EP2295786B1 - Agencement de liaison - Google Patents

Agencement de liaison Download PDF

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Publication number
EP2295786B1
EP2295786B1 EP10168213.6A EP10168213A EP2295786B1 EP 2295786 B1 EP2295786 B1 EP 2295786B1 EP 10168213 A EP10168213 A EP 10168213A EP 2295786 B1 EP2295786 B1 EP 2295786B1
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EP
European Patent Office
Prior art keywords
pressure
face
connection
accordance
fluid
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.)
Active
Application number
EP10168213.6A
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German (de)
English (en)
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EP2295786A1 (fr
Inventor
Edwin Fullagar
Gerhard Hangl
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.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
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Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP10168213.6A priority Critical patent/EP2295786B1/fr
Publication of EP2295786A1 publication Critical patent/EP2295786A1/fr
Application granted granted Critical
Publication of EP2295786B1 publication Critical patent/EP2295786B1/fr
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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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • 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
    • F02M55/004—Joints; Sealings
    • F02M55/005—Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
    • 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
    • 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
    • F02M2200/95—Fuel injection apparatus operating on particular fuels, e.g. biodiesel, ethanol, mixed fuels

Definitions

  • the invention relates to a connection arrangement with a pressure accumulator according to the preamble of the independent claim.
  • the invention further relates to a large diesel engine with such a with such a connection arrangement.
  • large diesel engines which may be configured as two-stroke or four-stroke engines, and often as drive units for ships or in stationary operation, e.g. be used to drive large generators for generating electrical energy.
  • the fuel which is transported to the injection nozzles with a pressure of up to more than 1000 bar, and on the other a hydraulic medium, commonly referred to as servo oil becomes.
  • the hydraulic medium is used for example hydraulic actuation of the exhaust valves.
  • These media are conveyed by pumps in accumulators, which are designed as pressure pipes and often extend along the entire cylinder area. From these pressure accumulators, which are also referred to as accumulators, the medium passes to the injectors or to the control or actuating devices for the hydraulic components.
  • connection between the pressure accumulators and the devices that require the medium are often based on screwed connections, in which the device is screwed directly onto the wall of the pressure accumulator, or on high pressure lines, which are pressed by a thread sealingly into a corresponding outlet bore of the pressure accumulator. Also, welded or soldered connections are known.
  • the object of the invention is to propose another, structurally simple and reliable high-pressure connection with which a pressurized fluid can be conducted from a pressure accumulator to a device. Furthermore, such a connection arrangement should be proposed. In particular, the high-pressure connection should be suitable for use in large diesel engines.
  • the active surface means the vertical projection of the respective end face onto that plane which is perpendicular to the longitudinal axis, that is to say the surface which is decisive for the force exerted by the fluid on the end face. Since the effective area for the second end surface is greater than for the first end surface, but the pressure exerted by the fluid is substantially equal on both end surfaces, a larger force acts on the second end surface by the fluid than on the first end surface by the fluid the high-pressure connection is pressed with its first end surface sealingly into the seat. Thus, a high-pressure-tight connection can be realized, which is sealed by the pressurized fluid. In principle, neither screws nor welds are necessary for this sealing function.
  • the first end surface is designed as a conical surface or truncated cone surface. With this geometry of the first end surface, a particularly good sealing effect can be achieved at the connection to the pressure accumulator.
  • the second end surface is designed as a circular surface. This is on the one hand structurally simple and maximizes the effective area of the second end face for a given diameter of the second end face.
  • the seal between the high-pressure connection and the pressure accumulator is effected mainly by the pressure of the fluid on the second end surface. Since their effective area is greater than the effective area of the first end surface, results in a force which presses the first end surface sealingly against the seat surface of the pressure accumulator.
  • the pressure accumulator is designed as a pressure tube.
  • the device is fastened laterally to the pressure accumulator with respect to the normal position of use. This makes it possible to avoid pressure surges that are in the operating state of the device occur, for example, by opening, closing or switching valves, lead to a force in the pressure tube.
  • a further advantageous measure is when a holder is provided which surrounds the pressure accumulator, wherein the high-pressure connection is attached to the holder.
  • the high-pressure connection is attached to the holder.
  • the second end surface of the high pressure connection is disposed in a bore of the device.
  • the fluid can exert a particularly good pressure on the second end surface.
  • the high-pressure connection is received without thread from the device, so that the force can be optimally transmitted from the second to the first end face.
  • the pressure accumulator is a pressure tube for hydraulic medium or fuel in a large diesel engine.
  • the invention further proposes a large diesel engine with a connection arrangement according to the invention.
  • the pressure accumulator is a pressure tube for hydraulic medium or fuel, wherein the pressure tube is supported by the device and wherein the pressure tube is fixed laterally relative to the normal position of use of the device. In this way, it is achieved that pressure surges in the device are derived in their support and do not lead to a significant force into the pressure tube.
  • a particularly relevant application in practice is when the device is a valve control unit for the hydraulic control of an exhaust valve.
  • Fig. 1 shows in a sectional view of a first embodiment of a connection arrangement according to the invention, which is provided overall with the reference numeral 10, and which includes an embodiment of the high-pressure connection, which is generally designated by the reference numeral 1.
  • the connection assembly 10 comprises a pressure accumulator 2 for a fluid and an only indicated device 3, which is operated by means of the pressurized fluid.
  • the fluid may be any gaseous or liquid medium used in pressurized working processes, such as hydraulic oil or servo oil for hydraulically actuating or controlling pistons, valves or the like, fuel for injection into the cylinder of an internal combustion engine, or water must be transported under pressure.
  • hydraulic oil or servo oil for hydraulically actuating or controlling pistons, valves or the like, fuel for injection into the cylinder of an internal combustion engine, or water must be transported under pressure.
  • the device 3 may be any device operated by means of a pressurized fluid, for example a control valve, a hydraulically operated piston, a pump, or a pressure line carrying the fluid.
  • the pressure accumulator 2 for example, tubular, in particular cylindrical, be designed as a pressure tube with a cylinder axis L, as well as the pressure accumulators, which are used today in common rail systems.
  • the pressure accumulator 2 comprises a wall 21, the inside of which has a storage space 22 for the pressurized fluid.
  • the pressure accumulator 2 comprises at least one connecting bore 23, which extends from the storage space 22 radially outwardly through the wall 21, and which opens into a seat surface 24.
  • the seat 24 is conical.
  • a plurality of connecting bores 23 are provided in the tubular pressure accumulator 2 of a common rail system, which are shown in relation to the cylinder axis L according to ( Fig. 1 ) are arranged one behind the other. Since it is sufficient for the understanding, the following explanations are limited to only one connection hole 23.
  • the high-pressure connection 1 comprises a body 11 which extends in the direction of a longitudinal axis A from a first end surface 12 to a second end surface 13.
  • the first end surface 12 is configured for sealing engagement with the seat surface 24.
  • the first end surface 12 is designed as a conical surface or as a frustoconical surface.
  • the associated cone angle of the first end face 12 can be the same size as the cone surface belonging to the seat surface 24 or-depending on the material-also somewhat smaller.
  • Fig. 1 It is understood that in the operating state, the high-pressure connection 1 is pressed with its first end face 12 in the seat surface 24, so as to create a high-pressure-tight connection between the pressure accumulator 2 and the high-pressure connection 1 , If the cone angle associated with the first seat surface 12 is undersized compared to the seat surface 24, the first end surface 12 deforms in the operating state by the prevailing pressure and adapts to the seat surface 24.
  • the first end face 12 has an inlet opening 14, through which the fluid from the storage space 22 of the pressure accumulator 2 can flow into the high-pressure connection 1. From the inlet opening 14 extends a centrally disposed passage bore 15 in the direction of the longitudinal axis A up to an outlet opening 16, which is provided in the second end face 13.
  • the second end face 13 is configured in this embodiment as a circular surface or as an annular surface.
  • the second end face 13 is designed such that it can be received by the device 3.
  • the device 3 has a cavity or bore 31 which is bounded by a wall 32, and which the second end surface 13 receives.
  • the body 11 of the high-pressure connection 1 has a groove which extends over the entire circumference, and in which a sealing element 17, for example an O-ring, inserted between the wall 32 and the body 11 seals.
  • the first and second end surfaces 12 and 13 each have an effective area. This means the effective area over which the pressure which acts on the respective end face 12, 13 can produce a force in the direction of the longitudinal axis-that is to say upward or downward as shown.
  • the active surface is thus the vertical projection of the respective end face 12, 13 on the plane which is perpendicular to the longitudinal axis A.
  • the effective area is the same size as the cross-sectional area at the in Fig. 1 indicated by the arrow W1 point.
  • the effective area is the same size as the second end face 13.
  • the effective area of the second end face 13 is greater than the effective area of the first end face 12.
  • the pressurized fluid flows from the storage space 22 of the pressure accumulator 2 through the connection bore 23 and the passage bore 15 in the part of the bore 31 of the device 3, which is located above the second end face 13 as shown. From there, the fluid may, for example, flow through a channel 33 in order to be available in the device 3.
  • the second end surface 13 is acted upon by the fluid at substantially the same pressure, which also prevails in the storage space 22. Since the second end face 13 has an effective area which is larger than the effective area of the first end face 12, in any case a result in the direction of the longitudinal axis - according to the drawing down - directed force, which presses the first end surface 12 sealingly against the seat surface 24. Thus, a sealing function caused by the pressure of the fluid can be achieved.
  • the fuel injection, the gas exchange, possibly the water injection and auxiliary system with common rail systems are operated.
  • the respective fluid for.
  • a hydraulic medium such as servo oil for actuating the exhaust valves or a working medium for controlling the injection under high pressure in a pressure accumulator promoted, which is also referred to as an accumulator.
  • the accumulators are each designed as a tube-like, closed at both ends components that extend approximately at the level of the cylinder heads along the engine.
  • the pressure can be up to 2000 bar, for example.
  • the pressure of the hydraulic medium eg servo oil
  • the pressure of the hydraulic medium can be up to 300 bar.
  • Fig. 2 shows in a partially schematic representation of those essential for the understanding of the invention parts of an embodiment of a large diesel engine according to the invention, which is provided overall with the reference numeral 100.
  • this embodiment is a slow-current, longitudinally-flushed 2-stroke large diesel engine 100 with a cross-head drive.
  • the large diesel engine 100 comprises a second exemplary embodiment of a connection arrangement 10 according to the invention, which in FIG Fig. 3 can be seen in a sectional view. The section is taken along the section line III-III in Fig. 2 ,
  • the large diesel engine 100 usually includes a plurality of cylinders 101, of which in Fig. 1 only one can be seen.
  • a piston 102 is arranged to be movable back and forth.
  • the piston 102 is connected via a piston rod 103 with a crosshead, not shown, which in turn is connected via a push rod with a crankshaft (not shown).
  • an exhaust valve 104 is provided, which is hydraulically actuated in a conventional manner. This actuation takes place via a common rail system which comprises the second exemplary embodiment of the connection arrangement 10 according to the invention.
  • the common rail system for the control of the exhaust valve 104 includes the pressure accumulator 2, which is designed as a pressure tube for the hydraulic medium.
  • the device 3 is here a valve control unit 3, which via the high-pressure connection 1 (see Fig. 3 ) is connected to the connection bore 23 of the pressure accumulator 2.
  • the second end face 13 of the high-pressure connection 1 is analogous to that in FIG Fig. 1 shown arranged in the bore 31 of the valve control unit 3. In this case, the high-pressure connection 1 is received without thread from the valve control unit.
  • the valve control unit 3 comprises an electrically piloted main control valve 35 and an electromagnetic pilot valve 36, which is controlled by a control unit 105 via a signal line 106. As soon as the pilot control valve 36 opens the main control valve 35, the hydraulic medium can flow from the pressure accumulator 2 through a pressure line 107 to the outlet valve 104 in order to open it.
  • a pump 108 is provided which conveys the hydraulic medium from a reservoir, not shown, via a line 109 into the pressure accumulator 2.
  • valve control unit 3 If only one valve control unit 3 is shown, it is understood, however, that for each cylinder 101 a respective valve control unit 3 is provided which is connected in each case via a high-pressure connection 1 to a separate connection bore 23 of the pressure accumulator 2.
  • the accumulator 2 is connected via a holder 4 with the valve control unit 3 (see also Fig. 3 ).
  • the holder 4 surrounds the pressure accumulator 2 in the manner of a pipe clamp.
  • a flange 18 is provided on the body 11, which is provided with two unthreaded holes for receiving first screws 41.
  • the first screws 41 which engage in threaded holes in the holder 4, the high-pressure connection 1 is attached to the holder 4, namely here screwed.
  • the first end surface 12 is pressed into the seat surface 24, so that already a seal between the high-pressure connection 1 and the pressure accumulator 2 takes place. As a result, at least one primary seal is achieved.
  • the second end face 13 is inserted into the bore 31, wherein the designed as an O-ring sealing member 17 between the wall 32 of the bore 31 and the body 11 of the high-pressure connection 1 seals. Then, the valve control unit 3 is mounted by means of second screws 42 to the Hält ceremonies 4 and tightened.
  • the hydraulic medium also acts on the second end face 13 of the high-pressure connection, which is located in the bore 31 of the valve control unit 3 (see also FIG Fig. 1 ) is arranged, with pressure. Since the effective area of the second end face 13 is greater than the effective area of the first end face 12, the high-pressure connection 1 is pressed with its first end face 12 sealingly into the seat surface 24 of the pressure accumulator 2.
  • connection assembly 10 comprising the pressure accumulator 2, the high-pressure connection 1, the valve control unit 3 and the holder 4 is preferably carried out only via the valve control unit 3. Since - as already mentioned - a plurality of valve control units 3 are provided supported the connection assembly 10 over several locations.
  • the valve control unit 3 is fixedly attached to the large diesel engine 100 or to a support 5 provided therefor, as shown in FIG Fig. 3 is indicated.
  • the pressure accumulator 2 is with respect to its normal position of use, which the representation in Fig. 2 and Fig. 3 corresponds, mounted on the bracket 4 laterally adjacent to the valve control unit 3.
  • the designed as a pressure tube pressure accumulator 2 has no direct support on the engine or on the motor housing, but is supported only on the valve control units 3.
  • a further advantage is that due to the holders 4, the pressure accumulator 2 no longer has to have a plane surface on its outside, which on the one hand increases the mechanical stability and on the other hand simplifies production.
  • the wall 21 of the accumulator 2 is free of holes and free of tapped holes, because both the first mounting screws 41 and the second mounting screws 42 engage in the holder 4, but not in the wall 21 of the pressure accumulator 2. This increases the mechanical stability the accumulator 2 quite considerably, which can lead to the pressure accumulator 2 can be made despite the same operating pressure with a thinner wall 21.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Quick-Acting Or Multi-Walled Pipe Joints (AREA)

Claims (9)

  1. Agencement de liaison comprenant un accumulateur de pression (2) destiné à un fluide sous pression, comprenant un dispositif (3) qui est actionné par l'intermédiaire du fluide, et un raccord haute pression (1) à travers lequel le fluide peut passer de l'accumulateur de pression (2) au dispositif (3), dans lequel l'accumulateur de pression (2) est conçu sous la forme d'un tube de pression et présente au moins un alésage de raccordement (23) qui débouche dans une surface de siège (24), dans lequel le dispositif (3) est fixe dans la position normale d'utilisation de l'accumulateur de pression (2) conçu sous la forme d'un tube de pression, sur le côté de l'accumulateur de pression (2), de sorte que l'accumulateur de pression (2) appuie uniquement contre le dispositif (3), dans lequel le raccord haute pression (1) comprend un corps (11) qui s'étend dans la direction d'un axe longitudinal (A) à partir d'une première surface d'extrémité (12) jusqu'à une seconde surface d'extrémité (13), dans lequel la première surface d'extrémité (12) est conçue pour une coopération étanche avec la surface de siège (24) et présente une ouverture d'entrée (14), et dans lequel la seconde surface d'extrémité (13) présente une ouverture de sortie (16), qui est reliée par l'intermédiaire d'un alésage traversant (15) à l'ouverture d'entrée (14), dans lequel le raccord à haute pression (1) vient en contact avec la surface de siège (24) via sa première surface d'extrémité (12), et est reçu via sa seconde surface d'extrémité (13) par une cavité du dispositif (3), de sorte que le fluide peut s'écouler depuis l'accumulateur de pression (2) à travers l'alésage traversant (15) du raccord haute pression (1) jusque dans le dispositif (3), dans lequel la seconde surface d'extrémité (13) présente une surface utile pour le fluide qui est plus grande que la surface utile de la première surface d'extrémité (12), dans lequel la première surface d'extrémité (12) est configurée sous la forme d'une surface conique ou tronconique, qui s'étend dans une direction s'éloignant de la seconde surface d'extrémité (13) avec un diamètre qui diminue progressivement.
  2. Agencement de liaison selon la revendication 1, dans lequel la seconde surface d'extrémité (13) est configurée sous la forme d'une surface circulaire.
  3. Agencement de liaison selon l'une quelconque des revendications 1 et 2, dans lequel un support (4) est prévu, qui enveloppe l'accumulateur de pression (2), dans lequel le raccord à haute pression (1) est fixé sur le support (4).
  4. Agencement de liaison selon l'une quelconque des revendications 1 à 3, dans lequel la seconde surface d'extrémité (13) du raccord haute pression (1) est disposée dans un alésage (31) du dispositif (1).
  5. Agencement de liaison selon l'une quelconque des revendications précédentes, dans lequel ledit raccord haute pression (1) est mis en prise avec le dispositif (3) sans filetage.
  6. Agencement de liaison selon l'une quelconque des revendications précédentes, dans lequel l'accumulateur de pression (2) est un tube de pression destiné à du fluide hydraulique ou du carburant dans un grand moteur Diesel (100).
  7. Grand moteur Diesel ayant un agencement de liaison selon l'une quelconque des revendications précédentes.
  8. Grand moteur Diesel selon la revendication 7, dans lequel l'accumulateur de pression (2) est un tube de pression destiné à du fluide hydraulique ou du carburant, dans lequel le tube de pression est supporté par le dispositif (3), et dans lequel le tube de pression est fixe dans la position normale d'utilisation, sur le côté du dispositif (3).
  9. Grand moteur Diesel selon la revendication 7 ou 8, dans lequel le dispositif (3) est une unité de commande de soupape pour la commande hydraulique d'une soupape d'échappement (104).
EP10168213.6A 2009-08-04 2010-07-02 Agencement de liaison Active EP2295786B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10168213.6A EP2295786B1 (fr) 2009-08-04 2010-07-02 Agencement de liaison

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP09167159 2009-08-04
EP10168213.6A EP2295786B1 (fr) 2009-08-04 2010-07-02 Agencement de liaison

Publications (2)

Publication Number Publication Date
EP2295786A1 EP2295786A1 (fr) 2011-03-16
EP2295786B1 true EP2295786B1 (fr) 2016-04-13

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Country Status (4)

Country Link
EP (1) EP2295786B1 (fr)
JP (1) JP5715354B2 (fr)
KR (1) KR101711652B1 (fr)
BR (1) BRPI1002285A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2511517B1 (fr) * 2011-04-15 2015-04-01 Wärtsilä Schweiz AG Rail fluide haute pression
RU2553917C1 (ru) * 2014-04-28 2015-06-20 Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ" Устройство для подачи жидкого топлива в форсунки дизельного двигателя

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2712458A (en) * 1950-06-05 1955-07-05 Lipson Leonard Pipe couplings
DE1295936B (de) * 1964-12-10 1969-05-22 Le Nii Khim Maschinos Rohrdichtung
JP2527268Y2 (ja) * 1990-05-11 1997-02-26 三菱重工業株式会社 内燃機関の動弁装置
JPH09133280A (ja) * 1995-11-08 1997-05-20 Kanzaki Kokyukoki Mfg Co Ltd 流体接続装置
JP3882964B2 (ja) * 1996-11-30 2007-02-21 臼井国際産業株式会社 コモンレールにおける分岐接続体の接続構造
DE19936535A1 (de) * 1999-08-03 2001-02-15 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
JP4212752B2 (ja) * 2000-02-18 2009-01-21 株式会社オティックス コモンレール
JP2003148283A (ja) * 2001-11-06 2003-05-21 Denso Corp 弁装置およびそれを用いた燃料噴射装置
DE10161438B4 (de) * 2001-12-14 2004-07-15 Man B&W Diesel A/S Hubkolbenmaschine
JP4075838B2 (ja) * 2003-06-27 2008-04-16 株式会社デンソー 配管継手装置
EP1752655B1 (fr) * 2005-07-08 2007-09-05 C.R.F. Società Consortile per Azioni Arrangement de connection entre un rail commun pour carburant sous pression et au moins un injecteur, pour moteur à combustion interne.
JP2007056816A (ja) * 2005-08-26 2007-03-08 Usui Kokusai Sangyo Kaisha Ltd 分岐接続管の接続構造

Also Published As

Publication number Publication date
JP5715354B2 (ja) 2015-05-07
EP2295786A1 (fr) 2011-03-16
JP2011033190A (ja) 2011-02-17
KR101711652B1 (ko) 2017-03-02
CN101988451A (zh) 2011-03-23
BRPI1002285A2 (pt) 2012-06-05
KR20110014111A (ko) 2011-02-10

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