EP2050946A1 - Cylindre doté de moyens de réception de lubrifiants - Google Patents

Cylindre doté de moyens de réception de lubrifiants Download PDF

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Publication number
EP2050946A1
EP2050946A1 EP08164867A EP08164867A EP2050946A1 EP 2050946 A1 EP2050946 A1 EP 2050946A1 EP 08164867 A EP08164867 A EP 08164867A EP 08164867 A EP08164867 A EP 08164867A EP 2050946 A1 EP2050946 A1 EP 2050946A1
Authority
EP
European Patent Office
Prior art keywords
slot
shaped recesses
cylinder
lubricant
sliding surface
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.)
Withdrawn
Application number
EP08164867A
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German (de)
English (en)
Inventor
Hans Sundén
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
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 Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP08164867A priority Critical patent/EP2050946A1/fr
Publication of EP2050946A1 publication Critical patent/EP2050946A1/fr
Withdrawn legal-status Critical Current

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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
    • F02F1/20—Other cylinders characterised by constructional features providing for lubrication
    • 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
    • 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

Definitions

  • the invention relates to a cylinder for a piston engine comprising means for receiving lubricant.
  • the distribution of the lubricant proves to be critical due to the large surfaces to be wetted.
  • the lubricant passes through a limited number arranged on the circumference of the cylinder feed openings in the cylinder interior. So that the liquid lubricant spreads evenly over the inner wall of the cylinder, circumferential grooves are provided, as for example in the FR1174532 to be shown.
  • the grooves especially in the most heavily loaded part of the cylinder, which extends to about 15% from the top dead center of the top piston ring starting in the direction of bottom dead center of the piston, are exposed to heavy abrasion.
  • the actual lubricant consumption is above the amount of lubricant necessary for the lubrication of the pair of pistons piston-cylinder.
  • the consumption of lubricants also represents an environmental burden. A large part of the emitted exhaust particles originates from the lubricant.
  • the task of the lubricant, especially for two-stroke engines, is not just an adequate one To ensure piston lubrication, but also to neutralize sulfuric acid, which passes through the use of sulfur-containing fuel in the combustion chamber.
  • a cylinder for a piston engine comprising means for receiving lubricant, the cylinder comprising a sliding surface for a piston, which encloses an upper dead zone and a row of scavenging slots arranged on the cylinder.
  • the upper deadband is defined as the plane in which the dead center of the uppermost piston ring is located.
  • This sliding surface has a plurality of slot-shaped recesses.
  • the slot-shaped recesses have a length, and a width and a depth, wherein the depth is greater than 0.4 mm.
  • the slot-shaped recesses are provided below an annular portion of the cylinder surface, which amounts to a length of up to 15% of the sliding surface, measured from the upper dead zone.
  • the slot-shaped recesses are provided according to an advantageous embodiment, in the region of the scavenging slots and below the same.
  • the width of the slot-shaped recesses is between 0.5 and 3 mm, but should in any case be less than 80%, preferably 70%, more preferably 60% of the width of the narrowest piston ring. This ensures that the piston ring is not in the slot-shaped Can tilt recess and slides over the recess without contact.
  • the length of the slot-shaped recesses is between 10 and 100 mm, preferably between 10 and 50 mm, particularly preferably between 10 and 30 mm.
  • a plurality of slot-shaped recesses may be arranged in a row.
  • the number of slot-shaped recesses in a row is preferably 10-150, depending on the length of the slot-shaped recess and the distance between two adjacent slot-shaped recesses.
  • the length and the distance of the slot-shaped recesses is preferably selected so that the notch effect caused by a slot-shaped recess is below the permissible weakening of the cylinder. According to a particularly advantageous embodiment, the length of the distance is greater than the length of the slot-shaped recess.
  • the row has a pitch which is preferably smaller than the pitch corresponding to the height of the piston ring. Therefore, the inclination angle of the slot-shaped recesses of a row is up to 1 °. This measure also serves to increase the smoothness of the piston ring. The contact between the edge of the slot-shaped recess and the piston ring thus always takes place only in one point. As a result of the angle of inclination, a flat support of the edge of the piston ring on one edge of a slot-shaped recess is consequently avoided, as a result of which no shear forces are introduced into the edge of the slot-shaped recess and thus scarcely any removal of material takes place at the edge. Thus, by adhering to a slope results in an increase in the life of the cylinder.
  • the maximum inclination angle is 0.96 °.
  • the number and / or the depth and / or the length and / or the width of the slot-shaped recesses may differ from one another.
  • the slot-shaped recesses of adjacent rows are arranged offset to one another.
  • the number of slot-shaped recesses is greater than or equal to 300 per m 2 sliding surface.
  • the number of slot-shaped recesses per m 2 sliding surface is variable, since parts of the sliding surface must withstand different loads.
  • a method for producing means for receiving lubricant in a cylinder according to the preceding embodiments comprises the step of producing the slot-shaped recesses by a mechanical machining method.
  • the cylinder is used in a large diesel engine, preferably in a 2-stroke engine or a 4-stroke engine.
  • Fig. 1 shows a section through a cylinder 1, which is arranged in a piston engine.
  • the piston engine is a 2-stroke engine or a 4-stroke engine, in particular a large diesel engine.
  • Such large diesel engines are currently equipped with cylinders whose inner diameter is usually greater than 190 mm. Typical diameters are between 250 and 1000 mm.
  • a piston reciprocates, which is connected via a connecting rod with a rotatable drive shaft. The reciprocating motion of the piston is between an upper and lower dead center.
  • Fig. 1 shows the piston in position at top dead center.
  • the upper dead zone 8 forms with vertical arrangement of the cylinder, the upper boundary of the sliding surface 7. If one places a similar cutting plane through the bottom dead center of the lowermost piston ring, the lower deadband 15 is obtained in the same way.
  • the length L (13) designates the distance between the upper dead zone 8 and the lower dead zone 15 and corresponds to the length of the sliding surface.
  • the sliding surfaces may have a length of 1 m to about 4 m.
  • the width of the sliding surface is formed by the circumference at the upper dead zone 8, and the circumference at the lower dead zone 15.
  • the width of the sliding surface on the upper dead zone 8 is greater than the width of the sliding surface of the lower dead zone 15, since the cylinder interior is usually not cylindrical but slightly conical. This taper has its cause in the different temperatures that exist in the individual zones of the sliding surface. In the area of the lower dead zone, air is sucked in from the surroundings, so that operating temperatures prevail in this area which are not significantly different from the ambient temperature of the air in the engine compartment. In the area of the upper dead zone, however, temperatures greater than 300.degree. C. may prevail.
  • a channel 17 extends along the cylinder inner wall, by means of which the delivery and distribution of the lubricant takes place.
  • the lubricant wets the entire sliding surface below the channel when the cylinder is aligned vertically. If the piston 2 moves past the feed openings 16 in the expansion phase, the lubricant is transported by the piston rings 3 sliding on the cylinder inner wall and is no longer available for further lubrication. This results in an increased consumption of lubricant, which represents a not inconsiderable cost factor in such large surfaces to be wetted with lubricant.
  • the cylinder 1 therefore comprises means 5 for receiving lubricant, which are arranged on the sliding surface 7 for the piston 2.
  • the sliding surface extends between the upper dead zone 8 and the lower dead zone 15.
  • the lower dead zone 15 is located vertically below a row of scavenging ports 6 arranged on the cylinder.
  • a plurality of slit-shaped recesses 5 are arranged on the sliding surface 7.
  • the slot-shaped recesses serve as lubricant pockets. If lubricant is supplied via feed openings 16, it flows along the cylinder inner wall and into the slot-shaped recesses in which a lubricant reservoir is formed. Slot-shaped recesses, which are located above an inlet opening, are filled with lubricant when a piston ring slides past the slot-shaped recess.
  • the piston ring transports lubricant during its movement, which dodges into a slot-shaped recess and fills it when the piston ring passes by such a slot-shaped recess.
  • the slot-shaped recesses have a length l (9), and a width b (10) and a depth t (11), which in Fig. 2 is shown in detail in a section of the developed cylinder surface.
  • the depth 11 is over 0.4 mm, which ensures that the slot-shaped recess is maintained even after several years of service, even if it comes to the cylinder inner wall to abrasion.
  • the great depth of the slot-shaped recesses has the further advantage that the lubricants pushed in by the piston ring pour out on the cylinder inner wall during the entire further stroke and wets them with a lubricant film.
  • the arrangement of a plurality of slot-like recesses ensures that the entire sliding surface or at least the part of the same, which is equipped with such slit-shaped recesses, is wetted.
  • the slot-shaped recesses 5 are provided in particular below an annular region 12 of the cylinder surface, which amounts to a length of up to 15% of the length L (13) of the sliding surface 7, measured from the upper dead zone 8.
  • the main reason for the reduced consumption of lubricant is that lubricant is stored in the slot-shaped recesses.
  • the lubricant thus does not flow off after one working cycle or is pushed out by the piston rings, but remains largely in the slot-shaped recesses.
  • the lubricant is available as a result of further working cycles.
  • the increase in the service life of the cylinder surface is due to the fact that in the highest stress zone no or at most a greatly reduced number of slot-shaped recesses is provided, so this highly loaded area of the cylinder inner wall not by a plurality of small notches, that is, slot-shaped recesses or through the From the prior art known circumferential grooves is weakened.
  • the range is 1 to 25%, preferably 10 to 25%, particularly preferably 15% to 20%, in which slot-shaped recesses are to be provided.
  • Fig. 1 is the zone of highest load, so the annular region 12 is shown free of slot-shaped recesses.
  • Below the piston three rows of slot-shaped recesses are shown, on the more detailed representation of other rows to the lubricant supply 4 has been omitted for reasons of clarity.
  • the entire sliding surface 7 is provided with slit-shaped recesses, with the exception of the highest stress zone.
  • the slot-shaped recesses may also be provided in the region of the scavenging slots 6 and below the same.
  • Fig. 2a shows a development of the cylinder with other possible arrangements of slot-shaped recesses and in Fig. 2b Such a slot-shaped recess 5 is shown enlarged.
  • the slot-shaped recess is determined by a length l (9), a width b (10) and a depth t (11).
  • the width of the slot-shaped recesses is advantageously between 0.5 and 3 mm.
  • the width b must just be large enough that a sufficient amount of lubricant can be stored in the recess.
  • the width b must be smaller than the width of a piston ring, so that the piston ring is not detected by edges of the slot-shaped recess and passes through the slot-shaped recess no gas from the compression chamber into the suction chamber.
  • the length of the slot-shaped recesses is between 10 and 100 mm, preferably between 10 and 50 mm, particularly preferably between 10 and 30 mm.
  • a plurality of slot-shaped recesses arranged in a row which may have a slope. The slope is from those related to the latitude The reasons mentioned the recess limited to a dimension which is smaller than the width of the piston ring.
  • the angle of inclination 18 of the slot-shaped recesses is up to 1 °.
  • the number of slot-shaped recesses in a row may differ from the number of slot-shaped recesses of an adjacent row. Also, the number and / or the depth t (11) and / or the length l (9) and / or the width b (10) of the slot-shaped recesses may differ from each other.
  • the slot-shaped recesses of adjacent rows are at least partially offset from each other.
  • the number of slot-shaped recesses per m 2 sliding surface can be increased so that a uniform distribution of lubricant is ensured as possible.
  • the number of slot-shaped recesses is preferably greater than or equal to 300 per m 2 sliding surface.
  • the number of slot-shaped recesses per m 2 sliding surface can be variably selected if in operation areas of the sliding surface can be detected with increased or reduced lubricant requirement. For example, a reduced number of slot-shaped recesses or a greater distance of adjacent rows of slot-shaped recesses may be provided, as in Fig. 2 is apparent.
  • Fig. 3 shows a representation of the pair of sliding piston ring and inner cylinder wall for the previous embodiment.
  • the annular region 12 which is up to 15% of the sliding surface and is located immediately below the upper dead zone 8, no slot-shaped recesses.
  • the piston 2 is located in a position below the annular region 12. It may be particularly advantageous to increase the region 12 to up to 25% of the sliding surface.
  • the region 12 is then 10 to 30%, preferably 15 to 30%, more preferably the range is greater than 25% up to and including 30%.
  • the slot-shaped recesses are produced by a mechanical processing method. These include machining processes, such as milling, but not processes which operate under thermal influence, such as structuring by means of laser.
  • a laser structuring method is mainly used for the production of grooves in the micrometer range and is not suitable for the production of the slot-shaped recesses according to the invention with depths in the millimeter range.
  • Cylinders already in use can be retrofitted with slot-like recesses as part of routine maintenance or repairs.
  • the lubricant requirement can be reduced by the targeted subsequent attachment of slot-like recesses.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP08164867A 2007-10-16 2008-09-23 Cylindre doté de moyens de réception de lubrifiants Withdrawn EP2050946A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08164867A EP2050946A1 (fr) 2007-10-16 2008-09-23 Cylindre doté de moyens de réception de lubrifiants

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP07118603 2007-10-16
EP08164867A EP2050946A1 (fr) 2007-10-16 2008-09-23 Cylindre doté de moyens de réception de lubrifiants

Publications (1)

Publication Number Publication Date
EP2050946A1 true EP2050946A1 (fr) 2009-04-22

Family

ID=39198217

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08164867A Withdrawn EP2050946A1 (fr) 2007-10-16 2008-09-23 Cylindre doté de moyens de réception de lubrifiants

Country Status (6)

Country Link
EP (1) EP2050946A1 (fr)
JP (1) JP2009097514A (fr)
KR (1) KR20090038829A (fr)
CN (1) CN101413457A (fr)
BR (1) BRPI0804363A2 (fr)
RU (1) RU2469202C2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2682572A1 (fr) 2012-07-04 2014-01-08 Wärtsilä Schweiz AG Système de lubrification
EP2678546A4 (fr) * 2011-02-22 2016-07-06 Univ George Washington Réduction des frottements pour des composants de moteurs
WO2018175255A1 (fr) * 2017-03-22 2018-09-27 Achates Power, Inc. Structures de surface d'alésage de cylindre pour un moteur à pistons opposés
GB2560902A (en) * 2017-03-27 2018-10-03 Ford Global Tech Llc A cylinder for receiving a reciprocating piston

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012060487A1 (fr) * 2010-11-03 2012-05-10 두산인프라코어 주식회사 Cylindre pourvu d'un profil irrégulier sur la surface d'une paroi interne
CN105221283B (zh) * 2015-09-22 2017-12-05 江苏大学 一种发动机缸孔及其加工方法
CN105221284B (zh) * 2015-11-11 2018-02-23 江苏大学 内燃机缸套
CN111520249A (zh) * 2020-05-07 2020-08-11 哈尔滨工程大学 一种菱形分布的气缸套表面织构结构
CN111520248A (zh) * 2020-05-07 2020-08-11 哈尔滨工程大学 一种仿生分布的气缸套表面织构结构

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1174532A (fr) 1956-05-05 1959-03-12 Sulzer Ag Machine à piston
DE3936813C1 (en) * 1989-11-04 1990-06-07 Man B & W Diesel Ag, 8900 Augsburg, De IC engine air buffer system - consists of blind bores in area of cylinder swept by piston rings
WO1998053192A1 (fr) 1997-05-16 1998-11-26 Man B & W Diesel A/S Chemise de cylindre pour moteur a combustion interne de type diesel
US6253724B1 (en) * 1999-12-06 2001-07-03 Samyoung Machinery Co., Ltd. Cylinder liner with oil pocket
EP1275864A1 (fr) * 2001-07-09 2003-01-15 Maschinenfabrik Gehring GmbH & Co. Pièce avec une surface chargée tribologiquement at procédé de fabrication une telle surface
GB2431976A (en) * 2005-11-05 2007-05-09 Ford Global Tech Llc I.c. engine cylinder bore wall with pockets for retaining lubricant
EP1818530A1 (fr) * 2004-12-03 2007-08-15 Daihatsu Motor Co., Ltd. Dispositif de lubrification pour paroi interieure de cylindre dans moteur a combustion interne a deux temps
DE102006060920A1 (de) * 2006-12-20 2008-07-03 Daimler Ag Laserstrukturierte Zylinderlaufbuchse

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60259750A (ja) * 1984-06-05 1985-12-21 Mitsubishi Heavy Ind Ltd シリンダライナ
JPH06105102B2 (ja) * 1985-01-23 1994-12-21 三菱重工業株式会社 往復動機関のシリンダライナ
KR20000011573U (ko) * 1998-12-04 2000-07-05 이경자 주철 실린더 라이너의 오일포켓
JP4434127B2 (ja) * 2005-10-20 2010-03-17 株式会社豊田自動織機 複合部材及びその製造方法

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1174532A (fr) 1956-05-05 1959-03-12 Sulzer Ag Machine à piston
DE3936813C1 (en) * 1989-11-04 1990-06-07 Man B & W Diesel Ag, 8900 Augsburg, De IC engine air buffer system - consists of blind bores in area of cylinder swept by piston rings
WO1998053192A1 (fr) 1997-05-16 1998-11-26 Man B & W Diesel A/S Chemise de cylindre pour moteur a combustion interne de type diesel
US6253724B1 (en) * 1999-12-06 2001-07-03 Samyoung Machinery Co., Ltd. Cylinder liner with oil pocket
EP1275864A1 (fr) * 2001-07-09 2003-01-15 Maschinenfabrik Gehring GmbH & Co. Pièce avec une surface chargée tribologiquement at procédé de fabrication une telle surface
EP1818530A1 (fr) * 2004-12-03 2007-08-15 Daihatsu Motor Co., Ltd. Dispositif de lubrification pour paroi interieure de cylindre dans moteur a combustion interne a deux temps
GB2431976A (en) * 2005-11-05 2007-05-09 Ford Global Tech Llc I.c. engine cylinder bore wall with pockets for retaining lubricant
DE102006060920A1 (de) * 2006-12-20 2008-07-03 Daimler Ag Laserstrukturierte Zylinderlaufbuchse

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2678546A4 (fr) * 2011-02-22 2016-07-06 Univ George Washington Réduction des frottements pour des composants de moteurs
US10245806B2 (en) 2011-02-22 2019-04-02 The George Washington University Friction reduction for engine components
US11020933B2 (en) 2011-02-22 2021-06-01 The George Washington University Friction reduction for engine components
EP2682572A1 (fr) 2012-07-04 2014-01-08 Wärtsilä Schweiz AG Système de lubrification
WO2018175255A1 (fr) * 2017-03-22 2018-09-27 Achates Power, Inc. Structures de surface d'alésage de cylindre pour un moteur à pistons opposés
US11598211B2 (en) 2017-03-22 2023-03-07 Achates Power, Inc. Cylinder bore surface structures for an opposed-piston engine
GB2560902A (en) * 2017-03-27 2018-10-03 Ford Global Tech Llc A cylinder for receiving a reciprocating piston
GB2560902B (en) * 2017-03-27 2019-07-03 Ford Global Tech Llc A cylinder for receiving a reciprocating piston

Also Published As

Publication number Publication date
JP2009097514A (ja) 2009-05-07
KR20090038829A (ko) 2009-04-21
RU2008140984A (ru) 2010-04-20
RU2469202C2 (ru) 2012-12-10
BRPI0804363A2 (pt) 2009-06-16
CN101413457A (zh) 2009-04-22

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