radial piston pump.
- the task is for a radial piston pump to generate high-pressure fuel
- Fuel injection systems of internal combustion engines in particular in a common rail injection system, with a drive shaft mounted in a housing, which has an eccentrically formed shaft section which interacts with preferably a plurality of pistons which can be moved radially back and forth with respect to the drive shaft in a respective element bore in order to draw in fuel and to apply high pressure in a high pressure area, solved in that a structure in the ⁇ m range is formed in the outer lateral surface of the piston and / or the inner lateral surface of the element bore.
- the raceways formed on the piston jacket surface and in the element bore can be made very smoothly and with a precise shape in the radial piston pump according to the invention. This means that no games can be realized, which is especially the case at high pressures because of the low pressures Gap losses lead to a good efficiency of the radial piston pump. However, the smooth surfaces would prevent sufficient lubrication during operation of the radial piston pump and lead to piston seizures.
- the targeted structuring of the surface of the pistons and / or the element bores has the function of lubrication pockets and lubrication channels. The structuring can be introduced specifically with the aid of a laser, for example. During operation, the lubricant is applied to the lubrication points to be supplied via the structure introduced into the surface
- the structuring serves as a reservoir for the lubricant.
- a special embodiment of the invention is characterized in that the structure is designed such that during operation there is no direct connection between the high-pressure area delimited by one end face of the respective piston and a low-pressure area delimited by the other end face. Leakage flows and gap losses are kept as low as possible.
- the size of the storage reservoir for the lubricant can be determined via the number of lubrication channels.
- a further special embodiment of the invention is characterized in that the structure is formed by paired lubrication channels of different lengths, each of which has two arms arranged at right angles to one another, one arm in the axial direction Direction and the other arm is arranged in the circumferential direction of the respective lateral surface. This results in a particularly good distribution of the lubricant over the surface to be lubricated.
- Another special embodiment of the invention is characterized in that the structure is formed by a plurality of channels running in the axial direction, which are arranged in groups and by channels running in the circumferential direction
- the flow resistance in the axial direction can be varied via the number of channels running in the axial direction.
- the lubrication can be improved in certain areas by additional connecting channels in the circumferential direction.
- the flow resistance is also depending on the parameters channel shape, channel cross-section and channel length. By a suitable choice of these parameters, the lubricant supply can be designed as required.
- Figure 2 is a perspective sectional view of an element bore according to the invention.
- Figure 3 shows a section of the processing of a
- Piston jacket surface according to a second embodiment of the invention.
- Figure 4 shows a section of the processing of a
- 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 something like common line or common rail.
- the injection nozzles in common-rail injection systems are fed from a common line.
- the radial piston pump shown there comprises a drive shaft mounted in a pump housing with an eccentrically designed shaft section.
- a ring is provided on the eccentric shaft section, with respect to which the eccentric shaft section can be rotated.
- the ring comprises three flats, each offset by 120 °, against which a piston is supported.
- the pistons are each received in an element bore relative to the drive shaft so that they can move back and forth in the radial direction and each delimit a cylinder space.
- a plate is attached by a plate holder, which lies against the associated flattening of the ring.
- the plate holder is attached to the piston by a snap ring.
- the radial piston pump is used to apply high pressure to fuel which is supplied by a pre-delivery pump from a tank.
- the fuel is preferably diesel fuel.
- the high-pressure diesel fuel is then fed into the common line mentioned above.
- the pistons are moved away from the axis of the drive shaft as a result of the eccentric movement of the ring.
- the pistons move radially towards the axis of the drive shaft in order to draw fuel into the cylinder chambers.
- the suction stroke movement of the pistons is achieved by a spring that is biased against the plate holder or plate.
- Figure 1 you can see a development of the outer surface of a piston of a radial piston pump according to the invention.
- 1 is the high pressure side and 2 the low pressure side of the radial piston pump.
- the development of the piston outer surface is generally designated 3.
- Several circumferential lubrication channels 4, 5, 6, 7 and 8 are arranged parallel to each other in the piston surface.
- the lubrication channels are spaced closer to each other on the high pressure side 1 than on the low pressure side 2.
- the individual lubrication channels are not connected to each other and are practically connected in parallel.
- an element bore 20 is shown in perspective in section.
- a plurality of lubrication channels 4, 5, 6, 7 and 8 running in the circumferential direction are formed on the inner circumferential surface of the element bore 20.
- FIG. 3 shows a development of the piston surface area of a piston according to a further embodiment of the invention.
- ten lubrication channels 9, 10, 11, 12, 13, 14, 15, 16, 17 and 18 are in a group together.
- the lubrication channels 9 to 18 are L-shaped.
- One leg of an L-shaped lubrication channel is arranged in the circumferential direction and the other leg in the axial direction.
- Two lubrication channels each with legs of the same length in the axial
- Direction are arranged in pairs to each other so that the legs face each other in the circumferential direction.
- a T-shaped lubrication channel 24 is arranged in the vicinity of the high pressure side 1.
- the center axis of the T-shaped lubrication channel faces the high-pressure side 1.
- the T-shaped lubrication channel 24 is surrounded by two L-shaped lubrication channels 25 and 26. Of the L-shaped legs arranged in the circumferential direction
- Lubrication channels 25 and 26 extend from a plurality of lubrication channels 27 in the axial direction.
- the lubrication channels 27 running in the axial direction are cut by a plurality of lubrication channels running in the circumferential direction.
- one of these lubrication channels running in the circumferential direction is designated by way of example at 28.
- the lubrication channels running in the circumferential direction in turn emanate from a plurality of lubrication channels running in the axial direction, one of which is designated 29 in FIG. Following this, run in the axial direction
- Lubrication channels are in turn arranged in the circumferential direction of lubrication channels 30. This is followed by lubrication channels 31 aligned in the axial direction and lubrication channels 32 aligned in the circumferential direction.
- the lubrication channels introduced by laser are not continuous in the axial direction.
- the lubrication channels are interrupted in order to keep the gap losses and leakage flows as low as possible.
- the lubrication channels can form regular patterns, but can also be arranged irregularly.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/070,314 US6837218B2 (en) | 2000-07-05 | 2001-06-15 | Radial piston pump |
JP2002507171A JP2004502092A (ja) | 2000-07-05 | 2001-06-15 | ラジアルピストンポンプ |
DE50112915T DE50112915D1 (de) | 2000-07-05 | 2001-06-15 | Radialkolbenpumpe |
EP01951390A EP1301708B1 (de) | 2000-07-05 | 2001-06-15 | Radialkolbenpumpe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10032577.7 | 2000-07-05 | ||
DE10032577A DE10032577A1 (de) | 2000-07-05 | 2000-07-05 | Radialkolbenpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002002937A1 true WO2002002937A1 (de) | 2002-01-10 |
Family
ID=7647814
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2001/002234 WO2002002937A1 (de) | 2000-07-05 | 2001-06-15 | Radialkolbenpumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US6837218B2 (de) |
EP (1) | EP1301708B1 (de) |
JP (1) | JP2004502092A (de) |
DE (2) | DE10032577A1 (de) |
WO (1) | WO2002002937A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7148803B2 (en) * | 2003-10-24 | 2006-12-12 | Symbol Technologies, Inc. | Radio frequency identification (RFID) based sensor networks |
JP4884135B2 (ja) | 2006-08-28 | 2012-02-29 | 日立建機株式会社 | 液圧回転機 |
DE102006040468A1 (de) * | 2006-08-29 | 2008-03-06 | Man Diesel Se | Kolbenpumpe mit Ablagerungsschutz |
DE102006052398B4 (de) * | 2006-10-31 | 2012-01-19 | Secop Gmbh | Kolben, insbesondere für einen Verdichter |
JP4530037B2 (ja) * | 2007-12-21 | 2010-08-25 | 株式会社デンソー | 内燃機関の吸気制御装置 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3153987A (en) * | 1960-06-29 | 1964-10-27 | Thoma Hans | Piston type hydrostatic power units |
DE2948346A1 (de) * | 1979-11-30 | 1981-06-04 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München | Hydraulisches pumpenelement |
WO1998034027A1 (fr) * | 1997-02-04 | 1998-08-06 | Komatsu Ltd. | Moteur de pompe a piston |
EP0967384A2 (de) * | 1998-04-24 | 1999-12-29 | Sumitomo Electric Industries, Ltd | Kraftstoffeinspritzpumpe |
DE19847044A1 (de) * | 1998-10-13 | 2000-04-20 | Bosch Gmbh Robert | Radialkolbenpumpe |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU8652675A (en) * | 1974-11-13 | 1977-05-19 | F.B.J. Engineering Services Pty. Ltd. | Piston |
DE2730034A1 (de) * | 1977-07-02 | 1979-01-18 | Bosch Gmbh Robert | Hydrostatische kolbenmaschine |
JPS5958172A (ja) * | 1982-09-27 | 1984-04-03 | Mitsubishi Heavy Ind Ltd | ピストン機械 |
US5239955A (en) * | 1993-01-07 | 1993-08-31 | Ford Motor Company | Low friction reciprocating piston assembly |
WO1994027040A1 (en) * | 1993-05-06 | 1994-11-24 | Cummins Engine Company, Inc. | Distributor for a high pressure fuel system |
JPH06332175A (ja) * | 1993-05-21 | 1994-12-02 | Konica Corp | 光重合性組成物 |
US5302450A (en) * | 1993-07-06 | 1994-04-12 | Ford Motor Company | Metal encapsulated solid lubricant coating system |
DE4401074B4 (de) * | 1994-01-15 | 2007-01-18 | Robert Bosch Gmbh | Pumpenanordnung, insbesondere zur Förderung von Kraftstoff aus einem Vorratsbehälter zu einer Brennkraftmaschine |
US5628625A (en) * | 1994-09-23 | 1997-05-13 | Kelsey-Hayes Company | High pressure fluid pump for use in vehicular braking system having anti-lock and traction assist feature |
DE19729793A1 (de) * | 1997-07-11 | 1999-01-14 | Bosch Gmbh Robert | Kolbenpumpe zur Kraftstoffhochdruckversorgung |
US6142125A (en) * | 1997-08-22 | 2000-11-07 | Isuzu Motors Limited | Supply pump for common rail fuel injection system |
JP4015278B2 (ja) * | 1998-05-28 | 2007-11-28 | 株式会社日本自動車部品総合研究所 | コモンレール式燃料噴射装置 |
DE19937802A1 (de) * | 1999-08-10 | 2001-03-01 | Bosch Gmbh Robert | Einzylinder-Hochdruckpumpe |
IT1310754B1 (it) * | 1999-11-30 | 2002-02-22 | Elasis Sistema Ricerca Fiat | Sistema di valvole per il controllo della pressione di ingresso di unliquido in una pompa ad alta pressione, e relativa valvola di |
-
2000
- 2000-07-05 DE DE10032577A patent/DE10032577A1/de not_active Withdrawn
-
2001
- 2001-06-15 US US10/070,314 patent/US6837218B2/en not_active Expired - Fee Related
- 2001-06-15 JP JP2002507171A patent/JP2004502092A/ja active Pending
- 2001-06-15 EP EP01951390A patent/EP1301708B1/de not_active Expired - Lifetime
- 2001-06-15 WO PCT/DE2001/002234 patent/WO2002002937A1/de active IP Right Grant
- 2001-06-15 DE DE50112915T patent/DE50112915D1/de not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3153987A (en) * | 1960-06-29 | 1964-10-27 | Thoma Hans | Piston type hydrostatic power units |
DE2948346A1 (de) * | 1979-11-30 | 1981-06-04 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München | Hydraulisches pumpenelement |
WO1998034027A1 (fr) * | 1997-02-04 | 1998-08-06 | Komatsu Ltd. | Moteur de pompe a piston |
EP0967384A2 (de) * | 1998-04-24 | 1999-12-29 | Sumitomo Electric Industries, Ltd | Kraftstoffeinspritzpumpe |
DE19847044A1 (de) * | 1998-10-13 | 2000-04-20 | Bosch Gmbh Robert | Radialkolbenpumpe |
Also Published As
Publication number | Publication date |
---|---|
EP1301708B1 (de) | 2007-08-22 |
EP1301708A1 (de) | 2003-04-16 |
US6837218B2 (en) | 2005-01-04 |
US20020179061A1 (en) | 2002-12-05 |
DE10032577A1 (de) | 2002-01-24 |
DE50112915D1 (de) | 2007-10-04 |
JP2004502092A (ja) | 2004-01-22 |
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