EP3023628B1 - Soupape de limitation de débit de carburant pour moteurs à combustion interne de grande taille - Google Patents

Soupape de limitation de débit de carburant pour moteurs à combustion interne de grande taille Download PDF

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Publication number
EP3023628B1
EP3023628B1 EP15192931.2A EP15192931A EP3023628B1 EP 3023628 B1 EP3023628 B1 EP 3023628B1 EP 15192931 A EP15192931 A EP 15192931A EP 3023628 B1 EP3023628 B1 EP 3023628B1
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EP
European Patent Office
Prior art keywords
valve
piston
flow limiting
housing
valve seat
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
EP15192931.2A
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German (de)
English (en)
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EP3023628B8 (fr
EP3023628A1 (fr
Inventor
Carlo Cocito
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.)
Omt Officine Meccaniche Torino SpA
Original Assignee
OMT Officine Meccaniche Torino SpA
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Publication of EP3023628A1 publication Critical patent/EP3023628A1/fr
Publication of EP3023628B1 publication Critical patent/EP3023628B1/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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0054—Check valves
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the present invention relates to a fuel flow limiting valve for large internal combustion engines.
  • valve according to the present invention is intended in particular to be used for large marine engines with common rail fuel injection systems.
  • Common rail fuel injection systems have resulted in greater flexibility in the control of internal combustion engines since they enable the selection of the pressure and of the timing of injection, irrespective of the engine speed and the design of the fuel cams, and the modulation of the injection flow by means of multiple injections.
  • the injectors are continuously connected to the high pressure fuel accumulator, so that the injection can be performed when requested by the injection control unit. It follows that if an injector were to remain locked in the open position due to a malfunction, all the fuel present in the high pressure accumulator would be discharged into the cylinder, with catastrophic consequences for the engine.
  • a first example of a fuel flow limiting valve for common rail injection systems is described in US3780716 .
  • This document describes a fuel flow limiting valve having an inlet connected to a fuel accumulator and an outlet connected to an injector.
  • the limiting valve comprises a housing and a piston movable within a valve chamber in a rectilinear direction.
  • a helical spring in compression pushes the piston towards the inlet channel of the fuel flow.
  • the injector opens, the pressure at the outlet of the valve decreases, and the piston starts to move towards the outlet channel.
  • the pressure drop between the upstream and downstream chambers of the piston is such so that it balances, in each position and instant, the spring force and the inertia of the piston itself.
  • the injectors are provided with a circulation valve which opens a passage towards the fuel tank when the fuel is maintained at a low pressure, and closes this passage when the pressure is increased. In this way, both the circulation at low pressure and the normal operation at high pressure are possible. If the valve seat of the injector is not in a perfect condition due to wear of the components, the fuel can flow out through the seat of the injector and reach the cylinder during circulation at low pressure. As large marine engines may remain in circulation mode for several days, this loss could cause serious problems because of serious damage which could occur when restarting the engine with a cylinder full of fuel.
  • This function can be integrated into the flow limiting valve by adding a second valve seat to the inlet fluid channel and which cooperates with a corresponding sealing element formed on the piston of the flow limiting valve. In this way, an important safety function is added without requiring an additional component.
  • EP2423498 A particular embodiment of this concept is described in EP2423498 .
  • This document describes a pressure limiting valve comprising a valve housing having a cylindrical surface which surrounds a valve chamber, an inlet channel with an inlet valve seat, and an outlet channel with an outlet valve seat.
  • a valve piston having a cylindrical wall is housed, which is guided in a longitudinal direction by the inner cylindrical surface of the valve housing.
  • the valve piston carries a closing element in pin-form, elongated in the longitudinal direction and having sealing surfaces at its opposite ends, which cooperate with the inlet valve seat and the outlet valve seat, respectively.
  • the present invention has the object of providing a fuel flow limiting valve which overcomes the limits of the prior art.
  • the present invention aims to reduce production costs, increase the reliability of operation and decrease the pressure drop required to accelerate the piston, thereby improving the dynamic behavior of the fuel flow limiting valve.
  • Figures 1 and 2 are axial cross-sections of a fuel flow limiting valve according to the present invention in a first and a second working position.
  • 10 indicates a fuel flow limiting valve intended to be used in common rail injection systems for large internal combustion engines.
  • the fuel flow limiting valve 10 comprises a valve housing 12 in which a valve chamber 14 is defined.
  • the valve housing 12 is formed by a first housing body 16 and a second housing body 18 fixed to each other.
  • the first housing body 16 comprises a bottom wall 20 and a side wall 22 extending from said bottom wall 20 and having an inner cylindrical surface 24 surrounding a valve chamber 14.
  • the side wall 22 of the first housing body 16 has an open end portion 26 in which the second housing body 18 is inserted and fixed.
  • an inlet channel 28 is formed, which communicates with the valve chamber 14.
  • the inner end of the inlet channel 28 has an inlet valve seat 30.
  • the inlet valve seat is formed by a concave conical surface.
  • the second housing body 18 comprises, in a unitary body, a base 32 and a pin formation 34, which extends within the valve chamber 14 along a longitudinal axis A.
  • the base 32 of the second housing body 18 is sealingly fixed to the open end portion 26 of the first housing body 16.
  • the pin formation 34 protrudes from an inner surface 36 of the base 32.
  • An outlet channel 38 is formed within the pin formation 34, which communicates with the valve chamber 14.
  • An outlet valve seat 40 is formed at the inner distal end of the pin formation 34.
  • the outlet valve seat 40 is a convex surface with a spherical shape.
  • the valve 10 comprises a valve piston 42 housed within the valve chamber 14 and movable in the longitudinal direction A.
  • the valve piston 42 is formed by a unitary body having a base wall 44 and a cylindrical wall 46.
  • the cylindrical wall 46 has an outer cylindrical surface 48, which is in guiding contact with the inner cylindrical surface 24 of the first housing body 16.
  • the base wall 44 of the valve piston 42 has an integral protrusion 50 located on the side facing the bottom wall 20 of the first housing body 16.
  • the integral protrusion 50 has a first sealing surface 52 formed by a convex surface which is designed to seal the inlet valve seat 30.
  • the base wall 44 has a second sealing surface 54 located at the side facing the base 32 of the second housing body 18.
  • the second sealing surface 54 is formed by a concave conical surface recessed in the base wall 20 and is intended to seal the outlet valve seat 40.
  • the first sealing surface 52 and the second sealing surface 54 are machined directly onto the base wall 44 of the valve piston 42.
  • the machining of the sealing surfaces 52, 54 can be carried out on the same machine that performs the machining of the outer cylindrical surface 48 of the valve piston 42 so as to ensure the concentricity of the sealing surfaces 52, 54 with respect to the outer cylindrical surface 48, necessary to seal the respective valve seats 30, 40.
  • the valve piston 42 comprises a calibrated fluid passage which connects together the two parts of the valve chamber 14 located on opposite sides of the valve piston 42.
  • the calibrated passage is formed by calibrated holes 56 formed in the base wall 44 of the valve piston 42.
  • a helical spring in compression 58 is arranged coaxially outside of the pin formation 34.
  • a first end of the spring 58 rests against the inner surface 36 of the second housing body 18 and a second end of the spring 58 rests against the base wall 44 of the valve piston 42.
  • the helical spring 58 is located internally with respect to the cylindrical wall 46 of the valve piston 42. The helical spring 58 tends to push the valve piston 42 towards the bottom wall 20 of the first housing body 16.
  • the inlet channel 28 is connected to the accumulator of a common rail injection system and the outlet channel 38 is connected to an electronically-controlled injector.
  • the valve piston 42 When the injector is closed, the valve piston 42 is located in the position illustrated in Figure 1 . In this position, the first sealing surface 52 sealingly closes the inlet valve seat 30 and prevents the entry of fluid into the valve chamber 14.
  • the injector opens, the pressure in the valve chamber 14 decreases and the valve piston 42 starts to move towards the outlet valve seat 40.
  • the injection is interrupted before the valve piston 42 reaches the outlet valve seat 40. Therefore, the pressure levels in the valve chamber 14 upstream and downstream of the valve piston 42 reach values that allow the spring 58 to return the valve piston 42 to the closed position of the inlet valve seat 30.
  • the valve piston 42 must return back to the closed position of the inlet valve seat 30 before performing the subsequent injection.
  • the closing speed is determined by the designer with an appropriate choice of the spring force and the sizes of the calibrated holes 56.
  • valve piston 42 When the injection duration becomes excessively long, the valve piston 42 reaches the position illustrated in Figure 2 . In this position, the second sealing surface 54 of the valve piston 42 sealingly closes the outlet valve seat 40. In this way, the injection is interrupted and prevents further discharge of fuel from the high pressure accumulator. The respective cylinder of the engine remains deactivated, but over-fueling and stopping of the engine is prevented due to a lack of injection pressure.
  • the maximum volume of fuel injection depends on the volume of the valve chamber 14 downstream of the valve piston 42 and on the flow passing through the calibrated holes 56 during the movement of the valve piston 42 towards the outlet valve seat 40.
  • each of the three main components of the valve (the first housing body 16, the second housing body 18 and the valve piston 42) is constituted by a single metallic piece.
  • the machining of the sealing surfaces and the guide surfaces can be carried out in a simple and rapid manner because the geometry of the components does not envisage areas located in difficult-to-reach positions to be machined with the tool.
  • the total mass of the moving parts (or rather only the valve piston 42) is reduced by 20% compared to an execution according to EP2423498 .
  • the reduction of the inertia force and the pressure drop between the upstream and downstream chambers of the piston 42 in the acceleration step is therefore considerable. This enables higher pressure injections during the opening step of the injector.

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

Claims (5)

  1. Vanne de régulation de débit de carburant pour moteurs à combustion interne de grande taille, comprenant :
    - un boîtier de vanne (12) incluant une surface cylindrique intérieure (24) entourant une chambre de vanne (14), une conduite d'admission (28) avec un siège de vanne d'admission (30), une conduite de refoulement (38) avec un siège de vanne de refoulement (40),
    - un piston de vanne (42) logé dans ladite chambre de vanne (14) et doté d'une paroi de base (44) et d'une paroi cylindrique (46) qui est orientée dans une direction longitudinale (A) depuis ladite surface cylindrique intérieure (24) du boîtier de vanne (12), le piston de vanne (42) étant doté d'une première surface d'étanchéité (52) coopérant avec le siège de vanne d'admission (30) et d'une seconde surface d'étanchéité (54) coopérant avec le siège de vanne de refoulement (40), le piston de vanne (42) pouvant être déplacé dans ladite direction longitudinale (A) entre une première position dans laquelle la première surface d'étanchéité (52) ferme le siège de vanne d'admission (30) et une seconde position dans laquelle la seconde surface d'étanchéité (54) ferme le siège de vanne de refoulement (40), et
    - un élément élastique (58) agencé entre le boîtier (12) et le piston de vanne (42), et tendant à pousser le piston de vanne (42) vers ladite première position,
    caractérisé en ce que les première et seconde surfaces d'étanchéité (52, 54) sont directement usinées sur ladite paroi de base (44) du piston de vanne (42), et en ce que le boîtier de vanne (12) comprend une formation en broche (34) qui s'étend dans la direction longitudinale à l'intérieur de ladite chambre de vanne (14), dans laquelle ladite conduite de refoulement (38) s'étend à travers ladite formation en broche (34) et dans laquelle ledit siège de vanne de refoulement (40) est formé à une extrémité intérieure distale de ladite formation en broche (34).
  2. Vanne de régulation de débit selon la revendication 1, caractérisée en ce que le boîtier de vanne (12) comprend un premier corps de boîtier (16) incluant une paroi inférieure (20) et une paroi latérale (22) s'étendant depuis ladite paroi inférieure (20) et dotée d'une section à extrémité ouverte (26), et en ce que ladite formation en broche (34) est entièrement solidaire d'un second corps de boîtier (18) fixé de façon étanche à ladite section à extrémité ouverte (26) dudit premier corps de boîtier (16).
  3. Vanne de régulation de débit selon la revendication 2, caractérisée en ce que ledit élément élastique (58) est un ressort de compression hélicoïdal agencé à l'extérieur de ladite formation en broche (34) et à l'intérieur de ladite paroi cylindrique (46) du piston de vanne (42).
  4. Vanne de régulation de débit selon la revendication 1, caractérisée en ce que la première surface d'étanchéité (52) est une surface convexe formée sur une saillie solidaire (50) de la paroi de base (44) du piston de vanne (42).
  5. Vanne de régulation de débit selon la revendication 1, caractérisée en ce que la seconde surface d'étanchéité (54) est une surface concave enfoncée dans la paroi de base (44) du piston de vanne (42).
EP15192931.2A 2014-11-21 2015-11-04 Soupape de limitation de débit de carburant pour moteurs à combustion interne de grande taille Active EP3023628B8 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITTO20140961 2014-11-21

Publications (3)

Publication Number Publication Date
EP3023628A1 EP3023628A1 (fr) 2016-05-25
EP3023628B1 true EP3023628B1 (fr) 2017-03-08
EP3023628B8 EP3023628B8 (fr) 2017-04-19

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Application Number Title Priority Date Filing Date
EP15192931.2A Active EP3023628B8 (fr) 2014-11-21 2015-11-04 Soupape de limitation de débit de carburant pour moteurs à combustion interne de grande taille

Country Status (4)

Country Link
EP (1) EP3023628B8 (fr)
KR (1) KR101800936B1 (fr)
CN (1) CN105626341B (fr)
DK (1) DK3023628T3 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10883458B2 (en) * 2017-07-03 2021-01-05 Vitesco Technologies USA, LLC. Asymmetric spring valve disk
CN107366597B (zh) * 2017-09-15 2019-12-10 河南柴油机重工有限责任公司 一种电控高压共轨系统在船用高速大功率柴油机的布置结构

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES177456Y (es) 1971-02-19 1973-03-01 C. A. V. Limited Disposicion de inyeccion de combustible.
DE4344190A1 (de) * 1993-12-23 1995-06-29 Orange Gmbh Kraftstoffeinspritzvorrichtung mit Hochdruck-Kraftstoffspeicher
JP3521811B2 (ja) 1999-08-05 2004-04-26 株式会社デンソー 内燃機関の安全装置
FI114501B (fi) * 2001-06-27 2004-10-29 Waertsilae Finland Oy Polttoainejärjestelmän virtausrajoitinventtiili
JP3903944B2 (ja) * 2002-06-24 2007-04-11 株式会社デンソー 安全装置およびその製造方法
US7481204B2 (en) * 2007-06-26 2009-01-27 Deere & Company Internal combustion engine flow regulating valve
DK2423498T3 (da) * 2010-08-26 2013-12-09 Waertsilae Nsd Schweiz Ag Passiv mængdebegrænsningsventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3023628B8 (fr) 2017-04-19
KR101800936B1 (ko) 2017-11-23
EP3023628A1 (fr) 2016-05-25
CN105626341B (zh) 2018-12-14
CN105626341A (zh) 2016-06-01
KR20160061252A (ko) 2016-05-31
DK3023628T3 (en) 2017-05-01

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