EP2511517B1 - Hochdruckflüssigkeitsschiene - Google Patents

Hochdruckflüssigkeitsschiene Download PDF

Info

Publication number
EP2511517B1
EP2511517B1 EP12155871.2A EP12155871A EP2511517B1 EP 2511517 B1 EP2511517 B1 EP 2511517B1 EP 12155871 A EP12155871 A EP 12155871A EP 2511517 B1 EP2511517 B1 EP 2511517B1
Authority
EP
European Patent Office
Prior art keywords
circumferential surface
radial bore
high pressure
pressure fluid
outer circumferential
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.)
Not-in-force
Application number
EP12155871.2A
Other languages
English (en)
French (fr)
Other versions
EP2511517A1 (de
Inventor
Leif Knipström
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.)
Winterthur Gas and Diesel AG
Original Assignee
Wartsila NSD Schweiz AG
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 Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP12155871.2A priority Critical patent/EP2511517B1/de
Publication of EP2511517A1 publication Critical patent/EP2511517A1/de
Application granted granted Critical
Publication of EP2511517B1 publication Critical patent/EP2511517B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • 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
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly

Definitions

  • the invention relates to a high pressure fluid rail for storage of a high pressure fluid to be employed in particular for a piston engine.
  • a high-pressure fuel storage such as a high-pressure accumulator or a so-called common rail.
  • the fuel is fed further along separate conduits to the fuel injector of each cylinder. From the fuel injector the fuel is led to the respective combustion chamber of the cylinder at a desired moment according to the operation of the engine.
  • the fuel pressure in a high-pressure fuel storage is high, even 2000 bar, whereby the fuel accumulator is exposed to strong stresses resulting in cracks that may develop in its construction material, especially in the area of the openings in the fuel storage wall and sharp-edged cross-sectional changes thereof.
  • the strength of the walls of the fuel space is in particular limited by radial bores extending from the central bore.
  • the local stresses introduced by these radial bores can be increased by a factor of three or four.
  • the document EP 1413744 discloses a fuel storage for a piston engine, where the fuel space consists of two elongated cylindrical bores, which are arranged so as to partially overlap in cross-section thereby forming a main bore.
  • the main bore in the rail of the Wärtsilä RT-flex engines is machined with two eccentric bores resulting in a cross-section of the main bore having a peanut shape.
  • an auxiliary bore connects the fuel space to the fuel injector supply conduit.
  • the junction drilling for this auxiliary bore is located at the intersection of the two eccentric bores. Thereby the stress at the crossing between the junction drilling and the two main rail drillings is reduced, since the crossing between the bores is not directly exposed to the main force lines.
  • WO2008/145818 discloses a fuel storage having an orifice opening into the fuel space which is configured such that the stresses exerted on the fuel storage in the area of orifice are reduced. Thereby the risk of crack formation in the construction material of the fuel space body is reduced. Consequently the durability of the fuel storage is increased.
  • the document FR-A-2 756 609 discloses a connecting structure for mounting a branch connector of a bypass or a bypass connection to a common header, such as a main tubular collector on which are connected the pipes Multiple fuel manifold for a high pressure or in a manifold block of a diesel internal combustion engine.
  • the connector consists of a conical thrust seat in the outer surface of the manifold wall for each of several branch pipes.
  • the inner surfaces of the manifold holes are chamfered and rounded to avoid any sharp edges, and the conical surfaces of the hole and pipe tip have a cross-section which is circular, elliptical parabolic or hyperbolic.
  • An object of the invention is to provide a fluid space having one or more auxiliary bores which can be employed in such long, thin fluid spaces.
  • a high pressure fluid feed device for a common rail system for a large internal combustion engine comprises a pressure accumulator unit for supplying high pressure fluid to a plurality of fluid injectors.
  • the pressure accumulator unit has an outer circumferential surface and is disposed with a central bore substantially extending along the longitudinal axis of the pressure accumulator unit and an inner circumferential surface. At least one radial bore extends from the central bore to the outer circumferential surface of the pressure accumulator unit.
  • the radial bore has a width measured in a plane normal to the longitudinal axis of the pressure accumulator unit which is greater at the inner circumferential surface than at the outer circumferential surface and the width decreases continuously from the inner circumferential surface to the outer circumferential surface preferably for at least half of the distance between the inner circumferential surface and the outer circumferential surface.
  • the radial bore has a first lateral wall and a second lateral wall. The width is measured as the distance between the first and second lateral walls of the radial bore in a plane containing the central axis of the radial bore and arranged normally the longitudinal axis of the pressure accumulator unit.
  • the continuous decrease is substantially linear.
  • the first lateral wall and the second lateral wall are represented as a straight line.
  • the opening angle between the first and second lateral wall is in a range of 10 to 75 °, preferably 10 to 60° particularly preferred 10 to 45°.
  • the opening angle is constant from the inner circumferential surface to the outer circumferential surface.
  • the width of the radial bore at the inner circumferential surface is at least twice the width at the outer circumferential surface.
  • the width of the radial bore at the inner circumferential surface is measured in a projection onto a plane containing the longitudinal axis of the pressure accumulator unit when viewed in the direction of the axis of the radial bore.
  • the width is the distance from the first lateral wall to the second lateral wall.
  • the stresses acting upon the inner circumferential surface of the pressure accumulator unit in the surroundings of the radial bore can be distributed over a considerably larger surface as compared to a cylindrical bore as disclosed e.g. in EP1426607 A1 .
  • the first lateral wall extending between the inner circumferential surface and the outer circumferential surface has a constant angle of inclination, the stresses are reduced also in a particular smooth way due to the fact that no local sharp transition of the wall surface is present, such as in WO2008/145818 .
  • the central bore has a circular cross-section.
  • a central bore is particularly easy to manufacture, which means that a length of the pressure accumulator unit of a couple of meters is possible and can be manufactured at a low cost. Due to the fact that the pressure of the high pressure fluid can be in the range of 600 to 2000 bar, a central bore of circular cross-section is the most advantageous shape for pressure distribution. However it is also possible to use an oval shape or a shape such as disclosed in EP1 413 744 A1 .
  • the radial bore has a thickness of approximately the same size as the width at the outer circumferential surface.
  • the thickness of the bore is measured in a direction normal to the width.
  • the thickness is measured in the direction of the longitudinal axis of the pressure accumulator unit.
  • the high pressure fluid feed device in accordance with one of the embodiments can be used advantageously for fuel or a servo oil or water as high pressure fluid.
  • An internal combustion engine for which the pressure fluid feed is most advantageously employed includes a cylinder, in which a piston is arranged to be movable along a longitudinal cylinder axis to and fro between a top dead centre position and a bottom dead centre position.
  • a combustion chamber is confined by a cylinder cover, by a cylinder wall of the cylinder and by a piston surface of the piston.
  • a fuel injector is provided for injecting fuel into the combustion chamber and a high pressure fluid feed device in accordance with one of the preceding embodiments can be used to supply the high pressure fuel to the fuel injector.
  • the combustion engine can be configured as a crosshead engine, in particular a crosshead large diesel engine, a trunk piston engine, a two-stroke or a four-stroke internal combustion engine, a dual fuel engine being operable either in diesel or otto mode or a gas engine.
  • a method for manufacturing a high pressure fluid feed device for any of the embodiments comprises the step of milling or of drilling the radial bore. If the radial bore is drilled, the drilling is performed by drilling a central radial bore and at least a further side radial bore, whereby the drill hole of the central radial bore and the side radial bore is the same on the outer circumferential surface and is inclined with respect to the central radial bore hole at the inner circumferential surface.
  • the milling or drilling step is performed from the outer circumferential surface to the inner circumferential surface of the pressure accumulator unit, which contains the central bore. Surprisingly it is possible to perform the milling or drilling step from the outside of the pressure accumulator unit.
  • the pressure accumulator unit can be particularly advantageously configured as an elongated tube.
  • the fluid space in the interior of the central bore can be a fuel space, a servo fluid space, but also a gas space or a space used for water injection.
  • the fluid space is surrounded by the inner circumferential surface and at least one of the ends, the bore can be closed by a closure stopper.
  • At least one of the outer circumferential surfaces or inner circumferential surfaces of the body of the pressure accumulator unit can have a circular, oval shaped or also a polygonal cross-section, for example a rectangular in particular square cross section, a triagonal or hexagonal cross-section.
  • the outer circumferential surface does not need to be concentric to the inner circumferential surface.
  • the central bore can have a longitudinal axis which is not the same as the longitudinal axis of the body of the pressure accumulator unit.
  • a fuel for the injection By means of pumps, a fuel for the injection, a hydraulic fluid for e.g. actuation of a valve or a working medium for controlling e.g. a fuel injector is fed under high pressure from the fluid space to the desired use.
  • the fluid space forms a central bore in the pressure accumulator unit.
  • the pressure accumulator unit forms a common rail for supplying the high pressure fluid to a plurality of users. For this reason a plurality of radial bores can be foreseen.
  • fuel is distributed by the common rail via fuel conduits to the fuel injectors located at each cylinder.
  • the fuel injector contains a fuel injection nozzle for supplying the fuel to the combustion chamber of each cylinder.
  • Figure 1 shows a fuel feed device 1 of a diesel engine comprising several cylinders, especially a large diesel engine.
  • Large diesel engine refers here to such engines that can be used, e.g., as main or auxiliary engines in ships or in power plants for the production of electricity and/or heat.
  • Fuel is fed from a fuel tank 2 by a pump 4 along a piping 3 to a high pressure fuel storage 5.
  • the high pressure fuel storage 5 is configured as a high pressure accumulator unit 7.
  • the flow rate of the pump can be regulated by an electronic control unit 20 based on the amount of fuel required by the fuel injectors 8.
  • the electronic control unit provides the timing for the operation of the fuel injectors 8 based on engine parameters, such as load of the engine or engine speed.
  • the control unit receives input from a pressure sensor 21 mounted at the pressure accumulator unit 7.
  • the pressure sensor 21 detects the fluid pressure in the pressure accumulator unit 7. Based on the detected pressure value, the operation of the pump is controlled, e.g. by controlling the rotational speed of a pump motor 24.
  • a plurality of high-pressure pumps 4 can be provided.
  • Each of the pumps can be provided with control valves and piston members (not shown).
  • the piston members can receive their guidance from cam members of a camshaft of the engine.
  • each cam member may include several cams, and thereby, when a high-pressure pump 4 provides a certain volume flow rate per time unit into a pressure accumulator unit 7, the outer dimensions of the pump may respectively be kept smaller and accordingly, the pressure shocks provided by it to the pressure accumulator are smaller.
  • the pressure accumulator 7 unit is, in turn, connected by separate fuel injection conduits 9 to the fuel injectors 8 of the cylinders.
  • the pressure accumulator unit 7 is thus connected to two or more fuel injectors 8.
  • the fuel pressure in the pressure accumulator unit 7 is at least 600 bar, typically 1000 - 2000 bar.
  • the operation of high-pressure pumps 4 and the injection pressures to be used can be controlled in accordance with the engine load, operating speed or other parameters in a manner known as such.
  • Fig. 1 shows, in a schematic illustration a cylinder arrangement 100 according to the invention with the fuel injection device according to the invention for an internal combustion engine which is in the present example a longitudinally scavenged crosshead large diesel engine.
  • the cylinder arrangement 100 according to Fig. 1 includes a cylinder 101 in which a piston 103 is arranged to be movable along a longitudinal cylinder axis 107 to and fro between a top dead centre position and a bottom dead centre position.
  • a combustion chamber 104 is defined by a cylinder cover 102, by a cylinder wall 105 of the cylinder 101 and by a piston surface 106 of the piston 103.
  • Only one charge-cycle valve 109 being here an outlet valve is provided in a gas exchange opening 110 of the cylinder cover 102 which gas exchange opening 110 is connected via a gas feeding conduct 111 I to a not shown turbocharger assembly in a per se known manner.
  • the charge-cycle valve 109 includes a valve disk 112 cooperating in the operation state with a valve seat 113 of the gas exchange opening 110 in such a way, that in a closed position of the charge-cycle valve 109, the combustion chamber 104 is sealed with respect to the gas feeding conduct 111, wherein in an open position of the charge-cycle valve 109 combustion gases can be fed out of the combustion chamber 104 to the turbocharger assembly.
  • Fig. 2 shows a section of a pressure accumulator unit 7 taken along its longitudinal axis.
  • the pressure accumulator unit 7 comprises a body 10 with an elongated fuel space for pressurised fuel.
  • the fuel space comprises a central bore 11 of cylindrical shape. As shown in Fig. 6 , the cross-section of the central bore 11 is circular.
  • the central bore 11 extends along the longitudinal axis of the pressure accumulator unit 7. Typically, the diameter of the bore is in the range of 20 to 100 mm.
  • the body 10 comprises a feed channel (not shown in Fig. 2 ) from piping 3, which opens into the fuel space. Pressurised fuel is led into the fuel space through the feed channel from the high-pressure pump 4 along the piping 3.
  • the body 10 comprises discharge channels, which open into the fuel space, through which channels fuel is discharged from the fuel space and led along to the injection nozzles of the fuel injectors 8 (see Fig. 1 ).
  • a separate discharge channel is foreseen each injection nozzle, which is in flow connection with the pressure accumulator unit 7.
  • a radial bore 13 is foreseen for each discharge channel. The radial bore extends from the inner circumferential surface 15 central bore 11 to the outer circumferential surface 16 of the body 10.
  • Each of the radial bores 13 has a longitudinal axis 17.
  • the radial bore 13 has a width measured in a plane normal to the longitudinal axis 14 of the pressure accumulator unit 7, which is greater at the inner circumferential surface 15 than at the outer circumferential surface 16 and is decreasing continuously from the inner circumferential surface 15 to the outer circumferential surface 16 as shown in Figs 3 to 7 .
  • the radial bore has a first lateral wall 18 and a second lateral wall 19.
  • Fig. 3 shows section B-B of Fig. 2 .
  • the radial bore 13 shown in Fig. 3 is manufactured by a drilling method.
  • the drilling is performed by drilling a central radial bore 25 and at a first and a second side radial bore 26, 27.
  • the central drill hole 28 of the central radial bore 25 and the first and second side radial bore 26, 27 is the same on the outer circumferential surface 16 of the body 10.
  • the first and second side radial bores 26, 27 are inclined with respect to the central radial bore 25. Therefore the first and second side drill holes 29, 30 of the first and second side radial bores 26, 27 only partially overlap with the central radial bore 25 at the inner circumferential surface 15.
  • Fig. 4 shows view C of a radial bore manufactured by drilling, which is essentially the radial bore shown in Fig. 3 .
  • a first and a second side wall 31, 32 extend between the first and second lateral walls 18, 19. Due to the circular shape of the drill, each of the central radial bore, the first and the second side radial bore is of cylindrical shape. Due to the fact that at the level of the inner circumferential surface 15, the central radial bore, the first and the second side radial bore do not overlap completely anymore, the first and second side walls 31, 32 contain protrusions and recesses.
  • the thickness of the radial bore at the inner circumferential surface is defined as the maximal distance between the first and second side walls 31, 32, which corresponds to the diameter of one of the central radial bore, first side radial bore or second side radial bore.
  • the thickness 23 of the bore 13 at the inner circumferential surface 15 is thus substantially the same as the thickness of the bore 13 at the outer circumferential surface 16. In this embodiment, the thickness at the inner circumferential surface 15 is at no location greater than the thickness at the outer circumferential surface 16.
  • Fig. 5 shows view C of a radial bore 13 manufactured by milling.
  • the side walls 31, 32 do not have any protrusions or recesses.
  • the thickness 23 of the bore 13 corresponds to the diameter of the bore 13.
  • the thickness 23 of the bore 13 at the inner circumferential surface 15 is thus substantially the same as the thickness of the bore 13 at the outer circumferential surface 16.
  • the thickness at the inner circumferential surface 15 is at least at one location somewhat greater than the thickness at the outer circumferential surface 16.
  • the advantageous distribution of stresses can be observed also if the thickness 23 of the bore deviates from the thickness at the outer circumferential surface not more than 15 %, preferably not more than 10 % particularly preferred not more than 5 %.
  • Fig. 6 shows a sectional view of a pressure accumulator unit 7 along a plane normal to its longitudinal axis 14.
  • the width 22 of the radial bore13 is measured as the distance between the first and second lateral walls 18, 19 of the radial bore in a plane containing the central axis 17 of the radial bore 13 and arranged normally to the longitudinal axis 14 of the pressure accumulator unit 7.
  • the width is greater at the inner circumferential surface 15 than at the outer circumferential surface 16 and decreases continuously from the inner circumferential surface 15 to the outer circumferential surface 16.
  • the decrease of the width occurs progressively, it is thus substantially linear. In the section shown in Fig. 6 , the decrease is shown as a straight line.
  • Fig. 7 is a view on a radial bore from the outer circumferential surface of the pressure accumulator unit.
  • the width 22 of the radial bore 11 at the inner circumferential surface 15 is at least twice the width of the radial bore 11 at the outer circumferential surface 16.
  • a flat surface 33 may be machined on the outer circumferential surface 16.
  • a segment of the body 10 of the pressure accumulator unit 7 may be removed.
  • the outer circumferential surface 16 of the body 10 is flattened at the location of the radial bore 13.
  • the maximal thickness of the segment is not more than 30% of the distance between the inner and outer circumferential surface, preferably not more than 25% of the distance, particularly preferred not more than 15% of the distance.
  • the maximal thickness is the distance from the raw outer circumferential surface before machining to the flat surface measured in an angle of 90° from the flat surface.
  • the maximal thickness is the shortest distance between the flat surface and the parallel plane forming a tangential plane to the raw outer circumferential surface.
  • the bore may also be disposed with a recess on the outer circumferential surface 16.
  • a recess may be used to attach an adapter element for a high pressure conduit leaving the radial bore 13.
  • the recess 34 is of conical shape.
  • the recess 35 is of cylindrical shape.
  • the depth of the recess is not more than 30% of the distance between the inner and outer circumferential surface, preferably not more than 25% of the distance, particularly preferred not more than 15% of the distance if the recess is machined directly into the raw outer circumferential surface.
  • the depth of the segment removed for obtaining the flat surface 33 and the depth of the recess 34, 35 in combination should be not more than 30% of the distance between the inner circumferential surface 15 and the outer circumferential surface 16, preferably not more than 25% of the distance, particularly preferred not more than 15% of the distance.
  • Fig. 11 there is shown a section through a body 10 of a pressure accumulator unit 7.
  • the outer circumferential surface 16 does not need to be concentric to the inner circumferential surface 15.
  • the central bore 11 has a longitudinal axis 36 which does not correspond to the longitudinal axis 14 of the body 10 of the pressure accumulator unit 7.
  • the longitudinal axis 14 can be parallel to the longitudinal axis 36 as shown in Fig. 11 , however it is also possible, that the longitudinal axis 14 and the longitudinal axis 36 form a staggered arrangement, are e.g. arranged in an angle to each other
  • a section through a body 10 of a pressure accumulator 7 of a further embodiment is shown.
  • the outer circumferential surface is square-shaped.
  • the inner circumferential surface 15 is circular.
  • at least one of the outer circumferential surfaces 16 and the inner circumferential surfaces 15 can have a polygonal cross-section, e.g. triangular, rectangular or hexagonal cross-section.
  • Tensions in the basic body of a pressure reservoir of a common rail system which occur due to the high difference in pressure or through dynamic pressure fluctuations in the system can be clearly reduced in a simple manner by means of the present invention.
  • stress increases in the wall of the pressure reservoir are lowered significantly.
  • the permissible interior pressure and the band width of dynamic pressure fluctuations can be raised significantly and/or the outer dimensions of the pressure reservoir, in particular its diameter, can be reduced because, for example, the wall of the basic body can be made thinner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (15)

  1. Eine Hochdruck Zuführeinrichtung (1) für ein Common-Rail System für einen Grossdieselmotor, umfassend eine Druckspeichereinheit (7) zur Zuführung eines Hochdruck Fluids zu einer Mehrzahl von Fluid Injektoren (8), wobei die Druckspeichereinheit (7) eine äussere Umfangsfläche (16) hat und mit einer zentralen Bohrung (11) ausgestattet ist, die sich im Wesentlichen entlang der longitudinalen Achse (14) der Druckspeichereinheit (7) erstreckt und eine innere Umfangsfläche (15) und mindestens eine radiale Bohrung (13) hat, die sich von der zentralen Bohrung (11) zu der äusseren Umfangsfläche (16) der Hochdruckeinheit (7) erstreckt, und die radiale Bohrung (13) eine erste laterale Wand (16) und eine zweite laterale Wand (19) aufweist, wobei eine Breite (22) als der Abstand zwischen der ersten und der zweiten lateralen Wand (18, 19) der radialen Bohrung (13) in einer Ebene gemessen wird, die die zentrale Achse (17) der radialen Bohrung umfasst und normal zur longitudinalen Achse (14) der Druckspeichereinheit (7) angeordnet ist, wobei die Breite (22) der radialen Bohrung (13) an der inneren Umfangsfläche (15) grösser ist als an der äusseren Umfangsfläche (16) und zumindest über den halben Abstand zwischen der inneren Umfangsfläche (15) und der äusseren Umfangsfläche (16) kontinuierlich abnimmt, dadurch gekennzeichnet, dass eine Dicke (23) der radialen Bohrung (13) an der inneren Umfangsfläche (15) normal zur Breite (22) in einer Richtung zur longitudinalen Achse (14) der Druckspeichereinheit (7) im Wesentlichen die dieselbe Dicke ist wie die Dicke der radialen Bohrung (13) an der äusseren Umfangsfläche (16).
  2. Eine Hochdruck Zuführeinrichtung (1) nach Anspruch 1, wobei die kontinuierliche Abnahme im Wesentlichen linear ist.
  3. Eine Hochdruck Zuführeinrichtung (1) nach einem der Ansprüche 1 oder 2, wobei die Breite (22) der radialen Bohrung (11) an der inneren Umfangsfläche (15) mindestens zweimal der Breite der radialen Bohrung (11) an der äusseren Umfangsfläche (16) entspricht.
  4. Eine Hochdruck Zuführeinrichtung (1) nach einem der vorangehenden Ansprüche, wobei die zentrale Bohrung (11) einen kreisförmigen Querschnitt hat.
  5. Eine Hochdruckzuführeinrichtung (1) nach einem vorangehenden Ansprüche, wobei der Druck des Hochdruck Fluids im Bereich zwischen 600 bis 2000 bar liegt.
  6. Eine Hochdruck Zuführeinrichtung nach einem der vorangehenden Ansprüche, wobei die radiale Bohrung (13) an der äusseren Umfangsfläche (16) eine Dicke (23) von ungefähr derselben Grösse hat wie die Breite an der äusseren Umfangsfläche (16).
  7. Eine Hochdruck Zuführeinrichtung (1) nach einem der vorangehenden Ansprüche, wobei die radiale Bohrung (13) eine zentrale Bohrung (25) umfasst und zumindest eine weitere seitliche Bohrung (26, 27) und / oder wobei das Bohrloch der zentralen radialen Bohrung (25) und die seitliche radiale Bohrung (26, 27) in derselben äusseren Umfangsfläche (16) vorgesehen ist.
  8. Eine Hochdruck Zuführeinrichtung (1) nach einem der vorangehenden Ansprüche, wobei das Hochdruckfluid ein Treibstoff ist.
  9. Eine Hochdruck Zuführeinrichtung (1) nach einem der vorangehenden Ansprüche, wobei die seitliche radiale Bohrung (26, 27) in Bezug auf die zentrale Bohrung (25) an der inneren Umfangsfläche (15) geneigt ist.
  10. Eine Hubkolbenbrennkraftmaschine (100) umfassend einen Zylinder (101) in welchem ein Kolben (103) entlang einer longitudinalen Zylinderachse und zwischen einem oberen Totpunkt und einem unteren Totpunkt hin- und herbewegbar angeordnet ist, wobei im Zylinder (10) ein Verbrennungsraum (104) durch einen Zylinderdeckel (102), eine Zylinderwand (105) des Zylinders (101) und eine Kolbenoberfläche (106) des Kolbens (103) begrenzt ist und ein Treibstoffinjektor zum Einspritzen von Treibstoff in die Verbrennungskammer vorgesehen ist, umfassend eine Hochdruck Zuführeinrichtung (2) nach einem der vorangehenden Ansprüche.
  11. Eine Hubkolbenbrennkraftmaschine (100) nach Anspruch 10, wobei die Hubkolbenbrennkraftmaschine ein Kreuzkopfmotor ist, insbesondere ein Kreuzkopf Grrossdieselmotor, ein Tauchkolbenmotor, eine Zweitakt oder Viertakt Verbrennungsmaschine, ein Dula-Fuel Motor der entweder in einem Diesel- oder in Otto-Modus betreibbar ist, oder ein Gasmotor ist.
  12. Ein Verfahren zur Herstellung einer Hochdruck Zuführeinrichtung (1) nach einem der Ansprüche 1 bis 7 umfassend den Schritt des Fräsens der radialen Bohrung (13).
  13. Ein Verfahren zur Herstellung der Hochdruck Zuführeinrichtung (1) nach einem der Ansprüche 1 bis 7 umfassend des Schritt des Bohrens der radialen Bohrung (13).
  14. Ein Verfahren zur Herstellung einer Hochdruck Zuführeinrichtung (1) nach Anspruch 13, wobei das Bohren durch Bohren einer zentralen radialen Bohrung (25) durchgeführt wird und mindestens einer seitlichen radialen Bohrung (26, 27), wobei das Bohrloch (28) der zentralen Bohrung (25) und die seitliche Bohrung (26, 27) in derselben äusseren Umfangsfläche (16) ist und in Bezug auf das radiale Bohrloch an der inneren Umfangsfläche (15) geneigt ist.
  15. Ein Verfahren zur Herstellung einer Hochdruck Zuführeinrichtung (1) nach einem der Ansprüche 12 bis 14, wobei der Fräs- oder Bohrschritt von der äusseren Umfangfläche (16) zur inneren Umfangfläche (15) der Druckspeichereinheit (7), die die zentrale Bohrung (13, 25) enthält, vorgenommen wird.
EP12155871.2A 2011-04-15 2012-02-17 Hochdruckflüssigkeitsschiene Not-in-force EP2511517B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12155871.2A EP2511517B1 (de) 2011-04-15 2012-02-17 Hochdruckflüssigkeitsschiene

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP11162593 2011-04-15
EP12155871.2A EP2511517B1 (de) 2011-04-15 2012-02-17 Hochdruckflüssigkeitsschiene

Publications (2)

Publication Number Publication Date
EP2511517A1 EP2511517A1 (de) 2012-10-17
EP2511517B1 true EP2511517B1 (de) 2015-04-01

Family

ID=44280651

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12155871.2A Not-in-force EP2511517B1 (de) 2011-04-15 2012-02-17 Hochdruckflüssigkeitsschiene

Country Status (4)

Country Link
EP (1) EP2511517B1 (de)
JP (3) JP2012225342A (de)
KR (2) KR20120117640A (de)
CN (1) CN102734021B (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3587788B1 (de) * 2018-06-25 2021-05-19 Delphi Technologies IP Limited Verfahren zur common-rail-herstellung
EP3587789A1 (de) * 2018-06-28 2020-01-01 Continental Automotive GmbH Verfahren zur herstellung einer kraftstoffaustrittsöffnung in einer rohrförmigen kraftstoffschiene und rohrförmige kraftstoffschiene

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2756609B1 (fr) * 1996-11-30 2002-02-15 Usui Kokusai Sangyo Kk Structure de liaison pour le montage de connecteurs de derivation sur un collecteur commun
JPH10213045A (ja) * 1996-11-30 1998-08-11 Usui Internatl Ind Co Ltd コモンレールにおける分岐接続体の接続構造
DE19948339C1 (de) * 1999-10-07 2000-12-14 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE19949963A1 (de) * 1999-10-16 2001-04-26 Bosch Gmbh Robert Verfahren zum Herstellen eines Kraftstoffhochdruckspeichers
DK1413744T3 (da) 2002-10-23 2006-02-13 Waertsilae Nsd Schweiz Ag Tryklager til et common rail system
EP1426607A1 (de) 2002-12-06 2004-06-09 Wärtsilä Schweiz AG Druckspeicher für ein Common Rail System
DE10305078A1 (de) * 2003-02-07 2004-04-22 Robert Bosch Gmbh Kraftstoffhochdruckspeicher
FI120844B (fi) 2007-05-31 2010-03-31 Waertsilae Finland Oy Polttoaineen syöttöjärjestelmän polttoainevarasto
CN100557227C (zh) * 2007-11-27 2009-11-04 无锡威孚高科技股份有限公司 用于高压共轨系统的组合式轨
EP2295786B1 (de) * 2009-08-04 2016-04-13 Wärtsilä Schweiz AG Verbindungsanordnung
EP2299102A1 (de) 2009-09-07 2011-03-23 OMT Officine Meccaniche Torino S.p.A. Hochdruck-Kraftstoffspeicher für Common-Rail Kraftstoffeinspritzsystemen

Also Published As

Publication number Publication date
KR20190040167A (ko) 2019-04-17
EP2511517A1 (de) 2012-10-17
JP2012225342A (ja) 2012-11-15
CN102734021B (zh) 2015-11-04
JP2017180465A (ja) 2017-10-05
KR20120117640A (ko) 2012-10-24
KR101986067B1 (ko) 2019-06-04
JP2018173086A (ja) 2018-11-08
CN102734021A (zh) 2012-10-17
JP6664442B2 (ja) 2020-03-13

Similar Documents

Publication Publication Date Title
US6497219B2 (en) Common rail fuel injection system
CN102057154B (zh) 用于活塞发动机的燃料喷射系统
CN101595297A (zh) 具有降低的腐蚀特性的球座阀
KR20130141594A (ko) 저장 탱크에서부터 내연기관까지 연료, 바람직하게는 디젤 연료를 공급하기 위한 펌프 유닛
EP3196457A1 (de) Kraftstoffverteiler
KR101986067B1 (ko) 고압 유체 레일
CN110761926A (zh) 一种低速机整体式共轨
CN103069151B (zh) 喷嘴系统和用于将喷嘴系统安装到喷嘴保持器上的方法
CN113494402A (zh) 喷射设备部件和混合压缩的外源点火式内燃机的喷射设备
KR101948936B1 (ko) 유체 주입 장치
EP2148982B1 (de) Brennstofflagerung in einem brennstoffzufuhrsystem
EP2299102A1 (de) Hochdruck-Kraftstoffspeicher für Common-Rail Kraftstoffeinspritzsystemen
EP1015758B1 (de) Hydraulisch betätigte kraftstoffpumpe für eine brennkraftmaschine
US9677521B2 (en) Component having high-pressure bores that lead into one another
US20230272766A1 (en) Fluid distributor for an injection system and injection system for mixture-compressing, externally ignited internal combustion engines
JP5715354B2 (ja) 高圧接続部及び接続構成
CN1512056A (zh) 公用干线系统用的压力罐
EP3408529B1 (de) Wasserinjektor
US20160245445A1 (en) Dual-Wall Fitting for Fluid Communication
EP3032091B1 (de) Kraftstoffeinspritzungsanordnung
CN114846234A (zh) 用于喷射设备的流体分配器，尤其是用于混合压缩的外源点火式内燃机的燃料喷射设备的燃料分配器条
US20070040137A1 (en) High-pressure inlet for a common rail injector
GB2581156A (en) Fuel injection system and a supply rail body thereof
CN115977843A (zh) 一种压力波动可控的分体式高压共轨系统
CN105937467A (zh) 燃料分配器块

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20130417

RIC1 Information provided on ipc code assigned before grant

Ipc: F02M 55/02 20060101AFI20140902BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

INTG Intention to grant announced

Effective date: 20150202

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 719239

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150515

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602012006256

Country of ref document: DE

Effective date: 20150521

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: WINTERTHUR GAS & DIESEL AG

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20150401

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 719239

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150401

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150803

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150701

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150801

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150702

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602012006256

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150401

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

26N No opposition filed

Effective date: 20160105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160229

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160217

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160229

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160229

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20161028

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160217

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160229

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20120217

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160229

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150401

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20210222

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20210217

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602012006256

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220217