WO1997003280A1 - Moteur a combustion interne dote d'un anneau de grattage du depot charbonneux dans un cylindre - Google Patents

Moteur a combustion interne dote d'un anneau de grattage du depot charbonneux dans un cylindre Download PDF

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Publication number
WO1997003280A1
WO1997003280A1 PCT/DK1996/000295 DK9600295W WO9703280A1 WO 1997003280 A1 WO1997003280 A1 WO 1997003280A1 DK 9600295 W DK9600295 W DK 9600295W WO 9703280 A1 WO9703280 A1 WO 9703280A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
cylinder
ring
scraping ring
coke scraping
Prior art date
Application number
PCT/DK1996/000295
Other languages
English (en)
Inventor
Ole Grundtmann
Original Assignee
Man B & W Diesel A/S
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 Man B & W Diesel A/S filed Critical Man B & W Diesel A/S
Priority to KR1019970706066A priority Critical patent/KR100291822B1/ko
Priority to DE69601375T priority patent/DE69601375T2/de
Priority to JP50542397A priority patent/JP3202243B2/ja
Priority to PL96322366A priority patent/PL179372B1/pl
Priority to EP96922776A priority patent/EP0837982B1/fr
Publication of WO1997003280A1 publication Critical patent/WO1997003280A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/18—Other cylinders
    • F02F1/22—Other cylinders characterised by having ports in cylinder wall for scavenging or charging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B77/00—Component parts, details or accessories, not otherwise provided for
    • F02B77/04—Cleaning of, preventing corrosion or erosion in, or preventing unwanted deposits in, combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F2001/006—Cylinders; Cylinder heads  having a ring at the inside of a liner or cylinder for preventing the deposit of carbon oil particles, e.g. oil scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines

Definitions

  • An internal combustion engine having a coke scraping ring in a cylinder.
  • the present invention relates to an internal combustion engine having a coke scraping ring in a cylinder and having a piston longitudinally displaceable in the cylinder and provided with piston rings, which slide along the substantially cylindrical inner surface of the cylinder at the displacement of the piston and create a pressure-sealing separation between the volume below the piston and the working chamber, which is located above the uppermost piston ring of the piston and is defined by the uppermost piston ring, the piston, the inner surface of the cylinder and the cylinder cover, the coke scraping ring protruding from the inner surface of the cylinder and extending annularly in an axial position so that the uppermost piston ring is positioned near the lower edge of the coke scraping ring when the piston is in its top dead centre position.
  • Such an engine having a coke scraping ring is known from four-stroke engines with both a suction valve and an exhaust valve in the cylinder cover.
  • the aim of the coke scraping ring is to scrape away coke deposits from the cylindrical uppermost piston section located above the uppermost piston ring.
  • the uppermost piston ring forms the lower limita ⁇ tion of the combustion chamber in the annular space located between the uppermost piston section above the piston ring and the inner surface of the cylinder. Therefore, part of the combustion products will pen- etrate into the annular space and be deposited on the outer surface of the uppermost piston section. Lubricat ⁇ ing oil from the inner surface of the cylinder may also sprinkle on to this outer surface.
  • the oil residues and the combustion products deposited are exposed to a strong heat influence from the combustion and, as the engine runs, will be transformed into a coherent coke layer on the outer piston surface. If a coke scraping ring is not used, the coke layer will grow in thickness until it touches the inner surface of the cylinder.
  • the coke scraping ring in the known four-stroke engine restricts the thickness of the coke layer when the piston is moved near its top dead centre position and the uppermost piston section is reciprocated past the coke scraping ring, the upper and lower annular edges of which plane away the coke touching the edges. As the scraping ring protrudes from the inner surface of the cylinder, the coke layer is prevented from attaining the thickness which results in contact between the coke layer and the inner surface of the cylinder.
  • the known engine with the coke scraping ring is a four-stroke engine and both the suction and the exhaust valves in the four-stroke engine are positioned in the cylinder cover, the other operating conditions of the engine are largely uninfluenced by the use or non-use of a coke scraping ring.
  • the scavenging of the cylinder is effected by an independent piston stroke between each working stroke, and the air supply to the combustion is made from above down through the suction valve at the subsequent downward suction stroke. Therefore, the coke scraping ring has no influence on the scavenging and charging of the cylinder.
  • a more important factor for the favourable results achieved with the coke scraping ring in the four-stroke engine is the movements of the piston itself in relation to the inner surface of the cylinder.
  • the four-stroke cycle involves a different load on the piston at every second upward stroke, and also at the downward strokes the type of load changes every second time.
  • the result is that the radial position of the piston near the top dead centre position varies all the time, so that the coke scraping ring scrapes off the coke to a greater depth than correspon- ding to its own internal diameter, whereby a clearance is automatically created between the coke-covered uppermost piston section and the coke scraping ring.
  • the object of the invention is to remedy the above disadvantages and render possible an advantageous use of a coke scraping ring in a two-stroke crosshead engine.
  • the invention is characterized in that the engine is a two-stroke crosshead engine with uniflow scavenging having scavenging air ports posi ⁇ tioned in a lower cylinder section, and that in its cylindrical inner surface the coke scraping ring is provided with several leakage grooves which extend obliquely relative to the longitudinal axis of the cylinder from the lower surface to the top surface of the coke scraping ring. It is presumed that the disadvantages demonstrated in using the known coke scraping ring in a two-stroke engine can be explained by the aid of the following mechanisms. In a two-stroke crosshead engine the piston carries out a compression stroke during each upward movement and a working stroke during each downward movement.
  • the leakage grooves in the cylindrical inner surface of the coke scraping ring reduce or eliminate the pressure build-up in the annular cavity, as the air in it can escape through the leakage grooves to the part of the working chamber located above the piston top. This avoids exposure of the uppermost piston ring to increased load owing to the presence of the coke scraping ring. This factor is of particular importance in the large two-stroke crosshead engines of today, which are being developed towards very high effective compression ratios, such as 1:16 - 1:20, which in themselves result in very large loads on the piston rings.
  • An oblique course of the leakage grooves may ensure that the coke is also scraped off in the areas opposite the leakage grooves.
  • the parts of the coke deposit opposite to the lower openings in the leakage grooves will not meet the lower edge of the coke scraping ring, but during the continued upward piston movement will pass the upper edges of the leakage grooves and be scraped off here to the desired dimension.
  • the coke particles scraped off in the grooves are passed up into the space above the piston by the leakage air blowing through the grooves.
  • the leakage grooves counteract increased fuel consumption. If there were no leakage grooves, the effective piston area would be reduced during the first part of the combustion, when the piston top is located at a level with or above the coke scraping ring, as the latter would prevent the pressure increase in the working chamber from being transmitted down to the uppermost piston ring, where the effective piston area covers the whole cross-sectional area of the cylinder.
  • the leakage grooves reduce or remove the pressure drop across the coke scraping ring both during the compression stroke and during the working stroke, and the specific fuel consumption is therefore substan- tially uninfluenced by the use or non-use of a coke scraping ring.
  • the coke scraping ring provides a further effect which is particularly advantageous in large two-stroke diesel engines having a high cylinder output, such as from 1500 to 5500 kW, where the fuel is injected into the cylinder by means of two, three or four fuel injectors emitting direction-specific mists of atomized fuel.
  • the combustion of the fuel generates relatively concentrated heat influences, but as the coke scraping ring covers the uppermost piston ring while the piston is near its top dead centre position, where the thermal load is greatest, and only passes the hot gas to the piston ring through the leakage grooves, the thermal load is distributed more evenly across the uppermost piston ring, thus also protecting the heat-sensitive lubricating oil film on the inner surface of the cylinder. Both factors contribute to better operating conditions for the piston ring pack and increase the effect of preventing the coke on the piston from touching the lubricating oil film.
  • the leakage grooves in the cylindrical inner surface of the coke scraping ring it is also possible within the scope of the invention to design the internal combustion engine mentioned in the introduction with a coke scraping ring in a cylinder in a manner characterized in that the engine is a two-stroke crosshead engine with uniflow scavenging having scavenging air ports positioned in a lower cylinder section, and that in its cylindrical outer surface the uppermost piston section located above the uppermost piston ring is provided with several leakage grooves which extend from the top of the piston section down to the area at the annular groove with the uppermost piston ring.
  • the cylindrical inner surface of the coke scraping ring can be formed as a coherent circularly cylindrical surface.
  • the substantially cylindrical inner surface of the cylinder is constituted by an upper cover section and a lower liner section, and the coke scraping ring is positioned at the top of the liner section.
  • the coke scraping ring may be a ring shrunk into a recess in the inner surface of the liner or alternatively may be a protruding part in the material of the liner itself, viz., an integral coherent part of the liner.
  • the piston with the piston rod has to be mounted before the liner is lowered into position in the engine at its assembly so that the piston is passed upwards from below through the liner.
  • the embodiment provides an advantage ⁇ ous possibility of post-mounting a coke scraping ring on already existing engines.
  • the substantially cylindrical inner surface of the cylinder is constituted by an upper cover section and a lower liner section, and the coke scraping ring is positioned at the bottom of the cover section.
  • the coke scraping ring may be a separate ring inserted in a recess in the upper cover section or be formed integrally with the cover section, the lower portion of the cover section being fine-turned to a smaller internal diameter than the section located above. If the leakage grooves are to be positioned in the coke scraping ring, they can subsequently be worked into said lowest part of the cover section.
  • the alternative embodiment is especially applicable in cylinders exposed to especially high thermal loads, where the cylinder cover is manufactured from a more heat-resistant material than the liner.
  • the leakage grooves constitute from 0.25 to 50 per cent of the axially-directed area of the coke scraping ring protruding from the substantially cylindrical inner surface of the cylinder, preferably from 5 to 40 per cent thereof, and suitably from 20 to 30 per cent thereof. If the area of the leakage grooves becomes smaller than 0.25 per cent, the pressure drops across the coke scraping ring become too large, and at a leakage area of more than 50% no further positive effects are achieved. The limit of 5 per cent still results in a pressure drop, but nevertheless a notice ⁇ able improvement of the operating conditions, while the limit of 40 per cent is normally fully satisfactory to prevent pressure drops across the coke scraping ring.
  • the scavenging air ports are preferably opened by the upper surface of the piston, which means that the coke scraping ring must not protrude too far from the inner surface of the cylinder, because the result of an excessive width of the annular space between the coke layer and the inner surface of the cylinder is that the passage by the uppermost piston ring of the upper side of the ports at the end of the working stroke will open the ports.
  • the coke scraping ring preferably protrudes at least 0.2 mm, such as from 0.5 to 5 mm from the inner surface of the cylinder.
  • the lower value of 0.2 mm, or 0.5 mm ensures complete obstruction of the scavenging air ports until the upper piston surface has passed.
  • the coke scraping ring may suitably protrude at least 1 mm, such as from 2 to 3 mm, while 0.5-2 mm may be suitable for small engines. If the ring protrudes less than 0.25 mm, it is more difficult to achieve certainty that the coke deposit does not touch the lubricating film oil on the inner surface of the cylinder.
  • the uppermost piston section located above the uppermost piston ring has a smaller diameter than the underlying piston section with the piston rings, and the internal diameter of the coke scraping ring is at least 0.5 mm, such as from 2 to 6 mm larger than the diameter of the uppermost piston section, suitably from 1 to 4 mm larger than it.
  • the coke layer may be built up to a thickness of from 0.5 to 3 mm, suitably from 0.75 to 2 mm, which provides a suitable clearance for the radial positioning of the piston in relation to the coke scraping ring, without any risk that the piston periph ⁇ ery touches the scraping ring.
  • the number of leakage grooves in the coke scraping ring or the piston depends on the desired leakage area and on the desired evening out of the thermal load on the uppermost piston ring, a larger leakage area and a more even distribution of the thermal load speaking for the use of a larger number of leakage grooves.
  • the coke scraping ring or the piston may suitably be provided with from 4 to 30 leakage grooves.
  • leakage grooves are formed in the periphery of the uppermost piston section, they may advantageously extend in parallel with the axis of the cylinder so that any broken-off pieces of coke are not immediately caught in a leakage groove with a consequent risk of clogging thereof. Otherwise, the number and size of the leakage grooves may be selected in the same manner as for the leakage grooves in the coke scraping ring, cf. the below description thereof.
  • FIG. 1 shows a simplified cross-sectional view through an engine with a coke scraping ring according to the invention
  • Fig. 2 is a partially sectional view of an enlarged section of the area around the coke scraping ring in the cylinder in the engine of Fig. 1,
  • Fig. 3 is an unfolded side view of part of the coke scraping ring
  • Fig. 4 is a top plane view of a section of the coke scraping ring
  • Fig. 5 is a perspective view of an uppermost piston section with leakage grooves in the area above the uppermost piston ring, and
  • Fig. 6 is a corresponding view of another embodi ⁇ ment of the piston with leakage grooves.
  • the engine illustrated in Fig. 1 is a large two- stroke diesel engine with uniflow scavenging and fuelled by oil, such as heavy fuel oil, the combustion of which forms residual products, which may be deposited as coke on the surfaces in the working chamber of the engine.
  • oil such as heavy fuel oil
  • the engine may generate outputs of from 2,000 to, for example, 70,000 kW.
  • Such an engine is conventionally used as a main engine of a ship or as a stationary power-generat ⁇ ing engine. In both cases it is of importance that the engine can operate for very long periods without any need for checking and overhauling of the engine compo- nents. It is desirable that the engine can be in continuous operation for more than 2 years without any overhauls, and this requires the best possible operating conditions for the cylinder elements.
  • the stationary parts of the engine comprise a bed plate 1, in which the crankshaft 2 is journalled, and an engine frame box 3 mounted on the bed plate and supporting a cylinder section 4 on its upper surface.
  • a cylinder liner 5 is clamped down against a top plate 6 in the cylinder section by means of cover studs 7 and a cylinder cover 8.
  • the cylinder liner has an upper section having a large wall thickness which, via an annular intermediate member 9, rests on the upper surface of the top plate, and an elongated lower section projecting down into the cylinder section 4.
  • the cylinder liner has a number of scavenging air ports 10, through which scavenging and charging air from a scavenging air receiver 11 flows into the cylinder, when the piston is near its bottom dead centre position.
  • An exhaust valve housing 12 with a hydrauli- cally actuatable exhaust valve is positioned centrally in the cylinder cover. When the exhaust valve is open, scavenging air from the scavenging air ports can flow up through the cylinder, and at the same time the combustion gases flow out through the exhaust valve and into an exhaust receiver 13, from where the gas flows into the exhaust pipe via a turbocharger.
  • the engine is high-pressure charged to a charging pressure of, for example, 3.5-4 bar.
  • a connecting rod 14 connects the crankshaft 2 with a crosshead 15, which by means of guide planes 16 in the engine frame box guides the lower end of a piston rod 17 in a translational reciprocal motion along the longitudinal axis of the cylinder.
  • a piston 18 is mounted at the top of the piston rod.
  • the piston has several, such as four, piston rings 19, 19' which slide along the inner surface of the cylinder liner and create a pressure-sealing separation between the working chamber 20 and the volume which is located below the piston and communicates with the cavity in the cylinder section filled with scaveng ⁇ ing air.
  • the combustion or working chamber 20 is defined by the inner surface of the cylinder cover 8, the inner surface of the cylinder liner 5, the top of the piston 18, the uppermost piston ring 19' and the periphery of an uppermost piston section 21 extending upwards from the uppermost piston ring.
  • the uppermost piston section 21 has a smaller diameter than the underlying part of the piston, so that between the outer surface of the uppermost piston section and the inner surface of the cylinder there is an annular space 22 in which coke will be deposited on the outer piston surface.
  • an annular coke scraping ring 23 in the cylinder protrudes from the inner surface of the cylinder and scrapes off the coke deposits on the outer surface of the uppermost piston section 21 so that these deposits can not exceed a maximum diameter corresponding to the internal diameter of the coke scraping ring.
  • the coke scraping ring has a position in the axial direction of the cylinder so that the upper piston ring 19' is less than one ring height below the coke scraping ring 23 when the piston is in its top dead centre position shown on the drawing, as this ensures that the coke layer is scraped off largely all the way down to the uppermost piston ring.
  • a substantial coke-scraping effect will, however, still be obtained even though the coke scraping ring is positioned somewhat higher up, for example 2 to 3 ring heights further up.
  • Figs. 3 and 4 show that in its inner surface, the coke scraping ring is provided with several leakage grooves 24 creating gas flow communication between the part of the annular space 22 located below the coke scraping ring and the remaining upper section of the working chamber 20.
  • the flow area of the leakage grooves is suitably adapted so that the pressure drop across the coke scraping ring becomes negligible.
  • the leakage grooves may advantageously be evenly distributed along the inner periphery of the coke scraping ring, as this results in the most uniform thermal load on the upper- most piston ring 19' .
  • the depth of the leakage grooves may correspond to the thickness of the projection of the coke scraping ring in relation to the inner surface of the cylinder.
  • the scraping ring only protrudes a small distance of at least 0.25 mm, such as 0.5 - 3 mm, from the inner surface.
  • the depth of the leakage grooves has to be smaller than the thickness of the inwardly protruding part of the coke scraping ring.
  • the leakage grooves are not deeper than from 3 to 4 mm, as the gas flows through the individual groove at larger depths may become so large that the thermal loads on the uppermost piston ring will locally become too high.
  • a very even thermal distribution may be obtained with grooves not deeper than 1.5 - 2 mm combined with a suitably large number of leakage grooves, such as 15 or more.
  • the width of the leakage grooves is selected on the basis of the number of leakage grooves, the groove depth and the desired total flow area, viz., the total axially-facing cross-sectional area of the groove ends. Groove widths of from 5 to 30 mm will be suitable in most cases, and a groove width of from 10 to 20 mm is preferred to achieve an even thermal load.
  • the leakage grooves 24 extend obliquely in relation to the longitudinal axis of the cylinder so that the upper groove end 25 is displaced in the circumferential direction in relation to the lower groove end 26. This provides the advantage that the coke layer is scraped off along the full periphery of the upper piston section 21.
  • the longitudinal axes of the leakage grooves form an angle of 45° with the longitudi- nal axis of the cylinder. It is, of course, possible to use other angles, such as from 15° to 80°.
  • the angle is adapted to the groove width so that the individual groove will not exhibit any overlap in the axial direction between the upper and lower groove ends 25 and 26.
  • the leakage grooves preferably extend in a straight line between the upper and lower groove ends, but other designs creating flow communication between the upper and lower groove ends 25 and 26 will naturally also function in practice, such as an L-shaped or otherwise non-linear course.
  • Figs. 5 and 6 show examples of embodiments in which the leakage grooves are positioned on the outer surface of the piston in the uppermost piston section.
  • the same reference numerals are used as above for elements of the same type.
  • the piston rings have been omitted from the figure.
  • a longitudi ⁇ nal section has been indicated through the innermost part of the liner 5 and the cylinder cover 8 in the area around a coke scraping ring 23', formed directly in the material of the cylinder cover, viz., as an integral and coherent part of the cover.
  • a corresponding longitudinal section through an alterna- tive design is indicated, in which the coke scraping ring 23' is manufactured directly in the material of the cylinder liner, viz., as an integral and coherent part of the liner.
  • the cover can be manufactured from a material, such as steel, which is more corrosion and heat resistant than the liner material, which is typically cast iron. The thermal influence is largest in the upper area of the cylinder, and consequently the cylinder can achieve a longer life by the cover extend ⁇ ing further downwards.
  • the coke scraping ring 23' which is either positioned on or in the liner 5 or on or in the cover 8, has a circularly cylindrical inner surface 28, which is annular and without leakage grooves.
  • the leakage grooves 24' are positioned in the uppermost section 21 of the piston and extend from a chamfer at the upper rim of the piston down to the uppermost annular groove 29 for the uppermost piston ring 19' .
  • the uppermost section 21 of the piston is of large height, and thus the piston rings are positioned further down in the cylinder when the piston is in its top dead centre point, which enables the cylinder cover to extend advantageously further down the cylinder.
  • the angle can be selected between 0° and 60° or larger, but preferably the groove along at least part of its length forms an angle of minimum 15° to prevent the upper and lower groove ends in lying one vertically above the other.
  • Fig. 6 shows an alternative embodiment of the piston, in which the leakage grooves 24'' have an upper section 24a extending in parallel with the longitudinal axis of the cylinder, and a lower section 24b extending obliquely in relation thereto.
  • the lower oblique section 24b displaces the lower groove end in the circumferen ⁇ tial direction in relation to the upper groove end so that the coke is scraped off along the full circumfer ⁇ ence.
  • the upper sections 24a of the leakage grooves do not contribute to scraping off coke and therefore do not risk becoming clogged by scraped-off coke particles.
  • the design shown of the oblique groove sections at the lower ends of the grooves is especially advantageous when the relatively large height of the uppermost section 21 of the piston is created by means of._.a separate piston top fixed to an underlying piston section with annular grooves for the piston rings.
  • the two sections of the leakage grooves can be manufactured in a simple manner as straight grooves in respective piston sections.
  • the leakage grooves can be formed correspondingly to the leakage grooves arranged in the coke scraping ring.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

Moteur à deux temps à crosse et à balayage longitudinal qui possède un anneau de grattage de dépôt charbonneux dans un cylindre et un piston (18) déplaçable longitudinalement dans ledit cylindre et doté de segments (19, 19') qui coulissent le long de la surface interne pratiquement cylindrique du cylindre lors du déplacement du piston et créent une séparation étanche par rapport à la pression entre le volume se trouvant sous le piston et la chambre de travail (20) qui est située au-dessus du segment de piston supérieur et qui est définie par le segment (19') de piston supérieur, le piston (18), la surface interne du cylindre et la culasse (8) du cylindre. L'anneau de grattage (23) de dépôt charbonneux fait saillie par rapport à la surface interne du cylindre et s'étend de manière annulaire le long de ladite surface dans une position axiale, si bien que le segment de piston supérieur est placé près du bord inférieur de l'anneau de grattage de dépôt charbonneux lorsque le piston est à son point mort haut. Dans sa surface interne cylindrique, l'anneau de grattage (23) de dépôt charbonneux possède plusieurs rainures de fuite (24) obliques par rapport à l'axe longitudinal du cylindre et qui vont de la surface inférieure à la surface supérieure dudit anneau. Dans une variante, les rainures de fuite peuvent être ménagées dans la surface externe cylindrique de la partie supérieure (21) de piston se trouvant au-dessus du segment de piston supérieur.
PCT/DK1996/000295 1995-07-07 1996-06-28 Moteur a combustion interne dote d'un anneau de grattage du depot charbonneux dans un cylindre WO1997003280A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
KR1019970706066A KR100291822B1 (ko) 1995-07-07 1996-06-28 실린더에코우크스스크레이핑링을지니는내연기관
DE69601375T DE69601375T2 (de) 1995-07-07 1996-06-28 Brennkraftmaschine mit einem koksschabring in einem zylinder
JP50542397A JP3202243B2 (ja) 1995-07-07 1996-06-28 シリンダ内にコーク掻き取りリングを有する内燃機関
PL96322366A PL179372B1 (pl) 1995-07-07 1996-06-28 Dwusuwowy silnik wodzikowy wewnetrznego spalaniaz pierscieniem zgarniajacym nagar PL PL PL
EP96922776A EP0837982B1 (fr) 1995-07-07 1996-06-28 Moteur a combustion interne dote d'un anneau de grattage du depot charbonneux dans un cylindre

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DK0804/95 1995-07-07
DK199500804A DK174074B1 (da) 1995-07-07 1995-07-07 Forbrændingsmotor med en koksskrabningsring i en cylinder

Publications (1)

Publication Number Publication Date
WO1997003280A1 true WO1997003280A1 (fr) 1997-01-30

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PCT/DK1996/000295 WO1997003280A1 (fr) 1995-07-07 1996-06-28 Moteur a combustion interne dote d'un anneau de grattage du depot charbonneux dans un cylindre

Country Status (11)

Country Link
EP (1) EP0837982B1 (fr)
JP (1) JP3202243B2 (fr)
KR (1) KR100291822B1 (fr)
CN (1) CN1080821C (fr)
DE (1) DE69601375T2 (fr)
DK (1) DK174074B1 (fr)
ES (1) ES2127645T3 (fr)
HR (1) HRP960326B1 (fr)
PL (1) PL179372B1 (fr)
RU (1) RU2153089C2 (fr)
WO (1) WO1997003280A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2763362A1 (fr) * 1997-05-13 1998-11-20 Semt Pielstick Dispositif de raclage de la tete d'un piston
EP0935061A3 (fr) * 1998-02-05 2000-04-26 Jenbacher Aktiengesellschaft Moteur stationnaire à combustion interne à gaz
EP0995890A1 (fr) * 1998-10-20 2000-04-26 Wärtsilä NSD Schweiz AG Cylindre pour un moteur à combustion interne
EP1561924A2 (fr) 2004-02-06 2005-08-10 General Motors Corporation Moteur diesel à vitesse moyenne et grand alésage ayant la cuvette de couronne de piston avec l'angle de réentrée aigu
EP1679434A1 (fr) * 2003-10-16 2006-07-12 Kabushiki Kaisha Riken Moteur a combustion interne et bague d'installation de chemise
WO2008074277A1 (fr) * 2006-12-20 2008-06-26 Mahle International Gmbh Insert pour une chemise de cylindre ou un cylindre de moteur à combustion
EP2243940A1 (fr) * 2009-04-06 2010-10-27 Wärtsilä Schweiz AG Dispositif de réduction destiné à la réduction d'une pression de gaz sur un paquet de bague de piston d'un moteur à combustion interne à piston élévateur
EP2165066B1 (fr) * 2007-06-15 2016-05-18 Federal-Mogul Corporation Piston et moteur à combustion interne et procédé de construction du piston
EP3192994A3 (fr) * 2016-01-15 2017-08-16 Caterpillar Energy Solutions GmbH Turbulateurs pour un moteur à combustion interne
CN107739623A (zh) * 2017-09-06 2018-02-27 大连亨利测控仪表工程有限公司 一种新型鹅颈管冶金焦化煤气控制装置
US11299362B2 (en) 2017-06-23 2022-04-12 Kimberly-Clark Worldwide, Inc. Tension regulating directly driven roller festoon

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KR100533489B1 (ko) * 2002-05-21 2005-12-06 맨 비 앤드 더블유 디젤 에이/에스 실린더 프레임 및 모듈식 소기공기 리시버
FI124135B (fi) * 2010-06-08 2014-03-31 Wärtsilä Finland Oy Mäntämoottorin sylinteriholkki
SE534911C2 (sv) * 2010-06-16 2012-02-14 Scania Cv Ab Arrangemang i en förbränningsmotor
EP2602453A1 (fr) * 2011-12-07 2013-06-12 Wärtsilä Schweiz AG Piston et agencement de cylindre pour un moteur à combustion interne à piston élévateur et procédé de suppression d'un dépôt depuis un piston
US9845764B2 (en) 2015-03-31 2017-12-19 Achates Power, Inc. Cylinder liner for an opposed-piston engine
EP3219970A1 (fr) * 2016-03-17 2017-09-20 Winterthur Gas & Diesel AG Cylindre pour un gros moteur diesel deux temps lave longitudinalement et gros moteur diesel
CN109869239A (zh) * 2019-04-15 2019-06-11 一汽解放汽车有限公司 一种发动机活塞

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US3476099A (en) * 1968-02-26 1969-11-04 Int Harvester Co Head,gasket,and protector assembly and method
US3489130A (en) * 1968-01-10 1970-01-13 Sealed Power Corp Piston and cylinder construction
FR2322269A1 (fr) * 1975-08-26 1977-03-25 Sulzer Ag Segment de piston de moteur a combustion interne
US4474147A (en) * 1981-12-10 1984-10-02 Mack Trucks, Inc. Combined fire ring and carbon scraping insert
US4770133A (en) * 1985-12-11 1988-09-13 M A N Nutzfahrzeuge Gmbh Cylinder liner for reciprocating-type internal combustion engines
CH672353A5 (en) * 1987-05-14 1989-11-15 Sulzer Ag Cylinder lining for IC engine - has cylinder wall shoulder, protruding into combustion chamber above top piston ring level

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DE800448C (de) * 1949-06-01 1950-11-06 Maschf Augsburg Nuernberg Ag Kolbendichtung, insbesondere fuer Brennkraftmaschinen
US3489130A (en) * 1968-01-10 1970-01-13 Sealed Power Corp Piston and cylinder construction
US3476099A (en) * 1968-02-26 1969-11-04 Int Harvester Co Head,gasket,and protector assembly and method
FR2322269A1 (fr) * 1975-08-26 1977-03-25 Sulzer Ag Segment de piston de moteur a combustion interne
US4474147A (en) * 1981-12-10 1984-10-02 Mack Trucks, Inc. Combined fire ring and carbon scraping insert
US4770133A (en) * 1985-12-11 1988-09-13 M A N Nutzfahrzeuge Gmbh Cylinder liner for reciprocating-type internal combustion engines
CH672353A5 (en) * 1987-05-14 1989-11-15 Sulzer Ag Cylinder lining for IC engine - has cylinder wall shoulder, protruding into combustion chamber above top piston ring level

Cited By (14)

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Publication number Priority date Publication date Assignee Title
FR2763362A1 (fr) * 1997-05-13 1998-11-20 Semt Pielstick Dispositif de raclage de la tete d'un piston
EP0935061A3 (fr) * 1998-02-05 2000-04-26 Jenbacher Aktiengesellschaft Moteur stationnaire à combustion interne à gaz
EP0995890A1 (fr) * 1998-10-20 2000-04-26 Wärtsilä NSD Schweiz AG Cylindre pour un moteur à combustion interne
EP1679434A4 (fr) * 2003-10-16 2009-04-29 Riken Kk Moteur a combustion interne et bague d'installation de chemise
EP1679434A1 (fr) * 2003-10-16 2006-07-12 Kabushiki Kaisha Riken Moteur a combustion interne et bague d'installation de chemise
EP1561924A2 (fr) 2004-02-06 2005-08-10 General Motors Corporation Moteur diesel à vitesse moyenne et grand alésage ayant la cuvette de couronne de piston avec l'angle de réentrée aigu
EP1561924A3 (fr) * 2004-02-06 2009-10-21 General Motors Corporation Moteur diesel à vitesse moyenne et grand alésage ayant la cuvette de couronne de piston avec l'angle de réentrée aigu
EP2282084A1 (fr) * 2004-02-06 2011-02-09 Electro-Motive Diesel, Inc. Moteur à combustion interne comprenant une chemise de cylindre avec un segment racleur intégral
WO2008074277A1 (fr) * 2006-12-20 2008-06-26 Mahle International Gmbh Insert pour une chemise de cylindre ou un cylindre de moteur à combustion
EP2165066B1 (fr) * 2007-06-15 2016-05-18 Federal-Mogul Corporation Piston et moteur à combustion interne et procédé de construction du piston
EP2243940A1 (fr) * 2009-04-06 2010-10-27 Wärtsilä Schweiz AG Dispositif de réduction destiné à la réduction d'une pression de gaz sur un paquet de bague de piston d'un moteur à combustion interne à piston élévateur
EP3192994A3 (fr) * 2016-01-15 2017-08-16 Caterpillar Energy Solutions GmbH Turbulateurs pour un moteur à combustion interne
US11299362B2 (en) 2017-06-23 2022-04-12 Kimberly-Clark Worldwide, Inc. Tension regulating directly driven roller festoon
CN107739623A (zh) * 2017-09-06 2018-02-27 大连亨利测控仪表工程有限公司 一种新型鹅颈管冶金焦化煤气控制装置

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HRP960326A2 (en) 1997-08-31
JP3202243B2 (ja) 2001-08-27
PL322366A1 (en) 1998-01-19
CN1181122A (zh) 1998-05-06
KR19980702660A (ko) 1998-08-05
DE69601375T2 (de) 1999-07-01
KR100291822B1 (ko) 2001-09-17
RU2153089C2 (ru) 2000-07-20
EP0837982B1 (fr) 1999-01-13
EP0837982A1 (fr) 1998-04-29
DK174074B1 (da) 2002-05-21
CN1080821C (zh) 2002-03-13
PL179372B1 (pl) 2000-08-31
HRP960326B1 (en) 2000-02-29
DE69601375D1 (de) 1999-02-25
ES2127645T3 (es) 1999-04-16
DK80495A (da) 1995-07-07
JPH11509288A (ja) 1999-08-17

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