EP2511517B1 - Rail fluide haute pression - Google Patents

Rail fluide haute pression Download PDF

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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
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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
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EP12155871.2A
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German (de)
English (en)
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EP2511517A1 (fr
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
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Priority to EP12155871.2A priority Critical patent/EP2511517B1/fr
Publication of EP2511517A1 publication Critical patent/EP2511517A1/fr
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Publication of EP2511517B1 publication Critical patent/EP2511517B1/fr
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    • 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.

Claims (15)

  1. Dispositif d'amenée de fluide sous haute pression (1) pour un système de rail commun pour un grand moteur à combustion interne, comprenant une unité d'accumulateur de pression (7) pour fournir du fluide sous haute pression à une pluralité d'injecteurs de fluide (8), et l'unité d'accumulateur de pression (7) possède une surface circonférentielle extérieure (16) et est disposée avec un perçage central (11) s'étendant sensiblement le long de l'axe longitudinal (14) de l'unité d'accumulateur de pression (7) et ayant une surface circonférentielle intérieure (15) et au moins un perçage radial (13) s'étendant du perçage central (11) à la surface circonférentielle extérieure (16) de l'unité d'accumulateur de pression (7), et le perçage radial (13) possède une première paroi latérale (18) et une deuxième paroi latérale (19, moyennant quoi une largueur (22) est mesurée comme la distance entre les première et deuxième parois latérales (18, 19) du perçage radial (13) dans un plan contenant l'axe central (17) du perçage radial et agencé normalement à l'axe longitudinal (14) de l'unité d'accumulateur de pression (7), moyennant quoi la largueur (22) du perçage radial (13) est plus grande à la surface circonférentielle intérieure (15) qu'à la surface circonférentielle extérieure (16) et diminue d'une manière continue sur au moins la moitié de la distance entre la surface circonférentielle intérieure (15) et la surface circonférentielle extérieure,
    caractérisé en ce qu'une épaisseur (23) du perçage radial (13) normal à la largueur (22) dans une direction de l'axe longitudinal (14) de l'unité d'accumulateur de pression (7) à la surface circonférentielle intérieure (15) est sensiblement la même que l'épaisseur du perçage radial (13) à la surface circonférentielle extérieure (16).
  2. Dispositif d'amenée de fluide sous haute pression (1) selon la revendication 1, dans lequel la diminution continue est sensiblement linéaire.
  3. Dispositif d'amenée de fluide sous haute pression (1) selon la revendication 1 ou 2, dans lequel la largueur (22) du perçage radial (11) à la surface circonférentielle intérieure (15) représente au moins le double de la largueur du perçage radial (11) à la surface circonférentielle extérieure (16).
  4. Dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications précédentes, dans lequel le perçage central (11) possède une section transversale circulaire.
  5. Dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications précédentes, dans lequel la pression du fluide sous haute pression est dans la plage de 600 à 2000 bar.
  6. Dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications précédentes, dans lequel le perçage radial (13) présente à la surface circonférentielle extérieure (16) une épaisseur (23) d'approximativement de la même grandeur que la largueur à la surface circonférentielle extérieure (16).
  7. Dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications précédentes, dans lequel le perçage radial (13) comprend un perçage radial central (25) et au moins un autre perçage radial latéral (26, 27) et/ou moyennant quoi le trou foré du perçage radial central (25) et le perçage radial latéral (26, 27) est le même sur la surface circonférentielle extérieure (16).
  8. Dispositif d'amenée de fluide sous haute pression selon l'une quelconque des revendications précédentes, dans lequel le fluide sous haute pression est un combustible.
  9. Dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications précédentes, dans lequel le perçage radial latéral (26, 27) est incliné relativement au trou de perçage radial central (25) à la surface circonférentielle intérieure (15).
  10. Moteur à combustion interne (100), incluant un cylindre (101) dans lequel un piston (103) est agencé pour être déplaçable le long d'un axe de cylindre longitudinal (105) à et d'une position de point mort haut et d'une position de point mort bas, où dans le cylindre (101), une chambre de combustion (104) est confinée par un couvercle de cylindre (102), par une paroi de cylindre (105) du cylindre (101) et par une surface de piston (106) du piston (103), et un injecteur de combustible est prévu pour injecter le combustible dans la chambre de combustion, incluant un dispositif d'amenée de fluide sous haute pression (2) en accord avec l'une des revendications précédentes.
  11. Moteur à combustion interne (100) selon la revendication 10, dans lequel le moteur à combustion est un moteur à crosse, en particulier un grand moteur Diesel à crosse, un moteur à piston à fourreau, un moteur à combustion interne à deux temps ou à quatre temps, un moteur à combustion double apte à fonctionner soit en mode Diesel soit en Otto, ou un moteur à gaz.
  12. Procédé de fabrication d'un dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications 1 à 7 comprenant l'étape de fraisage du perçage radial (13).
  13. Procédé de fabrication d'un dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications 1 à 7 comprenant l'étape de forage du trou radial (13).
  14. Procédé de fabrication d'un dispositif d'amenée de fluide sous haute pression (1) selon la revendication 13, dans lequel le forage est exécuté en forant un trou radial central (25) et au moins un autre trou radial latéral (26, 27), où le trou de forage (28) du trou radial central (25) et du trou radial latéral (26, 27) est le même sur la surface circonférentielle extérieure (16) et est incliné relativement au trou foré radial central à la surface circonférentielle intérieure (15).
  15. Procédé de fabrication d'un dispositif d'amenée de fluide sous haute pression (1) selon l'une quelconque des revendications 12 à 14, où l'étape de fraisage ou de forage est exécutée de la surface circonférentielle extérieure (16) à la surface circonférentielle intérieure (15) de l'unité d'accumulateur de pression (7), qui contient le perçage central (13, 25).
EP12155871.2A 2011-04-15 2012-02-17 Rail fluide haute pression Not-in-force EP2511517B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12155871.2A EP2511517B1 (fr) 2011-04-15 2012-02-17 Rail fluide haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP11162593 2011-04-15
EP12155871.2A EP2511517B1 (fr) 2011-04-15 2012-02-17 Rail fluide haute pression

Publications (2)

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

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EP12155871.2A Not-in-force EP2511517B1 (fr) 2011-04-15 2012-02-17 Rail fluide haute pression

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EP (1) EP2511517B1 (fr)
JP (3) JP2012225342A (fr)
KR (2) KR20120117640A (fr)
CN (1) CN102734021B (fr)

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EP3587788B1 (fr) * 2018-06-25 2021-05-19 Delphi Technologies IP Limited Procédé de fabrication d'un rail commun
EP3587789A1 (fr) * 2018-06-28 2020-01-01 Continental Automotive GmbH Procédé de production d'une ouverture de sortie de carburant dans un rail de carburant tubulaire et rail de carburant tubulaire

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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
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
DE19948339C1 (de) * 1999-10-07 2000-12-14 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
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DK1413744T3 (da) 2002-10-23 2006-02-13 Waertsilae Nsd Schweiz Ag Tryklager til et common rail system
EP1426607A1 (fr) 2002-12-06 2004-06-09 Wärtsilä Schweiz AG Accumulateur de pression pour un système à rampe commune
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 (fr) * 2009-08-04 2016-04-13 Wärtsilä Schweiz AG Agencement de liaison
EP2299102A1 (fr) 2009-09-07 2011-03-23 OMT Officine Meccaniche Torino S.p.A. Accumulateur de combustible haute pression pour systèmes d'injection à rampe commune

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

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