EP1592887A1 - Hochdruckpumpe - Google Patents
HochdruckpumpeInfo
- Publication number
- EP1592887A1 EP1592887A1 EP03773421A EP03773421A EP1592887A1 EP 1592887 A1 EP1592887 A1 EP 1592887A1 EP 03773421 A EP03773421 A EP 03773421A EP 03773421 A EP03773421 A EP 03773421A EP 1592887 A1 EP1592887 A1 EP 1592887A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- pressure pump
- pump according
- pressure
- cam ring
- 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
- 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
- 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
- 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
- F04B1/0413—Cams
-
- 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
- F04B53/04—Draining
-
- 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
- F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
Definitions
- the invention relates to a high pressure pump according to the preamble of claim 1, which is particularly suitable for use in a fuel injection system for internal combustion engines.
- DE-A-197 05 205 and the corresponding US-A-6,077,056 describe a generic high pressure pump for a fuel injection device for internal combustion engines, in which the piston of a piston pump unit is driven harmoniously by an eccentric drive.
- the piston At its end facing away from the working space of the piston pump unit, the piston carries a sliding shoe which rests with a sliding surface on a sliding bearing surface of a cam ring.
- the cam ring is rotatably mounted on an eccentric pin of a drive shaft and is driven in a rotating manner, but not rotating.
- the drive shaft, the eccentric pin, the cam ring and the sliding block are housed in a low-pressure chamber, which acts as a feed chamber for the medium to be conveyed, i.e. Fuel, serves.
- a relief chamber is formed in the sliding block, which is open to the sliding bearing surface and is in direct hydraulic connection with the working chamber via a passage which extends in the longitudinal direction of the pump piston. The relief chamber is therefore filled with the fuel to be delivered
- the lubrication of the slide bearing between the slide shoe and the cam ring is carried out by the fuel in the relief chamber.
- the bearing between the eccentric pin and the cam ring is lubricated by the fuel in the low pressure chamber.
- fuel is known to have poor lubricating properties and can therefore only have a limited lubricating effect.
- the present invention is based on the object of creating a high-pressure pump of the type mentioned at the outset for very high delivery pressures and large delivery quantities, the production costs of which are as low as possible and which can meet the high demands on operational reliability and on the service life.
- the relief chamber is separated from the working chamber by the pressure transmission element arranged in the passage in the piston. This also separates the medium to be pumped, for example fuel, from the medium in the relief chamber.
- a medium that is much more suitable for these tasks can be chosen, ie a those with excellent lubricating properties, such as lubricating oil.
- the pressure transmission element Since the pressure transmission element is acted upon on one side by the medium to be conveyed and is adjustable in the direction of the pressurization, the pressure in the work space is transmitted to the medium in the relief space, i.e. with increasing pressure in the work space, the pressure in the relief space also increases.
- This relief of the slide bearing not only permits higher delivery pressures, but also enables the piston area to be enlarged and thus an increased delivery volume without the number of piston pump units necessarily having to be increased. This has a favorable effect on the manufacturing costs.
- Fig. 1 in a longitudinal section a first
- Fig. 4 is a section along the line A-A in
- Fig. 5 in a representation corresponding to Fig. 2 shows a second
- Embodiment of a high pressure pump Embodiment of a high pressure pump.
- Each piston pump unit 2, 2 ' has a housing block 3 which is firmly connected to a pump housing 4 and projects into the interior 5 of this pump housing 4.
- Each piston pump unit 2, 2 ' has a piston 6 (plunger), which is guided in a linearly movable manner with a tight sliding fit in a cylinder bore 7 in the housing block 3.
- the piston 6 delimits a working space 8 with an end face 6a and widens at its opposite end to form a foot part 9.
- This foot part 9 has a flat sliding surface 10 which rests on a sliding bearing surface 11 which is provided on a cam ring 12.
- This cam ring 12 is common to both piston pump units 2, 2 '.
- a crank drive 13 is provided which has a drive shaft 14 shown in dashed lines and a firmly connected with this eccentric 15th
- the drive shaft 14 is driven to rotate about its axis of rotation 14a (FIG. 1).
- the cam ring 13 is rotatably but not co-rotating on the eccentric element 15.
- the eccentric element 15 is arranged with an eccentricity e (FIG. 1) with respect to the axis of rotation 14a of the drive shaft 14.
- the cam ring 12 When the drive shaft 14 is rotated, the cam ring 12 is moved on the one hand parallel to the slide bearing surfaces 12 and on the other hand at right angles to the axis of rotation 14a of the drive shaft 14, in each direction by the amount 2e. The cam ring 12 is thus moved back and forth in operation with respect to the foot part 9 of the piston 6.
- the pistons 6 of the piston pump units 2, 2a perform a stroke which is also 2e, ie twice the eccentricity e.
- An inlet line 18 is formed in the housing block 3 and is connected to the working space 8 via a pressure-controlled inlet valve 19 (FIG. 1).
- the inlet line 18 is connected to a feed line, not shown, which is connected to a liquid reservoir, ie in the present case to a fuel tank, for example via a pre-feed pump.
- a feed line not shown
- a liquid reservoir ie in the present case to a fuel tank
- a pre-feed pump for example via a pre-feed pump.
- an outlet line 20 which is pressure-controlled Exhaust valve 21 is connected to the working space 8 (Fig. 1).
- the outlet line 20 is connected to a high-pressure chamber, for example the common rail of a fuel injection system.
- a relief space 22 is formed in the foot part 9 of the piston 6, which is open to the sliding bearing surface 11.
- a continuous, coaxial passage 23 extends in the longitudinal direction of the piston 6 and is open on the one hand to the working chamber 8 and on the other hand to the relief chamber 22 (the passage 23 could also be unsecured).
- This passage 23, whose diameter changes, includes a longitudinal bore 24 in which a control piston 25 is slidably guided with a narrow sliding fit, which serves as a pressure transmission element.
- the control piston 25 rests on a compression spring 26 which is supported at the other end on a spring ring 27 (FIG. 2) which is held in the piston 6.
- annular groove 28 is formed, which extends around the piston 6 and for
- Cylinder bore 7 is open. In the piston 6 there is one
- Cross bore 29 is present, which passes through the piston 6 and which is connected to the annular groove 28 at both ends.
- a drain line 30 is connected to the annular groove 28, which runs in the housing block 3 and is connected to a return line, not shown, which leads to a collecting reservoir, which can be the fuel tank.
- a collecting reservoir which can be the fuel tank.
- leakage liquid collects in a manner to be described, which is returned via the drain line 30.
- the eccentric element 15 is provided with a lubrication groove 31 which extends along part of the circumference and is open towards the cam ring 12.
- the lubrication groove 31 is connected via a radial bore 32 in the eccentric element 15 to a feed channel 33 which extends in the direction of the axis of rotation 14a of the drive shaft 14 and which is connected to a lubricant reservoir via a lubricant pump (not shown).
- a lubricant preferably lubricating oil, is supplied via this feed channel 33 at a pressure of, for example, 2-6 bar.
- Two connecting channels 34, 35 are formed in the lifting ring 12, each of which leads from the inner surface 12a of the lifting ring 12 to one of the sliding bearing surfaces 11.
- the lubrication groove 31, which is permanently connected to the feed channel 33, is only connected to a connecting channel 34, 35 at certain rotational positions of the eccentric element 15, as can be seen from FIGS. 1-3.
- Figure 1 shows that rotational position of the eccentric element 15 in which the piston 6 of the one, in the figures upper piston pump unit 2 in the lower end position, i.e. is at the end of the suction stroke.
- the piston 6 of the other, lower piston pump unit 2 'has reached the end of the delivery stroke and thus its upper end position.
- the connection channels 34, 35 are neither in connection with the lubrication groove 31 nor with the associated relief space 22.
- the delivery stroke begins for the piston 6 of the upper piston pump unit 2, i.e. the piston 6 is moved in the direction of arrow A (Fig. 2) upwards.
- the inlet valve 19 is closed, which also applies to the outlet valve 21 at the beginning of the delivery stroke.
- the pressure in the work space 8 increases.
- the control piston 25, which is acted upon by the pressure of the liquid in the working chamber 8 on its end face facing the working chamber 8, is moved downward in the direction of arrow D in FIG. 2 against the action of the compression spring 26.
- the result of this is that the pressure of the lubricant, which is located in the relief chamber 22 and in the region of the passage 23 below the control piston 25, increases.
- FIG. 3 shows the situation after rotation of the drive shaft 14 by a total of 270 °.
- the piston 6 has reached its central position during the suction stroke.
- the cam ring 12 now assumes its left end position, which is shown in FIG. 4 by solid lines.
- This FIG. 4 shows that the cam ring 12 executes an overall stroke C in the direction of the slide bearing surface 11, which is equal to 2e, that is to say twice the eccentricity e.
- the connecting channel 34 in the lifting ring 12 is now connected to the relief chamber 22 and the lubrication groove 31.
- liquid-lubricant mixture i.e. as a fuel-lubricating oil mixture, collected in the annular groove 28.
- the mixture of liquid (fuel and lubricant (lubricating oil)) in the annular groove 28 is about
- Drain line 30 and e.g. in the
- Liquid reservoir i.e. the fuel tank.
- annular groove 36 is additionally formed in the foot part 9 of the piston 6 in the region of the sliding surface 10, which is arranged coaxially with the relief space 22 and to the plain bearing surface 11 is open.
- This annular groove 36 is connected to a longitudinal groove 37 formed in the cam ring 12 and open towards the sliding surface 10.
- This longitudinal groove 37 is offset in relation to the sectional plane of FIG. 3 (which runs perpendicular to the axis of rotation 14a and in the center of the lifting ring 12) in the direction of the axis of rotation 14a of the drive shaft 14 and opens at both ends into the interior 5 of the pump housing 4 (FIG. 4).
- the leakage fluid (lubricating oil) entering this annular groove 36 is returned to the interior 5 via the longitudinal groove 37.
- FIG. 5 differs from the first embodiment according to FIGS. 1-4 in another embodiment of the pressure transmission element arranged in the piston 6.
- FIG. 5 which corresponds to the representation of FIG. 2, the same reference numerals are used for parts that are the same in both embodiments as in FIGS. 1-4.
- the piston 6 consists of a piston element 38 guided in the cylinder bore 7 and a ring 39 which is firmly connected to the piston element 38 at the end remote from the working space 8, e.g. by pressing or shrinking.
- the ring 39 lies with a sliding surface 10 on the sliding bearing surface 11 on the cam ring 12 and has a flange 40 on which the compression spring 17 is supported.
- This compression spring 17 - as described with reference to FIGS. 1-3 - ensures that the ring 39 remains in contact with the cam ring 12.
- the sliding surface 10 is formed on the ring 39.
- the flange 40 could also be designed as a separate part, analogous to the bearing ring 16 from FIG. 2.
- An elastically deflectable membrane 41 is arranged between the ring 39 and the piston element 38 and is tightly clamped along its edge region between the ring 39 and the piston element 38.
- This membrane 41 which serves as a pressure transmission element, spans the relief space 22 delimited by the inner ring wall 39a and separates this relief space 22 from a chamber 42 formed in the piston element 38 this chamber 42 opens into a longitudinal bore 43 which extends in the direction of the longitudinal axis of the piston element 38 and via which the chamber 42 is connected to the working space 8.
- the longitudinal bore 43 and the chamber 42 form the passage 23.
- the chamber 42 is filled with the liquid to be pumped, ie with fuel.
- the pressure in the chamber 42 changes in the same direction as the pressure in the working space 8.
- the membrane 41 is pushed downwards in the direction of the pressurization. to the plain bearing surface 11, deflected. This leads to an increase in pressure in the relief chamber 22 containing lubricant and thus to a hydrostatic pressure relief, as has already been described with reference to FIGS. 1-4. Since the pressures on both sides of the membrane 41 are practically the same, the stress on the membrane 41 is low. This can be made thin-walled and elastic.
- annular groove 28 present in the first exemplary embodiment according to FIGS. 1-3, including the drain line 30 for collecting and carrying away leakage fluid, is not shown, but can also be provided if necessary.
- the membrane 41 is attached to the end face 6a of the piston 6 facing the working space 8.
- the membrane 41 could be attached by welding the same or, analogously to FIG. 5, with a screwed, pressed or shrunk holding part.
- the passage 23 is then located below the membrane 41, it is filled with the lubricant and communicates directly with the relief chamber 22.
- the mode of operation of the embodiment shown in FIG. 5 corresponds to the mode of operation described with reference to FIGS. 1-4.
- High-pressure pump 1, 1 have the advantage that
- Plain bearing which is formed by the sliding surface 10 on the piston 6 and the sliding bearing surface 11 on the cam ring 12, is achieved.
- the piston 6 has no transverse bore 29.
- control piston 25 has a larger diameter than shown in FIGS. 1-3.
- the longitudinal bore 24 for guiding the control piston 25 in a narrow sliding fit can be open towards the top in the direction of the working space 8.
- the part of the passage 23 which is narrower in cross section is again below the control piston 25 and communicates directly with the relief chamber 22.
- the control piston 25 is installed in the piston 6 from above.
- a spring ring analogous to the spring ring 27 according to FIG. 2, then prevents the control piston from exiting above the end surface 6a.
- the longitudinal bore 24 can also be continuous in the piston 6.
- the remaining part of the passage 23 has the same diameter as the longitudinal bore 24. It is also conceivable to make the remaining section of the passage 23 slightly larger than the diameter of the longitudinal bore 24.
- a separation of the foot part 9 and piston 6 into two parts can also be used.
- the inner surface 12a of the cam ring 12, together with the associated surface of the eccentric element 15, could also be slightly spherical in the direction of the axis of rotation 14a or even slightly spherical in the longitudinal and transverse directions. In this case, it is advisable to design the cam ring 12 in two parts for assembly reasons.
- piston pump unit 2 instead of two piston pump units 2, 2 ′ as shown in FIG. 1, only one piston pump unit 2 can also be provided.
- more than two piston pump units with corresponding sliding surfaces 11 of the cam ring 12 can also be attached radially, e.g. 3 piston pump units offset by 120 °, or 4 by 90 °, or also 6 by 60 ° with a common cam ring 12.
- high-pressure pumps 1, 1 ′ described are intended for use in fuel injection systems of internal combustion engines, in particular of diesel engines, these pumps can also be used in other fields.
- control piston 25 is moved solely by the pressure forces acting on the two end faces.
- control piston 25 it is also possible to design the control piston 25 with two different diameters. If the end face facing the working space 8 is then larger than that facing the relief space, a pressure translation takes place. In the opposite case, a pressure reduction. In these configurations, it can be advantageous to design the control piston 25 from two separate parts, each with the corresponding diameter. If the bore with the correspondingly larger diameter and the one with the correspondingly smaller diameter are not exactly aligned, tolerance and friction problems can be prevented.
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)
- Superconductors And Manufacturing Methods Therefor (AREA)
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06026525.3A EP1760312B1 (de) | 2003-02-11 | 2003-12-04 | Hochdruckpumpe |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH2022003 | 2003-02-11 | ||
CH202032003 | 2003-02-11 | ||
PCT/CH2003/000802 WO2004072477A1 (de) | 2003-02-11 | 2003-12-04 | Hochdruckpumpe |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06026525.3A Division EP1760312B1 (de) | 2003-02-11 | 2003-12-04 | Hochdruckpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1592887A1 true EP1592887A1 (de) | 2005-11-09 |
EP1592887B1 EP1592887B1 (de) | 2007-02-28 |
Family
ID=32855128
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06026525.3A Expired - Lifetime EP1760312B1 (de) | 2003-02-11 | 2003-12-04 | Hochdruckpumpe |
EP03773421A Expired - Lifetime EP1592887B1 (de) | 2003-02-11 | 2003-12-04 | Hochdruckpumpe |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06026525.3A Expired - Lifetime EP1760312B1 (de) | 2003-02-11 | 2003-12-04 | Hochdruckpumpe |
Country Status (8)
Country | Link |
---|---|
US (2) | US7108491B2 (de) |
EP (2) | EP1760312B1 (de) |
JP (1) | JP2006514195A (de) |
CN (1) | CN100392241C (de) |
AT (1) | ATE355460T1 (de) |
AU (1) | AU2003281906A1 (de) |
DE (1) | DE50306704D1 (de) |
WO (1) | WO2004072477A1 (de) |
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US7134846B2 (en) * | 2004-05-28 | 2006-11-14 | Stanadyne Corporation | Radial piston pump with eccentrically driven rolling actuation ring |
WO2006037672A1 (de) * | 2004-10-06 | 2006-04-13 | Siemens Aktiengesellschaft | Hochdruckpumpe |
US7278443B2 (en) | 2004-12-16 | 2007-10-09 | Diversified Dynamics Corporation | Pulsation causing valve for a plural piston pump |
US7290561B2 (en) | 2004-12-16 | 2007-11-06 | Diversified Dynamics Corporation | Pulsation causing valve for a plural piston pump |
US20060140778A1 (en) * | 2004-12-28 | 2006-06-29 | Warren Leslie J | Reciprocating positive displacement pump for deionized water and method of cooling and lubricating therefor |
FR2904665B1 (fr) * | 2006-08-04 | 2008-10-31 | Siemens Automotive Hydraulics | Pompe transfert pour injection d'essence a haute pression |
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US8328538B2 (en) * | 2007-07-11 | 2012-12-11 | Gast Manufacturing, Inc., A Unit Of Idex Corporation | Balanced dual rocking piston pumps |
HUE026768T2 (en) * | 2007-10-12 | 2016-07-28 | Delphi Int Operations Luxembourg Sarl | Fuel Pump Improvements |
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DE102008001713A1 (de) * | 2008-05-13 | 2009-11-19 | Robert Bosch Gmbh | Radialkolbenpumpe |
US8182247B2 (en) * | 2008-05-27 | 2012-05-22 | Txam Pumps Llc | Pump with stabilization component |
US8408421B2 (en) | 2008-09-16 | 2013-04-02 | Tandem Diabetes Care, Inc. | Flow regulating stopcocks and related methods |
AU2009293019A1 (en) | 2008-09-19 | 2010-03-25 | Tandem Diabetes Care Inc. | Solute concentration measurement device and related methods |
US8758323B2 (en) | 2009-07-30 | 2014-06-24 | Tandem Diabetes Care, Inc. | Infusion pump system with disposable cartridge having pressure venting and pressure feedback |
JP5633387B2 (ja) * | 2011-01-24 | 2014-12-03 | 株式会社デンソー | 燃料供給ポンプ |
US9180242B2 (en) | 2012-05-17 | 2015-11-10 | Tandem Diabetes Care, Inc. | Methods and devices for multiple fluid transfer |
US9555186B2 (en) | 2012-06-05 | 2017-01-31 | Tandem Diabetes Care, Inc. | Infusion pump system with disposable cartridge having pressure venting and pressure feedback |
EP2711547B1 (de) * | 2012-09-24 | 2019-06-05 | Continental Automotive GmbH | Kolbenanordnung für eine hochdruckpumpe |
DE102012024924A1 (de) | 2012-12-19 | 2014-06-26 | Volkswagen Aktiengesellschaft | Vorrichtung zum Antrieb einer Kolbenpumpe |
CN103967743A (zh) * | 2013-01-29 | 2014-08-06 | 王彦彬 | 磁力式同平面多缸多级组合压缩机 |
CN103967745A (zh) * | 2013-01-30 | 2014-08-06 | 王彦彬 | 同平面多缸多级凸轮组合压缩机 |
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DE19906626A1 (de) * | 1998-10-06 | 2000-04-13 | Mannesmann Rexroth Ag | Pumpenanordnung |
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WO2002097268A1 (de) * | 2001-05-26 | 2002-12-05 | Robert Bosch Gmbh | Hochdruckpumpe für ein kraftstoffsystem einer brennkraftmaschine |
DE10213625A1 (de) | 2001-05-26 | 2002-12-05 | Bosch Gmbh Robert | Kolbenpumpe, insbesondere Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine, sowie Kraftstoffsystem und Brennkraftmaschine |
JP2003074439A (ja) * | 2001-06-19 | 2003-03-12 | Denso Corp | 燃料噴射ポンプ |
JP2004537005A (ja) * | 2001-08-08 | 2004-12-09 | シーアールティー コモンレールテクノロジーズ エージー | 高圧供給ポンプ |
DE10345406A1 (de) * | 2002-10-14 | 2004-04-22 | Crt Common Rail Technologies Ag | Hochdruckpumpe, insbesondere für ein Common-Rail-Einspritzsystem |
JP2006514195A (ja) * | 2003-02-11 | 2006-04-27 | ガンサー−ハイドロマグ アーゲー | 高圧ポンプ |
DE10330757A1 (de) * | 2003-07-07 | 2005-02-03 | Bernhard-Rudolf Frey | Exzentertriebwerk für volumetrisch wirkende Pumpen oder Motoren |
-
2003
- 2003-12-04 JP JP2004568075A patent/JP2006514195A/ja not_active Ceased
- 2003-12-04 EP EP06026525.3A patent/EP1760312B1/de not_active Expired - Lifetime
- 2003-12-04 EP EP03773421A patent/EP1592887B1/de not_active Expired - Lifetime
- 2003-12-04 CN CNB2003801096660A patent/CN100392241C/zh not_active Expired - Fee Related
- 2003-12-04 AT AT03773421T patent/ATE355460T1/de active
- 2003-12-04 WO PCT/CH2003/000802 patent/WO2004072477A1/de active IP Right Grant
- 2003-12-04 DE DE50306704T patent/DE50306704D1/de not_active Expired - Lifetime
- 2003-12-04 AU AU2003281906A patent/AU2003281906A1/en not_active Abandoned
- 2003-12-04 US US10/544,004 patent/US7108491B2/en not_active Expired - Fee Related
-
2006
- 2006-08-14 US US11/503,118 patent/US20060275164A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO2004072477A1 * |
Also Published As
Publication number | Publication date |
---|---|
US20060275164A1 (en) | 2006-12-07 |
ATE355460T1 (de) | 2006-03-15 |
CN100392241C (zh) | 2008-06-04 |
US20060062677A1 (en) | 2006-03-23 |
EP1760312A2 (de) | 2007-03-07 |
EP1760312B1 (de) | 2013-05-01 |
WO2004072477A1 (de) | 2004-08-26 |
JP2006514195A (ja) | 2006-04-27 |
EP1592887B1 (de) | 2007-02-28 |
AU2003281906A1 (en) | 2004-09-06 |
CN1748083A (zh) | 2006-03-15 |
DE50306704D1 (de) | 2007-04-12 |
EP1760312A3 (de) | 2007-09-05 |
US7108491B2 (en) | 2006-09-19 |
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