WO1998053192A1 - Chemise de cylindre pour moteur a combustion interne de type diesel - Google Patents

Chemise de cylindre pour moteur a combustion interne de type diesel Download PDF

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Publication number
WO1998053192A1
WO1998053192A1 PCT/DK1998/000184 DK9800184W WO9853192A1 WO 1998053192 A1 WO1998053192 A1 WO 1998053192A1 DK 9800184 W DK9800184 W DK 9800184W WO 9853192 A1 WO9853192 A1 WO 9853192A1
Authority
WO
WIPO (PCT)
Prior art keywords
liner
recesses
running surface
cylinder liner
piston
Prior art date
Application number
PCT/DK1998/000184
Other languages
English (en)
Inventor
Erling Bredal Andersen
Allan ØSTERGAARD
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 JP54981998A priority Critical patent/JP2001525903A/ja
Priority to GB9924986A priority patent/GB2340547B/en
Priority to AU73313/98A priority patent/AU7331398A/en
Priority to PL98337002A priority patent/PL337002A1/xx
Publication of WO1998053192A1 publication Critical patent/WO1998053192A1/fr
Priority to NO995495A priority patent/NO995495D0/no

Links

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
    • F02F1/20—Other cylinders characterised by constructional features providing for lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general
    • F16J10/02—Cylinders designed to receive moving pistons or plungers
    • F16J10/04—Running faces; Liners
    • 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

Definitions

  • the present invention relates to a cylinder liner for an internal combustion engine of the diesel type, having a running surface in the form of a substantially cylindrical inner surface, and having at least one inwardly open oil track with external supply of 'lubricating oil and with at least one recess, which is only open towards the inside of the cylinder.
  • a cylinder liner for an internal combustion engine of the diesel type having a running surface in the form of a substantially cylindrical inner surface, and having at least one inwardly open oil track with external supply of 'lubricating oil and with at least one recess, which is only open towards the inside of the cylinder.
  • a pressure build-up takes place above the piston, the scavenge air fed from the turbocharger being compressed from an initial pressure of, for example, between 3 and 4 bar to a considerably higher pressure at the top position of the piston, such as a pressure of 100- 150 bar.
  • the pressure build-up is slow, and by far the majority of the pressure increase does not occur until the piston is reaching its top position.
  • the fuel valves open and the fuel is injected into the cylinder and ignited, whereupon the cylinder pressure during combustion increases to the maximum combustion pressure, which may, for example, be between 160 and 200 bar, and at the same time the temperature in the upper part of the cylinder increases to more than 500 °C.
  • the massive pressure rise in the combustion chamber above the piston crown causes combustion gas to spread into the annular spaces between the piston ring grooves and the piston rings, where the pressure affects the back of the rings and presses them out against the running surface of the liner.
  • the high temperature during combustion also causes lower viscosity of the lubricat- ing oil film on the running surface, so that the oil film is broken more easily.
  • the risk of the oil film being broken is further increased by the relatively slow movement of the piston around its top position.
  • the sliding speed of the piston rings vis-a-vis the running surface, required for maintaining the oil film on the running surface, is thus very low.
  • the piston is pushed downwards, and by far the majority of the pressure decrease takes place in the first half of the expansion stroke, whereupon the pressure decreases relatively slowly, and just before the piston passes the scavenge air ports the pressure may typically have decreased to about the pressure of the scavenge air.
  • the pressure load in the area around the top of the cylinder is thus very heavy compared with the pressure load on the rest of the cylinder.
  • the area around the top of the liner is thus in all respects the part of the running surface exposed to the heaviest load.
  • DK 170430 describes a cylinder liner with two annular recesses in the form of grooves, which are only open towards the inside of the cylinder and which are positioned immediately above and immediately below the scavenge air ports, respectively.
  • the recesses collect part of the lubricating oil which is pushed downwards by the piston rings during the expansion stroke, and prevent seizures, which have initiated and spread in the area below the scavenge air ports by the skirt of the piston touching the cylinder liner, from spreading to the area above the recesses .
  • JP-A 62-32207 shows a cylinder liner with inlets for the supply of lubricating oil in the upper part of the liner, and with a circumferential, zigzagging oil reservoir in the form of a recess positioned in the lower third of the liner slightly above the scavenge air ports .
  • the recess is only open towards the inside of the liner and serves to improve the distribution of the lubricating oil, oil being collected and retained in the recess during the downward movement of the piston past the recess, and subsequently released again to the piston rings. Due to the zigzag shape of the recess the oil is distributed along the rings when the piston moves upwards past the oil reservoir after having passed its bottom position below the scavenge air ports. The recess thus retains lubricating oil which would otherwise be lost in the scavenge air ports .
  • the object of the invention is to design a cylinder liner in a manner so that during operation the initiation of seizures between the piston rings and an area of the running surface where the contact pressure between the piston rings and the running surface is particularly high is counteracted.
  • the cylinder liner according to the invention is characterized in that the recesses include at least a first and a second group, each having at least two recesses which have a discontinuous extent in the circumferential direction of the liner, that the recesses in the groups are located in the top 15 per cent of the length of the running surface, and that the recesses in the different groups are arranged with mutual separation in the longitudinal direction of the liner and with such a mutual arrangement in the circumferential direction of the liner that any line on the running surface parallel to the axis of the cylinder liner is intersected by at least one of the recesses .
  • the top of the running surface is located at the longitudinal position in the liner where the top piston ring has its top dead centre, and the running surface extends downwards to the bottom dead centre of the lowest piston ring.
  • the length of the running surface is thus greater than the stroke by about the height of the ring pack.
  • the location of the recesses close to the top of the running surface in the area with the heaviest load does, in fact, remove a support area for the rings and introduces discontinuous ring support, which should lead to heavier load on the rings and an increased risk of seizures, but in spite of this the wear of the rings and the liner is reduced, because the recesses intervene in the initial formation of seizures.
  • the recesses according to the invention have a further advantage known per se of serving as passive oil reservoirs and preventing occurred seizures from spreading.
  • Such distortion of the piston rings and the resulting wear thereof can be avoided according to the invention by forming the recesses with a discontinuous extent in the circumferential direction of the liner, and by arranging them with mutual separation in the longitudinal direction of the liner. When a piston ring passes some of these recesses, it is supported by the remaining running surface between the recesses.
  • Arranging the discontinuous recesses so that any line on the running surface parallel to the axis of the cylinder liner is intersected by at least one of the recesses ensures that any point at the circumference of the piston rings will pass one or more cooling recesses at each piston stroke.
  • the recesses in the groups may be formed as grooves extending in the circumferential direction of the liner, which renders possible an advantageously simple manufacture of the liner.
  • the grooves may, for example, be cut or ground into the running surface .
  • the recesses in a group are preferably located at the same longitudinal position in the liner, which further simplifies the manufacture, because fewer positionings are required during machining.
  • the recesses in each group have a total extent in the circumferential direction of the liner of maximum 80 per cent, and preferably maximum 60 per cent, of the circumference of the running surface. If the recesses in a group have a total extent in the circumferential direction of the liner of more than 80 per cent of the circumference of the running surface, the piston rings need to have an inexpediently high rigidity in order to avoid excessive distortion in the piston ring grooves. If the recesses in a group have a total extent in the circumferential direction of the liner of maximum 60 per cent of the circumference of the running surface, this will provide satisfactory support of the piston rings, while at the same time just two groups of recesses are able to cover the entire circumference of the running surface.
  • each group comprising at least five, and preferably at least eight recesses.
  • the distance between the support areas for the piston rings in the circumferential direction is not large.
  • the recesses in each group may be distributed evenly along the circumference of the running surface, thus simplifying the manufacture of the liner and minimizing the length of the piston ring sections to pass the recesses.
  • the running surface is intended for the use of piston rings of a piston, which piston rings have a predetermined minimum height, and the recesses in the groups have a height which is smaller than said minimum height of the piston rings, preferably maximum 75 per cent of this minimum height, suitably a height in the interval from 1 to 3 mm. If the height of the recesses is bigger than the minimum height of the piston rings, they will shortcircuit the seal against the running surface of at least one of the piston rings when it passes the recesses. As the recesses are located in the area with maximum pressure during both compression and combustion, the shortcircuit will have a negative impact on the efficiency of the engine.
  • the height of the recesses is maximum 75 per cent of the minimum height of the piston rings, this will effectively ensure against leakage and improve support of the piston rings.
  • a recess height between 1 and 3 mm will effectively interrupt the formation of seizures while maintaining good support of the piston rings typically with ring heights of more than 10 mm.
  • Recesses belonging to different groups may have a mutual spacing in the longitudinal direction of the liner of at least 35 mm. In this way, interference is avoided between stress concentrations in the areas around the ends of the recesses in the different groups.
  • the invention further relates to a cylinder liner for an internal combustion engine of the diesel type, having a substantially cylindrical inner surface, which may constitute the running surface for the piston rings on a piston, which piston rings have a predetermined minimum height, and having at least one inwardly open oil track with external supply of lubricating oil and at least one groove which is only open towards the inside of the cylinder, which cylinder liner is characterized in that the at least one groove extends around the entire inner surface of the liner and has a height of less than 30 per cent of the minimum height of the piston rings, that the grooves have a bigger depth in the radial direction of the liner than half their height in the longitudinal direction of the liner, and are positioned in the top 15 per cent of the length of the running surface .
  • Distortion of the piston rings in the piston ring grooves with the resulting wear of the piston rings is prevented in this embodiment by the at least one groove having a height of less than 30 per cent of the minimum height of the piston rings .
  • a piston ring is thus always supported by the running surface over an area correspon- ding to at least 70 per cent of the height of the piston ring and can, accordingly, pass the groove without becoming inexpediently distorted in the ring groove.
  • the grooves counteract the initiation of seizures.
  • a suitable life of the liner can be obtained by the grooves having a bigger depth in the radial direction of the liner than half their height in the longitudinal direction of the liner.
  • the grooves will have a depth of 0.6 mm and will not be worn down until after approximately 3.4 years of constant operation.
  • marine engines are designed for approximately two years of constant operation between every service inspection, and in that perspective the determined depth of the grooves is considered a suitable lower limit.
  • Each groove may extend along the circumference of the running surface at a constant longitudinal position in the liner. Thus, as described above, the groove is prevented from shortcircuiting the piston rings.
  • At least three grooves can be made.
  • the grooves according to this embodiment are rela- tively narrow, it may be an advantage to arrange three or more grooves close to each other in order to improve the prevention of seizures.
  • each groove may extend upwards and downwards between the ends of a cylindrical section of the running surface, the height of which section is smaller than the minimum height of the piston rings. In this way, the grooves are prevented from shortcircuiting the piston rings, while at the same time the support area of the rings is increased for the same area of grooves .
  • the recesses or the grooves may suitably have a depth of at least 2 mm in the newly- manufactured liner to ensure a long life of the liner without remachining of the recesses or the grooves in the inner surface.
  • the oil track may be located below the recesses or the grooves to prevent the supply of oil from being affected by the high pressures occurring at the top of the liner.
  • Fig. 1 shows a partial side view, partial longitudinal sectional view of a cylinder liner, in which a segment of a piston at the top dead centre is outlined,
  • Fig. 2 shows a developed segmental view of the uppermost section of the cylinder liner with recesses in the inner surface
  • Fig. 3 shows a developed segmental view corresponding to that in Fig. 2 of a second embodiment of the uppermost section of the cylinder liner with recesses in the inner surface
  • Fig. 4 shows a developed segmental view on a larger scale of a third embodiment of the uppermost section of the cylinder liner with recesses in the inner surface
  • Fig. 5 shows a developed segmental view correspon- ding to that in Fig. 2 of a fourth embodiment of the uppermost section of the cylinder liner with recesses in the inner surface
  • Fig. 6 shows an enlarged cross-sectional view of a recess in the running surface of a cylinder liner with associated piston ring and piston.
  • Fig. 1 shows a cylinder liner 1 for a large two- stroke crosshead engine.
  • the cylinder liner may be manufactured in different sizes with bores typically in the interval from 250 mm to 1000 mm, and corresponding lengths typically in the interval from 100 cm to 420 cm.
  • the liner 1 is usually made from cast iron, and it may be integral or divided into several sections, which are assembled in extension of each other. In case of a divided liner, it is also possible to make the upper section from steel coated with a suitable running layer.
  • Crosshead engines of the above type may have high effective compression ratios, such as 1:16 - 1:20, which cause heavy loads on the piston rings.
  • the liner 1 may be mounted in a known manner in an engine, not shown, by positioning an annular, downward surface 2 on the top plate in the frame box or cylinder block of the engine, whereupon a piston 3 is mounted in the cylinder liner, and a cylinder cover 4 is positioned at the top of the liner on its annular, upward surface 5 and tightened to the top plate by means of cover studs, not shown.
  • the liner 1 has a substantially cylindrical inner surface, which constitutes a running surface 6 for the piston rings 7 on the piston 3.
  • An annular row of scavenge air ports 8 is positioned in the lower section of the cylinder liner.
  • the piston 3 is movable in the longitudinal direction of the liner between a top dead centre, at which the upward surface 9 of the piston is positioned in a bore in the cylinder cover 4, and a bottom dead centre, at which the upward surface of the piston is just below the lower end of the scavenge air ports 8.
  • the running surface 6 extends from an upper edge 10 located just above the top dead centre of the uppermost piston ring, to a lower edge 11 located just below the bottom dead centre of the lowest piston ring.
  • An undulate lubricating oil track 12 may be positioned in the inner surface of the liner below the upper third of the running surface, into which lubricating oil is admitted through inlet holes 13 for lubrication of the running surface 6 at the inner surface of the liner.
  • a number of recesses are positioned in the running surface 6, which are only open towards the inside of the cylinder liner.
  • Fig. 6 shows an enlarged longitudinal sectional view of a segment of the running surface 6 and the piston 3.
  • the piston 3 has a piston ring groove 16, in which a piston ring 7 is positioned in a known manner.
  • the piston ring groove 16 is higher than the piston ring 7, and, during combustion, combustion gas spreads from above through the gap 17 into the annular space 18, present between the bottom of the ring groove 16 and the cylindrical inner surface of the piston ring. Due to the high pressure of the combustion gas, the elastic piston ring 7 is pushed in the direction indicated by the arrow out against the running surface 6, which is covered by a lubricating oil film 19, whereby the piston ring 7 seals the piston 3 vis-a-vis the running surface 6.
  • the running surface 6 is provided with a recess 14, which in the present example is formed as a sharp-edged groove, but which may also have rounded edges 20 at the transition to the running surface 6.
  • a recess 14 which in the present example is formed as a sharp-edged groove, but which may also have rounded edges 20 at the transition to the running surface 6.
  • the height of the recess 14 is considerably smaller than that of the piston ring 7, and accordingly the piston ring is well supported by the running surface 6 when passing the recess 14.
  • the height of the recess 14 is bigger than that of the piston ring 7 to allow a certain leakage of gas across one or more of the piston rings 7. If a point 22 on the outer surface of the piston ring 7 has been overheated, this point is cooled when passing the recess 14. If, contrary to expectations, welding takes place between the point 22 on the piston ring 7 and the running surface 6, such welding may be prevented from spreading by the point passing the recess 14, and any major unevenness may be smoothed out by means of one of the edges 20 of the recess.
  • Fig. 2 shows a developed segmental view of the uppermost section of the cylinder liner, in which in the embodiment shown the area a (see Fig. 1) has two groups of recesses 14 in the running surface 6. Each group constitutes a row of recesses arranged with intervals 21, in the form of grooves 14 positioned along a line perpendicular to the longitudinal axis of the liner.
  • the intervals 21 constitute a supporting surface, which carries the piston rings 7 when they pass upwards or downwards across the row of grooves, so that the rings 7 do not become distorted in the ring groove.
  • each group may suitably comprise 11 grooves, each of a length of 125 mm, and a height of 2 mm - 3 mm, and a depth of 2 mm - 3 mm.
  • the uppermost row of grooves may be located approximately from 100 to 200 mm from the uppermost edge 10 of the running surface, and the bottom row of grooves may be located about 50 mm below the uppermost row. More groups improve the seizure-preventing effect, but manufacturing costs of the liner are increased accordingly.
  • Fig. 3 shows another embodiment of the cylinder liner, according to which three groups of recesses in the form of grooves 14, 15 are positioned in the running surface 6, mutually separated in the longitudinal direction of the liner.
  • the top and bottom groups both consist of a row of spaced grooves 14 arranged along a line perpendicular to the longitudinal axis of the liner.
  • the group in the middle consists of a row of grooves inclined alternately upwards and downwards .
  • the grooves overlap slightly in the circumferential direction, so that any line on the running surface parallel to the longitudinal direction of the liner intersects one or more grooves 14, 15.
  • the cylinder liner 1 shows another embodiment of the cylinder liner 1, in which the recesses comprise three groups, each having a row of circular recesses in the form of bores 23.
  • the bores 23 are distributed evenly and are mutually displaced in the circumferential direction, and they have a suitable diameter for overlapping slightly in the circumferential direction.
  • each group may thus be interpreted as the three bores arranged obliquely below each other, as the groups are then mutually displaced in the circumferential direction.
  • a group of recesses may comprise recesses arranged at differing longitudinal positions in the liner.
  • Fig. 5 shows another embodiment of the invention, in which the recesses include five narrow circular grooves 24, which extend continuously around the entire circumference of the running surface and are located in proximity to each other. The height of the grooves is maximum 30 per cent of the minimum height of the piston rings, largely corresponding to the outline in Fig. 6.
  • the recesses allow the piston ring to pass the groove without such distortion that make the edge of the ring hit against the edge of the groove .
  • the discontinuous recesses may be located closer to each other in the circumferential direction if they have a small height.
  • the location of the recesses or the grooves in the uppermost area of the running surface exposed to the heaviest load has a disruptive effect on the mechanism which causes seizures.
  • seizures do not occur in the uppermost area, the piston rings are practically unable to cause seizures, because the ring load is smaller further down on the running surface .

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

Abstract

L'invention concerne une chemise de cylindre (1) pour moteur à combustion interne de type diesel. Cette chemise de cylindre comporte au moins une rainure de graissage ouverte vers l'intérieur et dotée d'une alimentation externe en huile de lubrification, et au moins un premier et un deuxième groupe d'évidements ouverts vers l'intérieur, chaque groupe ayant au moins deux évidements (14) de profil discontinu dans le sens circonférentiel de la chemise. Les évidements (14) des différents groupes sont situés dans les 15 % supérieurs de la longueur de la surface de roulement (6) et sont répartis sur la longueur de la chemise (1) à une certaine distance les uns des autres et avec une disposition relative dans le sens circonférentiel de la chemise (1).
PCT/DK1998/000184 1997-05-16 1998-05-11 Chemise de cylindre pour moteur a combustion interne de type diesel WO1998053192A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP54981998A JP2001525903A (ja) 1997-05-16 1998-05-11 ディーゼル型内燃エンジン用シリンダライナ
GB9924986A GB2340547B (en) 1997-05-16 1998-05-11 A cylinder liner for an internal combustion engine of the diesel type
AU73313/98A AU7331398A (en) 1997-05-16 1998-05-11 A cylinder liner for an internal combustion engine of the diesel type
PL98337002A PL337002A1 (en) 1997-05-16 1998-05-11 Cylinder liner for a diesel-type internal combustion engine
NO995495A NO995495D0 (no) 1997-05-16 1999-11-10 Sylinderforing for en forbrenningsmotor av dieseltypen

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DK199700568A DK56897A (da) 1997-05-16 1997-05-16 Cylinderforing til en forbrændingsmotor af dieseltypen
DK0568/97 1997-05-16

Publications (1)

Publication Number Publication Date
WO1998053192A1 true WO1998053192A1 (fr) 1998-11-26

Family

ID=8095018

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DK1998/000184 WO1998053192A1 (fr) 1997-05-16 1998-05-11 Chemise de cylindre pour moteur a combustion interne de type diesel

Country Status (11)

Country Link
JP (1) JP2001525903A (fr)
KR (1) KR20010012501A (fr)
CN (1) CN1102994C (fr)
AU (1) AU7331398A (fr)
DK (1) DK56897A (fr)
ES (1) ES2165292B1 (fr)
GB (1) GB2340547B (fr)
NO (1) NO995495D0 (fr)
PL (1) PL337002A1 (fr)
RU (1) RU2189479C2 (fr)
WO (1) WO1998053192A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2050946A1 (fr) 2007-10-16 2009-04-22 Wärtsilä Schweiz AG Cylindre doté de moyens de réception de lubrifiants
CN101846010A (zh) * 2009-03-27 2010-09-29 瓦特西拉瑞士股份有限公司 具有用于润滑剂分布的装置的气缸
WO2012060487A1 (fr) * 2010-11-03 2012-05-10 두산인프라코어 주식회사 Cylindre pourvu d'un profil irrégulier sur la surface d'une paroi interne
DE102015006498A1 (de) * 2015-05-22 2016-11-24 Mahle International Gmbh Zylinderbohrung für ein Zylindergehäuse eines Verbrennungsmotors sowie Anordnung aus einer derartigen Zylinderbohrung und einem Kolben
US11002216B1 (en) * 2020-02-28 2021-05-11 Caterpillar Inc. Cylinder liner and cylinder liner-piston assembly for abnormal combustion protection in an engine

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DE50104298D1 (de) * 2001-07-09 2004-12-02 Gehring Gmbh & Co Kg Werkstück mit einer tribologisch beanspruchbaren Fläche und Verfahren zur Herstellung einer solchen Fläche
DE102004002759A1 (de) * 2004-01-20 2005-08-04 Daimlerchrysler Ag Brennkraftmaschine
RU2451810C1 (ru) * 2011-01-11 2012-05-27 Федеральное государственное образовательное учреждение высшего профессионального образования "Ульяновская государственная сельскохозяйственная академия" Цилиндропоршневая группа двигателя внутреннего сгорания
DE102016222299A1 (de) * 2016-11-14 2018-05-17 Man Diesel & Turbo Se Zylinder einer Brennkraftmaschine
CN108999714B (zh) * 2018-08-10 2021-05-28 重庆理工大学 一种高性能气缸套组件及制造方法
CN112228236B (zh) * 2020-10-20 2021-11-05 江苏大学 一种内燃机缸套及其加工方法
JP2022072289A (ja) * 2020-10-29 2022-05-17 株式会社ジャパンエンジンコーポレーション シリンダライナおよび舶用内燃機関

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DK173116B1 (da) * 1996-05-07 2000-01-31 Man B & W Diesel As Cylinderforing til en forbrændingsmotor

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FR1133041A (fr) * 1955-08-17 1957-03-20 Façonnage de la surface interne des cylindres de moteurs thermiques
GB1473058A (en) * 1974-09-26 1977-05-11 Sulzer Ag Reciprocating internal combustion engines

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2050946A1 (fr) 2007-10-16 2009-04-22 Wärtsilä Schweiz AG Cylindre doté de moyens de réception de lubrifiants
CN101846010A (zh) * 2009-03-27 2010-09-29 瓦特西拉瑞士股份有限公司 具有用于润滑剂分布的装置的气缸
EP2236800A1 (fr) 2009-03-27 2010-10-06 Wärtsilä Schweiz AG Cylindre doté de moyens de distribution de lubrifiant
WO2012060487A1 (fr) * 2010-11-03 2012-05-10 두산인프라코어 주식회사 Cylindre pourvu d'un profil irrégulier sur la surface d'une paroi interne
CN103201487A (zh) * 2010-11-03 2013-07-10 斗山英维高株式会社 在内壁面形成有凹凸的气缸
US20130220113A1 (en) * 2010-11-03 2013-08-29 Doosan Infracore Co., Ltd. Cylinder formed with uneven pattern on surface of inner wall
US9341267B2 (en) 2010-11-03 2016-05-17 Doosan Infracore Co., Ltd. Cylinder formed with uneven pattern on surface of inner wall
DE102015006498A1 (de) * 2015-05-22 2016-11-24 Mahle International Gmbh Zylinderbohrung für ein Zylindergehäuse eines Verbrennungsmotors sowie Anordnung aus einer derartigen Zylinderbohrung und einem Kolben
US11022063B2 (en) 2015-05-22 2021-06-01 Mahle International Gmbh Cylinder bore for a cylinder housing of an internal combustion engine, and arrangement having a cylinder bore and a piston
US11002216B1 (en) * 2020-02-28 2021-05-11 Caterpillar Inc. Cylinder liner and cylinder liner-piston assembly for abnormal combustion protection in an engine

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GB2340547A (en) 2000-02-23
NO995495L (no) 1999-11-10
RU2189479C2 (ru) 2002-09-20
GB2340547B (en) 2001-07-04
CN1102994C (zh) 2003-03-12
DK56897A (da) 1998-11-17
KR20010012501A (ko) 2001-02-15
NO995495D0 (no) 1999-11-10
ES2165292A1 (es) 2002-03-01
AU7331398A (en) 1998-12-11
JP2001525903A (ja) 2001-12-11
CN1256740A (zh) 2000-06-14
GB9924986D0 (en) 1999-12-22
ES2165292B1 (es) 2003-03-01
PL337002A1 (en) 2000-07-31

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